Fluid mixer and fluid circuit

Abstract

A fluid mixer (1) for use in a fluid circuit (40) that is mounted on a vehicle comprises a mixing container (2), a plurality of inlet passages (3, 4), and a discharge passage (5). The mixing container (2) has a cylindrical inner wall (24). The plurality of inlet passages (3, 4) supply fluids having different temperatures to the inside of the mixing container (2). The discharge passage (5) discharges the fluids from the inside of the mixing container (2). A passage axis (Ax1, Ax2) of a portion linearly extending from the mixing container (2) in at least one of the plurality of inlet passages (3, 4) is inclined in one direction along the circumferential direction of the cylindrical inner wall (24) with respect to a corresponding outer extension line (OE1, OE2) obtained by extending, to the outside of the mixing container (2), a line connecting the axial center (CL) of the mixing container (2) and the center (C1, C2) of an inlet port (6, 7) where the at least one inlet passage is connected to the mixing container (2).

Description

Fluid Mixer and Fluid Circuit Cross - Reference to Related Applications

[0001] This application is based on Japanese Patent Application No. 2024 - 208365 filed on November 29, 2024 and Japanese Patent Application No. 2024 - 208364 filed on November 29, 2024, the contents of which are incorporated herein by reference.

[0002] This disclosure relates to a fluid mixer used in a fluid circuit mounted on a vehicle and to the fluid circuit.

[0003] Conventionally, a vehicle thermal management system including a fluid circuit through which a fluid such as cooling water flows and a heat pump cycle is known. The vehicle thermal management system described in Patent Document 1 includes a water - to - water heat exchanger in a fluid circuit that exchanges heat between the cooling water flowing through the engine cooling circuit and the cooling water flowing through the condenser circuit. This vehicle thermal management system has a function of heating the cooling water flowing through the engine cooling circuit with the cooling water flowing through the condenser circuit by the water - to - water heat exchanger during engine warm - up and supplying warm water necessary for engine warm - up to the engine. Hereinafter, the cooling water on the higher - temperature side among the cooling water flowing through the water - to - water heat exchanger is referred to as warm water, and the cooling water on the lower - temperature side is referred to as cold water.

[0004] Japanese Patent No. 6398764

[0005] As described in Patent Document 1, a water - to - water heat exchanger employs a laminated heat exchanger in which a plurality of channels through which cold water flows and a plurality of channels through which warm water flows are alternately laminated via a plurality of plates inside. However, the heat exchange efficiency of a laminated heat exchanger is generally about 40 - 50%. Also, since an aluminum material is used for the plates of the laminated heat exchanger, heat loss may occur due to its heat capacity. Therefore, when using a laminated heat exchanger for heat exchange between cold water and warm water, the heat exchange efficiency may decrease.

[0006] In contrast, it is conceivable to create cooling water at a desired temperature by exchanging heat between hot and cold water flowing through pipes, without using a water-water heat exchanger. However, the inventors' research revealed that extremely long pipes (for example, pipes of 1300 mm or more) are required to bring cooling water at different temperatures to a uniform temperature by arranging pipes in parallel. Using such long pipes leads to problems such as the fluid circuit becoming large.

[0007] This disclosure aims to provide a fluid mixer and fluid circuit that can improve heat exchange efficiency and reduce size.

[0008] According to one aspect of this disclosure, a fluid mixer used in a fluid circuit mounted on a vehicle comprises a mixing vessel having a cylindrical inner wall, a plurality of inflow passages for supplying fluids of different temperatures to the inside of the mixing vessel, and a discharge passage for discharging fluid from the inside of the mixing vessel, wherein the flow path axis of a portion of at least one of the plurality of inflow passages that extends linearly from the mixing vessel is inclined to one side in the circumferential direction of the cylindrical inner wall with respect to an outer extension line obtained by extending the line connecting the center of the inlet to which the inflow passage connects to the mixing vessel and the axis of the mixing vessel to the outside of the mixing vessel.

[0009] According to this design, fluids of different temperatures supplied to the inside of the mixing vessel from multiple inflow passages form a swirling flow inside the vessel, quickly mixing to a uniform temperature. As a result, fluids of a stable temperature can be supplied from the discharge passage to each component of the fluid circuit. Therefore, this fluid mixer can improve heat exchange efficiency compared to a heat exchanger and can be made smaller in size compared to heat exchange using piping.

[0010] In this disclosure, "cylindrical inner wall" refers to a shape whose cross-section perpendicular to the axis is circular, elliptical, polygonal, or approximates thereof, and in three dimensions includes cylindrical, conical, and ball shapes, and also includes shapes with irregularities on the inner wall.

[0011] According to another aspect of this disclosure, a fluid circuit mounted on a vehicle comprises a fluid mixer as described in one aspect of this disclosure, a high-temperature valve that supplies a higher-temperature fluid to a mixing vessel via a predetermined inlet passage from among a plurality of inlet passages, and a low-temperature valve that supplies a lower-temperature fluid to the mixing vessel via another inlet passage from among a plurality of inlet passages, or to which fluid discharged from a discharge passage is supplied, wherein the high-temperature valve is located in a region on one radial side of the cylindrical inner wall relative to the mixing vessel, and the low-temperature valve is located in the other radial side of the cylindrical inner wall relative to the mixing vessel.

[0012] According to this, another aspect of the present disclosure can achieve the same effects as the first aspect of the present disclosure by incorporating the fluid mixer described in the first aspect of the present disclosure. Furthermore, in the other aspect of the present disclosure, the high-temperature valve and the low-temperature valve can be positioned at separate locations with the mixing vessel in between. Therefore, direct heat exchange between the high-temperature valve and the low-temperature valve can be suppressed. Consequently, when the fluid flowing through the high-temperature valve or the low-temperature valve is supplied directly to the equipment of the fluid circuit without passing through the fluid mixer, heat loss can be suppressed and the temperature of the fluid supplied to the equipment can be stabilized. Furthermore, when the fluid flowing through the high-temperature valve or the low-temperature valve is mixed in the fluid mixer and supplied to the equipment, the equipment can be supplied with fluid at a desired temperature.

[0013] This is a side view of a fluid mixer according to the first embodiment. This is a cross-sectional view taken along the line II-II in Figure 1. This is a cross-sectional view taken along the line III-III in Figure 2. This is a circuit diagram showing an example of a vehicle thermal management system equipped with a fluid circuit using the fluid mixer according to the first embodiment. This is an explanatory diagram for explaining the arrangement of the fluid mixer, flow path switching valve, and flow control valve according to the first embodiment. This is a plan view taken from direction VI in Figure 5. This is an explanatory diagram for explaining the arrangement of the fluid mixer, flow path switching valve, and flow control valve of the first comparative example, and is a plan view corresponding to Figure 6. This is a graph showing the results of a study on the flow path length until the fluid reaches a uniform temperature when heat exchange is performed between a high-temperature fluid and a low-temperature fluid using piping. This is an explanatory diagram for explaining the arrangement of the fluid mixer and flow path switching valve according to the second embodiment. This is an explanatory diagram for explaining the arrangement of the fluid mixer and flow control valve according to the third embodiment. This is a cross-sectional view of a fluid mixer according to the fourth embodiment, corresponding to Figure 3. This is a cross-sectional view of a fluid mixer according to the fifth embodiment, corresponding to Figure 3. This is a cross-sectional view of a fluid mixer according to the sixth embodiment, corresponding to Figure 2. This is a cross-sectional view of a fluid mixer according to the seventh embodiment, corresponding to Figure 3. This is a cross-sectional view of a fluid mixer according to the eighth embodiment, corresponding to Figure 2. This is a cross-sectional view of a fluid mixer according to the ninth embodiment, corresponding to Figure 2. This is a cross-sectional view of a fluid mixer according to the tenth embodiment, corresponding to Figure 2. This is a cross-sectional view taken along the line XVIII-XVIII in Figure 17. This is a cross-sectional view taken along the line XIX-XIX in Figure 17. This is a cross-sectional view taken along the line XX-XX in Figures 18 and 19. This is a cross-sectional view taken along the line XXI-XXI in Figure 20. This is an explanatory diagram for explaining the movement of swirling flow and bubbles generated in a fluid mixer according to the tenth embodiment. This is an explanatory diagram for explaining the movement of swirling flow and bubbles generated in a fluid mixer of the second comparative example. This is a side view of a fluid mixer according to the eleventh embodiment. This is a side view of an integrated fluid apparatus equipped with a fluid mixer according to the twelfth embodiment. This is a plan view taken from the XXVI direction in Figure 25. This is a cross-sectional view of the area corresponding to the line XXVII-XXVII in Figure 26 in an integrated fluid apparatus equipped with a fluid mixer according to the thirteenth embodiment.

[0014] The embodiments of this disclosure will be described below with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be denoted by the same reference numerals, and their descriptions will be omitted.

[0015] (First Embodiment) The first embodiment will now be described. The fluid mixer of the first embodiment is used in a fluid circuit mounted on a vehicle and mixes fluids of different temperatures flowing through the fluid circuit, making it possible to supply fluid at a desired temperature to downstream equipment (e.g., batteries, electric drive devices, etc.). As the fluid flowing through the fluid circuit, a liquid such as antifreeze mainly composed of ethylene glycol, LLC, or water can be used. LLC is an abbreviation for Long Life Coolant.

[0016] As shown in Figures 1 to 3, the fluid mixer 1 includes a mixing container 2, a plurality of inlet passages 3 and 4, and a discharge passage 5, etc.

[0017] The mixing container 2 comprises a side portion 21, a bottom portion 22, and an upper portion 23, and has an internal space through which fluid flows. Of the inner walls forming the internal space of the mixing container 2, the inner wall of the side portion 21 is called the "inner circumferential wall 24," the inner wall of the bottom portion 22 is called the "bottom wall 25," and the inner wall of the upper portion 23 is called the "upper wall 26." The inner circumferential wall 24 corresponds to a "cylindrical inner wall." Hereinafter, the direction in which the axis CL of the inner circumferential wall 24 extends is called the "axial direction." The bottom wall 25 is provided on one side in the axial direction, the upper wall 26 is provided on the other side in the axial direction, and the inner circumferential wall 24 is provided in a direction perpendicular to the axis CL. The mixing container 2 is formed from, for example, resin.

[0018] In the first embodiment, when the fluid mixer 1 is mounted on a vehicle, the axial direction corresponds to the vertical direction of the vehicle. One side of the axial direction corresponds to the lower side of the vehicle, and the other side of the axial direction corresponds to the upper side of the vehicle. Therefore, when the fluid mixer 1 is mounted on a vehicle, the bottom portion 22 is located on the lower side of the vehicle, and the upper portion 23 is located on the upper side of the vehicle.

[0019] The multiple inflow passages 3 and 4 are passages that supply fluids of different temperatures to the inside of the mixing container 2. Of the multiple inflow passages 3 and 4, the one that supplies the fluid on the higher temperature side to the mixing container 2 is called the "high-temperature side inflow passage 3," and the one that supplies the fluid on the lower temperature side to the mixing container 2 is called the "low-temperature side inflow passage 4."

[0020] The points where multiple inflow passages 3 and 4 connect to the mixing container 2 are called "inlets 6 and 7". The inlet 6 of the high-temperature side inflow passage 3 is called the "high-temperature side inlet 6", and the inlet 7 of the low-temperature side inflow passage 4 is called the "low-temperature side inlet 7". Both the high-temperature side inlet 6 and the low-temperature side inlet 7 are provided on the inner circumferential wall 24 of the mixing container 2.

[0021] Here, as shown in Figure 2, the imaginary lines extending outside the mixing container 2 from the lines connecting the centers C1 and C2 of the inlets 6 and 7, to which the multiple inflow passages 3 and 4 connect to the mixing container 2, and the axis CL of the mixing container 2, are called "outer extension lines OE1 and OE2". The flow path axes Ax1 and Ax2 of the portions of the multiple inflow passages 3 and 4 that extend linearly from the mixing container 2 are both inclined to one side in the circumferential direction of the cylindrical inner circumferential wall 24 with respect to the outer extension lines OE1 and OE2. Note that "circumferential direction of the inner circumferential wall 24" refers to the circumferential direction of a virtual circle drawn with the axis CL as the center on a plane perpendicular to the axis CL of the inner circumferential wall 24. Specifically, the imaginary line extending outside the mixing container 2 from the line connecting the center C1 of the inlet 6, to which the high-temperature side inflow passage 3 connects to the mixing container 2, and the axis CL of the mixing container 2, is called "outer extension line OE1". Furthermore, the imaginary line extending the line connecting the center C2 of the inlet 7 where the low-temperature side inflow passage 4 connects to the mixing container 2, and the axis CL of the mixing container 2, to the outside of the mixing container 2 is called the "outer extension line OE2". The flow path axis Ax1 of the portion of the high-temperature side inflow passage 3 that extends linearly from the mixing container 2 is inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension line OE1, which is the line extending the line connecting the center of the high-temperature side inlet 6 and the axis CL of the mixing container 2 to the outside of the mixing container 2. The flow path axis Ax2 of the portion of the low-temperature side inflow passage 4 that extends linearly from the mixing container 2 is also inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension line OE2, which is the line extending the line connecting the center of the low-temperature side inlet 7 and the axis CL of the mixing container 2 to the outside of the mixing container 2. Furthermore, the angles θ1 and θ2 at which the flow path axes Ax1 and Ax2 of the inflow passages 3 and 4 are inclined with respect to the outer extension lines OE1 and OE2 are greater than 0° and less than or equal to 90°. As a result, as shown by the arrows SF1 and SF2 in Figures 2 and 3, the fluid supplied to the mixing container 2 from the multiple inflow passages 3 and 4 forms a swirling flow that rotates inside the mixing container 2 toward the other side in the circumferential direction.

[0022] The centrifugal force of a swirling flow is expressed by the following equation 1: F = mrω ２... (Equation 1) where F is centrifugal force, m is mass, r is radius, and ω is angular velocity. Here, the density of the low-temperature fluid is greater than the density of the high-temperature fluid. Since a greater fluid density means a greater mass, the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid. Therefore, in the first embodiment, the low-temperature side inlet passage 4 and the high-temperature side inlet passage 3 are arranged as follows. That is, as shown in Figure 2, let D2 be the distance between the axis CL of the mixing container 2 and the inner extension line IE2 obtained by extending the flow path axis Ax2 of the low-temperature side inlet passage 4 inside the mixing container 2. Let D1 be the distance between the axis CL of the mixing container 2 and the inner extension line IE1 obtained by extending the flow path axis Ax1 of the high-temperature side inlet passage 3 inside the mixing container 2. At this time, the low-temperature side inlet passage 4 and the high-temperature side inlet passage 3 are arranged such that the distance D2 is closer than the distance D1. As a result, as shown in Figure 3, the low-temperature fluid flowing into the mixing container 2 from the low-temperature side inflow passage 4 forms a swirling flow SF2 closer to the axis CL of the mixing container 2 than the high-temperature fluid flowing into the mixing container 2 from the high-temperature side inflow passage 3. Since the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid, the speed at which the low-temperature fluid moves radially outward is faster than the speed at which the high-temperature fluid moves radially outward. Therefore, the low-temperature fluid moves radially outward while swirling due to the action of centrifugal force and mixes quickly with the high-temperature fluid swirling radially outward.

[0023] Furthermore, as shown in Figure 3, in the first embodiment, the low-temperature side inlet 7 is located further from the discharge passage 5 than the high-temperature side inlet 6 in the axial direction of the mixing container 2. As a result, the low-temperature fluid flowing into the mixing container 2 from the low-temperature side inlet passage 4 forms a swirling flow SF2. As this swirling flow SF2 of the low-temperature fluid moves toward the discharge passage 5 while swirling and spreading radially outward, the high-temperature fluid flows in from the high-temperature side inlet 6 and forms a swirling flow SF1. Since the density of the low-temperature fluid is greater than that of the high-temperature fluid, the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid inside the mixing container 2 is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid. Therefore, the speed at which the swirling flow SF2 of the low-temperature fluid moves radially outward is faster than the speed at which the swirling flow SF1 of the high-temperature fluid moves radially outward, so the low-temperature fluid and the high-temperature fluid mix quickly.

[0024] The discharge passage 5 is a passage through which fluid is discharged from the inside of the mixing container 2. The point where the discharge passage 5 connects to the mixing container 2 is called the "discharge port 8". The discharge port 8 is provided on the bottom wall 25. If multiple inlets 6, 7 and the discharge port 8 were all provided on the inner circumferential wall 24 of the mixing container 2, the fluids supplied from multiple inlet passages 3, 4, each with different temperatures, may be discharged from the discharge passage 5 before they can be mixed to a uniform temperature inside the mixing container 2. In contrast, in the first embodiment, since the discharge port 8 is provided on the bottom wall 25, the fluid that has been mixed to a uniform temperature inside the mixing container 2 can be discharged from the discharge passage 5. Note that the discharge port is not limited to the center of the bottom wall 25, but can be provided at any position on the bottom wall 25.

[0025] Here, an example of a vehicle thermal management system including a fluid circuit in which a fluid mixer 1 is used will be described. As shown in Figure 4, the vehicle thermal management system 30 includes a heat pump cycle 31 and a fluid circuit 40.

[0026] The heat pump cycle 31 is a vapor compression type refrigerator in which a compressor 32, a fluid-refrigerant condenser 33, an expansion valve 34, a fluid-refrigerant evaporator 35, etc. are connected by a refrigerant flow path 36. In the following description, the fluid-refrigerant condenser 33 will be referred to as the "water-cooled condenser 33," and the fluid-refrigerant evaporator 35 will be referred to as the "chiller 35." In Figure 4, the refrigerant flow path 36 is shown as a dashed line to distinguish it from the flow path of the fluid circuit 40. The heat pump cycle 31 uses, for example, an HFC-based refrigerant (e.g., R134a) or an HFO-based refrigerant (e.g., R1234yf) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.

[0027] The compressor 32 compresses the refrigerant drawn in from the refrigerant inlet and discharges high-temperature, high-pressure gaseous refrigerant from the refrigerant discharge port. The refrigerant discharged from the compressor 32 flows into the water-cooled condenser 33.

[0028] The water-cooled condenser 33 is a heat exchanger that performs heat exchange between the refrigerant discharged from the compressor 32 and the fluid circulating in the fluid circuit 40. The refrigerant flowing through the water-cooled condenser 33 condenses by releasing heat into the fluid, and the fluid flowing through the water-cooled condenser 33 becomes hot by absorbing heat from the refrigerant. The refrigerant that flows out of the water-cooled condenser 33 flows into the expansion valve 34.

[0029] The expansion valve 34 depressurizes and expands the refrigerant flowing out of the water-cooled condenser 33, creating a two-phase gas-liquid state. The refrigerant flowing out of the expansion valve 34 flows into the chiller 35.

[0030] The chiller 35 is a heat exchanger that performs heat exchange between the refrigerant flowing out from the expansion valve 34 and the fluid circulating in the fluid circuit 40. The refrigerant flowing through the chiller 35 absorbs heat from the fluid and evaporates, and the fluid flowing through the chiller 35 becomes cold as it releases heat into the refrigerant. The gaseous refrigerant flowing out from the chiller 35 is drawn into the refrigerant inlet of the compressor 32.

[0031] The fluid circuit 40 is composed of a high-temperature fluid circuit 41 and a low-temperature fluid circuit 42. High-temperature fluid heated by the water-cooled condenser 33 mainly flows through the high-temperature fluid circuit 41, and low-temperature fluid cooled by the chiller 35 mainly flows through the low-temperature fluid circuit 42.

[0032] The fluid circuit 40 is equipped with fluid valves in both the high-temperature side fluid circuit 41 and the low-temperature side fluid circuit 42. The fluid valve provided in the high-temperature side fluid circuit 41 is called the "high-temperature side valve 43," and the fluid valve provided in the low-temperature side fluid circuit 42 is called the "low-temperature side valve 44." The high-temperature side valve 43 is, for example, a flow control valve, and the low-temperature side valve 44 is, for example, a flow path switching valve.

[0033] A flow control valve, as an example of a high-temperature side valve 43, has the function of switching the fluid path through multiple fluid passages connected to it, as well as adjusting the fluid flow rate. Specifically, the flow control valve can switch the fluid path through fluid passages connected to the heater core 45, high-temperature side radiator 46, water-cooled condenser 33, and fluid mixer 1, respectively, and adjust the fluid flow rate through those fluid passages. The heater core 45 is a heat exchanger that exchanges heat between the air conditioning air blown into the vehicle cabin and the fluid. The high-temperature side radiator 46 is a heat exchanger that exchanges heat between the outside air and the fluid.

[0034] A flow path switching valve, as an example of a low-temperature side valve 44, has the function of switching the path of the fluid flowing through multiple fluid passages connected to it. Specifically, the flow path switching valve can switch the path of the fluid flowing through fluid passages connected to the chiller 35, the battery heat exchanger 47, the electric drive unit heat exchanger 48, the low-temperature side radiator 49, and the fluid mixer 1, respectively. The battery heat exchanger 47 is a heat exchanger that cools and warms the battery by exchanging heat between the battery and the fluid. The electric drive unit heat exchanger 48 is a heat exchanger that cools and warms the electric drive unit by exchanging heat between the electric drive unit and the fluid. The low-temperature side radiator 49 is a heat exchanger that exchanges heat between the outside air and the fluid.

[0035] The fluid circuit 40 is equipped with fluid pumps in both the high-temperature side fluid circuit 41 and the low-temperature side fluid circuit 42. The fluid pump provided in the high-temperature side fluid circuit 41 is called the "high-temperature side pump 50," and the fluid pumps provided in the low-temperature side fluid circuit 42 are called the "low-temperature side pumps 51 and 52." The high-temperature side pump 50 is, for example, provided in the middle of the fluid flow path connecting the high-temperature side valve 43 and the water-cooled condenser 33. The low-temperature side pumps 51 and 52 are, for example, a chiller pump 51 and an electric drive pump 52. The chiller pump 51 is provided in the middle of the fluid flow path connecting the chiller 35 and the low-temperature side valve 44. The electric drive pump 52 is provided in the middle of the fluid flow path connecting the electric drive heat exchanger 48 and the low-temperature side valve 44.

[0036] The fluid mixer 1 is supplied with high-temperature fluid from a flow control valve, which is an example of a high-temperature side valve 43, and with low-temperature fluid from a flow path switching valve, which is an example of a low-temperature side valve 44. The fluid mixer 1 can mix the high-temperature fluid and the low-temperature fluid to create a fluid at a desired temperature. By adjusting the flow rate of the high-temperature fluid supplied to the fluid mixer 1 from the flow control valve, which is the high-temperature side valve 43, the temperature of the fluid discharged from the discharge passage 5 can be adjusted. Furthermore, by connecting the discharge passage 5 of the fluid mixer 1 to the flow path switching valve, which is the low-temperature side valve 44, it is possible to switch the downstream equipment (specifically, a heat exchanger) that receives fluid at a predetermined temperature via the flow path switching valve from the discharge passage 5. The fluid at the desired temperature created in the fluid mixer 1 is supplied to a heat exchanger 47 for batteries, a heat exchanger 48 for electric drive devices, a chiller 35, etc.

[0037] In the vehicle thermal management system 30 described above, as shown in Figures 5 and 6, the high-temperature valve 43, the fluid mixer 1, and the low-temperature valve 44 can be configured as an integrated module (i.e., an integrated fluid device). In the integrated module (i.e., an integrated fluid device), the high-temperature valve 43, the fluid mixer 1, and the low-temperature valve 44 are arranged in a straight line. Specifically, the high-temperature valve 43 is provided in one radial region (α) of the inner circumferential wall 24 relative to the fluid mixer 1. The low-temperature valve 44 is provided in the other radial region (β) of the inner circumferential wall 24 relative to the fluid mixer 1. In other words, the high-temperature valve 43 and the low-temperature valve 44 are provided at separate positions with the fluid mixer 1 in between. This makes it possible to suppress direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44. Furthermore, "radial direction of the inner circumferential wall 24" refers to the radial direction of a virtual circle drawn on a plane perpendicular to the axis CL of the inner circumferential wall 24, with the axis CL as the center.

[0038] The fluid mixer 1 has a high-temperature side inlet passage 3 connected to a flow control valve acting as a high-temperature side valve 43. Therefore, high-temperature fluid is supplied to the fluid mixer 1 from the flow control valve acting as the high-temperature side valve 43 via the high-temperature side inlet passage 3. The fluid mixer 1 also has a low-temperature side inlet passage 4 connected to a flow path switching valve acting as a low-temperature side valve 44. Therefore, low-temperature fluid is supplied to the fluid mixer 1 from the flow path switching valve acting as the low-temperature side valve 44 via the low-temperature side inlet passage 4. Furthermore, the fluid mixer 1 has a discharge passage 5 connected to a flow path switching valve acting as a low-temperature side valve 44. Therefore, the fluid mixed in the fluid mixer 1 is discharged to the flow path switching valve acting as the low-temperature side valve 44 via the discharge passage 5.

[0039] Note that the above configuration is just one example. The fluid mixer 1 only needs to have at least one of its multiple inlet passages 3, 4 and discharge passage 5 connected to a flow control valve acting as a high-temperature side valve 43. Alternatively, the fluid mixer 1 only needs to have at least one of its multiple inlet passages 3, 4 and discharge passage 5 connected to a flow path switching valve acting as a low-temperature side valve 44.

[0040] Here, in order to compare with the first embodiment, the arrangement of the high-temperature valve 43, the fluid mixer 1, and the low-temperature valve 44 of the first comparative example will be described.

[0041] As shown in Figure 7, in the first comparative example, the high-temperature valve 43 and the low-temperature valve 44 are arranged adjacent to each other. That is, the high-temperature valve 43 and the low-temperature valve 44 are arranged without the fluid mixer 1 in between them. As a result, the high-temperature valve 43 and the low-temperature valve 44 directly exchange heat. Therefore, when the fluid flowing through the high-temperature valve 43 or the low-temperature valve 44 is supplied directly to the equipment of the fluid circuit 40 without passing through the fluid mixer 1, heat loss occurs, and problems arise such as the temperature of the fluid supplied to the equipment not being stable.

[0042] In contrast, in the first embodiment, since the high-temperature side valve 43 and the low-temperature side valve 44 are provided at positions separated from each other with the fluid mixer 1 interposed therebetween, direct heat exchange between the high-temperature side valve 43 and the low-temperature side valve 44 can be suppressed. Therefore, when the fluid flowing through the high-temperature side valve 43 or the low-temperature side valve 44 is directly supplied to the equipment provided in the fluid circuit 40 without passing through the fluid mixer 1, heat loss can be suppressed and the temperature of the fluid supplied to the equipment can be stabilized. Further, when the fluid flowing through the high-temperature side valve 43 or the low-temperature side valve 44 is mixed by the fluid mixer 1 and supplied to the equipment, a fluid having a desired temperature intended for the equipment can be supplied.

[0043] By the way, when a fluid having a desired temperature is created by heat-exchanging a part of the high-temperature fluid flowing through the high-temperature side fluid circuit 41 and a part of the low-temperature fluid flowing through the low-temperature side fluid circuit 42, it is conceivable to use piping without using the fluid mixer 1. FIG. 8 is a graph showing the results of the inventors' study on the flow path length required when high-temperature fluid and low-temperature fluid are arranged in parallel with piping to make the fluid have a uniform temperature.

[0044] As conditions for the study, the temperature difference between the high-temperature fluid and the low-temperature fluid was set to 40°C. The flow directions of the high-temperature fluid and the low-temperature fluid flowing through the piping were set to parallel flow. In this case, as shown in the graph of FIG. 8, it was found that a flow path length of 1300 mm or more is required to make fluids of different temperatures have a uniform temperature using piping. When such a long piping is used, problems such as the enlargement of the fluid circuit 40 occur. Therefore, it can be said that it is preferable to use the fluid mixer 1 when creating a fluid having a desired uniform temperature using a part of the high-temperature fluid flowing through the high-temperature side fluid circuit 41 and a part of the low-temperature fluid flowing through the low-temperature side fluid circuit 42.

[0045] The fluid mixer 1 of the first embodiment described above provides the following effects: (1) The fluid mixer 1 of the first embodiment is equipped with a plurality of inflow passages 3 and 4 that supply fluids of different temperatures to the inside of the mixing container 2. In at least one of the plurality of inflow passages 3 and 4, the flow path axes Ax1 and Ax2 of the portion extending linearly from the mixing container 2 are inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension lines OE1 and OE2. The outer extension lines OE1 and OE2 are imaginary lines that extend to the outside of the mixing container 2 from the lines connecting the centers C1 and C2 of the inlets 6 and 7 of each inflow passage 3 and 4 to the axis CL of the mixing container 2. According to this, the fluids of different temperatures supplied to the inside of the mixing container 2 from the plurality of inflow passages 3 and 4 form swirling flows SF1 and SF2 that swirl towards the other side in the circumferential direction inside the mixing container 2, and mix quickly to a uniform temperature inside the mixing container 2. Therefore, a fluid at a stable temperature can be supplied from the discharge passage 5 to each device in the fluid circuit 40. Consequently, this fluid mixer 1 can improve heat exchange efficiency compared to a heat exchanger, and can be made smaller in size compared to heat exchange using piping.

[0046] (2) In the fluid mixer 1 of the first embodiment, the flow path axes Ax1 and Ax2 of the portions of the multiple inlet passages 3 and 4 that extend linearly from the mixing container 2 are inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension lines OE1 and OE2 of each inlet passage 3 and 4. As a result, the fluids of different temperatures supplied to the inside of the mixing container 2 from the multiple inlet passages 3 and 4 each form swirling flows SF1 and SF2 that swirl towards the other side in the circumferential direction inside the mixing container 2, and mix quickly to a uniform temperature inside the mixing container 2. Therefore, fluids of a stable temperature can be supplied from the discharge passage 5 to each device of the fluid circuit 40. Consequently, this fluid mixer 1 can improve the heat exchange efficiency compared to a heat exchanger and can be made smaller in size compared to heat exchange using piping.

[0047] (3) In the fluid mixer 1 of the first embodiment, a plurality of inlets 6 and 7 are provided on the inner peripheral wall 24 of the mixing container 2, and an outlet 8 is provided on the bottom wall 25 of the mixing container 2. According to this, if all of the plurality of inlets 6 and 7 and the outlet 8 are provided on the inner peripheral wall 24 of the mixing container 2, the fluids with different temperatures supplied from the plurality of inflow passages 3 and 4 will be discharged from the discharge passage 5 before being mixed into a uniform temperature inside the mixing container 2. In contrast, in the first embodiment, since the plurality of inlets 6 and 7 are provided on the inner peripheral wall 24 and the outlet 8 is provided on the bottom wall 25, the fluid mixed into a uniform temperature inside the mixing container 2 can be discharged from the discharge passage 5. Therefore, a fluid with a stable temperature can be supplied from the discharge passage 5 to each device included in the fluid circuit 40.

[0048] (4) In the fluid mixer 1 of the first embodiment, at least one of the plurality of inflow passages 3 and 4 and the discharge passage 5 is connected to a flow rate adjustment valve. According to this, by connecting the inflow passages 3 and 4 to the flow rate adjustment valve, the flow rate of the fluid flowing into the mixing container 2 from the flow rate adjustment valve can be adjusted. Therefore, the temperature of the fluid discharged from the discharge passage 5 can be adjusted. Also, by connecting the discharge passage 5 to the flow rate adjustment valve, the flow rate of the fluid supplied to the device supplied with fluid from the discharge passage 5 (hereinafter referred to as "downstream device") can be adjusted. Therefore, a desired amount of heat can be supplied to the downstream device.

[0049] (5) In the fluid mixer 1 of the first embodiment, at least one of the plurality of inflow passages 3 and 4 and the discharge passage 5 is connected to a flow path switching valve. According to this, by connecting the discharge passage 5 to the flow path switching valve, the downstream device that is supplied with fluid at a predetermined temperature from the discharge passage 5 can be switched. Also, by connecting the inflow passages 3 and 4 to the flow path switching valve, it becomes possible to switch the device that supplies fluid to the inflow passages 3 and 4 (hereinafter referred to as "upstream device"). Therefore, the temperature of the fluid flowing into the mixing container 2 from the upstream device can be switched.

[0050] (6) In the first embodiment, D1 is defined as the distance between the axis CL of the mixing container 2 and the inner extension line IE1, which is an extension of the flow path axis Ax1 of the high-temperature side inlet passage 3 into the inside of the mixing container 2. Also, D2 is defined as the distance between the axis CL of the mixing container 2 and the inner extension line IE2, which is an extension of the flow path axis Ax2 of the low-temperature side inlet passage 4 into the inside of the mixing container 2. At this time, the high-temperature side inlet passage 3 and the low-temperature side inlet passage 4 are arranged such that the distance D2 is closer than the distance D1. As a result, the low-temperature fluid flowing into the mixing container 2 from the low-temperature side inlet passage 4 forms a swirling flow SF2 at a position closer to the axis CL of the mixing container 2 than the high-temperature fluid flowing into the mixing container 2 from the high-temperature side inlet passage 3. Since the density of the low-temperature fluid is greater than the density of the high-temperature fluid, the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid inside the mixing container 2 is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid. Therefore, since the velocity at which the low-temperature fluid moves radially outward is faster than the velocity at which the high-temperature fluid moves radially outward, the low-temperature fluid moves radially outward while swirling due to centrifugal force and quickly mixes with the high-temperature fluid swirling radially outward. Thus, the agitation of the low-temperature and high-temperature fluids is improved, allowing them to be mixed to a uniform temperature, and the size of the mixing container 2 can be reduced.

[0051] (7) In the first embodiment, the low-temperature side inlet 7 is located further from the discharge passage 5 than the high-temperature side inlet 6 in the axial direction of the mixing container 2. As a result, the low-temperature fluid that flows into the mixing container 2 from the low-temperature side inlet passage 4 forms a swirling flow SF2. As the swirling flow SF2 of the low-temperature fluid moves toward the discharge passage 5 while swirling and spreading radially outward, the high-temperature fluid flows in from the high-temperature side inlet 6 and forms a swirling flow SF1. Since the density of the low-temperature fluid is greater than that of the high-temperature fluid, the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid inside the mixing container 2 is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid. Therefore, the speed at which the swirling flow SF2 of the low-temperature fluid moves radially outward is faster than the speed at which the swirling flow SF1 of the high-temperature fluid moves radially outward, so the low-temperature fluid and the high-temperature fluid mix quickly. Therefore, the agitation of the low-temperature fluid and the high-temperature fluid is improved, allowing them to be mixed to a uniform temperature, and the size of the mixing container 2 can be reduced.

[0052] (8) In the first embodiment, the high-temperature valve 43 is provided in one radial region (α) of the inner circumferential wall 24 relative to the mixing container 2, and the low-temperature valve 44 is provided in the other radial region (β) of the inner circumferential wall 24 relative to the mixing container 2. This makes it possible to provide the high-temperature valve 43 and the low-temperature valve 44 at separate locations with the mixing container 2 in between. Therefore, direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44 can be suppressed. Consequently, when the fluid flowing through the high-temperature valve 43 or the low-temperature valve 44 is supplied directly to the equipment of the fluid circuit 40 without passing through the fluid mixer 1, heat loss can be suppressed and the temperature of the fluid supplied to the equipment can be stabilized. Furthermore, when the fluid flowing through the high-temperature valve 43 or the low-temperature valve 44 is mixed in the fluid mixer 1 and supplied to the equipment, the equipment can be supplied with fluid at the intended desired temperature.

[0053] (9) In the first embodiment, the high-temperature valve 43, the mixing container 2, and the low-temperature valve 44 are arranged in a straight line. This makes it possible to suppress direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44.

[0054] Furthermore, the fluid circuit 40 using the fluid mixer 1 of the first embodiment provides the following effects: (10) The fluid circuit 40 using the fluid mixer 1 of the first embodiment comprises the fluid mixer 1, a high-temperature valve 43, and a low-temperature valve 44. The high-temperature valve 43 is provided in one radial region (α) of the inner circumferential wall 24 relative to the mixing container 2. The low-temperature valve 44 is provided in the other radial region (β) of the inner circumferential wall 24 relative to the mixing container 2. With this, the fluid circuit 40 using the fluid mixer 1 of the first embodiment can supply a stable fluid at a desired temperature from the discharge passage 5 of the fluid mixer 1 to each device in the fluid circuit 40. In addition, the fluid circuit 40 can be made smaller in size compared to heat exchange using piping due to the fluid mixer 1. Furthermore, the fluid circuit 40 can suppress direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44.

[0055] (11) In the fluid circuit 40 of the first embodiment, the low-temperature side valve 44 is a flow path switching valve that switches the path of the fluid flowing through the fluid circuit 40, and the high-temperature side valve 43 is a flow control valve that adjusts the flow rate of the fluid flowing through the fluid circuit 40. At least one of the multiple inflow passages 3, 4 and discharge passage 5 provided in the fluid mixer 1 is connected to a flow control valve or a flow control valve. In this case, a flow path switching valve is exemplified as the low-temperature side valve 44, and a flow control valve is exemplified as the high-temperature side valve 43. By connecting the inflow passages 3, 4 to the flow control valve, the flow rate of the fluid flowing from the flow control valve into the mixing container 2 can be adjusted, and therefore the temperature of the fluid discharged from the discharge passage 5 can be adjusted. By connecting the discharge passage 5 to the flow control valve, the flow rate of the fluid supplied to downstream equipment from the discharge passage 5 can be adjusted. Therefore, a desired amount of heat can be supplied to downstream equipment. In addition, by connecting the discharge passage 5 to the flow path switching valve, it is possible to switch downstream equipment to which fluid at a predetermined temperature is supplied from the discharge passage 5. Furthermore, by connecting the inflow passages 3 and 4 to the flow path switching valve, it becomes possible to switch the upstream equipment that supplies fluid to the inflow passages 3 and 4.

[0056] (Second Embodiment) The second embodiment will now be described. The second embodiment is the same as the first embodiment except that some of the arrangement of the components constituting the fluid circuit 40 has been changed. Therefore, only the parts that differ from the first embodiment will be described.

[0057] As shown in Figure 9, in the second embodiment, the fluid mixer 1 and the low-temperature valve 44 are arranged side by side. On the other hand, the high-temperature valve 43 is positioned away from the fluid mixer 1 and the low-temperature valve 44. This suppresses direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44. The low-temperature valve 44 is, for example, a flow path switching valve, and the high-temperature valve 43 is, for example, a flow control valve.

[0058] (Third Embodiment) The third embodiment will now be described. The third embodiment is similar to the first embodiment in that some of the arrangement of the components constituting the fluid circuit 40 has been changed, and in other respects it is the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0059] As shown in Figure 10, in the third embodiment, the fluid mixer 1 and the high-temperature valve 43 are arranged side by side. On the other hand, the low-temperature valve 44 is positioned away from the fluid mixer 1 and the high-temperature valve 43. This suppresses direct heat exchange between the high-temperature valve 43 and the low-temperature valve 44. The high-temperature valve 43 is, for example, a flow control valve, and the low-temperature valve 44 is, for example, a flow path switching valve.

[0060] (Fourth Embodiment) The fourth embodiment will now be described. The fourth embodiment is a modification of the configuration of the fluid mixer 1 compared to the first embodiment, and is otherwise the same as the first embodiment. Therefore, only the parts that differ from the first embodiment will be described.

[0061] As shown in Figure 11, the fluid mixer 1 of the fourth embodiment is equipped with an air vent port 27 in the center of the upper wall 26 of the mixing container 2. The air vent port 27 has the function of discharging air from the inside of the mixing container 2. A float or valve (not shown) that suppresses the discharge of liquid may be provided inside the air vent port 27. When the fluid mixer 1 is mounted on a vehicle, the air vent port 27 is positioned on the upper side of the mixing container 2 above the vehicle.

[0062] As shown by arrows SF1 and SF2 in Figure 11, the fluids supplied to the mixing container 2 from the multiple inflow passages 3 and 4 form a swirling flow. Since the air B contained in the fluid has a lower density than the liquid, it gathers near the center of the swirling flow. This air B then moves upward in the direction of gravity due to buoyancy and is discharged from the air vent port 27.

[0063] The fluid mixer 1 of the fourth embodiment described above is equipped with an air vent port 27 in the center of the upper wall 26 of the mixing container 2. This allows air contained in the fluid supplied to the mixing container 2 from the multiple inflow passages 3 and 4 to be discharged from the air vent port 27, thereby suppressing the mixing of air into the fluid supplied to downstream equipment from the discharge passage 5. Therefore, this fluid mixer 1 enhances the air venting function of the fluid circuit 40 and enables a highly efficient temperature control function for equipment downstream of the discharge passage 5.

[0064] (Fifth Embodiment) The fifth embodiment will now be described. The fifth embodiment is also the same as the first embodiment in that some of the components of the fluid mixer 1 have been changed, and other aspects are the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0065] As shown in Figure 12, the fluid mixer 1 of the fifth embodiment is equipped with a heat storage material 28 inside the mixing container 2. The heat storage material 28 is a member having a predetermined heat capacity that can exchange heat with the fluid inside the mixing container 2 and can store heat itself. The heat storage material 28 extends from the upper wall 26 of the mixing container 2 along the axis CL toward the bottom wall 25 to partway inside the mixing container 2. If the temperature of the fluid supplied to the inside of the mixing container 2 from the multiple inflow passages 3 and 4 changes suddenly and unintentionally, the heat storage material 28 can exchange heat with that fluid, thereby delaying the temperature change of the fluid discharged from the discharge passage 5. As a result, the temperature of the fluid supplied to downstream equipment from the discharge passage 5 does not change suddenly, and the temperature change of the fluid becomes gradual. In other words, the heat storage material 28 can transport heat in the time axis as well.

[0066] The fluid mixer 1 of the fifth embodiment described above is equipped with a heat storage material 28 inside the mixing container 2. This makes it possible to gradually change the temperature of the fluid discharged from the discharge passage 5 even if the temperature of the fluid supplied to the inside of the mixing container 2 from the multiple inflow passages 3 and 4 changes suddenly and unintentionally. Therefore, thermal shock to equipment connected downstream of the discharge passage 5 can be suppressed.

[0067] (Sixth Embodiment) The sixth embodiment will now be described. The sixth embodiment is also the same as the first embodiment in that some of the components of the fluid mixer 1 have been changed, and other aspects are the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0068] As shown in Figure 13, the fluid mixer 1 of the sixth embodiment is equipped with an inlet guide member 29 on a part of the inner circumferential wall 24. The inlet guide member 29 is provided on one side of the inner circumferential wall 24 with respect to the inlets 6 and 7 of at least one of the plurality of inlet passages 3 and 4. In this embodiment, the inlet guide member 29 is provided on one side of the inner circumferential wall 24 with respect to the inlet 6 of the high-temperature side inlet passage 3. The inlet guide member 29 extends from the inner circumferential wall 24 toward the inside of the mixing container 2 so as to approach the inner extension line IE1, which is the extension of the flow path axis Ax1 of the high-temperature side inlet passage 3 on which the inlet guide member 29 is provided toward the inside of the mixing container 2. The length of the inlet guide member 29 extending from the inner circumferential wall 24 toward the inside of the mixing container 2 is less than half the radius of the mixing container 2. Also, the width of the inlet guide member 29 in the axial direction (i.e., the width in the depth direction of the paper in Figure 13) is the same as or greater than the width of the inlet 6.

[0069] As a result, the high-temperature fluid flowing into the mixing container 2 from the high-temperature side inflow passage 3 is guided by the inlet guide member 29, forming a swirling flow SF1 at a position further from the axis CL of the mixing container 2 than the swirling flow SF2 of the low-temperature fluid flowing into the mixing container 2 from the low-temperature side inflow passage 4. On the other hand, the low-temperature fluid flowing into the mixing container 2 from the low-temperature side inflow passage 4 forms a swirling flow SF2 at a position closer to the axis CL of the mixing container 2 than the swirling flow SF1 of the high-temperature fluid. Since the centrifugal force acting on the swirling flow SF2 of the low-temperature fluid is greater than the centrifugal force acting on the swirling flow SF1 of the high-temperature fluid, the low-temperature fluid moves radially outward due to the centrifugal force while swirling, and quickly mixes with the high-temperature fluid swirling radially outward. Therefore, the fluid mixer 1 of the sixth embodiment can further improve the agitation of the low-temperature fluid and the high-temperature fluid, mix the low-temperature fluid and the high-temperature fluid to a uniform temperature, and reduce the size of the mixing container 2.

[0070] (Seventh Embodiment) The seventh embodiment will now be described. The seventh embodiment is also the same as the first embodiment in that some of the components of the fluid mixer 1 have been changed, and in other respects it is the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0071] As shown in Figure 14, the fluid mixer 1 of the seventh embodiment is equipped with a central guide member 10 in the center of the inside of the mixing container 2. The central guide member 10 has a shape symmetrical with respect to the axis CL of the mixing container 2, and can be, for example, cylindrical or conical. For example, the central guide member 10 may have a shape in which the outer diameter gradually decreases from one side to the other in the axial direction. The central guide member 10 can promote swirling flow.

[0072] (Eighth Embodiment) The eighth embodiment will now be described. The eighth embodiment is also the same as the first embodiment in that some of the components of the fluid mixer 1 have been changed, and in other respects it is the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0073] As shown in Figure 15, the fluid mixer 1 of the eighth embodiment includes an outer guide member 11 extending inward from the inner circumferential wall 24 of the mixing container 2. The outer guide member 11 is formed in the shape of a plate that extends inward from the inner circumferential wall 24 of the mixing container 2 and inclined to the other side in the circumferential direction with respect to the radial direction of the mixing container 2. The number, size, shape, etc., of the outer guide member 11 can be arbitrarily determined. The outer guide member 11 can promote a swirling flow toward the center. Note that the outer guide member 11 does not have to be in contact with the inner circumferential wall 24, and may be provided near the inner circumferential wall 24.

[0074] (Ninth Embodiment) The ninth embodiment will now be described. The ninth embodiment is also the same as the first embodiment in that some of the components of the fluid mixer 1 have been changed, and in other respects it is the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0075] As shown in Figure 16, the fluid mixer 1 of the ninth embodiment is equipped with an inner guide member 12 near the center of the mixing container 2. The inner guide member 12 is formed in the shape of a plate that extends from the center of the mixing container 2 toward the inner circumferential wall 24 of the mixing container 2 and is inclined toward the other side in the circumferential direction with respect to the radial direction of the mixing container 2. The number, size, shape, etc. of the inner guide member 12 can be arbitrarily determined. The inner guide member 12 can promote swirling flow toward the outside.

[0076] (Tenth Embodiment) The tenth embodiment will now be described. The tenth embodiment is also a modification of the fluid mixer 1 compared to the first embodiment, and is otherwise the same as the first embodiment, so only the parts that differ from the first embodiment will be described.

[0077] As shown in Figures 17 to 19, the fluid mixer 1 of the tenth embodiment has a first fluid chamber 13 and a second fluid chamber 14 inside the mixing container 2. The first fluid chamber 13 and the second fluid chamber 14 are a single space that communicates in the axial direction.

[0078] The first fluid chamber 13 is a cylindrical space formed on the upper wall 26 side inside the mixing vessel 2. The first fluid chamber 13 is circular in shape when viewed from the axial direction of the fluid mixer 1. The inner circumferential wall 24 forming the first fluid chamber 13 is provided with a high-temperature side inlet 6 and a low-temperature side inlet 7.

[0079] On the other hand, the second fluid chamber 14 is a space formed inside the mixing container 2 on the bottom wall 25 side relative to the first fluid chamber 13. The cross-sectional area perpendicular to the axis CL in the second fluid chamber 14 is smaller than the cross-sectional area perpendicular to the axis CL in the first fluid chamber 13. The second fluid chamber 14 is fan-shaped when viewed from the axial direction of the fluid mixer 1. Therefore, the second fluid chamber 14 has a first plane 15 and a second plane 16 parallel to the axis CL of the mixing container 2, and an arc-shaped inner circumferential wall 24 connecting the radially outer portion of the first plane 15 and the radially outer portion of the second plane 16. The inner circumferential wall 24 forming the first fluid chamber 13 and the inner circumferential wall 24 forming the second fluid chamber 14 are continuous planes in the axial direction. In this embodiment, the angle between the first plane 15 and the second plane 16 is approximately 90°. However, the angle between the first plane 15 and the second plane 16 can be set arbitrarily.

[0080] As shown in Figure 19, a first discharge port 8 is provided in the bottom wall 25 that forms the second fluid chamber 14. A second discharge port 9 is provided in the arc-shaped inner circumferential wall 24 that forms the second fluid chamber 14. The centers of both the first discharge port 8 and the second discharge port 9 are located offset from the axis CL of the fluid mixer 1. As shown in Figure 22, the first discharge passage 5a extending from the first discharge port 8 extends approximately parallel to the axis CL. The second discharge passage 5b extending from the second discharge port 9 extends approximately perpendicular to the axis CL.

[0081] As shown in Figures 18 to 20, a connecting pipe 60 is provided on the upper wall 26 of the mixing container 2. The connecting pipe 60 is a pipe that connects the reserve tank 70, which stores fluid, to the mixing container 2. Of the connecting pipe 60, the opening on the upper wall 26 side of the mixing container 2 becomes an air vent port 27 that discharges air from the inside of the mixing container 2.

[0082] The connecting pipe 60 has a shape in which the flow path cross-sectional area gradually increases from the air vent port 27 side toward the reserve tank 70 side. Furthermore, when the fluid mixer 1 is mounted on the vehicle, the inner wall surface 61 of the connecting pipe 60 on the vehicle side is inclined toward the vehicle side toward the reserve tank 70 side from the air vent port 27 side. As a result, the air inside the mixing container 2 is guided by buoyancy toward the inner wall surface 61 of the connecting pipe 60 on the vehicle side toward the reserve tank 70.

[0083] Furthermore, the connecting pipe 60 has a bent section 62 where the flow path bends between the air vent port 27 and the reserve tank 70. In this embodiment, the portion of the connecting pipe 60 that extends from the bent section 62 toward the reserve tank 70 extends in a direction intersecting the axis CL of the mixing container 2.

[0084] As shown in Figure 20, multiple ribs 63 are provided on the upper wall 26 of the mixing container 2 and the connecting pipe 60. The multiple ribs 63 connect the upper wall 26 of the mixing container 2 and the connecting pipe 60, increasing their rigidity. As shown in Figure 21, the inner wall surface 64 of the multiple ribs 63 (hereinafter referred to as "inner wall surface 64 of the ribs 63") has a concave shape that is recessed towards the upper side of the vehicle. As shown in Figures 18 and 19, the concave shape of the inner wall surface 64 of the multiple ribs 63 is inclined upward towards the connecting pipe 60 from a position further away from the connecting pipe 60. As a result, the air inside the mixing container 2 is guided by buoyancy along the inner wall surface 64 of the multiple ribs 63 and led to the connecting pipe 60.

[0085] Next, the movement of the swirling flow and bubbles generated in the fluid mixer 1 of the tenth embodiment will be described.

[0086] Figure 22 shows the fluid mixer 1 of the 10th embodiment when fluid is supplied to the inside of the mixing container 2 from two inlet passages 3 and 4. As shown in Figure 22, when fluid is supplied to the inside of the mixing container 2 from the two inlet passages 3 and 4, a swirling flow SF is generated in the first fluid chamber 13, and the high-temperature fluid and the low-temperature fluid are mixed. In addition, because the cross-sectional area of ​​the second fluid chamber 14 is smaller than that of the first fluid chamber 13, the flow velocity of the swirling flow SF flowing through the second fluid chamber 14 is increased, promoting the mixing of the high-temperature fluid and the low-temperature fluid. Furthermore, the swirling flow SF flowing through the second fluid chamber 14 collides with at least one of the first plane 15 and the second plane 16, causing flow turbulence, which further promotes the mixing of the high-temperature fluid and the low-temperature fluid.

[0087] Furthermore, in the fluid mixer 1 of the tenth embodiment, the centers of the discharge ports 8 and 9 are offset from the axis CL of the mixing container 2, making it easier to separate the air B contained in the swirling flow SF from the liquid. As a result, the outflow of air B contained in the fluid in the mixing container 2 into the discharge passages 5a and 5b together with the liquid is suppressed. The air B (i.e., bubbles) separated from the liquid in the mixing container 2 gathers near the center of the swirling flow SF and moves upward in the direction of gravity due to buoyancy. This air B (i.e., bubbles) then moves from the air vent port 27 through the connecting pipe 60 to the reserve tank 70.

[0088] Incidentally, since the area from the fluid mixer 1 to the reserve tank 70 via the connecting pipe 60 is filled with fluid, there is a risk that the swirling flow SF generated in the mixing container 2 may propagate to the connecting pipe 60. However, since the connecting pipe 60 in this embodiment has a bent section 62, the swirling flow SF generated in the mixing container 2 disappears at the bent section 62, and its propagation to the reserve tank 70 is suppressed. Therefore, since no swirling flow SF is generated in the reserve tank 70, it is possible to prevent the air B in the reserve tank 70 from being guided by the swirling flow SF and entering the mixing container 2.

[0089] Here, in order to compare with the fluid mixer 1 of the tenth embodiment, the movement of the swirling flow SF and bubbles generated in the fluid mixer 1 of the second comparative example will be explained with reference to Figure 23.

[0090] As shown in Figure 23, the mixing container 2 of the second comparative example has only a cylindrical fluid chamber 20 and does not have the second fluid chamber 14 described in the tenth embodiment. Also, in the mixing container 2 of the second comparative example, the center of the discharge port 8 coincides with the axis CL of the mixing container 2. Furthermore, in the mixing container 2 of the second comparative example, the communication pipe 60 does not have a bent portion 62, and the reserve tank 70 is provided directly above the mixing container 2.

[0091] Figure 23 shows the fluid mixer 1 of the second comparative example when fluid is supplied to the inside of the mixing container 2 from two inlet passages 3 and 4. As shown in Figure 23, when fluid is supplied to the mixing container 2 from the two inlet passages 3 and 4, a swirling flow SF is generated in the fluid chamber 20, and the high-temperature fluid and the low-temperature fluid are mixed. In the fluid mixer 1 of the second comparative example, the center of the discharge port 8 coincides with the axis CL of the mixing container 2, so compared to the fluid mixer 1 of the 10th embodiment, a portion of the air B contained in the swirling flow SF (i.e., bubbles) is more easily released from the discharge port 8 to the discharge passage 5 along with the liquid.

[0092] Furthermore, in the second comparative example, the swirling flow SF generated in the mixing container 2 passes through the connecting pipe 60 and propagates to the reserve tank 70. As a result, a swirling flow SF is generated in the reserve tank 70, and as shown by arrow BF, the air B in the reserve tank 70 is guided by the swirling flow SF and flows into the mixing container 2. The air B that flows from the reserve tank 70 into the mixing container 2 flows out with the liquid from the discharge port 8 to the discharge passage 5, as described above. Therefore, in the second comparative example, the heat exchange efficiency of the mixing container 2 may deteriorate in the heat exchanger downstream of the discharge passage 5.

[0093] Compared to the fluid mixer 1 of the second comparative example described above, the fluid mixer 1 of the tenth embodiment provides the following effects: (1) In the fluid mixer 1 of the tenth embodiment, the centers of the discharge ports 8 and 9 are offset from the axis CL of the mixing container 2. This suppresses the outflow of air contained in the fluid in the mixing container 2 into the discharge passages 5a and 5b along with the liquid. Therefore, it is possible to suppress the mixing of air into the fluid supplied from the fluid mixer 1 to the equipment downstream of the discharge passages 5a and 5b, and to realize a highly efficient temperature control function for the equipment downstream of the fluid mixer 1.

[0094] (2) The mixing container 2 of the tenth embodiment has a cylindrical first fluid chamber 13 provided with a plurality of inlets 6, 7, and a second fluid chamber 14 communicating with the first fluid chamber 13 and provided with discharge ports 8, 9. The second fluid chamber 14 is formed in a fan shape when viewed from the axial direction of the mixing container 2 and has a first plane 15 and a second plane 16 parallel to the axis CL of the mixing container 2, and a curved surface (i.e., a part of the inner circumferential wall 24) connecting the radially outer portion of the first plane 15 and the radially outer portion of the second plane 16. With this, the swirling flow SF formed in the first fluid chamber 13 inside the mixing container 2 collides with at least one of the first plane 15 and the second plane 16, thereby promoting flow turbulence, so that fluids of different temperatures can be mixed in the mixing container 2 in a smaller volume and to a more uniform temperature.

[0095] (3) In the tenth embodiment, the mixing vessel 2 has a smaller cross-sectional area perpendicular to the axis CL in the second fluid chamber 14 compared to the cross-sectional area perpendicular to the axis CL in the first fluid chamber 13. This makes it possible to constrict the flow in the second fluid chamber 14 relative to the first fluid chamber 13, accelerating the flow velocity and further promoting flow turbulence. As a result, fluids of different temperatures supplied to the fluid chambers 13 and 14 from multiple inlet passages 3 and 4 can be quickly mixed to a uniform temperature in the small-capacity fluid chambers 13 and 14, and fluids of uniform temperature can be discharged from the discharge passages 5a and 5b. Therefore, this fluid mixer 1 can be made smaller in size, and by improving the heat exchange efficiency, it can achieve a highly efficient temperature control function for equipment downstream of the fluid mixer 1 in the fluid circuit 40.

[0096] (4) The fluid mixer 1 of the tenth embodiment is equipped with a connecting pipe 60 that connects the air vent port 27 and the reserve tank 70. When the fluid mixer 1 is mounted on a vehicle, the inner wall surface 61 of the connecting pipe 60 on the vehicle side is inclined upward toward the vehicle side from the air vent port 27 side toward the reserve tank 70 side. This allows the air contained in the fluid in the mixing container 2 to be guided by buoyancy through the inner wall surface 61 of the connecting pipe 60 on the vehicle side toward the reserve tank 70.

[0097] (5) The communication pipe 60 of the tenth embodiment has a shape in which the flow path cross-sectional area gradually increases from the air vent port 27 side to the reserve tank 70 side. With this, when the fluid mixer 1 is mounted on the vehicle, the inner wall surface 61 of the communication pipe 60 on the vehicle side can be inclined upwards toward the vehicle from the air vent port 27 side to the reserve tank 70 side.

[0098] (5) The connecting pipe 60 of the tenth embodiment has a bent portion 62 in which the flow path is bent. With this, the bent portion 62 can suppress the transmission of the swirling flow SF in the mixing container 2 into the reserve tank 70. If the connecting pipe 60 is not provided with a bent portion 62 as in the second comparative example described above, a swirling flow SF will be generated in the reserve tank 70, and the air in the reserve may flow into the mixing container 2 passing near the center of the swirling flow SF. In contrast, in the tenth embodiment, by providing a bent portion 62 in the connecting pipe 60, the generation of a swirling flow SF in the reserve tank 70 can be suppressed, and the air in the reserve tank 70 can be prevented from flowing into the mixing container 2.

[0099] (6) The fluid mixer 1 of the tenth embodiment further comprises a plurality of ribs 63 that connect the upper wall 26 of the mixing container 2 to the communication pipe 60. When the fluid mixer 1 is mounted on a vehicle, the inner wall surface 64 of the ribs 63 is inclined upward toward the vehicle toward the communication pipe 60 from a position further away from the communication pipe 60. This allows air contained in the fluid in the mixing container 2 to be guided by buoyancy through the inner wall surface 64 of the ribs 63 to the communication pipe 60.

[0100] (Eleventh Embodiment) The eleventh embodiment will now be described. The eleventh embodiment is a modification of the configuration of the connecting pipe 60 compared to the tenth embodiment, and is otherwise the same as the tenth embodiment, so only the parts that differ from the tenth embodiment will be described.

[0101] As shown in Figure 24, in the 11th embodiment, when the fluid mixer 1 is mounted on the vehicle, the flow path axis 65 of the communication pipe 60 is inclined upwards toward the vehicle, from the air vent port 27 side toward the reserve tank 70 side. The communication pipe 60 has a shape in which the flow path cross-sectional area gradually increases from the air vent port 27 side toward the reserve tank 70 side. As a result, the inclination angle of the inner wall surface 61 on the upper side of the vehicle of the communication pipe 60 in the 11th embodiment can be made larger. Therefore, the air inside the mixing container 2 is guided by buoyancy toward the inner wall surface 61 on the upper side of the vehicle of the communication pipe 60 and flows more easily toward the reserve tank 70. Consequently, the fluid mixer 1 in the 11th embodiment can suppress the outflow of air contained in the fluid inside the mixing container 2 into the discharge passages 5a and 5b along with the liquid.

[0102] (Twelfth Embodiment) In the twelfth embodiment, an integrated fluid apparatus 80 equipped with the fluid mixer 1 described in the first to eleventh embodiments will be described.

[0103] As shown in Figures 25 and 26, the integrated fluid device 80 of the twelfth embodiment integrates some of the components of the heat pump cycle 31 and some of the components of the fluid circuit 40 that are included in the vehicle thermal management system 30 described in the first embodiment with reference to Figure 4.

[0104] The integrated fluid device 80 includes a receiver 37, a water-cooled condenser 33, an expansion valve 34, a chiller 35, and other components of the heat pump cycle 31. In Figure 26, the receiver 37, water-cooled condenser 33, expansion valve 34, and chiller 35 are arranged in this order from right to left.

[0105] Furthermore, the integrated fluid device 80 includes, as part of the components of the fluid circuit 40, a high-temperature valve 43, a fluid mixer 1, a low-temperature valve 44, a high-temperature pump 50, a first low-temperature pump 51, a second low-temperature pump 52, and the like. In Figures 25 and 26, the high-temperature valve 43, the fluid mixer 1, and the low-temperature valve 44 are arranged in this order from right to left. The high-temperature pump 50 is located below the high-temperature valve 43, the first low-temperature pump 51 is located below the fluid mixer 1, and the second low-temperature pump 52 is located below the low-temperature valve 44.

[0106] The components of the heat pump cycle 31 and the components of the fluid circuit 40 are arranged opposite each other with a manifold plate 53 in between. The manifold plate 53 is a plate in which a refrigerant flow path and a fluid flow path are formed.

[0107] In this integrated fluid device 80, the distance Da between the fluid mixer 1 and the low-temperature valve 44 is greater than the distance Db between the fluid mixer 1 and the high-temperature valve 43. This suppresses heat transfer between the fluid mixer 1 and the low-temperature valve 44. Therefore, heat dissipation from the high-temperature valve 43 and the fluid mixer 1 to the low-temperature valve 44 can be suppressed, especially during winter.

[0108] Furthermore, as shown in Figure 27, in this integrated fluid device 80, the rotation axis 44a of the valve body of the low-temperature side valve 44 and the rotation axis 52a of the motor and impeller of the second low-temperature side pump 52 are coaxial. This suppresses vibrations of the low-temperature side valve 44 and the second low-temperature side pump 52. As a result, deformation of various parts of the integrated fluid device 80 (for example, pipe connection parts) due to vibration can be prevented.

[0109] Furthermore, the rotation axis 45a of the valve body of the high-temperature side valve 43 and the rotation axis 50a of the motor and impeller of the high-temperature side pump 50 are coaxial. This suppresses vibrations of the high-temperature side valve 43 and the high-temperature side pump 50. As a result, deformation of various parts of the integrated fluid device 80 (for example, pipe connection parts) due to vibration can be prevented.

[0110] (Third Embodiment) In the thirteenth embodiment, an example of the fluid flow path on the fluid circuit 40 side of the integrated fluid device 80 described in the twelfth embodiment will be described.

[0111] Figure 27 is a cross-sectional view of the integrated fluid device 80 of the 13th embodiment, corresponding to the line XXVII-XXVII in Figure 26, showing an example of a fluid flow path on the fluid circuit 40 side. As shown in Figure 27, the high-temperature side inflow passage 3, which supplies fluid from the high-temperature side valve 43 to the fluid mixer 1, and the fluid chambers 13, 14 and the first discharge passage 5a inside the fluid mixer 1 are adjacent to each other via a single wall 19. The single wall 19 includes a part of the side 21 and a part of the bottom 22 of the mixing container 2. This promotes heat transfer between the high-temperature side inflow passage 3 and the fluid mixer 1, and suppresses the temperature drop of the fluid mixer 1. In the 13th embodiment as well, the distance Da between the fluid mixer 1 and the low-temperature side valve 44 is greater than the distance Db between the fluid mixer 1 and the high-temperature side valve 43, so heat transfer between the fluid mixer 1 and the low-temperature side valve 44 is suppressed. Therefore, heat dissipation from the high-temperature valve 43 and fluid mixer 1 to the low-temperature valve 44 can be suppressed, mainly during winter.

[0112] (Other Embodiments) (1) In the above embodiments, the flow path axes Ax1 and Ax2 of the portion of each of the multiple inflow passages 3 and 4 that extends linearly from the mixing container 2 are described as being inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension lines OE1 and OE2 of each inflow passage 3 and 4. However, the embodiment is not limited to this. For example, in at least one of the multiple inflow passages 3 and 4, the flow path axes Ax1 and Ax2 of the portion that extends linearly from the mixing container 2 are inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension lines OE1 and OE2 of that inflow passage.

[0113] (2) In the above embodiments, the fluid mixer 1 has been described as having two inflow passages 3 and 4, but it is not limited to this, and for example, there may be three or more inflow passages. In that case, the flow path axis of the additional inflow passage does not have to be inclined to one side in the circumferential direction of the inner circumferential wall 24 with respect to the outer extension line, as long as it does not impede the mixing of the low-temperature fluid and the high-temperature fluid.

[0114] (3) In each of the above embodiments, the inlets 6 and 7 of the inflow passages 3 and 4 are provided on the inner circumferential wall 24 of the mixing container 2. However, the invention is not limited to this, and for example, the inlets 6 and 7 may be provided on the upper wall 26 of the mixing container 2.

[0115] (4) In each of the above embodiments, the fluid mixer 1 has been described as having one discharge passage 5, but it is not limited to this, and for example, there may be two or more discharge passages, and there may be two or more discharge ports 8 of the discharge passage 5.

[0116] (5) In each of the above embodiments, the discharge port 8 of the discharge passage 5 is provided on the bottom wall 25 of the mixing container 2. However, it is not limited to this, and for example, the discharge port 8 of the discharge passage 5 may be provided on the inner circumferential wall 24 of the mixing container 2 at a position close to the bottom wall 25.

[0117] (6) In the above embodiments, the mixing container 2 of the fluid mixer 1 has been described as being cylindrical, but it is not limited to this. The mixing container 2 may have a circular, elliptical, polygonal, or similar shape in cross-section perpendicular to the axis CL, and in three dimensions it may be cylindrical, conical, ball-shaped, etc., and may have irregularities on the inner circumferential wall 24.

[0118] (7) In each of the above embodiments, the fluid circuit 40 was described as using, for example, antifreeze, LLC, or water as the fluid, but it is not limited to these, and various fluids such as oil or nanofluids may be used.

[0119] (8) In each of the above embodiments, the heat pump cycle 31 has been described as constituting a subcritical refrigeration cycle, but it is not limited to this, and may also constitute a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant. Furthermore, the heat pump cycle 31 may use natural refrigerants such as carbon dioxide or hydrocarbon refrigerants as the refrigerant.

[0120] (9) In the above embodiments, the axial direction of the fluid mixer 1 was described as corresponding to the vertical direction of the vehicle when the fluid mixer 1 is mounted on the vehicle. However, the axial direction of the fluid mixer 1 may be in any direction when the fluid mixer 1 is mounted on the vehicle. For example, the axial direction of the fluid mixer 1 may be in the horizontal direction of the vehicle, or it may be in an oblique direction. Alternatively, the fluid mixer 1 may be arranged so that one side in the axial direction corresponds to the upper side of the vehicle and the other side in the axial direction corresponds to the lower side of the vehicle.

[0121] This disclosure is not limited to the embodiments described above and can be modified as appropriate. Furthermore, the embodiments and parts thereof are not unrelated to each other and can be combined as appropriate, except in cases where the combination is clearly impossible. In addition, it goes without saying that the elements constituting the embodiments are not necessarily essential unless they are explicitly stated to be particularly essential or are clearly considered essential in principle. Furthermore, when numerical values ​​such as the number, numerical values, quantities, or ranges of the components of the embodiments are mentioned in the embodiments, they are not limited to those specific numbers unless they are explicitly stated to be particularly essential or are clearly limited to a specific number in principle. Furthermore, when the shapes, positional relationships, etc. of the components are mentioned in the embodiments, they are not limited to those shapes, positional relationships, etc. unless they are explicitly stated to be particular or are clearly limited to a specific shape, positional relationship, etc. in principle.

[0122] (Perspective of this disclosure) The above disclosure can be understood, for example, from the following perspectives. [First perspective] A fluid mixer used in a fluid circuit (40) mounted on a vehicle, comprising: a mixing container (2) having a cylindrical inner wall (24); a plurality of inflow passages (3, 4) for supplying fluids of different temperatures to the inside of the mixing container; and a discharge passage (5) for discharging fluid from the inside of the mixing container, wherein the flow path axis (Ax1, Ax2) of a portion of at least one of the plurality of inflow passages that extends linearly from the mixing container is inclined to one side in the circumferential direction of the cylindrical inner wall with respect to an outer extension line (OE1, OE2) obtained by extending a line connecting the center (C1, C2) of the inlet (6, 7) to which the inflow passage connects to the mixing container and the axis (CL) of the mixing container to the outside of the mixing container. [Second viewpoint] The fluid mixer according to the first viewpoint, wherein the flow path axes (Ax1, Ax2) of the portions of the plurality of inlet passages that extend linearly from the mixing container are inclined to one side in the circumferential direction of the cylindrical inner wall with respect to the outer extension lines (OE1, OE2) of each of the inlet passages. [Third viewpoint] The fluid mixer according to the first or second viewpoint, wherein the plurality of inlets are provided on the cylindrical inner wall in a direction perpendicular to the axis of the mixing container, and the discharge port (8) of the discharge passage that connects to the mixing container is provided on the bottom wall (25) on one side of the mixing container in the direction in which the axis extends. [Fourth viewpoint] The fluid mixer according to any one of the first to third viewpoints, wherein the fluid circuit is equipped with a flow control valve (43) that adjusts the flow rate of the fluid flowing through the fluid circuit, and at least one of the plurality of inlet passages and discharge passages is connected to the flow control valve. [Fifth viewpoint] The fluid mixer according to any one of the first to fourth viewpoints, wherein the fluid circuit is equipped with a flow path switching valve (44) that switches the path of the fluid flowing through the fluid circuit, and at least one of the plurality of inflow passages and discharge passages is connected to the flow path switching valve.[Sixth viewpoint] When, among the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing vessel is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing vessel is called the low-temperature side inflow passage (4), the distance (D1) between the inner extension line (IE2) of the flow path axis (Ax2) of the low-temperature side inflow passage and the axis of the mixing vessel is shorter than the distance (D1) between the inner extension line (IE1) of the flow path axis (Ax1) of the high-temperature side inflow passage and the axis of the mixing vessel. This is the fluid mixer according to any one of the first to fifth viewpoints. [Seventh viewpoint] When, among the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing container is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing container is called the low-temperature side inflow passage (4), the low-temperature side inlet (7) to which the low-temperature side inflow passage connects to the mixing container is located further from the discharge passage in the direction in which the axis of the mixing container extends than the high-temperature side inlet (6) to which the high-temperature side inflow passage connects to the mixing container, the fluid mixer according to any one of the first to sixth viewpoints. [Eighth viewpoint] The fluid circuit comprises a high-temperature valve (43) that supplies a higher-temperature fluid to the mixing vessel via a predetermined inflow passage, and a low-temperature valve (44) that supplies a lower-temperature fluid to the mixing vessel via another inflow passage, or to which fluid discharged from the discharge passage is supplied, wherein the high-temperature valve is provided in a region (α) on one radial side of the cylindrical inner wall relative to the mixing vessel, and the low-temperature valve is provided in a region (β) on the other radial side of the cylindrical inner wall relative to the mixing vessel. This is the fluid mixer according to any one of the first to seventh viewpoints. [Ninth viewpoint] The high-temperature valve, the mixing vessel, and the low-temperature valve are arranged in a straight line. This is the fluid mixer according to the eighth viewpoint. [Tenth viewpoint] The fluid mixer according to any one of the first to ninth viewpoints, further comprising an air vent port (27) in the center of the upper wall (26) on the other side of the mixing vessel in the direction of the extending axis, for discharging air from the inside of the mixing vessel.[Aspect 11] The fluid mixer according to the tenth aspect, wherein, when the mixing container is mounted on a vehicle, the air vent port is located on the upper side in the vertical direction of the vehicle. [Aspect 12] The fluid mixer according to any one of the first to eleventh aspects, further comprising a heat storage material (28) provided inside the mixing container, capable of exchanging heat with the fluid inside the mixing container and having a predetermined heat capacity capable of storing heat itself. [Aspect 13] The fluid mixer according to any one of the first to twelfth aspects, further comprising an inlet guide member (29) provided on one side of the circumferential direction of the cylindrical inner wall with respect to the inlet of at least one of the plurality of inlet passages, wherein the inlet guide member extends from the cylindrical inner wall into the inside of the mixing container so as to approach an inner extension line (IE1) which extends the flow path axis of the inlet passage on which the inlet guide member is provided into the inside of the mixing container. [14th viewpoint] When, among the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing container is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing container is called the low-temperature side inflow passage (4), the inlet guide member is provided on one side of the circumferential direction of the cylindrical inner wall with respect to the inlet of the high-temperature side inflow passage, and extends from the cylindrical inner wall to the inside of the mixing container so as to approach the inner extension line (IE1) which extends the flow path axis of the high-temperature side inflow passage to the inside of the mixing container, as described in the 13th viewpoint. [15th viewpoint] The fluid mixer according to any one of the first to 14th viewpoints, further comprising a central guide member (10) in the central part of the inside of the mixing container, having a shape symmetrical with respect to the axis of the mixing container. [16th viewpoint] A fluid mixer according to any one of the first to 15 viewpoints, further comprising a plate-shaped outer guide member (11) that extends from the cylindrical inner wall of the mixing container toward the inside of the mixing container and inclined toward the other side in the circumferential direction with respect to the radial direction of the mixing container. [17th viewpoint] A fluid mixer according to any one of the first to 16 viewpoints, further comprising a plate-shaped inner guide member (12) that extends from the central part of the mixing container toward the cylindrical inner wall and inclined toward the other side in the circumferential direction with respect to the radial direction of the mixing container.[Aspect 18] A fluid circuit mounted on a vehicle, comprising: a fluid mixer (1) as described in the first aspect; a high-temperature side valve (43) that supplies a fluid on the higher temperature side to the mixing container via a predetermined inlet passage from among a plurality of inlet passages; and a low-temperature side valve (44) that supplies a fluid on the lower temperature side to the mixing container via another inlet passage from among a plurality of inlet passages, or to which fluid discharged from the discharge passage is supplied, wherein the high-temperature side valve is provided in a region on one side of the radial direction of the cylindrical inner wall with respect to the mixing container, and the low-temperature side valve is provided in a region on the other side of the radial direction of the cylindrical inner wall with respect to the mixing container. [Aspect 19] The fluid circuit as described in the eighteenth aspect, wherein the low-temperature side valve is a flow path switching valve that switches the path of the fluid flowing through the fluid circuit, and the high-temperature side valve is a flow rate control valve that adjusts the flow rate of the fluid flowing through the fluid circuit. [20th viewpoint] The fluid mixer according to any one of the first to 17th viewpoints, wherein the center of the discharge port (8, 9) to which the discharge passage connects to the mixing container is offset from the axis of the mixing container. [21st viewpoint] The fluid mixer according to the 20th viewpoint, wherein the mixing container has a cylindrical first fluid chamber (13) provided with a plurality of inlets and a second fluid chamber (14) communicating with the first fluid chamber and provided with the discharge port, the second fluid chamber is formed in a fan shape when viewed from the axial direction of the mixing container and has a first plane (15) and a second plane (16) parallel to the axis of the mixing container and an arc-shaped inner circumferential wall (24) connecting the radially outer portion of the first plane and the radially outer portion of the second plane. [22nd viewpoint] The fluid mixer according to the 21st viewpoint, wherein the cross-sectional area perpendicular to the axis in the second fluid chamber is smaller than the cross-sectional area perpendicular to the axis in the first fluid chamber.[23rd viewpoint] The fluid mixer according to any one of the first to 17th or 20 to 22nd viewpoints, further comprising: an air vent port (27) provided on the upper wall (26) of the mixing container on the other side in the direction in which the axis extends, for discharging air from the inside of the mixing container; a reserve tank (70) for storing fluid; and a connecting pipe (60) connecting the air vent port and the reserve tank, wherein, when the fluid mixer is mounted on a vehicle, the inner wall surface (61) of the connecting pipe on the vehicle side is inclined upward toward the vehicle toward the vehicle toward the air vent port side toward the reserve tank side. [24th viewpoint] The fluid mixer according to the 23rd viewpoint, wherein the connecting pipe has a shape in which the cross-sectional area of ​​the flow path gradually increases toward the reserve tank side toward the air vent port side. [25th Aspect] The fluid mixer according to the 23rd or 24th Aspect, wherein, when the fluid mixer is mounted on a vehicle, the flow path axis (65) of the communication pipe is inclined upward toward the vehicle toward the reserve tank side from the air vent port side. [26th Aspect] The fluid mixer according to any one of the 23rd to 25th Aspects, wherein the communication pipe has a bent portion (62) in which the flow path is bent. [27th Aspect] The fluid mixer according to any one of the 23rd to 26th Aspects, further comprising a plurality of ribs (63) that connect the upper wall of the mixing container and the communication pipe to increase rigidity, wherein, when the fluid mixer is mounted on a vehicle, the inner wall surface (64) of the ribs on the inside of the mixing container is inclined upward toward the vehicle toward the communication pipe from a position further away from the communication pipe. [Viewpoint 28] An integrated fluid device (80) comprising a fluid mixer (1) according to any one of claims 1 to 27, a high-temperature side valve (43) that supplies a fluid on the higher temperature side to the mixing container via a predetermined inlet passage (3) among a plurality of inlet passages, and a low-temperature side valve (44) that supplies a fluid on the lower temperature side to the mixing container via another inlet passage (4) among a plurality of inlet passages, or to which fluid discharged from the discharge passage is supplied, wherein the distance (Da) between the fluid mixer and the low-temperature side valve is greater than the distance (Db) between the fluid mixer and the high-temperature side valve.[29th Aspect] The integrated fluid apparatus according to the 28th aspect, wherein, among a plurality of inflow passages, the inflow passage (3) that supplies fluid from the high-temperature valve to the mixing vessel, the fluid chambers (13, 14) inside the mixing vessel, and the discharge passage (5a) are adjacent to each other via a single wall (19). [30th Aspect] The integrated fluid apparatus according to one of the 28th or 29th aspects, further comprising a low-temperature pump (52) that pumps fluid into the fluid circuit communicating with the low-temperature valve, wherein the rotation axis (44a) of the valve body of the low-temperature valve and the rotation axis (52a) of the motor and impeller of the low-temperature pump that flows fluid into the fluid circuit are coaxial.

Claims

1. A fluid mixer used in a fluid circuit (40) mounted on a vehicle, comprising: a mixing container (2) having a cylindrical inner wall (24); a plurality of inflow passages (3, 4) for supplying fluids of different temperatures to the inside of the mixing container; and a discharge passage (5) for discharging fluid from the inside of the mixing container, wherein the flow path axis (Ax1, Ax2) of a portion of at least one of the plurality of inflow passages that extends linearly from the mixing container is inclined to one side in the circumferential direction of the cylindrical inner wall with respect to an outer extension line (OE1, OE2) obtained by extending a line connecting the centers (C1, C2) of the inlet (6, 7) to which the inflow passage connects to the mixing container and the axis (CL) of the mixing container to the outside of the mixing container.

2. The fluid mixer according to claim 1, wherein the flow path axes (Ax1, Ax2) of the portions of each of the multiple inflow passages that extend linearly from the mixing vessel are inclined to one side in the circumferential direction of the cylindrical inner wall with respect to the outer extension lines (OE1, OE2) of each of the inflow passages.

3. The fluid mixer according to claim 1, wherein the plurality of inlets are provided on the cylindrical inner wall in a direction perpendicular to the axis of the mixing vessel, and the discharge port (8) on the bottom wall (25) on one side of the mixing vessel in the direction in which the axis extends.

4. The fluid mixer according to claim 1 or 2, wherein the fluid circuit includes a flow control valve (43) for adjusting the flow rate of the fluid flowing through the fluid circuit, and at least one of the plurality of inflow passages and discharge passages is connected to the flow control valve.

5. The fluid mixer according to claim 1 or 2, wherein the fluid circuit includes a flow path switching valve (44) that switches the path of the fluid flowing through the fluid circuit, and at least one of the plurality of inflow passages and discharge passages is connected to the flow path switching valve.

6. When, among the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing vessel is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing vessel is called the low-temperature side inflow passage (4), the distance (D2) between the inner extension line (IE2) of the flow path axis (Ax2) of the low-temperature side inflow passage and the axis of the mixing vessel is closer than the distance (D1) between the inner extension line (IE1) of the flow path axis (Ax1) of the high-temperature side inflow passage and the axis of the mixing vessel. The fluid mixer according to claim 1 or 2.

7. Of the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing container is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing container is called the low-temperature side inflow passage (4), wherein the low-temperature side inlet (7) to which the low-temperature side inflow passage connects to the mixing container is located further from the discharge passage in the direction in which the axis of the mixing container extends than the high-temperature side inlet (6) to which the high-temperature side inflow passage connects to the mixing container. The fluid mixer according to claim 1 or 2.

8. The fluid circuit comprises a high-temperature valve (43) that supplies a higher-temperature fluid to the mixing vessel via a predetermined inflow passage, and a low-temperature valve (44) that supplies a lower-temperature fluid to the mixing vessel via another inflow passage, or to which fluid discharged from the discharge passage is supplied, wherein the high-temperature valve is provided in one radial region (α) of the cylindrical inner wall relative to the mixing vessel, and the low-temperature valve is provided in the other radial region (β) of the cylindrical inner wall relative to the mixing vessel, the fluid mixer according to claim 1 or 2.

9. The fluid mixer according to claim 8, wherein the high-temperature valve, the mixing container, and the low-temperature valve are arranged in a straight line.

10. The fluid mixer according to claim 1 or 2, further comprising an air vent port (27) in the center of the upper wall (26) on the other side of the mixing container in the direction in which the axis extends, for discharging air from the inside of the mixing container.

11. The fluid mixer according to claim 10, wherein, when the mixing container is mounted on a vehicle, the air vent port is located on the upper side in the vertical direction of the vehicle.

12. The fluid mixer according to claim 1 or 2, further comprising a heat storage material (28) provided inside the mixing container, capable of exchanging heat with the fluid inside the mixing container and having a predetermined heat capacity capable of storing heat itself.

13. The fluid mixer according to claim 1 or 2, further comprising an inlet guide member (29) provided on a portion of the cylindrical inner wall adjacent to the inlet of at least one of the plurality of inlet passages, wherein the inlet guide member extends inward from the cylindrical inner wall of the mixing container so as to approach an inner extension line (IE1) which extends the flow path axis of the inlet passage on which the inlet guide member is provided inward into the mixing container.

14. Of the plurality of inflow passages, the one that supplies the fluid on the higher temperature side to the mixing container is called the high-temperature side inflow passage (3), and the one that supplies the fluid on the lower temperature side to the mixing container is called the low-temperature side inflow passage (4), wherein the inlet guide member is provided at a portion adjacent to the inlet on one side in the circumferential direction of the cylindrical inner wall with respect to the inlet of the high-temperature side inflow passage, and extends from the cylindrical inner wall inward into the mixing container so as to approach the inner extension line (IE1) which extends the flow path axis of the high-temperature side inflow passage inward into the mixing container, as described in claim 13.

15. The fluid mixer according to claim 1 or 2, further comprising a central guide member (10) having a shape symmetrical with respect to the axis of the mixing container, located in the central part of the inside of the mixing container.

16. The fluid mixer according to claim 1 or 2, further comprising a plate-shaped outer guide member (11) that extends from the cylindrical inner wall of the mixing container toward the inside of the mixing container and is inclined toward the other side in the circumferential direction with respect to the radial direction of the mixing container.

17. The fluid mixer according to claim 1 or 2, further comprising a plate-shaped inner guide member (12) that extends from the central part of the mixing container toward the cylindrical inner wall and is inclined toward the other side in the circumferential direction with respect to the radial direction of the mixing container.

18. A fluid circuit mounted on a vehicle, comprising: a fluid mixer (1) as described in claim 1; a high-temperature side valve (43) that supplies a fluid on the higher temperature side to the mixing container via a predetermined inlet passage from among a plurality of inlet passages; and a low-temperature side valve (44) that supplies a fluid on the lower temperature side to the mixing container via another inlet passage from among a plurality of inlet passages, or to which fluid discharged from the discharge passage is supplied, wherein the high-temperature side valve is provided in a region on one side of the radial direction of the cylindrical inner wall relative to the mixing container, and the low-temperature side valve is provided in a region on the other side of the radial direction of the cylindrical inner wall relative to the mixing container.

19. The fluid circuit according to claim 18, wherein the low-temperature valve is a flow path switching valve that switches the path of the fluid flowing through the fluid circuit, and the high-temperature valve is a flow control valve that adjusts the flow rate of the fluid flowing through the fluid circuit.

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