WO2024190093A1 - Control valve - Google Patents

Abstract

A control valve according to an aspect of the present disclosure comprises a casing, and a rotor having a valve body. A first communication port and a second communication port for providing communication between the inside and outside of an inner space are formed in the valve body at different locations around a central axis of the rotor. The valve body comprises a partition part that partitions the inner space into a first space that communicates with the first communication port and is open on a first side in the axial direction, and a second space that communicates with the second communication port and is open on a second side in the axial direction. The rotor rotates between a first state in which a first inlet communicates with a first outlet through the first space and a second inlet communicates with a second outlet through the second space, and a second state in which the first inlet communicates with the second outlet through the first space and the second inlet communicates with the first outlet through the second space.

Description

Control valve

The present disclosure relates to control valves.
This application claims priority to Japanese Patent Application No. 2023-039652, filed in Japan on March 14, 2023, the contents of which are incorporated herein by reference.

Vehicles are equipped with a cooling system. The cooling system cools heat-generating parts (e.g., engines, motors, etc.) with a coolant that circulates between the heat-generating parts and heat-dissipating parts (e.g., radiators, heaters, etc.). In the cooling system, the flow of the coolant is controlled by providing a control valve in the flow path that connects the heat-generating parts and heat-dissipating parts.

　Considerations are being made to further reduce the size of control valves. For example, the following Patent Document 1 discloses a configuration in which a first opening and a second opening are arranged in parallel in the axial direction of the valve body. In the following Patent Document 1, a third opening is arranged at a different circumferential position of the valve body from the first opening and the second opening, such that at least a portion of the first opening and the second opening overlap.

Japanese Patent Application Publication No. 2015-59615

However, in the conventional technology, for example, a sealing mechanism must be provided between the port and each opening, so there is still room for improvement in the conventional technology in terms of reducing the number of parts and reducing costs.
In the prior art, since only one inlet is provided, multiple control valves must be placed on the circuit in order to switch the circuit.

This disclosure provides a control valve that can switch circuits while reducing the number of parts and lowering costs.

In order to solve the above problems, the present disclosure employs the following aspects.
(1) A control valve according to one aspect of the present disclosure includes a casing having a first inlet and a second inlet through which a fluid flows in from the outside and a first outlet and a second outlet through which the fluid flows out to the outside, a shaft portion located on a first axial side and rotatably supported by the casing, and a rotor having a valve body that forms an internal space whose outer diameter gradually increases from the shaft portion toward a second axial side, the outer peripheral surface of the valve body being slidably supported on a support surface formed on the casing, and the valve body has a first communication port and a second communication port that communicate between the inside and the outside of the internal space at different positions around a central axis of the rotor. Two communication ports are formed, and the valve body is provided with a partition portion that separates the internal space into a first space that communicates with the first communication port and opens to a first side in the axial direction, and a second space that communicates with the second communication port and opens to a second side in the axial direction, and the rotor rotates between a first state in which the first inlet and the first outlet are communicated through the first space, and the second inlet and the second outlet are communicated through the second space, and a second state in which the first inlet and the second outlet are communicated through the first space, and the second inlet and the first outlet are communicated through the second space.

According to this aspect, since the outer peripheral surface of the valve disc is directly supported by the support surface of the casing, there is no need to provide a separate seal member or bearing, which reduces the number of parts and assembly steps, and enables the control valve to be made smaller and less expensive.
Because the valve disc is tapered, when the outer diameter of the rotor expands or contracts due to heat, the rotor displaces in the axial direction relative to the casing in response to the increase or decrease in the outer diameter. Therefore, the valve disc is stably supported by the casing regardless of the expansion or contraction of the rotor. This ensures the operational stability of the control valve.

In particular, in this aspect, the rotor is configured to rotate between a first state in which the first inlet and the first outlet are connected through the first space and the second inlet and the second outlet are connected through the second space, and a second state in which the first inlet and the second outlet are connected through the first space and the second inlet and the first outlet are connected through the second space.
According to this configuration, by installing a control valve between the two circuits, the circuits can be switched between a mode in which the fluid flows independently through each of the two circuits and a mode in which the fluid flows collectively between the two circuits. Moreover, in this aspect, the first space opens to a first axial side, while the second space opens to a second axial side, making it easy to keep the hydraulic pressure uniform in each space. Therefore, while ensuring the sealing between the valve body and the support surface, it is possible to suppress excessive sliding resistance and realize smooth rotation of the rotor.

(2) In the control valve relating to the above aspect (1), it is preferable that the first outlet and the second inlet are arranged at positions facing each other in a first radial direction that intersects the axial direction, and the first outlet and the second inlet are arranged at positions facing each other in a second radial direction that intersects the first direction when viewed from the axial direction.
According to this aspect, since the outlets and the inlets are arranged in different radial directions, the layout of the piping is facilitated.

(3) In the control valve according to either aspect (1) or (2) above, it is preferable that the volume of the second space is larger than the volume of the first space.
According to this aspect, it is easy to ensure the hydraulic pressure acting on the second space, which makes it easier to press the valve body against the support surface, thereby improving the sealing performance between the valve body and the support surface.

(4) In a control valve according to any one of aspects (1) to (3) above, it is preferable that the valve body, in a cross-sectional view along the axial direction, extends linearly toward the radially outward direction intersecting the axial direction as it moves from a first side to a second side in the axial direction.
However, for example, when the cross-sectional shape of the valve body is formed in an arc shape, the direction of the tangential direction of the outer peripheral surface of the valve body differs depending on the axial position. In this case, when the valve body shrinks due to heat, the deformation behavior differs depending on the axial position of the valve body. Specifically, the amount of deformation toward the radially inward direction increases toward the second axial side of the valve body (as the inclination of the tangential line increases), making it difficult to ensure sealing between the support surface and the valve body.
In contrast, according to the present embodiment, the cross-sectional shape of the valve disc is formed to be linear, which makes it easier to keep the deformation behavior of the valve disc due to thermal contraction uniform throughout the entire axial direction. As a result, the valve disc is stably supported on the support surface regardless of the expansion and contraction changes of the rotor. This ensures the operational stability of the control valve.

(5) In a control valve according to any one of aspects (1) to (4) above, it is preferable that, in a cross-sectional view along the axial direction, the angle between opposing parts of the valve body in a radial direction intersecting the axial direction is greater than 90° and smaller than 180°.
According to this aspect, by making the angle greater than 90°, when the outer diameter of the rotor expands or contracts due to heat, the rotor can be more smoothly displaced on the support surface in response to the increase or decrease in the outer diameter. Therefore, regardless of the expansion or contraction of the rotor, the valve body is stably supported on the support surface. This ensures the operational stability of the control valve.

(6) In the control valve according to any one of aspects (1) to (5) above, it is preferable that the second inlet and the second outlet are connected to a non-driving circuit that supplies fluid to a non-driving device of a vehicle.
According to this aspect, when the coolant is circulated only through the non-drive circuit while the vehicle is turned off, the hydraulic pressure in the second space is easily secured, which makes it easier to press the valve body against the support surface, thereby improving the sealing performance between the valve body and the support surface.

According to one aspect of the present disclosure, it is possible to perform circuit switching while reducing the number of components and lowering costs.

FIG. 2 is a block diagram of a cooling system (individual temperature adjustment mode) according to an embodiment. FIG. 2 is a block diagram of a cooling system (integrated mode) according to an embodiment. FIG. 2 is a perspective view of a control valve according to an embodiment. FIG. 2 is an exploded perspective view of the control valve according to the embodiment. 4 is a cross-sectional view corresponding to line VV in FIG. 3. 6 is a cross-sectional view corresponding to line VI-VI in FIG. FIG. 7 is an enlarged view of a portion VII in FIG. 5 . FIG. 4 is a bottom view of the cover according to the embodiment. FIG. 13 is a plan view of the control valve (individual temperature control mode) shown through the cover according to the embodiment. FIG. 13 is a plan view of a control valve (integrated mode) shown through a cover according to an embodiment.

Next, an embodiment of the present disclosure will be described with reference to the drawings. In the embodiments and modified examples described below, the same reference numerals may be used to designate corresponding configurations, and a description thereof may be omitted. In the following description, expressions indicating relative or absolute arrangements, such as "parallel," "orthogonal," "center," and "coaxial," do not only strictly indicate such arrangements, but also indicate a state in which there is a relative displacement with an angle or distance to the extent that a tolerance or the same function is obtained. In this embodiment, "facing" does not only mean a case in which the orthogonal directions (normal directions) of the two surfaces are aligned with each other, but also includes a case in which the orthogonal directions intersect with each other.

[Cooling system 1]
1 and 2 are block diagrams of a cooling system 1. In Fig. 1 and Fig. 2, Fig. 1 shows an individual temperature control mode, and Fig. 2 shows an integrated mode.
1 and 2, the cooling system 1 is mounted on, for example, an electric vehicle. Electric vehicles include electric vehicles, hybrid vehicles, plug-in hybrid vehicles, fuel cell vehicles, and other vehicles that are equipped with a motor as a drive source. The cooling system of this embodiment may be one that has only an engine (internal combustion engine) as a vehicle drive source.

The cooling system 1 includes a drive circuit 2, a non-drive circuit 3, and a control valve 5.

The drive circuit 2 is a circuit to which devices (drive devices) that drive the vehicle are connected, at least when the vehicle is powered on (READY ON). Devices whose operating temperature ranges tend to be relatively high are connected to the drive circuit 2. In the illustrated example, for example, a drive motor (drive source) 7 and a first water pump 8 are provided on the drive circuit 2. The first water pump 8 and the drive motor 7 are connected on the drive circuit 2 in order from the upstream side to the downstream side. An inverter, a radiator, etc. may be connected to the drive circuit 2 as a drive device.

The non-drive circuit 3 is a circuit to which devices (non-drive devices) are connected that are used not only when the vehicle is powered on, but also when the vehicle is powered off (READY OFF). Devices with a lower operating temperature range than the drive devices are connected to the non-drive circuit 3. For example, a battery 10 and a second water pump 11 are provided on the non-drive circuit 3. The second water pump 11 and the battery 10 are connected on the non-drive circuit 3 in order from the upstream side to the downstream side. An air conditioning device (for example, a chiller, heater core, compressor, etc.) may be connected to the non-drive circuit 3 as a non-drive device.

The control valve 5 functions as a so-called four-way valve. The control valve 5 is connected to the upstream end and downstream end of the drive circuit 2 and the upstream end and downstream end of the non-drive circuit 3. The control valve 5 switches the flow of the coolant in the cooling system 1.

The control valve 5 makes the drive circuit 2 and the non-drive circuit 3 separate closed circuits (individual temperature control mode) as shown in FIG. 1, for example, during normal vehicle operation or when the vehicle is powered off. In the individual temperature control mode, the water pumps 8, 11 provided in each circuit 2, 3 are operated to allow coolant to circulate in each of the drive circuit 2 and non-drive circuit 3 via the control valve 5. Normal vehicle operation refers to a state in which the drive device and non-drive device are each operating in their optimal temperature ranges when the vehicle is powered on.

When the drive device and non-drive device are operating outside the optimum temperature range, for example when starting or rapidly cooling the vehicle, the control valve 5 closes the drive circuit 2 and non-drive circuit 3 together as a single closed circuit (integrated mode) as shown in FIG. 2. In the integrated mode, the water pumps 8 and 11 provided in each circuit 2 and 3 are operated to allow coolant to circulate between the drive circuit 2 and non-drive circuit 3 via the control valve 5.

<Control valve 5>
Fig. 3 is a perspective view of the control valve 5. Fig. 4 is an exploded perspective view of the control valve 5.
As shown in FIGS. 3 and 4 , the control valve 5 includes a casing 21 , a drive unit 22 , a rotor 23 , and a biasing member 24 .

<Casing 21>
The casing 21 includes a casing body 31 and a cover 32. In the following description, the direction along the central axis O1 of the rotor 23 is simply referred to as the axial direction. In the axial direction, the drive unit 22 side is referred to as the lower side (first side), and the cover 32 side is referred to as the upper side (second side). A direction intersecting the central axis O1 as viewed from the axial direction is referred to as the radial direction, and a direction around the central axis O1 is referred to as the circumferential direction.

<Casing body 31>
The casing body 31 includes a base portion 33, a first outlet port 34, a second outlet port 35, and a first inlet port 36. The base portion 33, the first outlet port 34, the second outlet port 35, and the first inlet port 36 are integrally formed by, for example, injection molding a resin material.
The base portion 33 is formed in a cylindrical shape with a bottom that opens upward. Specifically, the base portion 33 includes a mounting seat 41 and a rotor accommodating portion 42.

Fig. 5 is a cross-sectional view corresponding to line VV in Fig. 3. Fig. 6 is a cross-sectional view corresponding to line VI-VI in Fig. 3.
5 and 6, the mounting base 41 is a portion to which the drive unit 22 is attached. The mounting base 41 includes a partition wall 41a and a standing wall 41b. The partition wall 41a is formed to a size that protrudes radially outward from the rotor accommodating portion 42 in a plan view seen from the axial direction. The standing wall 41b extends downward from the outer periphery of the partition wall 41a.

FIG. 7 is an enlarged view of a portion VII in FIG.
As shown in FIG. 7, a through hole 45 is formed in the partition wall 41a at a portion located on the central axis O1, penetrating the partition wall 41a in the axial direction. The through hole 45 is formed in a stepped shape. The inner diameter of the through hole 45 located at the axial center is smaller than the inner diameters of the upper end and the lower end. Specifically, the through hole 45 includes a first large diameter portion 45a located at the bottom, a small diameter portion 45b continuing upward from the first large diameter portion 45a, and a second large diameter portion 45c continuing upward from the small diameter portion 45b. In the illustrated example, the inner diameters of the first large diameter portion 45a and the second large diameter portion 45c are equal. A seal ring 46 such as an X-ring is accommodated in the second large diameter portion 45c. The seal ring 46 is fitted into the inner peripheral surface of the second large diameter portion 45c and is in close proximity to or in contact with the bottom surface of the second large diameter portion 45c. The inner diameter of the seal ring 46 is equal to the inner diameter of the small diameter portion 45b.

As shown in Figures 5 and 6, the rotor accommodating section 42 is a portion that accommodates the rotor 23. The rotor accommodating section 42 is formed in a cylindrical shape that extends upward from the partition wall 41a. The lower end opening of the rotor accommodating section 42 is closed by the partition wall 41a. The inner diameter of the rotor accommodating section 42 gradually increases from the bottom to the top. Specifically, the inner peripheral surface of the rotor accommodating section 42 includes a clearance surface 51, a transition surface 52, a support surface 53, and a positioning surface 54.

The clearance surface 51 extends radially outward from a position recessed downward with respect to an upper end opening edge of the through hole 45 (second large diameter portion 45c). The clearance surface 51 is formed into a flat surface perpendicular to the axial direction.
The transition surface 52 extends upward from the outer circumferential edge of the clearance surface 51. The transition surface 52 is a cylindrical surface coaxial with the central axis O1. The transition surface 52 surrounds the entire periphery of the clearance surface 51.

The support surface 53 is continuous around the entire circumference of the upper edge of the transition surface 52. The support surface 53 is a tapered surface that extends radially outward from the bottom to the top. In a cross-sectional view along the axial direction, the support surface 53 extends linearly. In a cross-sectional view along the axial direction, the angle θ1 (taper angle shown in FIG. 6) between radially opposing portions of the support surface 53 is preferably 90°<θ1<180°, and more preferably 110°<θ1<160°. In a cross-sectional view along the axial direction, the support surface 53 is formed symmetrically with respect to the central axis O1.

The positioning surface 54 extends upward from the upper edge of the support surface 53. The positioning surface 54 is a cylindrical surface coaxial with the central axis O1. The positioning surface 54 surrounds the entire periphery of the support surface 53.

As shown in Figures 5 and 6, the rotor accommodating section 42 has a first outlet 53a, a second outlet 53b, and a first inlet 53c that open on the support surface 53. Each outlet 53a, 53b and first inlet 53c opens upward (towards the second axial direction) on the support surface 53. It is preferable that the opening edges (boundary with the support surface 53) of each outlet 53a, 53b and first inlet 53c are formed in a curved shape.

Each outlet 53a, 53b is formed on the same circumference (at the same axial height) at a position that is 180° different in the circumferential direction. Each outlet 53a, 53b faces each other in a first radial direction (opposing direction). The first inlet 53c is disposed at a position that is shifted in the circumferential direction from each outlet 53a, 53b. In the illustrated example, the first inlet 53c is disposed at a position that is shifted in the circumferential direction from each outlet 53a, 53b. However, the positions and sizes of each outlet 53a, 53b and the first inlet 53c can be changed as appropriate. The inner diameters of each outlet 53a, 53b are the same.

As shown in FIG. 5, the first outlet port 34 connects, for example, the upstream end of the drive circuit 2 and the control valve 5 (first outlet 53a). The first outlet port 34 is integrally formed with the base portion 33. When viewed in cross section along the axial direction, the first outlet port 34 is formed in an L-shaped tube. Specifically, the first outlet port 34 has a pull-out portion 34a located on the upstream side and a joint portion 34b connected to the downstream side of the pull-out portion 34a.

The lead-out portion 34a extends downward from the opening edge of the first outlet 53a. The first outlet port 34 communicates with the first outlet 53a through the lead-out portion 34a. The lower end of the lead-out portion 34a is located between the lower surface of the partition wall 41a and the lower edge of the upright wall 41b.
The joint portion 34b extends outward in the first direction from the lower end of the drawn-out portion 34a. The outer end of the joint portion 34b in the first direction protrudes outward beyond the base portion 33. For example, the drive circuit 2 is connected to the outer end of the joint portion 34b.

The second outlet port 35 connects, for example, the upstream end of the non-driving circuit 3 and the control valve 5 (second outlet 53b). The second outlet port 35 is integrally formed with the base portion 33. The second outlet port 35 is formed symmetrically with the first outlet port 34 in the first direction with the central axis O1 as the axis of symmetry. Specifically, the second outlet port 35 has a pull-out portion 35a located on the upstream side and a joint portion 35b connected to the downstream side of the pull-out portion 35a.

The lead-out portion 35a extends downward from the opening edge of the second outlet 53b. The second outlet port 35 communicates with the second outlet 53b through the lead-out portion 35a. The lower end of the lead-out portion 35a is located between the lower surface of the partition wall 41a and the lower edge of the upright wall 41b.
The joint portion 35b extends outward in the first direction from the lower end of the drawn-out portion 35a. The outlet ports 34, 35 are aligned in a straight line in the first direction. The outer end of the joint portion 35b in the first direction protrudes outward beyond the base portion 33. For example, the non-driving circuit 3 is connected to the outer end of the joint portion 35b.

As shown in FIG. 6, the first inflow port 36 connects, for example, the downstream end of the drive circuit 2 and the control valve 5 (first inlet 53c). The first inflow port 36 is integrally formed with the base portion 33. When viewed in cross section along the axial direction, the first inflow port 36 is formed in an L-shaped tube. Specifically, the first inflow port 36 has a pull-out portion 36a located on the downstream side and a joint portion 36b connected to the upstream side of the pull-out portion 36a.

The lead-out portion 36a extends downward from the opening edge of the first inlet 53c. The first inlet port 36 communicates with the first inlet 53c through the lead-out portion 36a. The lower end of the lead-out portion 36a is located between the lower surface of the partition wall 41a and the lower edge of the upright wall 41b.
The joint portion 36b extends from the lower end of the drawn-out portion 36a toward one side in a second direction that is radially intersecting (orthogonal to) the first direction. An outer end of the joint portion 36b in the second direction protrudes outward beyond the base portion 33. For example, the drive circuit 2 is connected to the outer end of the joint portion 36b.

<Cover 32>
4 to 6, the cover 32 closes the upper end opening of the base portion 33 (rotor accommodating portion 42). Specifically, the cover 32 includes an opposing wall 61, a positioning portion 62, a spring support portion 63, and a second inlet port 64. The opposing wall 61, the positioning portion 62, the spring support portion 63, and the second inlet port 64 are integrally formed by, for example, injection molding a resin material.
The opposing wall 61 is formed in a plate shape with its thickness direction in the axial direction. The outer shape of the opposing wall 61 in a plan view is formed to be the same as the outer shape of the rotor accommodating portion 42 in a plan view. The opposing wall 61 is assembled to the rotor accommodating portion 42 in a state where it is superimposed on the upper surface of the rotor accommodating portion 42. As a result, the upper end opening of the base portion 33 is closed by the cover 32. A packing such as an O-ring is interposed between the opposing wall 61 and the base portion 33 (rotor accommodating portion 42).

Fig. 8 is a bottom view of the cover 32. Fig. 9 is a plan view of the control valve 5 (individual temperature adjustment mode) shown through the cover 32.
As shown in Fig. 8 and Fig. 9, a second inlet 65 is formed in the opposing wall 61. The second inlet 65 penetrates the opposing wall 61 in the axial direction and extends in the circumferential direction. In the illustrated example, the inlet 65 is formed in a C-shape in a plan view. Specifically, the second inlet 65 wraps around the other side (the opposite side to the first inlet port 36) with respect to the central axis O1 in the second direction. One end of the inlet 65 in the circumferential direction overlaps with the first outlet 53a in a plan view, and the other end of the inlet 65 in the circumferential direction overlaps with the second outlet 53b in a plan view.

As shown in Figures 5 and 6, the positioning portion 62 protrudes downward from the outer periphery of the opposing wall 61. The positioning portion 62 is formed in a cylindrical shape arranged coaxially with the central axis O1. The positioning portion 62 is inserted inside the rotor accommodating portion 42 when the cover 32 is assembled to the base portion 33. The positioning portion 62 abuts against the positioning surface 54 from the radial inside, thereby radially positioning the cover 32 relative to the base portion 33.

The spring support portion 63 protrudes downward from a portion of the opposing wall 61 that is located radially inward relative to the positioning portion 62. The spring support portion 63 is formed in a cylindrical shape that is arranged coaxially with the central axis O1. In this embodiment, the spring support portions 63 are formed in a stepped shape with an outer diameter that is smaller the lower they are located. Specifically, the spring support portion 63 includes an axial support portion 63a and a radial support portion 63b.

The axial support portion 63a constitutes the upper end portion of the spring support portion 63. The outer diameter of the axial support portion 63a is larger than the inner diameters of the large diameter portions 45a, 45c. The lower end surface of the axial support portion 63a is formed into a flat surface perpendicular to the axial direction.
The radial support portion 63b protrudes downward from the spring support portion 63. The outer diameter of the radial support portion 63b is smaller than the large diameter portions 45a and 45c and larger than the inner diameter of the small diameter portion 45b. Therefore, the radial support portion 63b faces the seal ring 46 in the axial direction. The inner diameter of the spring support portion 63 is uniformly formed over the entire axial support portion 63a and the radial support portion 63b. In the illustrated example, the inner diameter of the spring support portion 63 is equal to the inner diameter of the small diameter portion 45b.

5, 6 and 8, the second inlet port 64 connects the downstream end of the non-driving circuit 3 to the control valve 5 (second inlet 65). The second inlet port 64 includes a branch flow path 71 and a common flow path 72.
The branch flow passage 71 covers the inlet 65 from above and is formed in a dome shape that bulges upward relative to the opposing wall 61. The branch flow passage 71 (each of the branch portions 71a, 71b) is formed in a semicircular shape in a cross-sectional view perpendicular to the extension direction of the branch flow passage 71.

In the illustrated example, the branch flow passage 71 has the same external shape as the inlet 65 in a plan view and is formed in a C-shape extending in the circumferential direction. Specifically, the branch flow passage 71 has a first branch portion 71a extending to one side from the circumferential center of the branch flow passage 71, and a second branch portion 71b extending to the other side from the circumferential center of the branch flow passage 71. The branch flow passage 71 is connected to the inlet 65 over the entire length of the branch flow passage 71 in the extension direction (circumferential direction). The opening area of the lower end opening of the branch flow passage 71 is equal to the opening area of the inlet 65.

The common flow path 72 and the branch flow paths 71 are located on the same plane perpendicular to the central axis O1. Specifically, the common flow path 72 protrudes from the center of the branch flow paths 71 in the extension direction (circumferential direction) toward the other side in the second direction. In a plan view, the second inlet port 64 (common flow path 72) is aligned in a straight line at a position facing the first inlet port 36 (joint portion 36b) in the second direction. In this case, the inlet ports 36, 64 and the outlet ports 34, 35 extend in directions perpendicular to each other. The base end of the common flow path 72 is connected to the branch flow path 71. The tip of the common flow path 72 is connected to the non-driving circuit 3. The tip of the common flow path 72 protrudes outward in the second direction relative to the opposing wall 61. The cooling liquid that flows into the common flow path 72 from the downstream end of the non-drive circuit 3 is distributed to the first branch 71a and the second branch 71b at the tip of the common flow path 72.

The extension direction of the common flow passage 72 is perpendicular to the extension direction of the outlet ports 34, 35 ( joint portions 34b, 35b). The common flow passage 72 is formed in a circular shape in a cross-sectional view perpendicular to the second direction. The amount of upward expansion of the common flow passage 72 relative to the opposing wall 61 is greater than the amount of upward expansion of the branch flow passages 71 relative to the opposing wall 61. Therefore, the upper edge of the common flow passage 72 constitutes the uppermost edge of the control valve 5.

Here, the flow path cross-sectional areas (areas perpendicular to the extension direction of each) of the first branch portion 71a and the second branch portion 71b are uniformly formed over the entire circumferential length. It is preferable that the sum of the flow path cross-sectional areas of the first branch portion 71a and the second branch portion 71b is equal to or greater than the flow path cross-sectional area (area perpendicular to the extension direction) of the common flow path 72. However, the sum of the flow path cross-sectional areas of the first branch portion 71a and the second branch portion 71b may be smaller than the flow path cross-sectional area of the common flow path 72.

<Drive unit 22>
As shown in Fig. 4, the drive unit 22 is configured to house a motor, a reduction mechanism, a control board, etc. (not shown). The drive unit 22 is disposed below the mounting base 41. The drive unit 22 is assembled to the upright wall 41b in a state where it is overlapped with the mounting base 41 in the axial direction. As shown in Fig. 7, the drive unit 22 includes an output shaft 22a that protrudes upward. The output shaft 22a is formed in a cylindrical shape that is disposed coaxially with the central axis O1.

<Rotor 23>
4 and 5, the rotor 23 switches between communication and blocking between the inlets 53c, 65 and the outlets 53a, 53b by rotating inside the casing 21. Specifically, the rotor 23 includes a shaft portion 80 and a valve body 81. The rotor 23 is integrally formed by, for example, injection molding a resin material.

As shown in FIG. 7, the shaft portion 80 is disposed coaxially with the central axis O1. The shaft portion 80 passes through the through hole 45 in the axial direction. Specifically, the shaft portion 80 includes a connecting portion 80a that constitutes the lower end of the shaft portion 80, and a transmission portion 80b that is connected to the upper portion of the connecting portion 80a.

The connecting portion 80a is formed in a solid shape. The lower portion of the connecting portion 80a is fitted inside the output shaft 22a. In this embodiment, the connecting portion 80a is connected to the output shaft 22a with a male spline formed on the outer peripheral surface of the connecting portion 80a meshing with a female spline formed on the inner peripheral surface of the output shaft 22a in the circumferential direction. This allows the connecting portion 80a to rotate around the central axis O1 as the output shaft 22a rotates. The upper portion of the connecting portion 80a is disposed inside the first large diameter portion 45a. A hollow portion 80a1 recessed upward is formed on the lower end surface of the connecting portion 80a. The connecting portion 80a may be formed in a hollow shape.

The transmission part 80b is formed in a bottomed cylindrical (hollow) shape coaxial with the central axis O1. The inside of the transmission part 80b defines a recess 84 that opens upward. The transmission part 80b includes a connection part 85 and a peripheral wall part 86.
The connecting portion 85 is formed in a disk shape larger than the outer shape of the coupling portion 80a in a plan view. The connecting portion 85 is connected to the upper end surface of the coupling portion 80a while projecting radially outward from the outer circumferential surface of the coupling portion 80a. The connecting portion 85 is disposed inside the small diameter portion 45b. A lightening portion 85a recessed downward is formed on the upper end surface of the connecting portion 85. The lightening portion 85a is connected to the recess 84 on the upper end surface of the connecting portion 85. The lightening portion 85a reaches the coupling portion 80a.

The peripheral wall portion 86 extends upward from the outer periphery of the connecting portion 85. The peripheral wall portion 86 is formed in a multi-stage cylindrical shape in which the outer diameter gradually increases in the upward direction. Specifically, the peripheral wall portion 86 includes a small cylindrical portion 86a, a protruding portion 86b, and a large cylindrical portion 86c.
The small cylinder portion 86a is formed in a cylindrical shape with an outer diameter equal to that of the connecting portion 85. The small cylinder portion 86a is disposed inside the second large diameter portion 45c. The inner peripheral surface of the seal ring 46 is in close contact with the outer peripheral surface of the small cylinder portion 86a. This blocks communication between the inside and outside of the casing 21 through the through hole 45.

The protruding portion 86b protrudes radially outward from the upper end opening edge of the small cylinder portion 86a. The protruding portion 86b faces the second large diameter portion 45c in the axial direction with at least a portion of the protruding portion 86b protruding into the rotor accommodating portion 42. This prevents the seal ring 46 from coming off through the upper end opening of the second large diameter portion 45c. The outer diameter of the protruding portion 86b is equal to or smaller than the inner diameter of the second large diameter portion 45c.
The large cylinder portion 86c is formed in a cylindrical shape extending upward from the outer circumferential edge of the protruding portion 86b. The large cylinder portion 86c faces the radial support portion 63b in the axial direction.

As shown in Figures 5 and 6, the valve body 81 is formed in a truncated cone shape that opens upward. The valve body 81 is provided in the rotor accommodating portion 42 so as to be rotatable about the central axis O1 as the shaft portion 80 rotates. Specifically, the valve body 81 includes a valve bottom wall 91, a sliding wall 92, and a partition portion 93. The space of the valve body 81 that is surrounded by the valve bottom wall 91 and the sliding wall 92 constitutes the internal space K of the valve body 81. The internal space K is open upward. Therefore, the inlet 65 is constantly connected to the internal space K. Meanwhile, the internal space K is connected to the recess 84 at the lower end.

The valve bottom wall 91 protrudes radially outward from the lower end of the large cylinder portion 86c. Therefore, the large cylinder portion 86c protrudes upward from the valve bottom wall 91 toward the internal space K of the valve body 81. The valve bottom wall 91 faces the relief surface 51 with a gap in the axial direction. In the illustrated example, the lower surface of the valve bottom wall 91 is located below the upper end of the transition surface 52. The upper surface of the valve bottom wall 91 is located above the upper end of the transition surface 52.

The sliding wall 92 is connected to the outer peripheral edge of the valve bottom wall 91. The sliding wall 92 is formed in a tapered cylindrical shape that gradually expands in diameter as it goes upward. The upper end opening of the sliding wall 92 faces the opposing wall 61. The spring support portion 63 enters the internal space K through the upper end opening of the sliding wall 92. In the illustrated example, the entire radial support portion 63b and the lower end of the axial support portion 63a of the spring support portion 63 enter the internal space K. At least a portion of the spring support portion 63 may enter the internal space K, or may be located above the internal space K.

In a cross-sectional view along the axial direction, the sliding wall 92 has a uniform thickness over the entire vertical range, and extends linearly radially outward as it goes upward. The outer peripheral surface of the sliding wall 92 extends following the support surface 53. Therefore, in a cross-sectional view along the axial direction, the angle θ2 (taper angle shown in FIG. 6) between the radially opposing portions of the outer peripheral surface of the sliding wall 92 is equal to the taper angle θ1 of the support surface 53. The angle θ2 is preferably 90°<θ2<180°, and more preferably 110°<θ2<160°. The outer peripheral surface of the sliding wall 92 slides on the support surface 53 as the valve body 81 rotates. The support surface 53 rotatably supports the valve body 81 via the sliding wall 92. The upper edge of the sliding wall 92 is close to the positioning surface 54 from the radially inner side.

The sliding wall 92 is formed with a first communication port 92a and a second communication port 92b that penetrate the sliding wall 92 in the axial direction. The first communication port 92a and the second communication port 92b are arranged at intervals in the circumferential direction. Each communication port 92a, 92b is formed in an arc shape that extends circumferentially around the valve bottom wall 91.

The partition portion 93 blocks communication between the first communication port 92a and the second communication port 92b in the internal space K. The partition portion 93 surrounds the first communication port 92a from the side and above on one radial side of the sliding wall 92 relative to the shaft portion 80. The partition portion 93 is formed in an L-shape in cross section. Specifically, the partition portion 93 includes a side wall portion 93a and a top wall portion 93b.

The side wall portion 93a extends upward from the opening edge of the first communication port 92a. The side wall portion 93a surrounds the entire periphery of the first communication port 92a. The lower edge of the side wall portion 93a extends upward along the inner surface of the sliding wall 92 and radially outward.
The top wall portion 93b closes the upper end opening edge of the side wall portion 93a. The top wall portion 93b and the opposing wall 61 face each other with a gap therebetween in the axial direction. The side wall portion 93a may be formed only on a radially inner portion and on both circumferential sides of the opening edge of the first communication port 92a.

A space surrounded by the partition portion 93 (a space positioned radially outward from the partition portion 93) of the internal space K constitutes a first space K1. The first space K1 is open downward through the first communication port 92a.
The space surrounded by the partition 93 and the sliding wall 92 (the space located radially inward from the partition 93) of the internal space K constitutes a second space K2. The second space K2 is open downward through the second communication port 92b and upward through the upper end opening of the valve body 81. In this embodiment, the volume of the second space K2 is larger than the volume of the first space K1.

FIG. 9 is a plan view of the control valve 5 in the first state, with the cover 32 shown through.
9, the rotor 23 rotates between a first state and a second state in response to the driving force of the drive unit 22. The first state is a state in which the first inlet 53c and the first outlet 53a at least partially communicate with each other through the first space K1, and the second inlet 65 and the second outlet 53b at least partially communicate with each other through the second space K2.

In the first state, the first communication port 92a is disposed across the first inlet 53c and the first outlet 53a in the circumferential direction, so that the first inlet 53c and the first outlet 53a communicate with the first space K1 through the first communication port 92a.
In the first state, the second communication port 92b overlaps with the second outlet port 53b in a plan view, thereby communicating the second outlet port 53b with the second space K2. The second inlet port 65 is constantly in communication with the second space K2 through the upper end opening of the valve body 81. When the communication ports 92a, 92b do not overlap with any of the outlet ports 53a, 53b, the communication between the internal space K and the outlet ports 53a, 53b is blocked by the valve body 81 (sliding wall 92).

FIG. 10 is a plan view of the control valve 5 in the second state, showing the cover 32 through the cover 32. FIG.
As shown in FIG. 10, the second state is a state in which the first inlet 53c and the second outlet 53b communicate with each other through the first space K1, and the second inlet 65 and the first outlet 53a communicate with each other through the second space K2.

In the second state, the first communication port 92a is arranged across the first inlet 53c and the second outlet 53b in the circumferential direction. As a result, the first inlet 53c and the second outlet 53b are connected to the first space K1 through the first communication port 92a. The first communication port 92a may be provided in multiple numbers as long as it is configured to connect the first inlet 53c and the first outlet 53a to the first space K1 in the first state and to connect the first inlet 53c and the second outlet 53b to the first space K1 in the second state. The multiple first communication ports 92a may be configured to individually connect to the first inlet 53c and the first outlet 53a in the first state and individually connect to the first inlet 53c and the second outlet 53b in the second state.

In the second state, the second communication port 92b overlaps with the first outlet 53a in a plan view, thereby communicating the first outlet 53a with the second space K2. The second inlet 65 is constantly in communication with the second space K2 through the upper end opening of the valve body 81. The position and shape of the second communication port 92b can be changed as appropriate, so long as it is configured to communicate with the second outlet 53b in the first state and to communicate with the first outlet 53a in the second state.

<Using member 24>
The biasing member 24 is, for example, a flat coil spring. The biasing member 24 is sandwiched between the valve bottom wall 91 and the axial support portion 63a in a state where it is disposed coaxially with the central axis O1. The biasing member 24 is entirely located in the internal space K (second space K2). The biasing member 24 is provided inside the rotor 23. It is sufficient that the biasing member 24 is provided at least inside the rotor 23.

The biasing member 24 biases the valve body 81 downward. The sliding wall 92 is pressed against the support surface 53 by the biasing force of the biasing member 24. The radial support portion 63b is inserted into the inside of the upper end portion of the biasing member 24. The biasing member 24 abuts against the radial support portion 63b from the radial direction, thereby restricting radial movement of the biasing member 24 relative to the casing 21. The large cylinder portion 86c is inserted into the inside of the lower end portion of the biasing member 24. The biasing member 24 abuts against the large cylinder portion 86c from the radial direction, thereby restricting radial movement of the biasing member 24 relative to the casing 21. In this embodiment, a configuration in which the biasing member 24 is indirectly supported by the opposing wall 61 via the spring support portion 63 is described, but this configuration is not limited to this. The biasing member 24 may be directly supported by the opposing wall 61.

[Operation method of control valve 5]
Next, a description will be given of a method for operating the control valve 5. In the following description, the individual temperature control mode and the integrated mode will be described.
In order to circulate the coolant in each of the drive circuit 2 and the non-drive circuit 3 as in the individual temperature control mode shown in Fig. 1, the rotor 23 is set to the first state shown in Fig. 9. In the first state, the coolant pumped out by the first water pump 8 on the drive circuit 2 is heat exchanged in the drive motor 7, and then flows into the first space K1 through the first inlet 53c and the first communication port 92a. The coolant that has flowed into the first space K1 is returned to the drive circuit 2 through the first communication port 92a and the first outlet 53a, and then is pumped out again downstream on the drive circuit 2 by the first water pump 8.

　In the non-driving circuit 3, the cooling liquid pumped out by the second water pump 10 is heat exchanged in the battery 11, and then flows into the second space K2 through the second inlet 65 and the upper end opening of the valve body 81. The cooling liquid that flows into the second space K2 is returned to the non-driving circuit 3 through the second communication port 92b and the second outlet 53b, and is then pumped out again downstream on the non-driving circuit 3 by the second water pump 10. In the individual temperature control mode, the cooling liquid that flows into the internal space K through the first inlet 53c and the second inlet 65 is deflected by the partition 93 so that it does not merge with each other and flows out from the corresponding outlets 53a, 53b. In the individual temperature control mode, only one of the driving circuit 2 and the non-driving circuit 3 (the first water pump 8 and the second water pump 10) may be operated.

To switch from the individual temperature control mode to the integrated mode, the rotor 23 is switched from the first state to the second state shown in FIG. 10. Specifically, the drive unit 22 is driven to rotate the rotor 23 around the central axis O1. At this time, the rotor 23 rotates around the central axis O1 while the outer circumferential surface of the sliding wall 92 slides on the support surface 53. Then, when the first inlet 53c and the second outlet 53b are connected through the first space K1 and the second inlet 65 and the first outlet 53a are connected through the second space K2, the rotation of the rotor 23 stops.

In the integrated mode, the coolant flows between the drive circuit 2 and the non-drive circuit 3 in a lump via the control valve 5. Specifically, on the drive circuit 2, the coolant pumped out by the first water pump 8 is heat exchanged in the drive motor 7, and then flows into the first space K1 through the first inlet 53c and the first communication port 92a. The coolant that flows into the first space K1 flows out to the non-drive circuit 3 through the first communication port 92a and the second outlet 53b. The coolant that flows out to the non-drive circuit 3 is pumped downstream by the second water pump 10, and is heat exchanged with the battery 11. The coolant then flows into the second space K2 through the second inlet 65 and the upper end opening of the valve body 81. The coolant that flows into the second space K2 flows out to the drive circuit 2 through the second communication port 92b and the first outlet 53a. The cooling liquid is then pumped downstream by the first water pump 8, where heat is exchanged between the cooling liquid and the drive motor 7. The cooling liquid then flows back into the first space K1.

As described above, in the control valve 5 of this embodiment, the rotor 23 has a valve body 81 whose outer diameter gradually increases upward from the shaft portion 80, and the outer peripheral surface of the valve body 81 is slidably supported by the casing 21.
According to this configuration, there is no need to provide a separate seal member or bearing because the valve element 81 is directly supported by the casing 21. This reduces the number of parts and assembly steps, and allows the control valve 5 to be made smaller and less expensive.
Since the valve body 81 is formed in a tapered shape, when the outer diameter of the rotor 23 expands or contracts due to heat, the rotor 23 displaces in the axial direction on the support surface 53 in response to the increase or decrease in the outer diameter. Therefore, the valve body 81 is stably supported on the support surface 53 regardless of the expansion or contraction of the rotor 23. This ensures the operational stability of the control valve 5.

In particular, in the control valve 5 of this embodiment, the rotor 23 is configured to rotate between a first state and a second state. The first state is a state in which the first inlet 53c and the first outlet 53a communicate with each other through the first space K1, and the second inlet 65 and the second outlet 53b communicate with each other through the second space K2. The second state is a state in which the first inlet 53c and the second outlet 53b communicate with each other through the first space K1, and the second inlet 65 and the first outlet 53a communicate with each other through the second space K2.
According to this configuration, by installing the control valve 5 between the two circuits, the circuits can be switched between an individual temperature control mode in which the coolant flows through each of the two circuits independently, and an integrated mode in which the coolant flows through the two circuits together. Moreover, in this embodiment, the first space K1 opens downward, while the second space K2 opens upward, making it easy to keep the liquid pressure in each space K1, K2 uniform. Therefore, while ensuring the sealing between the valve body 81 and the support surface 53, it is possible to suppress excessive sliding resistance and realize smooth rotation of the rotor 23.

In the control valve 5 of this embodiment, the first outlet 53a and the second outlet 53b are arranged in positions facing each other in the first direction, and the first inlet 53c and the second inlet 65 are arranged in positions facing each other in the second direction.
According to this configuration, the outlets 53a, 53b and the inlets 53c, 65 are arranged in different radial directions, which facilitates the layout of the piping.

In the control valve 5 of this embodiment, the volume of the second space K2 is larger than the volume of the first space K1.
According to this configuration, it is easy to ensure the hydraulic pressure acting on the second space K2. Therefore, it is easy to press the valve body 81 against the support surface 53, so that the sealing performance between the valve body 81 and the support surface 53 can be improved.

In the control valve 5 of this embodiment, the valve body 81 is configured to extend linearly radially outward from the bottom to the top in a cross-sectional view along the axial direction.
For example, when the cross-sectional shape of the valve body 81 is formed in an arc shape, the direction of the tangential direction of the outer circumferential surface of the valve body 81 differs depending on the axial position. In this case, when the valve body 81 shrinks due to heat, the deformation behavior differs depending on the axial position of the valve body 81. Specifically, the amount of radially inward deformation increases toward the upper side of the valve body 81 (as the inclination of the tangent increases), making it difficult to ensure sealing between the support surface 53 and the valve body 81.
In contrast, by forming the valve body 81 to have a linear cross-sectional shape as in this embodiment, it is easy to keep the deformation behavior of the valve body 81 due to thermal contraction uniform throughout the entire axial direction. As a result, the valve body 81 is stably supported on the support surface 53 regardless of the expansion and contraction changes of the rotor 23. This ensures the operational stability of the control valve 5.

In the control valve 5 of this embodiment, the valve body 81 is configured such that the angle θ2 between the radially opposing portions is set to 90°<θ2<180°.
According to this configuration, by making the angle θ2 larger than 90°, when the outer diameter of the rotor 23 expands or contracts due to heat, the rotor 23 can be more smoothly displaced on the support surface 53 in response to the increase or decrease in the outer diameter. Therefore, regardless of the expansion or contraction of the rotor 23, the valve body 81 is stably supported on the support surface 53. This ensures the operational stability of the control valve 5.
Moreover, by setting the angle θ2 in the range of 110°<θ2<160°, excess material during molding can be suppressed, enabling further size reduction in the axial direction.

In the control valve 5 of this embodiment, the second inlet 65 and the second outlet 53b are configured to be connected to the non-driving circuit 3 that supplies fluid to a non-driving source of the vehicle.
According to this configuration, when the coolant is circulated only through the non-drive circuit 3 while the vehicle is turned off, it is easy to ensure the hydraulic pressure in the second space K2. Therefore, it is easy to press the valve body 81 against the support surface 53, so that the sealing performance between the valve body 81 and the support surface 53 can be improved.

(Other Modifications)
Although the preferred embodiments of the present disclosure have been described above, the present disclosure is not limited to these embodiments. Addition, omission, substitution, and other modifications of the configuration are possible without departing from the spirit of the present disclosure. The present disclosure is not limited by the above description, but is limited only by the scope of the attached claims.
For example, in the above embodiment, the control valve 5 is mounted on the vehicle cooling system 1, but the present invention is not limited to this configuration and may be mounted on other systems.
In the above embodiment, the configuration including the two outlets 53a, 53b has been described, but the present invention is not limited to this configuration. Three or more outlets may be provided.
In the above embodiment, the outflow ports 34, 35 are integrally formed with the base portion 33, but the present invention is not limited to this configuration. The outflow ports 34, 35 may be formed separately from the base portion 33.

In the above embodiment, the second inlet 65 is constantly in communication with the internal space K. However, the present invention is not limited to this configuration. The second inlet 65 may also be configured to be switched between communication with and cut off from the internal space K in response to the rotation of the rotor 23.
In the above embodiment, the valve body 81 extends linearly in cross section, but is not limited to this configuration. The valve body 81 may extend in an arc shape in cross section, for example.

In the above embodiment, the biasing member 24 is provided in the internal space K, but the present invention is not limited to this configuration. The position of the biasing member can be changed as appropriate as long as the biasing member is configured to press the valve body 81 against the support surface 53. The biasing member is not an essential component.
In the above embodiment, the second inlet 65 is formed in the cover 32, but the present invention is not limited to this configuration. The second inlet may be formed in the casing body 31.

In the above embodiment, a configuration in which the volume of the second space K2 is larger than the volume of the first space K1 has been described, but this is not limited to this configuration. The volume of the second space K2 may be equal to or smaller than the volume of the first space K1.

In addition, the components in the above-described embodiments may be replaced with well-known components as appropriate without departing from the spirit of this disclosure, and the above-described modified examples may be combined as appropriate.

3: Non-driving circuit 5: Control valve 21: Casing 23: Rotor 53: Support surface 53a: First outlet 53b: Second outlet 53c: First inlet 65: Second inlet 80: Shaft 81: Valve body 92a: First communication port 92b: Second communication port 93: Partition K1: First space K2: Second space O1: Central axis θ2: Angle

Claims (6)

1. a casing having a first inlet and a second inlet through which a fluid flows in from the outside and a first outlet and a second outlet through which the fluid flows out to the outside;
   a rotor having a shaft portion located on a first axial side and rotatably supported by the casing, and a valve body that forms an internal space whose outer diameter gradually increases from the shaft portion toward a second axial side, the outer peripheral surface of the valve body being supported slidably on a support surface formed on the casing,
   a first communication port and a second communication port that communicate between the inside and the outside of the internal space are formed in the valve body at different positions around a central axis of the rotor,
   the valve body includes a partition portion that divides the internal space into a first space that communicates with the first communication port and opens to a first side in the axial direction and a second space that communicates with the second communication port and opens to a second side in the axial direction,
   The rotor is a control valve that rotates between a first state in which the first inlet and the first outlet are connected through the first space and the second inlet and the second outlet are connected through the second space, and a second state in which the first inlet and the second outlet are connected through the first space and the second inlet and the first outlet are connected through the second space.
2. The first outlet and the second outlet are disposed at positions facing each other in a first direction in a radial direction intersecting the axial direction,
   The control valve according to claim 1 , wherein the first inlet and the second inlet are disposed at positions facing each other in a second direction intersecting the first direction when viewed from the axial direction.
3. The control valve according to claim 1 or 2, wherein the volume of the second space is greater than the volume of the first space.
4. The control valve according to claim 1 or claim 2, wherein the valve body extends linearly from a first side to a second side in the axial direction toward the outside in a radial direction intersecting the axial direction in a cross-sectional view along the axial direction.
5. The control valve according to claim 1 or 2, wherein the valve body has an angle between opposing radial portions intersecting the axial direction that is greater than 90° and less than 180° in a cross-sectional view along the axial direction.
6. The control valve according to claim 1 or 2, wherein the second inlet and the second outlet are connected to a non-driving circuit that supplies fluid to a non-driving device of a vehicle.

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