Valve device

Abstract

This valve device comprises a valve member, a housing, a biasing body, and a first seal. The valve member includes a shaft part that is rotatable about a rotation axis, and a rotor that is connected to the shaft part and that has a first flow path having a first opening in the outer peripheral surface. The housing is formed with an accommodating portion that accommodates the valve member, and a second flow path having a second opening that communicates with the first opening in the inner peripheral surface of the accommodating portion. The biasing body biases the rotor in a first direction. The first seal is placed between the outer surface of the rotor and the inner surface of the accommodating portion. The rotor is pressed against the first seal by the biasing body in a state in which the surface of the rotor facing the first direction does not come into contact with the inner surface of the accommodating portion.

Description

[Technical Field]

[0001] The present invention relates to a valve device for controlling a liquid. [Background technology]

[0002] Valve devices that switch fluid flow paths have been proposed. For example, Patent Document 1 discloses a switching valve that includes a rotatable shaft, a valve element connected to one end of the shaft, and a main body that houses the valve element. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2013-92176 Summary of the Invention [Problem to be solved by the invention]

[0004] In the configuration of Patent Document 1, the underside of the valve disc is always in contact with the base of the main body. In this configuration, the distance between the conical surface that forms the outer circumferential surface of the valve disc and the conical surface that forms the inner circumferential surface of the main body depends on the dimensional error of the valve disc or the main body. Therefore, there is a problem in that the surface pressure (contact pressure) acting on the seal between the outer circumferential surface of the valve disc and the inner circumferential surface of the main body is affected by the dimensional error of the valve disc or the main body. In consideration of the above circumstances, one aspect of the present invention aims to apply an appropriate surface pressure to the seal member regardless of the dimensional error of the valve member or the housing. [Means for solving the problem]

[0005] A valve device according to one aspect of the present invention is a valve device for controlling a coolant for an automobile, and comprises: a valve member including a shaft portion rotatable around a rotation axis, and a rotor connected to the shaft portion and having a first flow path formed on its outer peripheral surface with a first opening; a housing having a storage portion for accommodating the valve member and a second flow path having a second opening on the inner peripheral surface of the storage portion that can communicate with the first opening; a biasing body for biasing the rotor in a first direction; and a first seal installed between the outer surface of the rotor and the inner surface of the storage portion, wherein the rotor is pressed against the first seal by the biasing body while the surface of the rotor facing the first direction is not in contact with the inner surface of the storage portion. [Effects of the Invention]

[0006] According to the present invention, it is possible to apply an appropriate surface pressure to the seal member regardless of dimensional errors in the valve member or the housing. [Brief explanation of the drawings]

[0007] [Figure 1] 1 is a cross-sectional view illustrating the configuration of a valve device according to a first embodiment. [Figure 2] FIG. 2 is a side view of the first seal. [Figure 3] FIG. 10 is a cross-sectional view illustrating the configuration of a valve device in Comparative Example 2. [Figure 4] FIG. 6 is a cross-sectional view illustrating the configuration of a valve device according to a second embodiment. [Figure 5] FIG. 10 is a side view of the first seal in the second embodiment. [Figure 6] FIG. 10 is a cross-sectional view illustrating the configuration of a valve device according to a third embodiment. [Figure 7] FIG. 10 is a cross-sectional view illustrating the configuration of a valve device according to a fourth embodiment. [Figure 8] FIG. 10 is a cross-sectional view illustrating the configuration of a valve device according to a fifth embodiment. [Figure 9] FIG. 13 is a cross-sectional view illustrating the configuration of a valve device according to a modified example of the fifth embodiment. [Figure 10]FIG. 10 is a cross-sectional view illustrating the configuration of a valve device according to a sixth embodiment. [Figure 11] FIG. 10 is a cross-sectional view illustrating the configuration of a valve device according to a sixth embodiment. [Figure 12] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 13] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 14] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 15] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 16] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 17] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 18] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. [Figure 19] 10A and 10B are cross-sectional views illustrating the configuration of a valve device according to a modified example. DETAILED DESCRIPTION OF THE INVENTION

[0008] A: First embodiment 1 is a cross-sectional view illustrating the configuration of a valve device 100 according to a first embodiment of the present invention. The valve device 100 is a switching valve that controls a flow path through which a liquid flows. Specifically, the valve device 100 is installed in an automobile as a multi-control valve that controls a coolant (e.g., cooling water) for the automobile, for example.

[0009] 1, the valve device 100 includes a valve member B, a housing 30, a first seal 40, a second seal 50, and a spring 61. The valve member B is a rotary valve that switches the flow path of the coolant by rotating about a rotation axis C. The housing 30 is a structure that accommodates and supports the valve member B. The first seal 40 and the second seal 50 are elastic bodies installed between the valve member B and the housing 30.

[0010] In the following description, one direction along the rotation axis C will be referred to as the "first direction Z1," and the direction opposite to the first direction Z1 will be referred to as the "second direction Z2." For example, the first direction Z1 is the downward vertical direction, and the second direction Z2 is the upward vertical direction. Furthermore, the direction of the circumference of an imaginary circle of any diameter centered on the rotation axis C will be referred to as the "circumferential direction," and the direction of the radius of the imaginary circle will be referred to as the "radial direction."

[0011] The valve member B comprises a shaft portion 10 and a rotor 20. The shaft portion 10 and the rotor 20 are integrally formed, for example, from various resin materials. The shaft portion 10 is a cylindrical portion that can rotate around a rotation axis C. The rotation axis C corresponds to the central axis of the shaft portion 10. The end of the shaft portion 10 facing the first direction Z1 is connected to the rotor 20. The end of the shaft portion 10 facing the second direction Z2 is connected directly or indirectly to a motor (not shown). The shaft portion 10 rotates around the rotation axis C in conjunction with the operation of the motor. Note that the shaft portion 10, which is configured separately from the rotor 20, may be fixed to the rotor 20.

[0012] The rotor 20 is a rotating body that can rotate together with the shaft portion 10 around the rotation axis C. The outer surface U of the rotor 20 includes a first surface F1, a second surface F2, and an outer peripheral surface Qb. The first surface F1 and the second surface F2 are circular planes perpendicular to the rotation axis C. The first surface F1 is a lower surface facing the first direction Z1, and the second surface F2 is an upper surface facing the second direction Z2. The shaft portion 10 protrudes from the center of the second surface F2 in the second direction Z2. The first surface F1 is an example of a "surface of the rotor facing the first direction."

[0013] The outer peripheral surface Qb of the rotor 20 includes a cylindrical surface 21 and a conical surface 22. The conical surface 22 is located in the first direction Z1 relative to the cylindrical surface 21 and is continuous with the first surface F1. The cylindrical surface 21 is located in the second direction Z2 relative to the conical surface 22 and is continuous with the second surface F2. The conical surface 22 is a tapered surface of revolution whose diameter increases in the second direction Z2. That is, the outer diameter Da1 at the end Ea1 of the conical surface 22 in the first direction Z1 is smaller than the outer diameter Da2 at the end Ea2 of the conical surface 22 in the second direction Z2 (Da1 <Da2)。

[0014] The rotor 20 is formed with a first flow passage 23 and a vertical flow passage 24. The first flow passage 23 is a flow passage extending in a direction (e.g., a radial direction) perpendicular to the rotation axis C. The first flow passage 23 has a first opening O1. The first opening O1 is a circular opening formed in the outer peripheral surface Qb of the rotor 20. Specifically, the first opening O1 is formed in a conical surface 22. A plurality of first openings O1 are formed at intervals from one another in the circumferential direction. Note that, in the following description, for convenience, attention will be focused on one first opening O1 among the plurality of first openings O1. The vertical flow passage 24 is a flow passage extending from the first flow passage 23 in the first direction Z1. Specifically, the vertical flow passage 24 extends along the rotation axis C from the inner wall surface of the first flow passage 23 to the first surface F1, passing through the rotor 20.

[0015] Furthermore, a communication passage 25 is formed in the rotor 20. The communication passage 25 is a passage that extends along the rotation axis C, passing through the rotor 20 from the inner wall surface of the first passage 23 to the second surface F2. That is, the first passage 23 inside the rotor 20 and the space outside the rotor 20 are in communication with each other via the communication passage 25.

[0016] The housing 30 is formed with a storage portion R. The storage portion R is a space that stores the valve member B. The inner surface H of the storage portion R in the housing 30 includes a cylindrical surface 31, a third surface F3, an inner circumferential surface Ha, and a fourth surface F4. The cylindrical surface 31 is a rotation surface that faces the outer circumferential surface Qa of the shaft portion 10 at a distance. The third surface F3 is an annular flat surface that is perpendicular to the rotation axis C and faces the second surface F2 of the rotor 20 at a distance.

[0017] The spring 61 is an elastic body that biases the valve member B (rotor 20) in the first direction Z1. The spring 61 is installed between the second surface F2 and the third surface F3. Specifically, the spring 61 is a coil spring that is installed so as to surround the shaft portion 10. The spring 61 is an example of a "biasing body."

[0018] The inner peripheral surface Ha includes a cylindrical surface 32 and a conical surface 33. The third surface F3 connects the cylindrical surface 31 and the cylindrical surface 32. The cylindrical surface 32 is a rotating surface that faces the outer peripheral surface Q (Qa, Qb) of the valve member B with a gap therebetween. The cylindrical surface 32 connects the third surface F3 and the conical surface 33.

[0019] The conical surface 33 is a tapered rotating surface that expands in diameter in the second direction Z2. That is, the outer diameter Db1 at the end Eb1 in the first direction Z1 of the conical surface 33 is smaller than the outer diameter Db2 at the end Eb2 in the second direction Z2 of the conical surface 22 (Db1 < Db2). The conical surface 33 faces the conical surface 22 of the rotor 20 with a predetermined gap therebetween. That is, the angles of the conical surface 22 and the conical surface 33 with respect to the rotation axis C are equal. The conical surface 33 connects the cylindrical surface 32 and the fourth surface F4. The fourth surface F4 is a circular plane orthogonal to the rotation axis C and faces the first surface F1 of the rotor 20 with a gap therebetween. That is, the fourth surface F4 is the bottom surface facing in the second direction Z2 in the housing portion R.

[0020] A second flow path 34 and a third flow path 35 are formed in the housing 30. The second flow path 34 is a flow path extending in a direction orthogonal to the rotation axis C (that is, the radial direction). The second flow path 34 has a second opening O2. The second opening O2 is a circular opening formed in the inner peripheral surface Ha of the housing portion R. Specifically, the second opening O2 is formed in the conical surface 33 of the housing portion R. A plurality of second openings O2 are formed at intervals in the circumferential direction. In the following description, one of the plurality of second openings O2 is arbitrarily focused on for convenience. The third flow path 35 is a flow path extending from the housing portion R in the first direction Z1.

[0021] In a state where the valve member B is at a predetermined rotation angle centered on the rotation axis C (hereinafter referred to as "communication state"), one first opening O1 and one second opening O2 overlap each other in the radial direction. Specifically, in the communication state, the first flow path 23 and the second flow path 34 are linearly connected. That is, the first opening O1 and the second opening O2 can communicate with each other.

[0022] The first seal 40 is an elastic body disposed between the outer surface U of the rotor 20 and the inner surface H of the housing portion R. Specifically, the first seal 40 is disposed between the outer peripheral surface Qb of the rotor 20 and the inner peripheral surface Ha of the housing portion R. The first seal 40 seals the gap between the outer peripheral surface Qb and the inner peripheral surface Ha and elastically supports the rotor 20. Examples of materials for the first seal 40 include various rubber materials such as chloroprene rubber (CR) or polyurethane rubber (PUR).

[0023] 2 is a side view of the first seal 40. As illustrated in FIG. 2, the first seal 40 includes a first portion 41, a second portion 42, and a plurality of connecting portions 43. The first portion 41 and the second portion 42 are annular portions. The outer diameter of the first portion 41 is smaller than the outer diameter of the second portion 42. The plurality of connecting portions 43 connect the first portion 41 and the second portion 42 to each other. The plurality of connecting portions 43 are arranged at intervals from each other along the circumferential direction of the first portion 41 and the second portion 42.

[0024] 1, a protrusion 45 is formed on the inner circumferential surface of the first seal 40. Specifically, a protrusion 45 extending in the circumferential direction is formed on the inner circumferential surface of each of the first portion 41 and the second portion 42, and a protrusion 45 extending along the connecting portion 43 is formed on the inner circumferential surface of each of the connecting portions 43. The inner circumferential surface of the first seal 40 may be coated with a low-friction material such as PTFE (polytetrafluoroethylene) resin. The entire first seal 40 may be formed from a low-friction material such as PTFE resin.

[0025] 1 , a groove 36 extending in the circumferential direction is formed in the conical surface 33 of the housing 30. The first seal 40 is installed in the groove 36 of the conical surface 33. That is, the outer circumferential surface of the first seal 40 contacts the conical surface 33 of the housing 30. On the other hand, the inner circumferential surface of the first seal 40 contacts the conical surface 22 of the rotor 20. Specifically, the protrusion 45 on the inner circumferential surface of the first seal 40 contacts the conical surface 22. As described above, the first seal 40 is installed between the conical surface 22 of the rotor 20 and the conical surface 33 of the housing 30.

[0026] The valve member B is biased in the first direction Z1 by the spring 61, so that the rotor 20 is pressed against the first seal 40. Therefore, it is possible to maintain a sufficient surface pressure (contact pressure) between the first seal 40 and the rotor 20. For example, the characteristics of the spring 61, such as the elastic coefficient, are set so that the surface pressure between the outer peripheral surface Qb of the rotor 20 and the first seal 40 exceeds the pressure of the coolant in the accommodation portion R.

[0027] The first seal 40 is fixed to the housing 30. On the other hand, the rotor 20 rotates with its outer peripheral surface Qb (conical surface 22) in contact with the inner peripheral surface of the first seal 40. In other words, the outer peripheral surface Qb of the rotor 20 slides against the inner peripheral surface of the first seal 40.

[0028] 1 , the first portion 41 of the first seal 40 is located in the first direction Z1 relative to the first opening O1 and the second opening O2. That is, the position of the first portion 41 on the rotation axis C is located further in the first direction Z1 than the positions of the first opening O1 and the second opening O2 on the rotation axis C. On the other hand, the second portion 42 is located in the second direction Z2 relative to the first opening O1 and the second opening O2. That is, the position of the second portion 42 on the rotation axis C is located further in the second direction Z2 than the positions of the first opening O1 and the second opening O2 on the rotation axis C. As can be understood from the above description, a plurality of first openings O1 and a plurality of second openings O2 are located between the first portion 41 and the second portion 42 of the first seal 40 in a side view along the radial direction.

[0029] The second seal 50 is disposed between the outer peripheral surface Qa of the shaft portion 10 and the inner peripheral surface Ha (specifically, the cylindrical surface 31) of the housing R, and seals the gap between the outer peripheral surface Qa and the inner peripheral surface Ha. The second seal 50 is located in the second direction Z2 with respect to the second portion 42 of the first seal 40. That is, the position of the second seal 50 on the rotation axis C is located further in the second direction Z2 than the position of the second portion 42 on the rotation axis C. In a side view along the radial direction, the second portion 42 is located between the first portion 41 and the second seal 50.

[0030] In the above configuration, for example, the coolant is supplied from the second flow path 34 to the first flow path 23 via one of the multiple second openings O2 that is in communication with the first opening O1 in accordance with the rotation angle of the valve member B, and the coolant is discharged from the first flow path 23 to the outside via the vertical flow path 24 and the third flow path 35. Furthermore, for example, the coolant supplied to the first flow path 23 from the third flow path 35 via the vertical flow path 24 is discharged from the first flow path 23 to the second flow path 34 via one of the multiple second openings O2 that is in communication with the first opening O1 in accordance with the rotation angle of the valve member B. As described above, the coolant is controlled in accordance with the angle of the valve member B.

[0031] 1, there is no direct contact between the outer surface U (F1, F2, Qb) of the rotor 20 and the inner surface H of the housing 30. Therefore, the rotor 20 is pressed against the first seal 40 by the spring 61 in a state where the first surface F1 is not in contact with the fourth surface F4 of the accommodating portion R. In other words, the pressing force acting on the rotor 20 from the spring 61 does not act directly from the rotor 20 to the housing 30, but is received by the first seal 40.

[0032] In a configuration in which the first surface F1 of the rotor 20 and the fourth surface F4 of the housing 30 contact each other (hereinafter referred to as "Comparative Example 1"), the distance between the conical surface 22 of the rotor 20 and the conical surface 33 of the housing 30 (hereinafter referred to as the "sealing gap") depends on the dimensional error of the valve member B or the housing 30. For example, when the dimension of the rotor 20 along the rotation axis C is smaller than the design value, the sealing gap exceeds the design value. Conversely, when the dimension of the rotor 20 along the rotation axis C exceeds the design value, the sealing gap falls below the design value. Therefore, there is a problem in that the surface pressure (contact pressure) acting on the first seal 40 from the conical surface 22 of the rotor 20 and the conical surface 33 of the housing 30 is affected by the dimensional error of the valve member B or the housing 30. For example, in a configuration designed so that an appropriate surface pressure acts on the first seal 40 when the sealing gap is at the maximum dimension within the tolerance, the surface pressure will be excessive when the sealing gap is at the minimum dimension within the tolerance. On the other hand, in a configuration designed so that an appropriate surface pressure acts on the first seal 40 when the sealing gap is at the minimum dimension within the tolerance, the surface pressure is insufficient when the sealing gap is at the maximum dimension.

[0033] In contrast to Comparative Example 1, in the first embodiment, the rotor 20 is pressed against the first seal 40 by the spring 61 in a state in which the first surface F1 of the rotor 20 is not in contact with the fourth surface F4 of the housing R. That is, the rotor 20 is urged in the first direction Z1 by the spring 61 without the first surface F1 hitting the fourth surface F4. Therefore, it is possible to apply an appropriate surface pressure to the first seal 40 regardless of dimensional errors of the valve member B or the housing 30. That is, the surface pressure acting on the first seal 40 can be determined according to the mechanical characteristics (e.g., elastic coefficient) of the spring 61.

[0034] In the configuration of Comparative Example 1, if a design is adopted in which an appropriate surface pressure acts on the first seal 40 when the sealing gap is the maximum dimension within the tolerance, excessive surface pressure will act on the first seal 40 when the sealing gap is the minimum dimension within the tolerance. That is, the sliding resistance of the rotor 20 will become excessive. In this state, excessive torque is required to rotate the rotor 20. In the first embodiment, as described above, an appropriate surface pressure acts on the first seal 40 regardless of the dimensional error of the sealing gap. That is, the possibility of excessive surface pressure acting on the first seal 40 is reduced, and as a result, the sliding resistance of the rotor 20 can be kept within an appropriate range. This also has the advantage of reducing the torque required to rotate the rotor 20.

[0035] Furthermore, in the first embodiment, the first seal 40 includes a first portion 41 and a second portion 42 that are located at different positions on the rotation axis C. Therefore, compared to a configuration in which the first seal 40 is configured with only one of the first portion 41 and the second portion 42, it is possible to stably maintain the attitude of the rotor 20.

[0036] 1 is a space surrounded by the outer peripheral surface Q (Qa, Qb) of the valve member B, the inner surface H of the housing portion R, the second portion 42 of the first seal 40, and the second seal 50. In other words, the space S is the space between the second portion 42 and the second seal 50 in the space between the outer peripheral surface Q and the inner surface H. The aforementioned communicating passage 25 is a flow passage that connects the space S and the first flow passage 23. In other words, the space S is connected to the first flow passage 23 via the communicating passage 25.

[0037] FIG. 3 illustrates a configuration (hereinafter referred to as "Comparative Example 2") in which the communication passage 25 is not formed. In Comparative Example 2, the space S is sealed. However, from a design perspective in which reducing the torque required to rotate the rotor 20 takes priority over sealing performance, slight leakage of the coolant through the first seal 40 may be tolerated. Furthermore, in the switching valve, the coolant that leaks through the first seal 40 flows into another flow path when the flow path is switched by the switching valve, resulting in circulating, so slight leakage of the coolant is not a particular problem. Given the above circumstances, as illustrated by the dashed arrows in FIG. 3, the coolant flowing through the first flow path 23 and the second flow path 34 may leak into the space S from between the second portion 42 of the first seal 40 and the outer peripheral surface Qb of the rotor 20. Because the space S is sealed, the coolant entering the space S increases the pressure within the space S. In other words, pressure buildup occurs in the space S. As pressure accumulation progresses, excessive pressure acts on the first seal 40 or the second seal 50, which may result in problems such as deformation. Furthermore, the rotor 20 is pressed downward due to pressure accumulation in the space S, and the first seal 40 may be pressed excessively by the rotor 20. When the first seal 40 is pressed excessively by the rotor 20, the sliding resistance between the rotor 20 and the first seal 40 may increase.

[0038] In contrast to Comparative Example 2, in the first embodiment, the space S and the first flow path 23 are connected to each other by the communication path 25. Therefore, an increase in pressure due to leakage of coolant into the space S does not occur. That is, according to the first embodiment, pressure accumulation in the space S can be suppressed compared to Comparative Example 2. Therefore, deformation of the first seal 40 or the second seal 50 and an increase in sliding resistance due to pressure accumulation in the space S are suppressed. In particular, in the first embodiment, the communication path 25 is formed to extend along the rotation axis C from the second surface F2 of the rotor 20 to the first flow path 23. Therefore, there is an advantage that the communication path 25 is easier to form than, for example, a configuration in which the communication path 25 is bent within the rotor 20.

[0039] In the first embodiment, the first area S1 of the first region on the surface of the rotor 20 of the valve member B, on which pressure in the first direction Z1 from the coolant in the housing R acts, is greater than the second area S2 of the second region on which pressure in the second direction Z2 from the coolant acts (S1>S2). The first region is, for example, a region including the second surface F2. The first region includes not only a plane perpendicular to the rotation axis C (e.g., the second surface F2) but also an inclined surface on which the component of the coolant pressure in the first direction Z1 acts. The second region is, for example, a region including the first surface F1. The second region includes not only a plane perpendicular to the rotation axis C (e.g., the first surface F1) but also an inclined surface on which the component of the coolant pressure in the second direction Z2 acts.

[0040] Assume that an equal pressure acts on the entire surface of the rotor 20. Because the first area S1 exceeds the second area S2, the pressing force from the coolant acting on the first area in the first direction Z1 exceeds the pressing force from the coolant acting on the second area in the second direction Z2. That is, a resultant force equivalent to the difference between the pressing force in the first direction Z1 and the pressing force in the second direction Z2 acts to urge the valve member B in the first direction Z1. Therefore, the elastic force of the spring 61 required to adequately urge the valve member B in the first direction Z1 is reduced. That is, the spring 61 urging the valve member B in the first direction Z1 is smaller than in a configuration in which the first area S1 and the second area S2 are equal. Note that if the difference between the first area S1 and the second area S2 is sufficient to urge the valve member B in the first direction Z1, the spring 61 may be omitted. As described above, the spring 61 that biases the valve member B in the first direction Z1 is eliminated or made smaller, which makes it possible to reduce the size of the valve device 100. That is, according to the first embodiment, it is possible to reduce the constraints on size reduction that are caused by the configuration for biasing the valve member B (for example, the spring 61).

[0041] In particular, in the first embodiment, the first seal 40 contacts the conical surface 22 of the rotor 20. In the above configuration, the difference between the first area S1 and the second area S2 urges the valve member B in the first direction Z1, thereby pressing the rotor 20 against the first seal 40. This makes it easy to ensure the surface pressure between the outer peripheral surface Qb of the rotor 20 and the first seal 40. In other words, according to the first embodiment, the cooling liquid sealing performance of the first seal 40 can be maintained at a high level.

[0042] B: Second embodiment A second embodiment of the present disclosure will be described. Note that, in the following exemplary embodiments, for elements whose functions are similar to those of the first embodiment, the reference numerals used in the description of the first embodiment will be used, and detailed descriptions of each element will be omitted as appropriate.

[0043] FIG. 4 is a cross-sectional view illustrating the configuration of a valve device 100 according to a second embodiment. Similar to the first embodiment, the valve device 100 according to the second embodiment is installed in an automobile as a multi-control valve that controls a coolant (e.g., cooling water) for the automobile. As illustrated in FIG. 4, similar to the first embodiment, the valve device 100 includes a valve member B, a housing 30, a first seal 40, and a second seal 50. In the valve device 100 according to the second embodiment, the configuration of the rotor 20 in the valve member B differs from that of the first embodiment.

[0044] The rotor 20 of the second embodiment is a rotating body having an outer surface U. The outer surface U includes a first surface F1, a second surface F2, and an outer peripheral surface Qb. As in the first embodiment, the first surface F1 is a lower surface facing in the first direction Z1, and the second surface F2 is an upper surface facing in the second direction Z2. The shaft portion 10 protrudes in the second direction Z2 from the center of the second surface F2.

[0045] The outer peripheral surface Qb of the rotor 20 includes a conical surface 26 and a cylindrical surface 27. The conical surface 26 is located in the second direction Z2 relative to the cylindrical surface 27 and is continuous with the second surface F2. The conical surface 26 is a tapered surface of revolution whose diameter increases in the first direction Z1. That is, the outer diameter Da1 of the conical surface 26 at an end Ea1 in the first direction Z1 is greater than the outer diameter Da2 of the conical surface 26 at an end Ea2 in the second direction Z2 (Da1>Da2). The cylindrical surface 27 is located in the first direction Z1 relative to the conical surface 26 and is continuous with the first surface F1.

[0046] Similar to the first embodiment, the rotor 20 of the second embodiment is formed with a first flow passage 23 and a vertical flow passage 24. The first flow passage 23 has a first opening O1 formed in the outer peripheral surface Qb of the rotor 20. The vertical flow passage 24 is a flow passage extending from the first flow passage 23 in a first direction Z1. Specifically, the vertical flow passage 24 extends along the rotation axis C, passing through the rotor 20 from the inner wall surface of the first flow passage 23 to the first surface F1.

[0047] The accommodation portion R of the housing 30 in the second embodiment has an inner surface H. The inner surface H includes a cylindrical surface 31, a third surface F3, an inner circumferential surface Ha, and a fourth surface F4. The cylindrical surface 31 and the third surface F3 are the same as those in the first embodiment. The inner circumferential surface Ha includes a conical surface 37 and a cylindrical surface 38. The third surface F3 connects the cylindrical surface 31 and the conical surface 37.

[0048] The conical surface 37 is a tapered surface of revolution whose diameter increases in the first direction Z1. That is, the outer diameter Db1 of the conical surface 37 at an end Eb1 in the first direction Z1 is greater than the outer diameter Db2 of the conical surface 37 at an end Eb2 in the second direction Z2 (Db1>Db2). The conical surface 37 faces the conical surface 26 of the rotor 20 at a predetermined distance. That is, the angle of the conical surface 26 with respect to the rotation axis C is equal to the angle of the conical surface 37. The conical surface 37 connects the third surface F3 and the cylindrical surface 38.

[0049] The cylindrical surface 38 is a rotation surface that faces, with a gap therebetween, the outer peripheral surface Qb of the rotor 20. The cylindrical surface 38 connects the conical surface 37 and the fourth surface F4. The fourth surface F4 is a circular flat surface that is perpendicular to the rotation axis C and faces, with a gap therebetween, the first surface F1 of the rotor 20.

[0050] As in the first embodiment, the housing 30 of the second embodiment is formed with a second flow path 34 and a third flow path 35. The second flow path 34 has a second opening O2 formed in the inner circumferential surface Ha of the accommodation portion R. Specifically, the second opening O2 is formed in the conical surface 37 of the accommodation portion R. In a communication state in which the valve member B is at a predetermined rotation angle around the rotation axis C, one first opening O1 and one second opening O2 overlap each other in the radial direction. That is, as in the first embodiment, in the second embodiment, the first opening O1 and the second opening O2 can communicate with each other. The third flow path 35 is a flow path extending from the accommodation portion R in the first direction Z1.

[0051] The first seal 40 is an elastic body disposed between the outer peripheral surface Qb of the rotor 20 and the inner peripheral surface Ha of the housing portion R. FIG. 5 is a side view of the first seal 40. As illustrated in FIG. 5, the first seal 40 includes a first portion 41, a second portion 42, and a plurality of connecting portions 43, similar to the first embodiment. As in the first embodiment, a protrusion 45 is formed on the inner peripheral surface of the first seal 40. In the first embodiment, the outer diameter of the first portion 41 is smaller than the outer diameter of the second portion 42, whereas in the second embodiment, the outer diameter of the first portion 41 is larger than the outer diameter of the second portion 42.

[0052] The first seal 40 is installed in a groove 36 formed in the conical surface 37 of the housing 30. That is, the outer peripheral surface of the first seal 40 contacts the conical surface 37 of the housing 30. On the other hand, the inner peripheral surface of the first seal 40 contacts the conical surface 26 of the rotor 20. Specifically, a protrusion 45 on the inner peripheral surface of the first seal 40 contacts the conical surface 26. As in the first embodiment, the first seal 40 is fixed to the housing 30, and the outer peripheral surface Qb of the rotor 20 slides against the inner peripheral surface of the first seal 40.

[0053] As in the first embodiment, the second seal 50 is disposed between the outer peripheral surface Qa of the shaft portion 10 and the inner peripheral surface Ha (specifically, the cylindrical surface 31) of the housing R, and seals the gap between the outer peripheral surface Qa and the inner peripheral surface Ha. The second seal 50 is positioned in the second direction Z2 with respect to the second portion 42 of the first seal 40. That is, the second portion 42 is positioned between the first portion 41 and the second seal 50 in a side view along the radial direction.

[0054] As in the first embodiment, a communicating passage 25 is formed in the rotor 20 of the second embodiment. The communicating passage 25 is a flow path that extends along the rotation axis C, passing through the rotor 20 from the inner wall surface of the first flow passage 23 to the second surface F2. In other words, the first flow passage 23 and a space S outside the rotor 20 communicate with each other via the communicating passage 25. As in the first embodiment, the space S is the space between the second portion 42 of the first seal 40 and the second seal 50 in the space between the outer peripheral surface Qb and the inner peripheral surface Ha.

[0055] As described above, in the second embodiment, since the space S and the first flow path 23 communicate with each other through the communication path 25, an increase in pressure due to leakage of the coolant into the space S does not occur. That is, also in the second embodiment, similar to the first embodiment, the accumulation of pressure in the space S can be suppressed as compared with the comparative example 2 in FIG. 3.

[0056] In the second embodiment, of the surface of the rotor 20 of the valve member B, the first area S1 of the first region where the pressure in the first direction Z1 acts from the coolant in the housing portion R is less than the second area S2 of the second region where the pressure in the second direction Z2 acts from the coolant (S1 < S2). Therefore, assuming that the same pressure acts on the entire surface of the rotor 20, the pressing force in the first direction Z1 acting on the first region from the coolant is less than the pressing force in the second direction Z2 acting on the second region from the coolant. That is, a resultant force corresponding to the difference between the pressing force in the first direction Z1 and the pressing force in the second direction Z2 acts to bias the valve member B in the second direction Z2. Therefore, in the second embodiment, a configuration such as a spring for biasing the valve member B in the second direction Z2 can be omitted. That is, also in the second embodiment, similar to the first embodiment, the miniaturization constraints due to the configuration for biasing the valve member B can be reduced. However, if the biasing in the second direction Z2 is insufficient only by the difference in the pressing forces, a spring for biasing the rotor 20 in the second direction Z2 may be provided (see FIG. 7).

[0057] Particularly in the second embodiment, the first seal 40 contacts the conical surface 26 of the rotor 20. In the above configuration, due to the difference between the first area S1 and the second area S2, the valve member B is biased in the second direction Z2, and thus the rotor 20 is pressed against the first seal 40. Therefore, it is easy to ensure the surface pressure between the outer peripheral surface Qb of the rotor 20 and the first seal 40. That is, according to the first embodiment, the sealing performance of the coolant by the first seal 40 can be maintained at a high level.

[0058] C: Third Embodiment 6 is a cross-sectional view illustrating the configuration of a valve device 100 according to a third embodiment. The valve device 100 according to the third embodiment has a configuration in which a spring 62 is added to the valve device 100 according to the second embodiment. The spring 62 is an elastic body disposed between the second surface F2 and the third surface F3, similar to the spring 61 according to the first embodiment. The spring 62 is a coil spring disposed so as to surround the shaft portion 10, and biases the valve member B in the first direction Z1.

[0059] In the second embodiment, it is assumed that the valve member B is excessively biased in the second direction Z2 due to the configuration in which the first area S1 is smaller than the second area S2. In this state, the rotor 20 is excessively pressed against the first seal 40. In the third embodiment, the valve member B is biased in the first direction Z1 by the spring 62. That is, the spring 62 acts to push back, in the first direction Z1, the bias in the second direction Z2 due to the configuration in which the first area S1 is smaller than the second area S2. Therefore, it is possible to reduce the possibility that the rotor 20 will be excessively pressed against the first seal 40. That is, according to the third embodiment, the surface pressure between the first seal 40 and the rotor 20 can be adjusted within an appropriate range.

[0060] D: Fourth embodiment FIG. 7 is a cross-sectional view illustrating the configuration of a valve device 100 according to a fourth embodiment. The valve device 100 according to the fourth embodiment has a configuration in which a spring 63 is added to the valve device 100 according to the second embodiment. The spring 63 is an elastic body that biases the valve member B (rotor 20) in the second direction Z2. The spring 63 is installed between the first surface F1 and the fourth surface F4. The spring 63 is an example of a "biasing body."

[0061] In the fourth embodiment, the outer surface U (F1, F2, Qb) of the rotor 20 and the inner surface H of the housing 30 do not come into direct contact with each other. Therefore, the rotor 20 is pressed against the first seal 40 by the spring 63 without the second surface F2 coming into contact with the third surface F3. In other words, the pressing force acting on the rotor 20 from the spring 63 does not act directly from the rotor 20 to the housing 30, but is received by the first seal 40. Therefore, similar to the first embodiment, it is possible to apply an appropriate surface pressure to the first seal 40 regardless of dimensional errors in the valve member B or the housing 30.

[0062] E: Fifth embodiment 8 is a cross-sectional view illustrating the configuration of a valve device 100 according to a fifth embodiment. In the first embodiment, a configuration in which a communication passage 25 that communicates between the space S and the first flow path 23 is formed in the rotor 20 is exemplified. In the fifth embodiment, a communication passage 28 that functions in the same manner as the communication passage 25 is formed in the housing 30. The configuration other than the communication passage 28 is the same as that of the first embodiment.

[0063] 8, the housing 30 of the fifth embodiment has a communication passage 28 that communicates the space S with the second flow passage 34. The communication passage 28 is a flow passage from the inner surface H of the storage portion R (specifically, the cylindrical surface 32) to the inner wall surface of the second flow passage 34.

[0064] In the fifth embodiment, the space S and the second flow path 34 are connected to each other by the connecting passage 28. Therefore, no increase in pressure occurs due to leakage of the coolant into the space S. That is, according to the fifth embodiment, similar to the first embodiment, pressure accumulation in the space S can be suppressed compared to Comparative Example 2 in FIG.

[0065] 8 is based on the first embodiment including a rotor 20 whose diameter increases in the second direction Z2, but the second embodiment including a rotor 20 whose diameter increases in the first direction Z1 also employs a configuration similar to that of the fifth embodiment. Specifically, as illustrated in Fig. 9, in the configuration of the second embodiment, a communication passage 28 that communicates the space S with the second flow path 34 may be formed in the housing 30. Also, the spring 62 of the third embodiment may be added to the configuration of Fig. 9.

[0066] F: Sixth embodiment 10 and 11 are cross-sectional views illustrating the configuration of a valve device 100 according to a sixth embodiment. In the valve device 100 according to the sixth embodiment, the rotor 20 (valve member B) is movable in the directions (Z1, Z2) of the rotation axis C. Specifically, the rotor 20 according to the sixth embodiment is movable along the rotation axis C between a first position shown in FIG. 10 and a second position shown in FIG. 11. The second position is a position in the second direction Z2 relative to the first position. In other words, the second position is a position higher than the first position. The first position corresponds to the lower end of the range in which the rotor 20 can move, and the second position corresponds to the upper end of that range.

[0067] As illustrated in Figures 10 and 11, the housing 30 of the sixth embodiment includes a protrusion 71 in addition to the same elements as in the first embodiment. The protrusion 71 is a portion that protrudes from the fourth face F4 in the second direction Z2. The protrusion 71 is formed integrally with the fourth face F4. However, the protrusion 71 formed separately from the housing 30 may be fixed to the fourth face F4. Furthermore, a recess 72 is formed in the first face F1 (lower face) of the rotor 20 in the sixth embodiment. The recess 72 is a depression formed in a shape and dimensions that can accommodate the protrusion 71.

[0068] When the rotor 20 is in the first position (hereinafter referred to as the "first state"), as illustrated in FIG. 10, the protrusion 71 is located inside the recess 72 as viewed in the direction of the rotation axis C. In the first state, the top surface of the protrusion 71 does not contact the bottom surface of the recess 72. That is, in the first state, as in the first embodiment, the outer surface U of the rotor 20 does not contact the inner surface H of the housing 30. The inner surface H of the housing 30 includes the surface (e.g., the top surface) of the protrusion 71. That is, in the first state, the first surface F1 does not contact either the fourth surface F or the top surface of the protrusion 71. Therefore, as in the first embodiment, the rotor 20 is pressed against the first seal 40 by the spring 61 in a state in which the first surface F1 does not contact the fourth surface F4 of the accommodating portion R. That is, the pressing force acting on the rotor 20 from the spring 61 does not act directly from the rotor 20 to the housing 30, but is received by the first seal 40.

[0069] When the rotor 20 is moved from the first position in the second direction Z2 and rotated a predetermined angle about the rotation axis C, the first surface F1 of the rotor 20 comes into contact with the top surface of the protrusion 71, as illustrated in FIG. 11 . The rotor 20 is biased in the first direction Z1 by the spring 61, but the contact of the first surface F1 with the top surface of the protrusion 71 prevents the rotor 20 from moving in the first direction Z1. As described above, the rotor 20 is positioned in a state where the outer surface U (first surface F1) of the rotor 20 comes into contact with the inner surface H (top surface of the protrusion 71) of the housing 30. That is, when the rotor 20 is in the second position (hereinafter referred to as the "second state"), the first surface F1 of the rotor 20 comes into contact with the top surface of the protrusion 71.

[0070] In the second state, the gap (sealing gap) between the conical surface 22 of the rotor 20 and the conical surface 33 of the housing 30 is enlarged compared to the first state. The enlarged sealing gap separates the conical surface 22 from the first seal 40. Therefore, the surface pressure acting on the first seal 40 from the rotor 20 and the housing 30 is lower than the surface pressure in the first state. That is, the sliding resistance of the rotor 20 is reduced compared to the first state. Therefore, in the second state, the torque required to rotate the rotor 20 is reduced compared to the first state. As can be understood from the above explanation, the second position corresponds to a temporary or transitional position for switching the flow path by rotating the rotor 20. Note that in the second state, the conical surface 22 of the rotor 20 may be maintained in contact with the first seal 40.

[0071] The sixth embodiment also achieves the same effects as the first embodiment. For example, in the first state, the rotor 20 is pressed against the first seal 40 by the spring 61 while the first surface F1 of the rotor 20 is not in contact with the fourth surface F4 of the housing R. Therefore, it is possible to apply an appropriate surface pressure to the first seal 40 regardless of dimensional errors in the valve member B or the housing 30. Furthermore, in the sixth embodiment, the rotor 20 is held in the second position by the first surface F1 contacting the top surface of the protrusion 71, so the torque required to rotate the rotor 20 can be reduced.

[0072] As can be understood from the example of the sixth embodiment, in the present invention, it is not necessary for the first surface F1 and the fourth surface F4 to be constantly out of contact with each other. Specifically, it is sufficient that the first surface F1 and the fourth surface F4 are not in contact with each other in a state where the surface pressure acting on the first seal 40 from the rotor 20 should be maintained within a predetermined range (i.e., during sealing), and the first surface F1 and the fourth surface F4 may be in contact with each other in other states.

[0073] G: Variation Specific modified embodiments that can be added to each of the embodiments exemplified above are exemplified below. Two or more embodiments arbitrarily selected from the following examples may be appropriately combined within the scope of not being mutually contradictory.

[0074] (1) In the above-described embodiments, the second seal 50 is disposed between the outer peripheral surface Qa of the shaft portion 10 and the inner surface H (cylindrical surface 31) of the housing portion R. However, the location where the second seal 50 is disposed is not limited to the above examples. For example, as illustrated in FIG. 12, the second seal 50 may be disposed between the outer peripheral surface Qb of the rotor 20 and the inner peripheral surface Ha (cylindrical surface 32) of the housing portion R. In the configuration of FIG. 14, the space S is a space surrounded by the outer peripheral surface Qb (cylindrical surface 27) of the rotor 20, the inner peripheral surface Ha (cylindrical surface 32) of the housing portion R, the first seal 40 (second portion 42), and the second seal 50. Therefore, the communication passage 25 is formed from the outer peripheral surface Qb (cylindrical surface 27) of the rotor 20 to the inner wall surface of the first flow path 23. Note that while FIG. 14 illustrates an embodiment that is a modification of the first embodiment, a similar configuration is also adopted in the second to sixth embodiments.

[0075] (2) In the above-described embodiments, the vertical flow passage 24 of the rotor 20 and the third flow passage 35 of the housing 30 are constantly in communication with each other. However, a configuration in which communication between the vertical flow passage 24 and the third flow passage 35 is switched by rotation of the valve member B is also envisioned. For example, as illustrated in FIG. 13 , the vertical flow passage 24 and the third flow passage 35 are formed at positions spaced apart radially from the rotation axis C. In the configuration of FIG. 13 , a third seal 39 surrounding the third flow passage 35 is provided on the fourth surface F4 of the housing 30. The third seal 39 is provided between the first surface F1 of the rotor 20 and the fourth surface F4 of the housing 30. In the above configuration, when the vertical flow passage 24 is located inside the third seal 39, the vertical flow passage 24 and the third flow passage 35 are in communication with each other. On the other hand, when the vertical flow passage 24 is located outside the third seal 39, the vertical flow passage 24 and the third flow passage 35 are blocked from each other. That is, depending on the rotation angle of the valve member B, the vertical flow path 24 and the third flow path 35 are switched between communication and blockage.

[0076] (3) In the third embodiment (FIG. 6), the valve member B is biased in the first direction Z1 by the spring 62 to counteract the bias in the second direction Z2 caused by the configuration in which the first area S1 is smaller than the second area S2. A similar configuration is also adopted in the first embodiment. In the first embodiment, the valve member B is biased in the first direction Z1 by the configuration in which the first area S1 exceeds the second area S2. Therefore, as illustrated in FIG. 14, a spring 64 is provided to bias the valve member B in the second direction Z2. The spring 64 is an elastic body disposed between the first surface F1 of the rotor 20 and the fourth surface F4 of the housing 30. The configuration of FIG. 14 reduces the possibility of the rotor 20 being excessively pressed against the first seal 40. In other words, the surface pressure between the first seal 40 and the rotor 20 can be adjusted within an appropriate range.

[0077] (4) As illustrated in FIG. 15 , a pressure regulating valve 80 may be installed in the communication passage 25. The pressure regulating valve 80 is a valve mechanism for adjusting the pressure difference between two adjacent flow passages that are sandwiched between the pressure regulating valve 80. As described above, the communication passage 25 connects the first flow passage 23 and the space S. Therefore, the pressure regulating valve 80 adjusts the pressure difference between the first flow passage 23 and the space S. For example, the characteristics of the pressure regulating valve 80 are set in advance so that the pressure difference between the first flow passage 23 and the space S is maintained at a target value.

[0078] 15, as described in the first embodiment, the first area S1 of the first region on the surface of the rotor 20, on which pressure from the coolant acts in the first direction Z1, is greater than the second area S2 of the second region on which pressure from the coolant acts in the second direction Z2 (S1>S2). Therefore, the pressing force from the coolant acting on the first region in the first direction Z1 is greater than the pressing force from the coolant acting on the second region in the second direction Z2. By adjusting the pressure difference between the first flow path 23 and the space S using the pressure adjustment valve 80, the relationship between the pressing force acting on the first region and the pressing force acting on the second region can be adjusted. Therefore, the biasing force acting on the valve member B due to the difference between the first area S1 and the second area S2 can be adjusted by the pressure adjustment valve 80.

[0079] In the above description, the pressure adjustment valve 80 maintains the pressure difference between the first flow path 23 and the space S at a target value. However, a control device 81 illustrated in FIG. 15 may dynamically control the characteristics of the pressure adjustment valve 80 (e.g., the pressure difference between the first flow path 23 and the space S). For example, the control device 81 dynamically controls the pressure adjustment valve 80 in accordance with the pressure in the first flow path 23 or the space S. With the above configuration, even if the pressure in the first flow path 23 or the space S changes over time, the pressure adjustment valve 80 can adjust the pressure difference between the first flow path 23 and the space S so that a target biasing force corresponding to the difference between the first area S1 and the second area S2 acts on the valve member B. The pressure in the first flow path 23 or the space S is measured by a pressure sensor installed in the accommodation section R, for example.

[0080] 15 illustrates an example in which a pressure regulating valve 80 is added to the first embodiment, but a similar configuration is also adopted in the second to sixth embodiments. For example, in the fifth embodiment (FIGS. 8 and 9), a pressure regulating valve 80 is installed in the communication passage 28 formed in the housing 30. The pressure regulating valve 80 adjusts the pressure difference between the second flow path 34 and the space S.

[0081] (5) A configuration is envisioned in which the biasing force of the spring 61 that biases the rotor 20 can be adjusted. Fig. 16 illustrates an example in which the movable part 30a is installed in the housing 30. The movable part 30a is a cylindrical member with a threaded groove formed on its outer circumferential surface, and is inserted into the cylindrical surface 31 of the housing 30. A second seal 50 is installed between the inner circumferential surface of the movable part 30a and the outer circumferential surface Qa of the shaft part 10.

[0082] A thread groove that meshes with the thread groove on the outer peripheral surface of the movable part 30a is formed on the cylindrical surface 31 of the housing 30. By rotating the movable part 30a around the rotation axis C, the movable part 30a moves in the direction of the rotation axis C. As illustrated in FIG. 16 , a spring 61 is installed between the lower surface of the movable part 30a and the second surface F2 of the rotor 20. Therefore, by moving the movable part 30a along the rotation axis C, the overall length of the spring 61 changes. In other words, by moving the movable part 30a, the biasing force acting from the spring 61 on the rotor 20 can be adjusted.

[0083] A control device 82 illustrated in FIG. 16 may move the movable part 30a in the direction of the rotation axis C. For example, the control device 82 moves the movable part 30a in accordance with the state of the valve device 100. The state of the valve device 100 may be, for example, the surface pressure acting on the first seal 40 from the rotor 20 or the housing 30, the pressure in the accommodation part R, or the biasing force acting on the rotor 20 from the spring 61. The state of the valve device 100 is measured, for example, by various sensors installed in the accommodation part R. With the above configuration, even if the state of the valve device 100 changes over time, the valve device 100 can be maintained in an appropriate state by adjusting the biasing force of the spring 61 by moving the movable part 30a. For example, if the surface pressure of the first seal 40 decreases due to aging, the surface pressure on the first seal 40 can be restored by moving the movable part 30a in the first direction Z1.

[0084] In the above description, a configuration in which the movable part 30a is moved has been exemplified, but any configuration can be used to adjust the biasing force acting from the spring 61 to the rotor 20, and is not limited to the above example. In the above description, the biasing force of the spring 61 has been adjusted, but any of the springs (62, 63, 64) exemplified in the above-described embodiments can also be adjusted using a similar configuration.

[0085] (6) In the above-described embodiments, a coil spring is used as the spring 61, but the type of spring 61 is arbitrary and is not limited to the above examples. For example, any type of elastic body, such as a leaf spring, may be used as the spring 61. Furthermore, the biasing body that biases the rotor 20 is not limited to the spring 61. For example, other types of elastic bodies, such as rubber, may be used to bias the rotor 20 instead of (or together with) the spring 61. Note that while the above description focuses on the spring 61, the other springs (62, 63, 64) exemplified in the above-described embodiments can also be modified in the same manner.

[0086] (7) In each of the above forms, Configuration A: A configuration in which the space S communicates with the first flow path 23 or the second flow path 34; Configuration B: A configuration in which the valve member B is biased by the difference between the first area S1 and the second area S2. Configuration C: The rotor 20 is pressed against the first seal 40 by the spring 61 in a state where the outer surface U of the rotor 20 does not contact the inner surface H of the housing 30. The following is an example. Configuration A, Configuration B, and Configuration C can exist independently of each other.

[0087] For example, focusing on configuration A, a configuration in which the vertical flow path 24 and the third flow path 35 are not formed is also conceivable, as illustrated in Fig. 17. In the configuration of Fig. 17, the space between the first surface F1 of the rotor 20 and the fourth surface F4 of the housing 30 is not filled with coolant, and therefore pressure from the coolant does not act on the first surface F1. In other words, in configuration A, the pressure from the coolant acting on the first surface F1 may be omitted.

[0088] Furthermore, the relationship between the first area S1 and the second area S2 is not important for configuration A. Therefore, as illustrated in Fig. 18, a cylindrical rotor 20 may be employed in which the outer peripheral surface Qb is a simple cylindrical surface. In the configuration of Fig. 18, the inner peripheral surface Ha of the housing 30 is also formed as a cylindrical surface, and the first portion 41 and the second portion 42 of the first seal 40 have the same diameter. In the configuration of Fig. 18, a communicating passage 25 is also formed that communicates the space S with the first flow path 23, so similar to the first embodiment, the effect of suppressing pressure accumulation in the space S is achieved compared to Comparative Example 2 of Fig. 3.

[0089] (8) In the configuration C, the configuration for preventing contact between the outer surface U of the rotor 20 and the inner surface H of the housing 30 is not limited to the examples described above. For example, as illustrated in FIG. 19 , in a configuration in which the outer peripheral surface Qb of the rotor 20 is a simple cylindrical surface, a fourth seal 90 may be installed between the first surface F1 of the rotor 20 and the fourth surface F4 of the housing 30. In the configuration of FIG. 19 , the rotor 20 is pressed against the fourth seal 90 by the spring 61 without the first surface F1 contacting the fourth surface F4. That is, the pressing force acting on the rotor 20 from the spring 61 is received by the first seal 40. Therefore, as in the first embodiment, an appropriate surface pressure can be applied to the fourth seal 90 regardless of dimensional errors in the valve member B or the housing 30. The fourth seal 90 in FIG. 19 is an example of a “first seal.”

[0090] (9) The term "nth" (n is a natural number) in this application is used only as a formal and convenient label to distinguish each element in the description and does not have any substantive meaning. Therefore, the term "nth" does not allow for any restrictive interpretation regarding the position or manufacturing order of each element. [Explanation of symbols]

[0091] 100...valve device, 10...shaft portion, 20...rotor, 21,31,32,38...cylindrical surface, 22,26,37...conical surface, 23...first flow path, 24...vertical flow path, 25,28...communicating passage, 27...cylindrical surface, 30...housing, 33...conical surface, 34...second flow path, 35...third flow path, 36...groove, 39...third seal, 40...first seal, 41...first part, 42...second part, 43...connecting portion, 50...second seal, 61,62,63,64...spring, 71...protrusion portion, 72...recess, 81,82...control device.

Claims

1. 1. A valve device for controlling a coolant for a motor vehicle, comprising: a valve member including a shaft portion rotatable around a rotation axis, and a rotor connected to the shaft portion and having a first flow path formed on an outer circumferential surface thereof, the first flow path having a plurality of first openings; a housing formed with a housing portion that houses the valve member and a second flow path having a second opening on an inner circumferential surface of the housing portion that can communicate with any one of the plurality of first openings; a biasing body that biases the rotor in a first direction; a first seal disposed between an outer surface of the rotor and an inner surface of the housing; the rotor is pressed against the first seal by the biasing body in a state where a surface of the rotor facing the first direction is not in contact with an inner surface of the accommodating portion, The first seal is a first portion extending in the first direction relative to the first openings and the second openings across the plurality of first openings in a circumferential direction of the rotor; a second portion extending along the circumferential direction of the rotor across the plurality of first openings in a second direction opposite to the first direction relative to the first openings and the second openings; a plurality of connecting portions that are spaced apart from one another along the circumferential direction of the rotor and that connect the first portion and the second portion; Valve gear.

2. an outer surface of the rotor includes a conical surface having an outer diameter at an end in the first direction that is smaller than an outer diameter at an end in the second direction; an outer diameter of the first portion is less than an outer diameter of the second portion; The first seal contacts the conical surface. The valve device of claim 1.

3. the surface of the rotor facing the first direction is a lower surface of the rotor; the inner surface of the storage portion includes a bottom surface facing the lower surface with a gap therebetween, the housing includes a protrusion protruding from the bottom surface, when the rotor is at a first position in the first direction, the lower surface of the rotor is not in contact with the inner surface including the top surface of the protrusion; When the rotor is at a second position opposite to the first position in the first direction, the lower surface of the rotor comes into contact with the top surface of the protrusion. The valve device according to claim 1 or 2.

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