Valve device

Abstract

The valve device (1) includes an inlet flow path (21), an outlet flow path (221, 222), valve cores (131, 132) for switching the connection and closure of the flow paths (21, 221, 222), valve seats (121, 122) for each valve core (131, 132) to sit on, a valve shaft (14) for moving the valve cores (131, 132) as a whole, an actuator (15) for driving the valve shaft (14), a spring (37) for applying force to the valve shaft (14) in one direction, a sealing member (18, 19) provided on one side of the contact portion between the valve cores (131, 132) and the valve seats (121, 122), and a valve seat protrusion (121a, 122a) provided on the other side. Here, the sealing member (19) and the valve seat protrusion (122a) are selectively combined by combining one of a plurality of sealing members with different characteristics and one of a plurality of valve seat protrusions with different characteristics to suppress the surface pressure at the contact portion between the valve core (132) and the valve seat (122) where the seat load is higher than that of the valve core (132) and the valve seat (122).

Description

Technical Field

[0001] The technology disclosed in this specification relates to valve devices for adjusting the flow of fluid in a flow path. Background Technology

[0002] Conventionally, such technology is known, for example, as described in Patent Document 1. This technology relates to a flow divider valve (valve device) for diverting fluid, which includes an input port (inlet flow path), a first output port (first outlet flow path), a second output port (second outlet flow path), a first valve seat formed between the inlet flow path and the first outlet flow path, a second valve seat formed between the inlet flow path and the second outlet flow path, a first valve core that abuts against and separates from the first valve seat, a second valve core that abuts against and separates from the second valve seat, a shaft (valve shaft) for mounting the first valve core and the second valve core, and a motor (drive unit) for driving the valve shaft, and is configured as a three-way valve.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2005-3190 Summary of the Invention

[0006] The problem the invention aims to solve

[0007] However, in the valve device described in Patent Document 1, due to differences in the pressure of the fluid acting on each flow path, the force of the spring installed in the drive unit, the driving force of the drive unit, and the pressure loss of each flow path, a difference sometimes occurs between the load (seat load) when the first valve core sits on the first valve seat and the seat load when the second valve core sits on the second valve seat. Here, to improve sealing, an elastic member such as a sealing member is considered to be provided at the contact portion between each valve core and its corresponding valve seat, so that the rigid member abuts against this elastic member. However, when there is a difference in seat load between the first and second valve seats, the surface pressure at the contact portion between the elastic member and the rigid member is too high on the side with the higher seat load, causing the elastic member to age easily and potentially deteriorate in durability. Here, "aging" refers to permanent deformation and performance degradation of an object during long-term use.

[0008] This disclosure is made in view of the above circumstances, and its object is to provide a valve device such that, for the elastic and rigid members provided at the abutment portions of a plurality of valve cores and corresponding plurality of valve seats, the surface pressure at the abutment portions where the seating load of the valve cores and valve seats is higher than that of other abutment portions can be suppressed, thereby suppressing the aging of the elastic members at the abutment portions.

[0009] Solution for solving the problem

[0010] (1) In order to achieve the above objective, one technical solution disclosed in this application is a valve device comprising: an inlet flow path; a plurality of outlet flow paths, which branch out from the inlet flow path in at least two directions to outlet fluid; a plurality of valve cores, which switch the connection and closure of the inlet flow path and one of the plurality of outlet flow paths; a plurality of valve seats, which are respectively provided corresponding to the plurality of outlet flow paths for one of the plurality of valve cores to be seated; a valve shaft, which moves the plurality of valve cores integrally along the axial direction; a drive unit, which drives the valve shaft along the axial direction; a spring, which applies force to one side of the valve shaft along the axial direction; and an elastic member and a rigid member, wherein when one of the plurality of valve cores is seated on one of the corresponding plurality of valve seats, the elastic member is provided on one side of the contact portion between the valve core and the valve seat, and the rigid member is provided on the other side. The main purpose is to selectively combine one of the plurality of elastic members with different properties and one of the plurality of rigid members with different properties to suppress the surface pressure at the contact portion where the seating load of the valve core and the valve seat is higher than that of other parts.

[0011] According to the structure described in (1) above, when one of the multiple valve cores is seated on one of the corresponding multiple valve seats, an elastic member provided on one side of the contact portion between the valve core and the valve seat abuts against a rigid member provided on the other side. Here, one of the multiple elastic members with different properties and one of the multiple rigid members with different properties are selectively combined to suppress the surface pressure at the contact portion where the seating load of the valve core and the valve seat is higher than that of other parts.

[0012] (2) In order to achieve the above objective, in the structure of (1) above, it is preferable that the rigid member includes a protrusion that abuts against the corresponding elastic member as one of the characteristics. Based on the driving force of the drive part, the force of the spring, the pressure of the fluid and the pressure loss of the inlet flow path and the outlet flow path, the protrusion of the abutment part with a higher load when the valve core is seated on the valve seat has a smaller radial size.

[0013] According to the structure described in (2), in addition to the effect of the structure described in (1), the valve core that corresponds to the convex part of the contact portion with a higher load (seat load) when the valve core is seated on the valve seat will actually have a lower pressure of fluid.

[0014] (3) In order to achieve the above objective, in the structure of (1) above, it is preferable that the elastic member of the contact part with a higher load when the valve core is seated on the valve seat is harder, based on the driving force of the drive part, the action force of the spring, the pressure of the fluid and the pressure loss of the inlet flow path and the outlet flow path.

[0015] According to the structure described in (3), in addition to the effect of the structure described in (1), the elastic member with a higher settling load has a higher hardness, and therefore the deformation strain of the elastic member is smaller.

[0016] (4) In order to achieve the above objective, in the structure of (1) above, it is preferable that the thickness of the elastic member of the contact part is greater when the load is higher when the valve core is seated on the valve seat, based on the driving force of the drive part, the action force of the spring, the pressure of the fluid and the pressure loss of the inlet flow path and the outlet flow path.

[0017] According to the structure described above (4), in addition to the effect of the structure described above (1), the elastic member of the contact part with a higher load is thicker, so the stress concentration of the elastic member is alleviated.

[0018] (5) In order to achieve the above objective, in the structure of (1) above, it is preferable that the rigid member includes a protrusion that abuts against the corresponding elastic member as one of the characteristics. Based on the driving force of the drive part, the force of the spring, the pressure of the fluid and the pressure loss of the inlet flow path and the outlet flow path, the protrusion of the abutment part with a higher load when the valve core is seated on the valve seat has a larger bending radius at the top.

[0019] According to the structure described in (5), in addition to the function of the structure described in (1), the convex part with a higher load has a larger bending radius at its top, thus suppressing the rise of surface pressure at the top of the convex part.

[0020] (6) In order to achieve the above objective, in the structure of (1) above, it is preferable that the rigid member includes a protrusion that abuts against the corresponding elastic member as one of its characteristics. Based on the driving force of the drive part, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the protrusion of the abutment part with a higher load when the valve core is seated on the valve seat has a larger width.

[0021] According to the structure described above (6), in addition to the function of the structure described above (1), the ridge of the abutment part with a higher load is wider, thus suppressing the rise of surface pressure at the ridge.

[0022] (7) In order to achieve the above objective, in the structure of (1) above, it is preferable that the rigid member includes a protrusion that abuts against the corresponding elastic member as one of its characteristics. Based on the driving force of the drive part, the force of the spring, the pressure of the fluid and the pressure loss of the inlet flow path and the outlet flow path, the protrusion of the protrusion of the abutment part is smaller when the load is higher when the valve core is seated on the valve seat.

[0023] According to the structure described above (7), in addition to the function of the structure described above (1), the protrusion height of the convex part of the abutment part is smaller when the sitting load is higher. Therefore, the sitting load is borne by the convex part and the surrounding plane, which can suppress the rise of surface pressure at the convex part.

[0024] (8) In order to achieve the above objectives, in any of the structures in (1) to (7) above, it is preferred that the valve device is used in the cooling system of an electric vehicle.

[0025] Based on the structure described in (8) above, as a valve device used in a cooling system mounted on an electric vehicle, it can achieve the same function as any of the structures described in (1) to (7) above.

[0026] The effects of the invention

[0027] According to the structure described above (1), the elastic and rigid members provided at the contact points between the multiple valve cores and the corresponding multiple valve seats can suppress the surface pressure at the contact points where the seat load of the valve cores and valve seats is higher than that of other valve seats, and can suppress the aging of the elastic members at the contact points.

[0028] According to the structure described in (2), it has the same effect as the structure described in (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0029] According to the structure described above (3), it has the same effect as the structure described above (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0030] According to the structure described above (4), it has the same effect as the structure described above (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0031] According to the structure described above (5), it has the same effect as the structure described above (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0032] According to the structure described above (6), it has the same effect as the structure described above (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0033] According to the structure described above (7), it has the same effect as the structure described above (1), and can suppress the surface pressure at the abutment where the sitting load is higher than that of other abutment parts, and can suppress the aging of the elastic member of the abutment part.

[0034] Based on the structure described in (8) above, the same effect as any of the structures described in (1) to (7) above can be obtained. Attached Figure Description

[0035] Figure 1 This is a cross-sectional view of a valve device representing a first open valve state, relating to a first embodiment.

[0036] Figure 2 This is a cross-sectional view of a valve device showing a second open valve state, relating to the first embodiment.

[0037] Figure 3 This is a cross-sectional view showing an integrated first valve seat and winding drum, relating to the first embodiment.

[0038] Figure 4 This relates to the connection between the first valve seat and the winding bobbin in the first embodiment. Figure 3 A sectional view along line AA.

[0039] Figure 5 This refers to the representation of the first embodiment. Figure 1 An enlarged sectional view of the valve core and valve seat.

[0040] Figure 6 It is a cross-sectional view relating to the first embodiment, showing the flow of fluid in a valve device in a first open state.

[0041] Figure 7 It is a cross-sectional view relating to the first embodiment, showing the flow of fluid in a valve device in a second open valve state.

[0042] Figure 8 It is a graph relating to the first embodiment, showing the relationship between the pressure on the valve seat surface and the aging of the sealing member.

[0043] Figure 9 It is a graph relating to the first embodiment, showing the relationship between the pressure on the valve seat surface and the leakage at the sealing member.

[0044] Figure 10 This is a circuit diagram illustrating an example of the use of the valve device according to the first embodiment.

[0045] Figure 11 This relates to the fluid pressure acting on the second valve core in the seated state, as described in the first embodiment. Figure 5 A magnified sectional view of a portion of the structure.

[0046] Figure 12 This is a partial enlarged cross-sectional view relating to the second embodiment, showing the seated state of the first valve core relative to the first valve seat.

[0047] Figure 13 This is a partial enlarged cross-sectional view relating to the second embodiment, showing the seated state of the second valve core relative to the second valve seat.

[0048] Figure 14 This is a partial enlarged cross-sectional view relating to the third embodiment, showing the seated state of the first valve core relative to the first valve seat.

[0049] Figure 15 This is a partial enlarged cross-sectional view relating to the third embodiment, showing the seated state of the second valve core relative to the second valve seat.

[0050] Figure 16 This is a graph relating to the third embodiment, showing the relationship between the top bending radius of the valve seat protrusion and the pressure on the valve seat surface.

[0051] Figure 17 This is a partial enlarged cross-sectional view relating to the fourth embodiment, showing the seated state of the first valve core relative to the first valve seat.

[0052] Figure 18 This is a partial enlarged cross-sectional view relating to the fourth embodiment, showing the seated state of the second valve core relative to the second valve seat.

[0053] Figure 19 This is a partial enlarged cross-sectional view relating to the fifth embodiment, showing the seated state of the first valve core relative to the first valve seat.

[0054] Figure 20 This is a partial enlarged cross-sectional view relating to the fifth embodiment, showing the seated state of the second valve core relative to the second valve seat.

[0055] Figure 21 This is a cross-sectional view of a valve device showing the first open valve state, relating to the sixth embodiment.

[0056] Figure 22 This is a cross-sectional view of a valve device showing the second open valve state, relating to the sixth embodiment.

[0057] Figure 23 This is a cross-sectional view of a valve device showing the first open valve state, relating to the seventh embodiment.

[0058] Figure 24 This is a cross-sectional view of a valve device showing the second open valve state, relating to the seventh embodiment.

[0059] Figure 25 This is a schematic cross-sectional view of the second valve core and the second valve seat, representing the open valve state, relating to the first to sixth embodiments.

[0060] Figure 26 This is a schematic cross-sectional view of the second valve core and the second valve seat, representing the valve open state, relating to the eighth embodiment. Detailed Implementation

[0061] Hereinafter, several embodiments embodying the "valve device" of the present disclosure will be described in detail with reference to the accompanying drawings.

[0062] <First Implementation Method>

[0063] First, refer to Figures 1-11 The valve device 1 of the first embodiment will be described in detail.

[0064] [Regarding the structure of the valve assembly]

[0065] exist Figure 1 , Figure 2 The valve device 1 of this embodiment is shown in a cross-sectional view. For example... Figure 1 , Figure 2 As shown, the valve device 1 includes a flow path housing 11 with multiple flow paths, a valve seat 12, a valve core 13, a valve shaft 14, and an actuator 15.

[0066] The valve device 1 constitutes a three-way valve. The flow path housing 11 includes a valve chamber 20 for receiving the valve core 13, an inlet flow path 21, and two outlet flow paths 22. The valve chamber 20 forms one end of the inlet flow path 21. In this embodiment, the flow path housing 11 is formed of resin.

[0067] The inlet flow path 21 is the flow path through which fluid flows into the valve chamber 20. The outlet flow path 22 is the flow path through which fluid flows out of the valve chamber 20. There are two outlet flow paths 22, including a first outlet flow path 221 and a second outlet flow path 222. The first outlet flow path 221 is located on the actuator 15 side relative to the valve chamber 20. The second outlet flow path 222 is located on the opposite side of the actuator 15 relative to the valve chamber 20.

[0068] The valve seat 12 includes a first valve seat 121 and a second valve seat 122. The first valve seat 121 is disposed on the side of the first outlet flow path 221 of the valve chamber 20. The second valve seat 122 is disposed on the side of the second outlet flow path 222 of the valve chamber 20. Both the first valve seat 121 and the second valve seat 122 are formed in annular shape, and each has a first valve hole 16 and a second valve hole 17 in the center. In addition, the valve seat 12 is formed of resin, but it can also be formed of rubber.

[0069] The valve core 13 is mounted on the lower end of the valve shaft 14, and opens and closes the first valve port 16 and the second valve port 17 by abutting and separating from the valve seat 12. In this embodiment, the valve core 13 includes a first valve core 131 and a second valve core 132 disposed axially spaced 26 apart from each other on the valve shaft 14. A first sealing member 18 is provided at the abutting portion of the first valve core 131 with the first valve seat 121. The first sealing member 18 abuts and separates from the first valve seat 121. In addition, a second sealing member 19 is provided at the abutting portion of the second valve core 132 with the second valve seat 122. The second sealing member 19 abuts and separates from the second valve seat 122. Furthermore, in this embodiment, the valve core 13 is formed of resin, but it can also be formed of metal. Each sealing member 18, 19 is formed of rubber into a ring-shaped plate of the same size, but it can also be formed of other elastic materials.

[0070] The valve shaft 14 is disposed inside the flow path housing 11 and the actuator 15. One end of the valve shaft 14 is disposed in the actuator 15. The other end of the valve shaft 14 is disposed in the valve chamber 20, where the valve core 13 is mounted. The valve shaft 14 is capable of reciprocating in the thrust direction that is its axial direction. Furthermore, in this embodiment, the valve shaft 14 is formed of metal, but it can also be formed of resin.

[0071] The actuator 15 is a component that moves the valve shaft 14 and the valve core 13 together along their axial direction, and is an example of the "drive unit" of the present disclosure. In this embodiment, the actuator 15 includes a movable core 31, a fixed core 32, a winding bobbin 33, a coil 34, and a housing 35, and is configured as a "solenoid".

[0072] The movable core 31 is integrally disposed with the valve shaft 14, and the valve shaft 14 moves axially by moving axially. The fixed core 32 is disposed opposite the movable core 31 in the axial direction of the valve shaft 14. A thrust bearing 36 for the valve shaft 14 is disposed between the upper end of the valve shaft 14 and the fixed core 32. Furthermore, on the outer periphery of the valve shaft 14, between the thrust bearing 36 and the movable core 31, a bearing for moving the movable core 31 towards... Figure 1 , Figure 2 The compression spring 37 applies force from below.

[0073] The movable core 31 and the fixed core 32 are formed of a magnetic material (e.g., metal). When a current flows in the coil 34, generating a magnetic field around the coil 34, the movable core 31 and the fixed core 32 are magnetized by this magnetic field. When the movable core 31 and the fixed core 32 are magnetized, the movable core 31 is attracted to the fixed core 32 by magnetic force, and the movable core 31, together with the valve shaft 14, overcomes the force of the compression spring 37 and approaches the fixed core 32. When no current flows in the coil 34, the movable core 31 and the fixed core 32 are not magnetized, the movable core 31 is not attracted to the fixed core 32, and the movable core 31, together with the valve shaft 14, separates from the fixed core 32 by the force of the compression spring 37.

[0074] The winding bobbin 33 is cylindrical, with a movable core 31 and a fixed core 32 on the inner side, and a coil 34 on the outer side. A resin housing 35 is formed by molding and covering the winding bobbin 33, coil 34, etc., with resin. A laterally protruding connector 35a is integrally formed on the housing 35. A terminal 34a extending from the coil 34 is provided on the connector 35a.

[0075] The valve device 1 configured as described above can move the valve shaft 14 axially using the actuator 15, thereby enabling... Figure 1 The first valve opening state shown and Figure 2 Switching between the second valve opening state shown.

[0076] Furthermore, the "first open valve state" refers to the state where the first valve seat 121 and the first valve core 131 are fully open, and the second valve seat 122 and the second valve core 132 are fully closed. Conversely, the "second open valve state" refers to the state where the first valve seat 121 and the first valve core 131 are fully closed, and the second valve seat 122 and the second valve core 132 are fully open. Moreover, the "fully closed state" refers to the state where the valve seat 12 and the valve core 13 are in full circumference contact across one end of the annular valve seat 12, thus sealing the valve seat 12 and the valve core 13.

[0077] Here, in Figure 1 In the first open valve state shown, the fluid introduced from the inlet flow path 21 is discharged from the first outlet flow path 221. Figure 2 In the second open valve state shown, the fluid introduced from the inlet flow path 21 is discharged from the second outlet flow path 222.

[0078] In this embodiment, the first valve seat 121 and the winding bobbin 33 are integrally formed. Figure 3 In this embodiment, a cross-sectional view is used to show the integrated first valve seat 121 and winding drum 33. Figure 4 In this embodiment, the method utilizes... Figure 3 The AA-line cross-sectional view shows the connection portion 40 between the first valve seat 121 and the winding bobbin 33. In this embodiment, as... Figure 3 As shown, the first valve seat 121 is integrally formed with the winding bobbin 33, which is separate from the flow path housing 11. The winding bobbin 33 has a connecting portion 40 at the connection between the inlet flow path 21 and the first outlet flow path 221, and this connecting portion 40 is coaxial with the valve shaft 14. That is, the first valve seat 121 and the winding bobbin 33 are integrally formed via the connecting portion 40. Furthermore, the first valve seat 121 and the connecting portion 40 are housed inside the flow path housing 11 (part of the first outlet flow path 221).

[0079] In this embodiment, such as Figure 4 As shown, the connecting portion 40 includes four pillars 41. The number of pillars 41 is not limited to four; there can be more than four. The four pillars 41 are arranged at equal angular intervals around the annular first valve seat 121 in the circumferential direction. That is, the four pillars 41 are equally spaced at 90° intervals in the circumferential direction of the first valve seat 121. The cross-section of each pillar 41 is generally rectangular, with its long side aligned with the radial direction of the first valve seat 121. Furthermore, adjacent pillars 41 form openings 42 for fluid flow.

[0080] [Regarding the shape of the valve core]

[0081] Next, the shape of the valve core 13 in this embodiment will be described. Figure 5 In this embodiment, an enlarged cross-sectional view is used for representation. Figure 1 The valve core 13 and valve seat 12. For example... Figure 5 As shown, a predetermined interval 26 is provided between the first valve core 131 and the second valve core 132. In this interval 26, the opposing surfaces of the first valve core 131 and the second valve core 132 are configured to be flat.

[0082] like Figure 5 As shown, a first sealing member 18 capable of abutting against the first valve seat 121 is provided at the seating portion of the first valve core 131 where it rests. Similarly, a second sealing member 19 capable of abutting against the second valve seat 122 is provided at the seating portion of the second valve core 132 where it rests. Each sealing member 18 and 19 is elastic in nature, representing an example of an "elastic member" of this disclosure. Each valve core 131 and 132 has opposing walls 131a and 132a that converge toward the valve holes 16 and 17 of the corresponding valve seats 121 and 122.

[0083] [Regarding the shape of the valve seat]

[0084] Next, the shape of the valve seat 12 in this embodiment will be described. For example... Figure 5 As shown, an annular first valve seat protrusion 121a is formed at the valve core side opening edge of the first valve hole 16, capable of abutting against the first sealing member 18. Additionally, as... Figure 5 As shown, an annular second valve seat protrusion 122a is formed at the valve core side opening edge of the second valve hole 17, capable of abutting against the second sealing member 19. Each valve seat protrusion 121a, 122a protrudes from the flat surface of the corresponding valve seat 121, 122, forming a shape that surrounds each valve hole 16, 17. Each valve seat protrusion 121a, 122a is more rigid in shape than each sealing member 18, 19, representing an example of a "rigid member" in this disclosure. Here, "rigid member" refers to a member with higher rigidity than an "elastic member".

[0085] [Topics related to sealing components]

[0086] Here, issues related to the sealing members 18 and 19 will be explained. In the valve device 1 of the three-way valve of this embodiment, the load (seat load) when each valve core 131, 132 sits on its corresponding valve seat 121, 122 results in a difference between the first valve core 131 and the first valve seat 121, and between the second valve core 132 and the second valve seat 122. This difference arises due to the pressure of the fluid flowing into the inlet flow path 21 (fluid pressure), the force of the compression spring 37 (spring force), and the driving force of the actuator 15 (actuator driving force), etc. On the side with a higher seat load, the surface pressure at the contact portion between the valve core 131, 132 and the valve seat 121, 122 is higher. This contact portion is formed by each sealing member 18, 19 and the corresponding valve seat protrusions 121a, 122a. The rubber sealing components 18 and 19 have the following characteristics: excellent sealing performance, but on the other hand, the surface pressure generated by the contact with the corresponding valve seat protrusions 121a and 122a is high. The higher the surface pressure, the more easily the sealing components 18 and 19 age.

[0087] exist Figure 6 In this embodiment, a cross-sectional view is used to show the flow of fluid in the valve device 1 in the first open state. Figure 7 In this embodiment, a cross-sectional view is used to show the flow of fluid in the valve device 1 in the second open state. Here, it is envisioned, for example, in... Figure 6 In the first open valve state shown, the high-pressure pump discharge pressure acts on the inlet flow path 21, in Figure 7 In the second open valve state shown, the medium-pressure pump discharge pressure acts on the inlet flow path 21. In this design, based on the relationship between fluid pressure, spring force, and actuator driving force, in the first open valve state, a larger flow path differential pressure and spring force act on the second valve core 132; in the second open valve state, a moderate flow path differential pressure and the difference between the actuator driving force and the spring force act on the first valve core 131. Therefore, the influence of the differential pressure before and after each valve core 131 and 132 is significant. In the first open valve state, the seating load of the second valve core 132 and the second valve seat 122 is high; in the second open valve state, the seating load of the first valve core 131 and the first valve seat 121 is low. In this design, if a sealing design prioritizing the sealing performance between the first valve core 131 and the first valve seat 121 is adopted as the specification, the surface pressure at the contact point between the second valve core 132 and the second valve seat 122 in the first open valve state would be too high, potentially degrading the aging resistance of the second sealing member 19.

[0088] exist Figure 8 In this embodiment, a graph is used to illustrate the relationship between the "surface pressure (valve seat surface pressure)" acting on each valve seat 121, 122 and the "aging" of each sealing member 18, 19. Figure 9In this embodiment, a graph is used to show the relationship between the "valve seat surface pressure" and the "leakage" at each sealing component 18 and 19. Figure 8 , Figure 9 The dotted line L1 indicates the position of the first valve seat 121, and the dotted line L2 indicates the position of the second valve seat 122. For example... Figure 8 As shown, the degree of "aging" of each sealing member 18 and 19 increases curvilinearly as the "valve seat surface pressure" exceeds a certain level. In this embodiment, no "aging" occurs at the "valve seat surface pressure" at the first valve seat 121. "Aging" occurs at the "valve seat surface pressure" at the second valve seat 122. Furthermore, as... Figure 9 As shown, the leakage of each sealing component 18 and 19 decreases curvilinearly from near zero "seat surface pressure" to a certain height. In this embodiment, the "seat surface pressure" at each valve seat 121 and 122 is set such that the leakage is zero.

[0089] [Characteristics of sealing components and valve seat protrusions]

[0090] Therefore, in this embodiment, to suppress the surface pressure at the contact portion where one valve core 131, 132 and the corresponding valve seat 121, 122 are subjected to a higher seating load than the other, one of a plurality of sealing members with different characteristics and one of a plurality of valve seat protrusions with different characteristics are selectively combined. That is, the characteristics of each sealing member 18, 19 are selected from a plurality of characteristics, and the characteristics of each valve seat protrusion 121a, 122a are selected from a plurality of characteristics. The sealing members 18, 19 having the selected characteristics and the valve seat protrusions 121a, 122a having the selected characteristics are combined and used.

[0091] Specifically, in this embodiment, each sealing member 18 and 19 is formed into a circular plate of the same size using the same rubber material. In contrast, based on the driving force of the actuator 15 (actuator driving force), the force of the compression spring 37 (spring force), the fluid pressure (fluid pressure), and the pressure loss of the inlet flow path 21 and the outlet flow paths 221 and 222 (flow path pressure loss), the second valve seat protrusion 122a of the abutment portion with a higher seating load when each valve core 131 and 132 sits on its corresponding valve seat 121 and 122 is set to have a radial dimension smaller than that of the first valve seat protrusion 121a. That is, as... Figure 5 As shown, the diameter Φ2D of the second valve seat protrusion 122a (second protrusion diameter) is set to be smaller than the diameter Φ1D of the first valve seat protrusion 121a (first protrusion diameter). The height, width, and cross-sectional shape of each valve seat protrusion 121a and 122a are set to be the same.

[0092] In addition, in this embodiment, based on the actuator driving force, spring force, fluid pressure, and flow path pressure loss, the second sealing member 19, whose abutment load is higher when each valve core 131, 132 sits on its corresponding valve seat 121, 122, has its hardness set higher than that of the first sealing member 18. That is, the first sealing member 18 is made of ethylene propylene diene monomer (EPDM) rubber, and the second sealing member 19 is made of fluororubber (FKM) rubber, which has a smaller compression set compared to EPDM.

[0093] [Examples of valve device usage]

[0094] Next, an example of using the valve device 1 in this embodiment will be described. Figure 10 In this embodiment, a circuit diagram is used to illustrate an example of the use of valve device 1. For example... Figure 10 As shown, in this embodiment, the valve device 1 is used in the cooling system 81 of the electric vehicle 80. This cooling system 81 is an example of a "cooling system" according to the present disclosure. In this usage example, the refrigerant flowing in the cooling system 81 is an example of a "fluid" according to the present disclosure. The electric vehicle 80 refers to, for example, a vehicle equipped with a motor powered by electricity from a secondary battery as its drive source and moving by driving the drive wheels using that motor, including electric vehicles, hybrid vehicles, etc.

[0095] In this embodiment, valve device 1 includes a first valve device 82 and a second valve device 83. In addition to the valve devices 82 and 83, the cooling system 81 also includes a heater 84, a battery 85, a DC-DC converter 86, a battery charger 87, a radiator 88, and an electric pump 89. Each valve device 82 and 83 has an inlet 82a and 83a of the inlet flow path 21, a first outlet 82b and 83b of the first outlet flow path 221, and a second outlet 82c and 83c of the second outlet flow path 222. These components 82-89 are arranged along a main piping 90 that circulates the refrigerant. The main piping 90 includes a first piping section 90a, a second piping section 90b, and a third piping section 90c.

[0096] The outlet 89a of the electric pump 89 is connected to the inlet 82a of the first valve device 82 via a first piping section 90a. The second outlet 82c of the first valve device 82 is connected to the inlet 82a of the second valve device 83 via a second piping section 90b. A heater 84, a battery 85, a DC-DC converter 86, and a battery charger 87 are sequentially arranged upstream of the second piping section 90b. The first outlet 82b of the first valve device 82 is connected to the first piping section 90a upstream of the DC-DC converter 86 via a first bypass piping 91. The second outlet 83c of the second valve device 83 is connected to the suction inlet 89b of the electric pump 89 via a third piping section 90c. A radiator 88 is arranged midway through the third piping section 90c. The first outlet 83b of the second valve device 83 is connected to the third piping section 90c upstream of the suction inlet 89b of the electric pump 89 via a second bypass piping 92.

[0097] Therefore, in the cooling system 81, the electric pump 89 is started to drive the valve devices 82 and 83 to switch the flow path, thereby switching the flow of refrigerant to each component 84-88.

[0098] In this embodiment, the flow path is switched between the first and third flow path modes by switching the flow paths of each valve device 82 and 83. Here, the first flow path mode is switched to prevent overheating and overcooling of the battery 85. In this first flow path mode, the electric pump 89 is started and the heater 84 is turned off, the first valve device 82 is switched to the first outlet 82b, and the second valve device 83 is switched to the second outlet 83c. As a result, the refrigerant sprayed from the electric pump 89 flows sequentially from the first valve device 82 through the first bypass pipe 91, the second pipe section 90b, and the third pipe section 90c, passing through the DC-DC converter 86, the battery charger 87, the second valve device 83, and the radiator 88, and returns to the suction port 89b of the electric pump 89, repeating this cycle. This first flow path mode is switched during low-speed operation in spring and autumn to appropriately maintain the temperature of the battery 85.

[0099] In the event of cooling the battery 85 or overheating due to waste heat, the system switches to a second flow path mode. In this mode, the electric pump 89 is started and the heater 84 is turned off. The first valve device 82 is switched to the second outlet 82c, and the second valve device 83 is switched to the second outlet 83c. As a result, the refrigerant ejected from the electric pump 89 flows sequentially from the first valve device 82 through the second piping section 90b and the third piping section 90c, passing through the heater 84, the battery 85, the DC-DC converter 86, the battery charger 87, the second valve device 83, and the radiator 88, before returning to the suction port 89b of the electric pump 89, repeating this cycle. This second flow path mode is used to cool the battery 85 when summer temperatures rise or when the battery 85 becomes hot.

[0100] When heating the battery 85 using the heater 84, the system switches to a third flow path mode. In this mode, the electric pump 89 is started and the heater 84 is turned on. The first valve device 82 is switched to the second outlet 82c, and the second valve device 83 is switched to the first outlet 83b. As a result, the refrigerant ejected from the electric pump 89 flows sequentially from the first valve device 82 through the second piping section 90b, the second bypass piping section 92, and the third piping section 90c, passing through the heater 84, the battery 85, the DC-DC converter 86, the battery charger 87, and the second valve device 83, before returning to the suction port 89b of the electric pump 89, repeating this cycle. This third flow path mode is used when the temperature is low in winter or when it is desired to quickly warm up the battery 85.

[0101] The battery 85 of the electric vehicle 80 has the characteristic that its performance degrades outside a certain temperature range. Therefore, in this embodiment, while monitoring the temperature of the battery 85 and the refrigerant, the above-mentioned flow path modes are switched to make the temperature of the battery 85 "25~35°C".

[0102] [Regarding the function and effect of the valve device and the cooling system equipped with it]

[0103] According to the structure of the valve device 1 of this embodiment described above, when each valve core 131, 132 is seated on its corresponding valve seat 121, 122, each sealing member 18, 19 provided on one side of the contact portion between each valve core 131, 132 and each valve seat 121, 122 abuts against the corresponding valve seat protrusion 121a, 122a provided on the other side. Here, in order to suppress the seating load of each valve core 131, 132 and its corresponding valve seat 121, 122 from being higher than the surface pressure at the contact portion between the other second valve core 132 and the second valve seat 122, the second sealing member 19 and the second valve seat protrusion 122a are selectively combined with one of a plurality of sealing members with different characteristics and one of a plurality of valve seat protrusions with different characteristics. Therefore, for the contact portions of each valve core 131, 132 and the corresponding valve seats 121, 122, the surface pressure (the surface pressure applied to the second sealing member 19) at the contact portions of the second valve core 132 and the second valve seat 122, which have a higher seating load than others, can be suppressed, and the aging of the second sealing member 19 can be suppressed.

[0104] Specifically, in this embodiment, based on the actuator driving force, spring force, fluid pressure, and flow path pressure loss, the second valve seat protrusion 122a of the second valve seat 122 with a higher seating load when each valve core 131, 132 sits on its corresponding valve seat 121, 122, has its second protrusion diameter Φ2D set to be smaller than the first protrusion diameter Φ1D of the first valve seat protrusion 121a as a characteristic feature. Therefore, the second valve core 132 corresponding to the second valve seat protrusion 122a of the contact portion with a higher seating load when each valve core 131, 132 sits on its corresponding valve seat 121, 122, actually experiences a lower fluid pressure compared to the first valve core 131.

[0105] exist Figure 11 In this embodiment, the method utilizes... Figure 5 The magnified cross-sectional view shows the relationship of fluid pressure acting on the second valve core 132 in the seated state. Figure 11 In the diagram, the thick solid arrows and thick dashed arrows represent the effect of fluid pressure on the second valve core 132. Here, the fluid pressures indicated by the solid arrows are substantially canceled out due to their opposing forces, and the load acting on the second valve core 132 is only the amount indicated by the dashed arrows. Therefore, the smaller the diameter Φ2D of the second convex strip, the smaller the load acting on the second valve core 132. Consequently, corresponding to the reduced load acting on the second valve core 132, the surface pressure at the contact point between the second valve core 132 and the second valve seat 122 (the surface pressure applied to the second sealing member 19), which has a higher seating load than others, can be suppressed, thus inhibiting the aging of the second sealing member 19.

[0106] Furthermore, specifically in this embodiment, based on the actuator driving force, spring force, fluid pressure, and flow path pressure loss, the second sealing member 19, as a characteristic feature, has its hardness set higher than that of the first sealing member 18 at the abutment portion where the seating load is higher. Therefore, the second sealing member 19, with a higher seating load at the abutment portion, has a higher hardness compared to the first sealing member 18, resulting in smaller deformation strain of the second sealing member 19. Consequently, the surface pressure (surface pressure applied to the second sealing member 19) at the abutment portion where the seating load is higher than others can be suppressed, thus suppressing the aging of the second sealing member 19.

[0107] Furthermore, according to the structure of this embodiment, the valve device 1 (82, 83) used in the cooling system 81 installed in the electric vehicle 80 can achieve the same function as described above, and obtain the same effect as described above.

[0108] <Second Implementation Method>

[0109] Next, refer to Figure 12 , Figure 13The valve device 1 of the second embodiment will be described in detail. Furthermore, in the following description, the same reference numerals are used for components identical to those in the first embodiment described above, and the description will focus on the differences.

[0110] [Regarding the structure of the sealing component]

[0111] In this embodiment, the structure of each sealing member 18, 19 differs from that in the first embodiment. Figure 12 In this embodiment, a partial enlarged cross-sectional view is used to show the seated state of the first valve core 131 relative to the first valve seat 121. Figure 13 In this embodiment, an enlarged cross-sectional view is used to show a portion of the seated state of the second valve core 132 relative to the second valve seat 122. In this embodiment, there are differences from the first embodiment, such as... Figure 12 , Figure 13 As shown, based on the actuator driving force, spring force, fluid pressure and flow path pressure loss, the second sealing member 19 of the contact portion with a higher seating load when each valve core 131, 132 sits on the corresponding valve seat 121, 122, has its thickness T2 set to be greater than the thickness T1 of the first sealing member 18.

[0112] [Regarding the function and effects of valve devices]

[0113] According to the structure of the valve device 1 of this embodiment described above, unlike the first embodiment, the thickness T2 of the second sealing member 19 at the abutment portion where the seating load is higher is greater than the thickness T1 of the first sealing member 18, thus alleviating the stress concentration of the second sealing member 19. Therefore, the surface pressure (the surface pressure applied to the second sealing member 19) at the abutment portion where the seating load is higher than others can be suppressed, and the aging of the second sealing member 19 can be suppressed.

[0114] <Third Implementation Method>

[0115] Next, refer to Figures 14-16 The valve device 1 of the third embodiment will be described in detail.

[0116] [Regarding the structure of the valve seat protrusion]

[0117] In this embodiment, the structure of the valve seat protrusions 121a and 122a differs from that in the embodiments described above. Figure 14 In this embodiment, a partial enlarged cross-sectional view is used to show the seated state of the first valve core 131 relative to the first valve seat 121. Figure 15 In this embodiment, an enlarged cross-sectional view is used to show a portion of the seated state of the second valve core 132 relative to the second valve seat 122. In this embodiment, there are differences from the first embodiment, such as... Figure 14 , Figure 15 As shown, based on the actuator driving force, spring force, fluid pressure and flow path pressure loss, the second valve seat protrusion 122a of the abutment part with a higher seating load when each valve core 131, 132 sits on the corresponding valve seat 121, 122, has its top bending radius R2 set to be greater than the bending radius R1 of the first valve seat protrusion 121a.

[0118] exist Figure 16 In this embodiment, a graph is used to illustrate the relationship between the top bending radius of the valve seat protrusion and the pressure on the valve seat surface. For example... Figure 16 As shown, the "seat surface pressure" of each valve seat 121 and 122 decreases curvilinearly as the top bending radius increases.

[0119] [Regarding the function and effects of valve devices]

[0120] According to the structure of the valve device 1 of this embodiment described above, unlike the first embodiment, the bending radius R2 of the top of the second valve seat protrusion 122a at the abutment portion where the seating load is higher is larger than the bending radius R1 of the top of the first valve seat protrusion 121a. Therefore, it is possible to suppress the rise of surface pressure at the top of the second valve seat protrusion 122a. Thus, it is possible to suppress the surface pressure (surface pressure applied to the second sealing member 19) at the abutment portion where the seating load is higher than others, and it is possible to suppress the aging of the second sealing member 19.

[0121] <Fourth Implementation Method>

[0122] Next, refer to Figure 17 , Figure 18 The valve device 1 of the fourth embodiment will be described in detail.

[0123] [Regarding the structure of the valve seat protrusion]

[0124] In this embodiment, the structure of the valve seat protrusions 121a and 122a differs from that in the embodiments described above. Figure 17 In this embodiment, a partial enlarged cross-sectional view is used to show the seated state of the first valve core 131 relative to the first valve seat 121. Figure 18 In this embodiment, an enlarged cross-sectional view is used to show a portion of the seated state of the second valve core 132 relative to the second valve seat 122. In this embodiment, there are differences from the first embodiment, such as... Figure 17 , Figure 18As shown, based on the actuator driving force, spring force, fluid pressure and flow path pressure loss, the second valve seat protrusion 122a of the abutment portion with a higher seating load when each valve core 131, 132 sits on the corresponding valve seat 121, 122, is set to have a protrusion width W2 that is greater than the protrusion width W1 of the first valve seat protrusion 121a.

[0125] [Regarding the function and effects of valve devices]

[0126] According to the structure of the valve device 1 of this embodiment described above, unlike the first embodiment, the width W2 of the second valve seat protrusion 122a at the abutment portion where the seating load is higher is larger than the width W1 of the first valve seat protrusion 121a. Therefore, it is possible to suppress the rise of surface pressure at the second valve seat protrusion 122a. Thus, it is possible to suppress the surface pressure (surface pressure applied to the second sealing member 19) at the abutment portion where the seating load is higher than others, and it is possible to suppress the aging of the second sealing member 19.

[0127] <Fifth Implementation Method>

[0128] Next, refer to Figure 19 , Figure 20 The valve device 1 of the fifth embodiment will be described in detail.

[0129] [Regarding the structure of the valve seat protrusion]

[0130] In this embodiment, the structure of the valve seat protrusions 121a and 122a differs from that in the embodiments described above. Figure 19 In this embodiment, a partial enlarged cross-sectional view is used to show the seated state of the first valve core 131 relative to the first valve seat 121. Figure 20 In this embodiment, an enlarged cross-sectional view is used to show a portion of the seated state of the second valve core 132 relative to the second valve seat 122. In this embodiment, there are differences from the first embodiment, such as... Figure 19 , Figure 20 As shown, based on the actuator driving force, spring force, fluid pressure and flow path pressure loss, the second valve seat protrusion 122a of the abutment portion with a higher seating load when each valve core 131, 132 sits on the corresponding valve seat 121, 122, is set to have a protrusion height H2 that is smaller than the protrusion height H1 of the first valve seat protrusion 121a.

[0131] Here, if we take Figure 19 If the protrusion height H1 of the first valve seat protrusion 121a and the protrusion height H2 of the second valve seat protrusion 122a are set to be the same, then due to tolerances and other deviations, the surface pressure at the top of the first valve seat protrusion 121a may be insufficient. Conversely, for... Figure 20As shown in the diagram, the second valve seat protrusion 122a experiences a large settling load at the second valve seat 122. Consequently, the adjacent flat portion 122b of the second valve seat protrusion 122a comes into contact with the second sealing member 19. Therefore, the second sealing member 19 also displaces at the flat portion 122b in accordance with the increased load. This reduces the surface pressure on the second sealing member 19 caused by contact with the second valve seat protrusion 122a.

[0132] [Regarding the function and effects of valve devices]

[0133] According to the structure of the valve device 1 of this embodiment described above, unlike the first embodiment, the protrusion height H2 of the second valve seat protrusion 122a at the abutment portion where the seating load is higher is smaller than the protrusion height H1 of the first valve seat protrusion 121a. Therefore, the seating load is borne by the second valve seat protrusion 122a and the surrounding flat portion 122b, which can suppress the rise of surface pressure on the second valve seat protrusion 122a. Thus, the surface pressure (surface pressure applied to the second sealing member 19) at the abutment portion where the seating load is higher than others can be suppressed, and the aging of the second sealing member 19 can be suppressed.

[0134] <Sixth Implementation Method>

[0135] Next, refer to Figure 21 , Figure 22 The valve device 2 of the sixth embodiment will be described in detail.

[0136] [Regarding the structure of the actuator]

[0137] The valve device 2 in this embodiment differs from the embodiments described above in the structure of the actuator 15. Figure 21 In this embodiment, the valve device 2 in the first open state is shown in a cross-sectional view. Figure 22 In this embodiment, the valve device 2 in the second open state is shown in a cross-sectional view. For example... Figure 21 , Figure 22 As shown, the valve device 2 is similar to the embodiments described above, including a flow path housing 11 with flow paths 21 and 22, a valve seat 12 (first valve seat 121 and second valve seat 122), a valve core 13 (first valve core and second valve core 132), a valve shaft 14, and an actuator 15, and constitutes a three-way valve.

[0138] The flow path housing 11 differs in form from the embodiments described above, but includes an inlet flow path 21, a first outlet flow path 221, and a second outlet flow path 222. The valve core 13 is similar to the embodiments described above, including a first valve core 131 with a first sealing member 18 and a second valve core 132 with a second sealing member 19. Each valve seat 121, 122 is separately formed into annular shapes relative to the flow path housing 11 and is pressed into the inlet of each outlet flow path 221, 222, and has a first valve hole 16 and a second valve hole 17, respectively. The relationship between each valve seat 121, 122 and each valve core 131, 132 is the same as in the embodiments described above, and is "inwardly open".

[0139] In contrast, in this embodiment, the actuator 15 is composed of a "stepper motor". In this embodiment, the valve shaft 14 is disposed between the actuator 15 and the valve core 13, and is positioned in the assembly hole 11a formed in the flow path housing 11. A thrust bearing 51, etc., is disposed in the assembly hole 11a with the valve shaft 14 as the center. Each valve core 131, 132 is fixed to the lower end of the valve shaft 14, and abuts against or separates from each valve seat 121, 122. A spring seat 14a is integrally provided at the upper end of the valve shaft 14. A mechanical stop 14b protruding upwards is provided on the upper surface of the spring seat 14a. This mechanical stop 14b... Figure 22 In the second open valve state shown, it engages with one end of the rotor body 53A described later, restricting further rotation of the valve shaft 14.

[0140] The actuator 15 includes a stator 52 containing a coil 34, a permanent magnet rotor 53 disposed inside the stator 52, and an output shaft 54 ​​disposed at the center of the permanent magnet rotor 53. These components 52-54 are molded and covered using a resin housing 35.

[0141] The output shaft 54 ​​has an external thread 54a on its outer circumference. The lower end of the output shaft 54 ​​is connected to a spring seat 14a located at the upper end of the valve shaft 14. The permanent magnet rotor 53 includes a rotor body 53A and a cylindrical plastic magnet 53B integrally disposed on the outer circumference of the rotor body 53A. A first radial bearing 55A is disposed on the upper outer circumference of the rotor body 53A between it and the housing 35. A second radial bearing 55B is disposed on the lower inner circumference of the plastic magnet 53B between it and the thrust bearing 51. Through these upper and lower radial bearings 55A and 55B, the permanent magnet rotor 53 is supported inside the stator 52 to be rotatable. An internal thread 53Aa is formed at the center of the rotor body 53A, which is threaded into the external thread 54a of the output shaft 54. A first compression spring 56A is disposed between the permanent magnet rotor 53 and the lower second radial bearing 55B. A second compression spring 56B is provided between the spring seat 14a and the second radial bearing 55B to apply force to the valve shaft 14 toward the permanent magnet rotor 53.

[0142] Here, in Figure 21 In the first open valve state shown, the permanent magnet rotor 53 rotates in one direction, thereby utilizing the threaded connection between the external thread 54a of the output shaft 54 ​​and the internal thread 53Aa of the rotor body 53A, and the force of the second compression spring 56B, causing the output shaft 54 ​​to rotate in one direction while simultaneously pushing in the direction of thrust. Figure 21 The valve core 13 moves upwards through the stroke of the output shaft 54. Through this stroke, the valve core 13 and valve shaft 14 move together... Figure 21 The first valve core 131 moves upwards and approaches the first valve seat 121 to become... Figure 22 The second open valve state.

[0143] On the other hand, Figure 22 In the second open valve state shown, the permanent magnet rotor 53 rotates in the opposite direction, thereby utilizing the threaded connection between the external thread 54a of the output shaft 54 ​​and the internal thread 53Aa of the rotor body 53A to overcome the force of the second compression spring 56B, causing the output shaft 54 ​​to rotate in the opposite direction while simultaneously moving in the direction of thrust. Figure 22 The valve core 13 moves downwards through the stroke of the output shaft 54. Through this stroke, the valve core 13 and valve shaft 14 move together... Figure 22 The first valve core 131 separates from the first valve seat 121 during its downward stroke. Figure 21 The first open valve state.

[0144] [Regarding the function and effects of valve devices]

[0145] The structure of the valve device 2 in this embodiment, as described above, differs from the embodiments described above. The actuator 15 is composed of a stepper motor, but it can achieve the same function and effect as the embodiments described above.

[0146] In this embodiment, Figure 21 In the first open valve state shown, the second valve core 132 is seated (grounded) on the second valve seat 122, thereby restricting the movement of the valve core 13 (mechanically stopped). Consequently, the actuator 15 (stepper motor) loses its step in response to this mechanical stop, and the valve core 13 is pushed upward by the second compression spring 56B. Therefore, the valve core 13 itself stops after moving upward by an amount corresponding to the loss of step. Thus, the second valve core 132 and the second valve seat 122, with a gap, are in contact with the second valve seat protrusion 122a and the second sealing member 19 under a certain degree of surface pressure.

[0147] In this embodiment, Figure 22In the second open valve state shown, before the mechanical stop 14b engages with the rotor body 53A, the first valve core 131 sits on the first valve seat 121, and the first sealing member 18 of the first valve core 131 stops touching the plane of the first valve seat 121. Therefore, the surface pressure of the first valve seat 121 becomes the surface pressure of the first valve seat protrusion 121a contacting the first sealing member 18 in a state where the clearance is zero due to the plane touching the ground. Therefore, the action of the actuator 15 increases the surface pressure of the first sealing member 18, but this effect can be mitigated by increasing the bending radius of the top of the first valve seat protrusion 121a.

[0148] <Seventh Implementation Method>

[0149] Next, refer to Figure 23 , Figure 24 The valve device 3 of the seventh embodiment will be described in detail.

[0150] [Regarding the structure of the valve seat and valve core]

[0151] In this embodiment, the structure of each valve seat 121, 122 and each valve core 131, 132 differs from the embodiments described above. In the aforementioned embodiments, a so-called internally opening three-way valve is disclosed, in which two valve cores 131, 132 are disposed in a valve chamber 20 between two valve seats 121, 122 and are arranged such that they can sit on their respective valve seats 121, 122. In contrast, in this embodiment, a so-called externally opening three-way valve is disclosed, in which the two valve cores 131, 132 are not disposed in the valve chamber 20 between two valve seats 121, 122, but rather each valve core 131, 132 is respectively disposed in its respective outlet flow path 221, 222 such that it can sit on its respective valve seat 121, 122.

[0152] exist Figure 23 In this embodiment, the valve device 3 in the first open state is shown in a cross-sectional view. Figure 24 In this embodiment, the valve device 3 in the second open state is shown in a cross-sectional view. For example... Figure 23 , Figure 24 As shown, the valve device 3 is similar to the first to fifth embodiments described above, including a flow path housing 11 with flow paths 21, 22 (221, 222), a valve seat 12 (121, 122), a valve core 13 (131, 132), a valve shaft 14, and an actuator 15.

[0153] The flow path housing 11 differs in form from other embodiments, but includes an inlet flow path 21 and an outlet flow path 22 (221, 222). The valve core 13 is similar to those in the above embodiments, including a first valve core 131 with a first sealing member 18 and a second valve core 132 with a second sealing member 19, but the first sealing member 18 is disposed on the lower side of the first valve core 131, and the second sealing member 19 is disposed on the upper side of the second valve core 132. Each valve seat 121, 122 is integrally formed with the flow path housing 11, and each has a first valve hole 16 and a second valve hole 17. Furthermore, a first valve seat protrusion 121a is disposed on the upper side of the first valve seat 121, and a second valve seat protrusion 122a is disposed on the lower side of the second valve seat 122.

[0154] The actuator 15 has a different configuration of components, but it is similar to the first to fifth embodiments described above, including a movable core 31, a fixed core 32, a winding bobbin 33, a coil 34, a compression spring 37, and a housing 35. The movable core 31 and the fixed core 32 are arranged vertically opposite to those in the first to fifth embodiments, but the lower second valve seat 122 has a larger seating load.

[0155] Here, in Figure 23 In the first open valve state shown, the spring force generated by the extension of the compression spring 37 acts upwards, while the fluid pressure corresponding to the area inside the second valve seat 122 (which is larger than the area of ​​the second valve seat protrusion 122a) acts downwards. In this case, the upward spring force is greater than the downward fluid pressure, thereby maintaining the closed valve state of the second valve core 132.

[0156] On the other hand, Figure 24 In the second open valve state shown, the larger spring force generated by the compression of the spring 37 acts upward, and the larger actuator driving force acts downward. Additionally, in the first valve seat 121, the fluid pressure corresponding to the area inside the first valve seat protrusion 121a acts upward. In this case, the downward actuator driving force is greater than the sum of the upward spring force and the fluid pressure, thereby maintaining the closed valve state of the first valve core 131. At this time, the seating load at the first valve seat 121 is greater than the seating load at the second valve seat 122 in the first open valve state.

[0157] Typically, valve devices need to overcome the spring force and the differential pressure across the valve core to operate. Furthermore, the actuators of valve devices are configured to switch between various systems, making the seating load susceptible to the influence of the actuator's driving force.

[0158] [Regarding the function and effects of valve devices]

[0159] The structure of the valve device 3 in this embodiment, as described above, is different from the internally open three-way valves in the above embodiments. It is configured as an externally open three-way valve, but it can achieve the same function and effect as the above embodiments.

[0160] <Eighth Implementation Method>

[0161] Next, refer to Figure 25 , Figure 26 The valve device of the eighth embodiment will be described in detail.

[0162] [Regarding the configuration of sealing components]

[0163] In this embodiment, the arrangement of the elastic and rigid members differs from the embodiments described above. Figure 25 In the first to sixth embodiments, a schematic cross-sectional view is used to show the second valve core 132 and the second valve seat 122 in the open valve state. Figure 26 In this embodiment, the second valve core 132 and the second valve seat 122 in the open valve state are also shown using a schematic cross-sectional view. Figure 25 , Figure 26 In the text, the second valve seat 122 and the second valve core 132 are shown only as examples.

[0164] In the first to sixth embodiments described above, such as Figure 25 As shown, a second sealing member 19, serving as an elastic member, is provided in the second valve core 132, and a second valve seat protrusion 122a, serving as a rigid member, is provided in the second valve seat 122 in a manner that allows it to abut against the second sealing member 19. The configuration of the first sealing member 18 is similar. In contrast, in this embodiment, as... Figure 26 As shown, a second sealing member 19, which is an elastic member, is provided on the second valve seat 122, and a second valve core protrusion 132b, which is a rigid member, is provided on the second valve core 132 in such a way that it can abut against the second sealing member 19.

[0165] [Regarding the function and effects of valve devices]

[0166] The structure of the valve device according to the above-described embodiment differs from that of the first to sixth embodiments in terms of the arrangement of the elastic and rigid components, but it can basically achieve the same function and effect as the first to sixth embodiments.

[0167] Here, we compare the advantages of the configuration of the elastic and rigid members in this embodiment with those in the first to sixth embodiments described above. Figure 25 , Figure 26In this embodiment, when the diameters (valve hole diameters) ΦDA and ΦDB of each valve hole 17 are set to be the same, for the second valve core protrusion 132b (rigid member), considering the inclination of the second valve core 132, in order to reliably contact the second sealing member 19 (elastic member), the pressure-bearing diameter ΦDPB depicted at the top of the second valve core protrusion 132b needs to be set with a margin. In contrast, in the first to sixth embodiments described above, for the second valve seat protrusion 122a (rigid member), it is not necessary to consider the inclination of the second valve core 132, and the pressure-bearing diameter ΦDPA depicted at the top of the second valve seat protrusion 122a can be set to be smaller than the pressure-bearing diameter ΦDPB. Therefore, in the first to sixth embodiments described above, the valve opening force of the second valve core 132 based on fluid pressure can be reduced, and the actuator 15 can be miniaturized accordingly.

[0168] On the other hand, in this embodiment, the second sealing member 19 (elastic member) is fixed to the vicinity of the valve hole 17 of the second valve seat 122 by bonding or sintering. In contrast, in the first to sixth embodiments described above, the second sealing member 19 can be fixed to each valve core 131, 132 by fitting. Figure 25 , Figure 26 In the text, "WS" represents the inclined absorption width of the valve shaft 14 in the second sealing member 19.

[0169] <Other Implementation Methods>

[0170] Furthermore, the present disclosure is not limited to the above-described embodiments, and can also be implemented by appropriately modifying a part of the structure without departing from the spirit of the disclosure.

[0171] (1) In the above embodiments, valve devices 1 to 3 are configured as three-way valves, but are not limited thereto.

[0172] (2) In the above embodiments, a sealing member is provided in the valve core or valve seat as an elastic member, but the elastic member can also be used to form the whole of the valve core or valve seat.

[0173] (3) In the above embodiments, a protrusion is provided on the valve core or valve seat as a rigid member, but the rigid member can also be used to form the whole of the valve core or valve seat.

[0174] Industrial availability

[0175] The technology disclosed herein can be used in the fluid circuit of cooling systems installed in electric vehicles and the like.

[0176] Explanation of reference numerals in the attached figures

[0177] 1. Valve assembly; 2. Valve assembly; 3. Valve assembly; 12. Valve seat; 121. First valve seat; 121a. First valve seat protrusion (rigid member); 122. Second valve seat; 122a. Second valve seat protrusion (rigid member); 13. Valve core; 131. First valve core; 132. Second valve core; 132b. Second valve core protrusion (rigid member); 14. Valve shaft; 15. Actuator (drive unit); 18. First sealing member (elastic member); 19. Second sealing member (elastic member); 21. Inlet flow path; 22. Outlet flow path; 221. First outlet flow path; 222. Two outlet flow paths; 37, compression spring; 56B, second compression spring; 80, electric vehicle; 81, cooling system; 82, first valve device; 83, second valve device; Φ1D, diameter of the first convex strip; Φ2D, diameter of the second convex strip; T1, thickness of the first sealing member; T2, thickness of the second sealing member; R1, bending radius of the top of the first valve seat convex strip; R2, bending radius of the top of the second valve seat convex strip; W1, convex width of the first valve seat convex strip; W2, convex width of the second valve seat convex strip; H1, protrusion height of the first valve seat convex strip; H2, protrusion height of the second valve seat convex strip.

Claims

1. A valve device comprising: Import flow path; Multiple outflow paths, which branch out from the inflow path in at least two directions, outflowing fluid; Multiple valve cores that switch the connection and closure of the inlet flow path and one of the multiple outlet flow paths; Multiple valve seats are respectively provided corresponding to multiple outlet flow paths, for one of the multiple valve cores to be seated; A valve shaft that causes the plurality of valve cores to move integrally along the axial direction; The drive unit drives the valve shaft axially; A spring that applies force to one side of the valve axis; and The resilient member is disposed on one side of the contact portion between the valve core and the valve seat, and the rigid member is disposed on the other side, when one of the plurality of valve cores is seated on one of the corresponding plurality of valve seats. Its features are, Selectively combining one of the multiple elastic members with different morphological properties and one of the multiple rigid members with different morphological properties to suppress the surface pressure at the contact portion where the seat load of the valve core and the valve seat is higher than that of other parts.

2. The valve device according to claim 1, characterized in that, The rigid member includes a protrusion that abuts against the corresponding elastic member as one of the morphological characteristics. Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the radial size of the protrusion of the abutment portion is smaller when the load is higher when the valve core is seated on the valve seat.

3. The valve device according to claim 1, characterized in that, Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the elastic member of the abutment portion has a higher hardness when the load is higher when the valve core is seated on the valve seat.

4. The valve device according to claim 1, characterized in that, Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the elastic member of the abutment portion has a larger thickness when the load is higher when the valve core is seated on the valve seat.

5. The valve device according to claim 1, characterized in that, The rigid member includes a protrusion that abuts against the corresponding elastic member as one of the morphological characteristics. Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the convex strip of the abutment portion has a larger bending radius at its top when the load is higher when the valve core is seated on the valve seat.

6. The valve device according to claim 1, characterized in that, The rigid member includes a protrusion that abuts against the corresponding elastic member as one of the morphological characteristics. Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the wider the convex strip of the abutment portion is, the higher the load when the valve core sits on the valve seat.

7. The valve device according to claim 1, characterized in that, The rigid member includes a protrusion that abuts against the corresponding elastic member as one of the morphological characteristics. Based on the driving force of the drive unit, the force of the spring, the pressure of the fluid, and the pressure loss of the inlet and outlet flow paths, the protrusion height of the convex strip of the abutment part is smaller when the load is higher when the valve core is seated on the valve seat.

8. The valve device according to any one of claims 1 to 7, characterized in that, The valve device is used in the cooling system of an electric vehicle.

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