Flow passage switching device

Abstract

To suppress deviation (displacement) of posture caused by sliding of a valve seal member during driving of a rotary disc, and to secure substantially even sealing performance and wear resistance over the entire periphery of the valve seal member.SOLUTION: A flow passage switching device 1 includes a rotary disc 40 and a fixed disc 50 in a housing 11. The housing, the fixed disc and the rotary disc include a plurality of communication paths 20, 30, 60 and 70, with an annular valve seal member 81 arranged between the rotary disc and the housing and fixed disc. A plurality of flow passages are selectively formed in a switching manner by rotating the rotary disc and connecting the communication path 60, the housing and the communication paths 20, 30 and 70 of the fixed disc. The rotary disc includes assembling grooves 41c, 41d into which the valve seal member is attached. A driving deviation suppression structure 10 for suppressing deviation that can be caused by sliding of the seal member during driving of the rotary disc with the valve seal member attached to the assembling grooves is provided between the valve seal member and sidewalls of the assembling grooves.SELECTED DRAWING: Figure 9

Description

[Technical field]

[0001] The technology disclosed in this specification relates to a flow path switching device used to switch a flow path of a fluid in a fluid circuit. [Background technology]

[0002] Conventionally, as this type of technology, for example, a flow path switching device described in Patent Document 1 below is known. As described in paragraphs

[0156] to

[0166] and FIG. 10 of Patent Document 1, this device includes a housing 71 and a valve body portion 73 arranged inside the housing 71. The valve body portion 73 includes a fixed disk 75 and a drive disk 74 that is driven to rotate. The fixed disk 75 is arranged so as to divide the inside of the housing 71, and has a plurality of communication passages 75a, 75b. The drive disk 74 is formed in a plate shape of a size capable of closing the communication passages 75a, 75b. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent Publication No. 2022-21966 Summary of the Invention [Problem to be solved by the invention]

[0004] Incidentally, in the device described in Patent Document 1, it is possible to provide seal members around the communication passages 75a, 75b between the fixed disk 75 and the driving disk 74. In this case, when the driving disk 74 is rotated to switch the communication between the communication passages 75a, 75b, the edges of the communication passages 75a, 75b or the edges of the driving disk 74 cross the seal members with high surface pressure. In this case, sliding wear may occur in the seal members, or the seal members may become biased (displaced) in the opposite direction to the sliding direction, causing the seal surface pressure by the seal members to become non-uniform, which may deteriorate the sealing performance and wear resistance.

[0005] More specifically, the seal member is not a perfect circle centered on the rotation axis of the drive disk 74, but has an irregular shape. Therefore, when the seal member is rotated, the state of displacement of the seal member differs depending on the sliding resistance of each part and the direction of movement, causing stress concentration and surface pressure fluctuations in each part, which may result in uneven wear and fluid leakage.

[0006] This disclosed technology has been made in consideration of the above circumstances, and its purpose is to suppress deviation (misalignment) of the position of the sealing means due to sliding when the valve body is driven in a flow path switching device in which a sealing means is provided between a stator and a valve body that moves relative to the stator, and to ensure approximately uniform sealing performance and wear resistance around the entire circumference of the sealing means. [Means for solving the problem]

[0007] In order to achieve the above object, the technology described in claim 1 is a flow path switching device comprising at least one stator, a valve body that drives relative to the stator, the stator and the valve body each including at least one communicating passage, and an annular sealing means that is provided between the stator and the valve body and slides against the stator or the valve body as the valve body is driven, and is configured to selectively connect the communicating passage of the valve body and the communicating passage of the stator by driving the valve body to switch and form a series of flow paths, wherein the valve body or the stator includes an assembly groove for assembling the sealing means, and the sealing means is assembled into the assembly groove by fitting, and in this assembled state, a drive slippage suppression structure is provided between the sealing means and a side wall of the assembly groove to suppress slippage due to sliding of the sealing means when the valve body is driven.

[0008] According to the configuration of the above technology, a drive slippage suppression structure is provided between the seal means assembled by fitting into the assembly groove of the valve body or the stator and the side wall of the assembly groove, and therefore, when the valve body is driven, the drive slippage suppression structure suppresses slippage caused by sliding of the seal means.

[0009] In order to achieve the above object, the technology described in claim 2 is the technology described in claim 1, in which the drive deviation suppression structure is a convex portion provided on a side wall of the assembly groove and abuts against the sealing means so as to sandwich the sealing means from the inside and outside.

[0010] According to the configuration of the above technology, in addition to the effect of the technology described in claim 1, the drive deviation suppression structure is configured by the protrusions that sandwich the sealing means from the inside and outside on the side walls of the assembly groove.

[0011] In order to achieve the above object, the technology described in claim 3 is the technology described in claim 2, in which the sealing means includes a plurality of curved portions and a plurality of inflection points where adjacent curved portions are connected, and the convex portion abuts against a portion near the inflection points other than the inflection points.

[0012] According to the configuration of the above technology, in addition to the effect of the technology described in claim 2, the convex portion abuts on the sealing means in a portion near the inflection point other than the inflection point where adjacent curved portions are connected. Therefore, when the sealing means passes through the opening of the communication passage as the valve disc is driven, stress concentration due to the convex portion at the inflection point of the sealing means is suppressed.

[0013] In order to achieve the above object, the technology recited in claim 4 is the technology recited in claim 3, wherein the assembly groove includes a groove arc portion, as well as an outer peripheral side wall and an inner peripheral side wall, the sealing means includes a seal arc portion that fits into the groove arc portion, the convex portion includes an outer peripheral side wall and an inner peripheral side wall, and the convex portion includes an outer peripheral side convex portion provided on the outer peripheral side wall and an inner peripheral side convex portion provided on the inner peripheral side wall, and the smaller the radii of the groove arc portion and the seal arc portion, the larger the projection allowance of the outer peripheral side convex portion is compared to the projection allowance of the inner peripheral side convex portion.

[0014] According to the configuration of the above technology, in addition to the effect of the technology described in claim 3, the convex portion includes an outer circumferential convex portion and an inner circumferential convex portion, and the smaller the radius of the groove arc portion and the seal arc portion, the larger the projection allowance of the outer circumferential convex portion is compared to that of the inner circumferential convex portion. Therefore, the sealing means corrects the imbalance between the compressive stress caused by the inner circumferential convex portion and the compressive stress caused by the outer circumferential convex portion.

[0015] In order to achieve the above-mentioned object, the technology described in claim 5 is the technology described in claim 1, in which the drive deviation suppression structure is a seal side convex portion provided on a side surface of the sealing means and configured to press against a side wall of the assembly groove.

[0016] According to the configuration of the above technique, in addition to the effect of the technique recited in claim 1, the drive deviation suppression structure is constituted by a seal side protrusion provided on the side surface of the sealing means so as to press the side wall of the assembly groove.

[0017] In order to achieve the above object, the technology described in claim 6 is such that, in the technology described in any one of claims 1 to 5, a gap is provided between the sealing means and the assembly groove, and the gap on the outer periphery side is larger than the gap on the inner periphery side.

[0018] According to the configuration of the above technology, in addition to the effect of the technology described in any one of claims 1 to 5, a gap is provided between the sealing means and the assembly groove, and the gap on the outer periphery side is larger than the gap on the inner periphery side. Therefore, even if stress is concentrated on the outer periphery side of the assembly groove when the valve body is driven or the sealing means passes through the opening of the communication passage, the gap on the outer periphery side is larger than the gap on the inner periphery side, so that the gap on the outer periphery side provides more escape routes for the sealing means.

[0019] In order to achieve the above object, the technology described in claim 7 is directed to the technology described in claim 6, in which the edge of the assembly groove at a position intersecting the drive direction of the valve body has a larger R shape or tapered shape than the edge at other positions.

[0020] According to the configuration of the above technique, in addition to the effect of the technique described in claim 6, the edge of the assembly groove at the position intersecting the drive direction of the valve disc has a larger R-shape or tapered shape than the edges at other positions. Therefore, when the sealing means moves from the opening of the communication passage onto the sliding surface of the valve disc, the sealing means is allowed to escape more by the amount that the edge of the assembly groove has a larger R-shape or tapered shape.

[0021] In order to achieve the above object, the technology described in claim 8 is the technology described in any one of claims 1 to 5, wherein the valve body is configured to be rotatably driven around a rotation axis, the sealing means comprises a rotation line portion along the rotation direction of the valve body and a rotation intersecting portion intersecting the rotation direction, the rotation line portion includes an inner rotation line portion close to the rotation center of the valve body and an outer rotation line portion far from the rotation center, and the curvature of the inner rotation line portion is smaller than the curvature of the rotation trajectory of the valve body.

[0022] According to the configuration of the above technology, in addition to the effect of the technology described in any one of claims 1 to 5, the curvature of the inner rotating portion among the rotating portion (including the inner rotating portion and the outer rotating portion) and the rotating intersection portion that constitute the sealing means is smaller than the curvature of the rotational trajectory of the valve body, so that the stress action at the boundary between the inner rotating portion and the rotating intersection portion becomes approximately horizontal. Effect of the Invention

[0023] According to the technology recited in claim 1, it is possible to suppress deviation (displacement) of the position of the sealing means due to sliding when the valve disc is driven, and it is possible to ensure approximately uniform sealing performance and wear resistance around the entire circumference of the sealing means.

[0024] According to the technology described in claim 2, in addition to the effects of the technology described in claim 1, a drive deviation suppression structure can be realized with an extremely simple structure, and deviation (deviation) in posture due to sliding of the sealing means when the valve body is driven can be suppressed, and approximately uniform sealing performance and wear resistance can be ensured around the entire circumference of the sealing means.

[0025] According to the technique recited in claim 3, in addition to the effect of the technique recited in claim 2, it is possible to reduce stress concentration in the sealing means.

[0026] According to the technology described in claim 4, in addition to the effect of the technology described in claim 3, it is possible to further suppress the deviation (deviation) of the position of the sealing means due to sliding when the valve body is driven, and it is possible to ensure more uniform sealing performance and wear resistance around the entire circumference of the sealing means.

[0027] According to the technology described in claim 5, in addition to the effects of the technology described in claim 1, a drive deviation suppression structure can be realized with an extremely simple structure, deviation (deviation) of the attitude of the sealing means can be suppressed, and when the valve body is driven in one direction, stress concentration on the other side of the sealing side convex portion can be suppressed.

[0028] According to the technology recited in claim 6, in addition to the effects of the technology recited in any one of claims 1 to 5, when the valve body is actuated or the sealing means passes through the opening of the communicating passage, the deformation of the sealing means can be released to a greater extent into the gap on the outer periphery, thereby suppressing stress concentration on the sealing means.

[0029] According to the technology recited in claim 7, in addition to the effect of the technology recited in claim 6, it is possible to further suppress the stress concentration on the sealing means.

[0030] According to the technology recited in claim 8, in addition to the effect of the technology recited in any one of claims 1 to 5, it is possible to suppress stress concentration at the boundary between the rotational line portion and the rotational tolerance portion of the sealing means that occurs when the valve body is driven. [Brief description of the drawings]

[0031] [Figure 1] FIG. 2 is a perspective view showing the appearance of the flow path switching device in the first embodiment. [Diagram 2] FIG. 2 is an exploded perspective view showing the flow path switching device in the first embodiment. [Diagram 3] FIG. 2 is a cross-sectional view showing the flow path switching device in the first embodiment. [Figure 4] FIG. 2 is a plan view showing the upper surface of the rotating disk in the first embodiment. [Diagram 5] FIG. 3 is a plan view showing the upper surface of the fixed disk in the first embodiment. [Figure 6] FIG. 3 is an image diagram illustrating a flow path pattern A according to the first embodiment. [Figure 7] FIG. 11 is an image diagram illustrating a flow path pattern B in the first embodiment. [Figure 8] FIG. 11 is a plan view showing an upper valve seal member provided on a part of the upper surface of the rotating disk and a part of the upper housing, according to a comparative example of the first embodiment. [Figure 9] 9 is a plan view equivalent to FIG. 8 showing one upper valve seal member provided on a part of the upper surface of the rotary disk and a part of the upper housing in the first embodiment. FIG. [Figure 10] FIG. 11 is a plan view showing one upper valve seal member provided on a part of the upper surface of the rotating disk in the second embodiment. [Figure 11] 10 is a plan view equivalent to FIG. 8 showing a part of an upper valve seal member provided on a part of the upper surface of a rotary disk and a part of an upper housing according to a comparative example of the third embodiment. FIG. [Figure 12] FIG. 13 is a plan view showing one valve seal member provided on a part of the upper surface of the rotating disk in the third embodiment. [Figure 13] FIG. 13 is an enlarged plan view showing first to third in-groove convex portions provided as a drive deviation suppression structure in a part of an assembly groove of a rotating disk in a fourth embodiment. [Figure 14] 14 is a plan view according to the fifth embodiment, which is an enlarged view of first to third in-groove protrusions provided as a drive deviation suppression structure in a part of an assembly groove of a rotary disc 40, and corresponds to FIG. [Figure 15] FIG. 23 is a bottom view showing one lower valve seal member 81B provided on a part of the lower surface of the rotating disc in the sixth embodiment. [Figure 16] 16 is a cross-sectional view taken along line CC in FIG. 15 , illustrating a portion of a convex portion in a second groove according to the sixth embodiment. [Figure 17] FIG. 13 is an enlarged bottom view showing a protruding portion in each assembly groove in the sixth embodiment. [Figure 18] 13A and 13B are enlarged plan and bottom views showing convex portions in assembly grooves as a drive deviation suppression structure according to a comparative example of the seventh embodiment. [Figure 19] 18, showing the seal-side convex portions of the seal member as the drive misalignment suppression structure according to the seventh embodiment. FIG. [Figure 20]FIG. 23 is a schematic view showing a part of a rotating disk in an eighth embodiment, a part of an assembly groove provided on an upper surface of the rotating disk, and a part of an upper valve seal member assembled thereto. [Figure 21] 20 according to the eighth embodiment, showing an assembly groove; FIG. [Figure 22] 20 according to the eighth embodiment, showing an assembly groove; FIG. [Diagram 23] 20 according to the eighth embodiment, showing an assembly groove; FIG. [Figure 24] A cross-sectional view of the 9th embodiment when the rotating disc is rotating counterclockwise, showing the first shear sliding portion of the lower valve seal member and the corresponding assembly groove, as well as the fixed disc and a portion of the opening of the fixed flow path formed therein. [Diagram 25] A cross-sectional view of the 9th embodiment when the rotating disc is rotating clockwise, showing the first shear sliding portion of the lower valve seal member and the corresponding assembly groove, as well as the fixed disc and a portion of the opening of the fixed flow path formed therein. [Figure 26] FIG. 13 is a schematic diagram illustrating the ninth embodiment, in which a first shear sliding portion (indicated by a thick two-dot chain line) moving counterclockwise and a first shear sliding portion (indicated by a thick solid line) moving clockwise each ride up from the opening of the fixed flow path onto the upper surface of the fixed disk. [Figure 27] FIG. 23 is a bottom view illustrating a first shear sliding portion of the lower valve seal member and a portion of the assembly groove corresponding to the first shear sliding portion in the ninth embodiment. [Figure 28] 23 is a plan view or bottom view showing one valve seal member provided on the rotating disk of each embodiment, as a comparison with the tenth embodiment. FIG. [Figure 29] FIG. 29 is a plan view or bottom view equivalent to FIG. 28 showing one valve seal member provided on the rotating disk in the tenth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0032] Hereinafter, several embodiments of the flow path switching device will be described in detail.

[0033] First Embodiment The first embodiment will be described in detail with reference to FIGS.

[0034] [Overview of the flow switching device] Fig. 1 shows an external perspective view of the flow path switching device 1 of this embodiment. Fig. 2 shows an exploded perspective view of the flow path switching device 1 of this embodiment (illustration of the drive unit 13 is omitted). Fig. 3 shows a cross-sectional view of the flow path switching device 1 of this embodiment (illustration of the drive unit 13 is omitted). As shown in Figs. 1 to 3, the flow path switching device 1 includes a housing 11, a valve body portion 12, and a drive unit 13.

[0035] [About housing] As shown in FIG. 1 to FIG. 3, the housing 11 is configured by fastening the upper housing 11A and the lower housing 11B with a plurality of screws 16. The housing 11 includes an inflow flow path 20 through which the liquid flows in and an outflow flow path 30 through which the liquid flows out. In this embodiment, the flow path switching device 1 is configured as a six-way valve as an example, and the housing 11 has three inflow flow paths 20 and three outflow flow paths 30. As the three inflow flow paths 20, a first inflow flow path 21, a second inflow flow path 22, and a third inflow flow path 23 are provided in the upper housing 11A. As shown in FIG. 3, an opening 20a that can communicate with a rotation flow path 60 to be described later is provided at one end of the inflow flow path 20 facing a rotary disk 40 to be described later. In addition, as the three outflow flow paths 30, a first outflow flow path 31, a second outflow flow path 32, and a third outflow flow path 33 are provided in the lower housing 11B.

[0036] The housing 11 is formed of, for example, resin. The housing 11 (upper housing 11A and lower housing 11B) corresponds to an example of a "stator" in the disclosed technology, and the inflow passage 20 (first inflow passage 21, second inflow passage 22, and third inflow passage 23) and the outflow passage 30 (first outflow passage 31, second outflow passage 32, and third outflow passage 33) correspond to an example of a "communication passage" in the disclosed technology.

[0037] [About the valve body] The valve body portion 12 is provided inside the housing 11. As shown in Figures 2 and 3, the valve body portion 12 includes a fixed disk 50 that does not rotate, a rotating disk 40 that is stacked on the fixed disk 50 and rotates relative to the upper housing 11A and the fixed disk 50, and a rotating shaft 42 that is provided integrally with the rotating disk 40 at the center of the rotating disk 40.

[0038] The rotating disk 40 (including the rotating shaft 42) and the fixed disk 50 are formed of, for example, resin. The rotating disk 40 corresponds to an example of a "valve body" in the technology disclosed herein, and the fixed disk 50 constitutes a part of a "stator" in the technology disclosed herein.

[0039] [About the rotating disk] FIG. 4 shows a plan view of the upper surface of the rotary disk 40 according to this embodiment. As shown in FIGS. 2 to 4, the rotary disk 40 is disposed between the upper housing 11A and the fixed disk 50. The rotary disk 40 includes a disk portion 41 and a rotary shaft 42. The rotary disk 40 (disk portion 41) is formed in a disk shape and includes a plurality of rotary flow paths 60. The rotary flow paths 60 penetrate the rotary disk 40 in the plate thickness direction (axial direction), extend along the plate surface direction, and can communicate with the inlet flow path 20 and a fixed flow path 70 described later. In this embodiment, the rotary disk 40 includes three rotary flow paths 60. As shown in FIGS. 2 and 4, the three rotary flow paths 60 include a first rotary flow path 61, a second rotary flow path 62, and a third rotary flow path 63. These rotary flow paths 60 are formed in the rotary disk 40 in a curved long hole shape ("cocoon-shaped") in a plan view. These rotational channels 60 (the first rotational channel 61, the second rotational channel 62, and the third rotational channel 63) correspond to an example of a “communication channel” in the technology disclosed herein.

[0040] [About the rotation axis] The rotating shaft 42 is connected to the rotating disk 40 (disk portion 41) at one axial end thereof, and is connected to the driving unit 13 at the other axial end thereof. The rotating shaft 42 is formed integrally with the disk portion 41 such that its central axis coincides with the central axis L of the rotating disk 40. The rotating shaft 42 receives a rotational driving force from the driving unit 13 and rotates, whereby the rotating disk 40 rotates.

[0041] [About fixed disks] Fig. 5 shows a plan view of the upper surface of the fixed disk 50 according to this embodiment. As shown in Figs. 2, 3 and 5, the fixed disk 50 includes a disk portion 51 and a plurality of cylindrical portions 52 formed integrally with the disk portion 51. A retaining spring 82 for urging and retaining the fixed disk 50 in the direction of the rotating disk 40 is provided between the fixed disk 50 and the lower housing 11B. The retaining spring 82 is disposed on the lower surface of the fixed disk 50 so as to include each cylindrical portion 52 therein.

[0042] The disk portion 51 is formed in a disk shape and includes fixed flow passages 70 penetrating in the axial direction. In this embodiment, the three fixed flow passages 70 include a first fixed flow passage 71, a second fixed flow passage 72, and a third fixed flow passage 73. The three fixed flow passages 70 are disposed at equal angular intervals from each other. The fixed flow passages 70 correspond to an example of a "communicating passage" in the technology disclosed herein.

[0043] The cylindrical portion 52 is formed to extend in the axial direction from the disk portion 51 so as to surround the fixed flow passage 70. In this embodiment, three cylindrical portions 52 are formed corresponding to the three fixed flow passages 70. The tips of these fixed flow passages 70 are connected to the outlet flow passages 30 formed in the lower housing 11B. As shown in FIGS. 2 to 4, an opening 70a that can communicate with the rotary flow passage 60 is provided at one end of the fixed flow passage 70 facing the rotating disc 40.

[0044] [About the drive unit] The drive unit 13 includes a motor, a reduction mechanism, and the like (not shown) for applying a rotational drive force to the rotating shaft 42.

[0045] The flow path switching device 1 configured as above forms a flow path through which liquid flows by connecting the inflow flow path 20, the rotating flow path 60, and the fixed flow path 70 (outflow flow path 30). The flow path switching device 1 rotates the rotary disk 40 via the rotary shaft 42 by the drive unit 13, and switches the combination of connections between the three rotating flow paths 60 (61-63), the three inflow flow paths 20 (21-23), the three fixed flow paths 70 (71-73), and the three outflow flow paths 30 (31-33), thereby switching the liquid flow path between several patterns.

[0046] [About the flow path pattern] For example, as shown in Fig. 6, as flow path pattern A, three rotary flow paths 60 (61-63) communicate the first inflow flow path 21, the first fixed flow path 71, and the first outflow flow path 31, communicate the second inflow flow path 22, the second fixed flow path 72, and the second outflow flow path 32, and communicate the third inflow flow path 23, the third fixed flow path 73, and the third outflow flow path 33. Fig. 6 is a schematic image diagram showing flow path pattern A according to this embodiment.

[0047] Then, by rotating the rotary disk 40 clockwise by "60°" using the drive unit 13, the state of the flow path pattern A shown in Fig. 6 can be switched to the flow path pattern B shown in Fig. 7. Fig. 7 shows a schematic image diagram of the flow path pattern B according to this embodiment.

[0048] That is, in flow path pattern B, three rotary flow paths 60 (61-63) connect the first inflow flow path 21, the third fixed flow path 73, and the third outflow flow path 33, connect the second inflow flow path 22, the first fixed flow path 71, and the first outflow flow path 31, and connect the third inflow flow path 23, the second fixed flow path 72, and the second outflow flow path 32.

[0049] It should be noted that the flow path pattern B shown in Fig. 7 can be switched to the flow path pattern A shown in Fig. 6 by rotating the rotating disk 40 counterclockwise by "60°" using the driving unit 13. Alternatively, the flow path pattern can be switched to a state equivalent to the flow path pattern A shown in Fig. 6 by further rotating the rotating disk 40 clockwise by "60°" (in this case, the combination of the rotating flow paths 60 is different).

[0050] [Valve seal material] In this embodiment, as shown in FIG. 3, in the flow path switching device 1, valve seal members 81 for suppressing leakage of liquid in the flow paths are provided between the upper housing 11A and the rotary disk 40 and between the rotary disk 40 and the fixed disk 50. Here, as the valve seal members 81, an upper valve seal member 81A is provided between the upper housing 11A and the rotary disk 40, and a lower valve seal member 81B is provided between the rotary disk 40 and the fixed disk 50. An assembly groove 41c having a curved elongated hole shape ("cocoon-shaped") for assembling the upper valve seal member 81A is provided on the upper surface 41a of the disc part 41 of the rotary disk 40, and an assembly groove 41d having a "cocoon-shaped" shape for assembling the lower valve seal member 81B is provided on the lower surface 41b. These assembly grooves 41c and 41d are formed along the outer periphery of the "cocoon-shaped" rotation flow path 60 of the rotary disk 40. The valve seal member 81 has a "cocoon shape" similar to the assembly grooves 41c, 41d, and is press-fitted and fixed into the assembly grooves 41c, 41d.

[0051] As shown in Figs. 2 to 4, the valve seal member 81 is provided on the upper surface 41a and the lower surface 41b of the rotating disk 40 (disk portion 41) in a protruding manner so as to surround the periphery of the opening edge 60a of the "cocoon-shaped" rotating flow passage 60. The upper valve seal member 81A provided on the upper surface 41a of the rotating disk 40 is provided so as to protrude toward the upper housing 11A and contacts the inner surface 11a of the upper housing 11A to seal the flow passage formed between the inflow flow passage 20 and the rotating flow passage 60 communicating with the inflow flow passage 20 from the outside. The lower valve seal member 81B provided on the lower surface 41b of the rotating disk 40 (disk portion 41) is provided so as to contact the fixed disk 50 to seal the flow passage formed between the fixed flow passage 70 and the rotating flow passage 60 communicating with the fixed flow passage 70 from the outside.

[0052] In this embodiment, each valve seal member 81 (81A, 81B) is formed, for example, from a rubber material which is an elastic body. Alternatively, each valve seal member 81 may be formed from a fluororesin (for example, Teflon (registered trademark)), from rubber to which a fluororesin is attached, or from a material other than fluororesin or rubber. These valve seal members 81 correspond to one example of the "sealing means" of this disclosed technology. In Figures 2, 4, 6 and 7, the shape of the valve seal member 81 is shown diagrammatically. Details of the shapes of the valve seal member 81 and related members will be described later.

[0053] [Other sealing materials] 3, a lip seal 83 is provided between the upper housing 11A and the rotating shaft 42. In addition, another lip seal 84 is provided between each cylindrical portion 52 of the fixed disk 50 and the lower housing 11B.

[0054] [Issues with valve seal materials when rotating disks rotate] Fig. 8 shows a plan view of one upper valve seal member 81A provided on a part of the upper surface 41a of the rotating disk 40 and a part of the upper housing 11A in a comparative example of this embodiment. In Fig. 8, the curved parts indicated by the arrows at both ends of the longitudinal direction (rotation direction Y of the rotating disk 40) of the cocoon-shaped upper valve seal member 81A are defined as a "first shear sliding part A1" and a "second shear sliding part A2", respectively, the curved part indicated by the inner arrow in the radial direction of the rotating disk 40 along the longitudinal direction is defined as an "inner peripheral sliding part B1", and the curved part indicated by the outer arrow in the radial direction of the rotating disk 40 along the longitudinal direction is defined as an "outer peripheral sliding part B2". Here, each shear sliding portion A1, A2 and the corresponding portion of the mounting groove 41c correspond to a position intersecting with the rotation direction (driving direction) of the rotating disk 40, and each sliding portion B1, B2 on the inner and outer circumferences and the corresponding portion of the mounting groove 41c correspond to a position along the rotation direction (driving direction) of the rotating disk 40.

[0055] As shown in Fig. 8, when the rotary disk 40 rotates in the counterclockwise direction Y1 indicated by the white arrow, the upper valve seal member 81A appears to move clockwise (is left behind) due to the sliding resistance between the upper valve seal member 81A and the upper housing 11A. Therefore, at the front side (first shear sliding portion A1) of the upper valve seal member 81A, the portion A1 is pulled and the diameter is reduced, and one rotating tip portion P1 surrounded by a broken line circle is in a low surface pressure state, and at the rear side (second shear sliding portion A2) of the rotation, the portion A2 is compressed and the diameter is increased, and the other rotating tip portion P2 surrounded by a broken line circle is in a high surface pressure state. Therefore, the surface pressure of the upper valve seal member 81A varies between the upper valve seal member 81A and the upper housing 11A, and as a result, there is a concern that the sliding resistance of the upper valve seal member 81A increases, uneven wear occurs, and the sealing performance deteriorates. That is, when the rotary disk 40 rotates, there is a concern that the upper valve seal member 81A may slip due to sliding (driving slippage), which may deteriorate the sealing performance. When the rotary disk 40 rotates clockwise, the first shear sliding portion A1 becomes the rear side of the rotation and is compressed, and the second shear sliding portion A2 becomes the front side of the rotation and is pulled, which may cause a similar concern. There is a similar concern between the lower valve seal member 81B provided on the lower surface 41b of the rotary disk 40 and the fixed disk 50. In FIG. 8, the thickness of each curved arrow C1, C2, C3 indicates the difference in tension and compression. Therefore, in this embodiment, the following "driving slippage suppression structure" is provided to address the problem of the "cocoon-shaped" valve seal member 81 described above.

[0056] [Drive slippage prevention structure] FIG. 9 shows one upper valve seal member 81A provided on a part of the upper surface 41a of the rotary disk 40 and a part of the upper housing 11A in this embodiment in a plan view equivalent to FIG. 8. The upper valve seal member 81A is assembled by fitting into the assembly groove 41c. In this assembled state, a drive slippage suppression structure 10 for suppressing slippage due to sliding of the upper valve seal member 81A during rotation of the rotary disk 40 is provided between the upper valve seal member 81A and the side wall of the assembly groove 41c in a portion surrounded by a dashed circle (excluding P1 and P2) in FIG. 9. In this embodiment, the drive slippage suppression structure 10 is a first groove inner convex portion 44 and a second groove inner convex portion 45 provided on the side wall of the assembly groove 41c and abutting against the upper valve seal member 81A so as to sandwich the upper valve seal member 81A from both the inside and outside.

[0057] Here, the first groove inner convex portion 44 is provided at the boundary between each of the shear sliding parts A1, A2 and the inner circumferential sliding part B1 and the outer circumferential sliding part B2, where the sliding direction of the upper valve seal member 81A is significantly different when the rotary disk 40 rotates in the counterclockwise direction Y1. Each of the shear sliding parts A1, A2 and the inner circumferential sliding part B1 and the outer circumferential sliding part B2 correspond to a plurality of "curved parts" constituting the upper valve seal member 81A, and the above-mentioned "boundary" corresponds to an "inflection point" where adjacent curved parts are connected to each other. In addition, the second groove inner convex portion 45 is provided at approximately the center of the outer circumferential sliding part B2, where the interval between the adjacent first groove inner convex portions 44 is long.

[0058] Although not shown and not described, the lower valve seal member 81B provided on the lower surface 41b of the rotary disk 40 is also provided with a drive deviation suppression structure similar to that of the upper valve seal member 81A.

[0059] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, the above problem related to the "cocoon-shaped" valve seal member 81 is solved as follows. That is, between the valve seal members 81 (upper valve seal member 81A, lower valve seal member 81B) assembled by fitting into the assembly grooves 41c, 41d of the rotary disk 40 and the side walls of the assembly grooves 41c, 41d, the drive deviation suppression structure 10 is provided. Therefore, when the rotary disk 40 rotates (when driven), the drive deviation suppression structure 10 suppresses deviation due to sliding of the valve seal member 81. Therefore, deviation (deviation) of the position of the valve seal member 81 due to sliding can be suppressed when the rotary disk 40 rotates, and approximately uniform sealing performance and wear resistance can be ensured around the entire circumference of the valve seal member 81.

[0060] According to the configuration of this embodiment, the drive slippage suppression structure 10 is composed of the first groove protrusions 44 and the second groove protrusions 45 that sandwich the valve seal member 81 from the inside and outside on the side walls of the assembly grooves 41c, 41d. In this sense, the drive slippage suppression structure 10 can be realized with an extremely simple structure, and deviation (deviation) in the position of the valve seal member 81 due to sliding when the rotating disk 40 is driven can be suppressed, and approximately uniform sealing performance and wear resistance can be ensured around the entire circumference of the valve seal member 81.

[0061] <Second embodiment> Next, the second embodiment will be described in detail with reference to Fig. 10. In the following description, components equivalent to those in the first embodiment will be given the same reference numerals and description thereof will be omitted, and differences will be mainly described.

[0062] [Drive slippage prevention structure] This embodiment is different from the first embodiment in terms of the "drive slippage suppression structure". FIG. 10 shows a plan view of one upper valve seal member 81A provided on a part of the upper surface 41a of the rotary disk 40 according to this embodiment. In this embodiment, when the upper valve seal member 81A rotates together with the rotary disk 40, the rotating tip portions P1 and P2 where the compressive stress is concentrated at each shear sliding portion A1 and A2 are not provided with an in-groove convex portion (drive slippage suppression structure). In other words, in each shear sliding portion A1 and A2, the in-groove convex portion (drive slippage suppression structure) is provided at a position avoiding the rotating tip portions P1 and P2. That is, in this embodiment, as shown in FIG. 10, a third in-groove convex portion 46 (drive slippage suppression structure 10) is provided between each rotating tip portion P1 and P2 and the first in-groove convex portion 44.

[0063] Although not shown and not described, the lower valve seal member 81B provided on the lower surface 41b of the rotary disk 40 is also provided with a drive deviation suppression structure similar to that of the upper valve seal member 81A.

[0064] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the first embodiment, the following actions and effects can be obtained. That is, in this embodiment, the third groove inner convex portion 46 (drive deviation suppression structure 10) is provided at each shear sliding portion A1, A2, so that the deviation (deviation) of the posture due to the sliding of each shear sliding portion A1, A2 can be further suppressed during the rotation of the rotating disk 40, and more uniform sealing performance and wear resistance can be secured over the entire circumference of the valve seal member 81. Also, in each shear sliding portion A1, A2, the third groove inner convex portion 46 is provided at a position avoiding the rotation leading end portions P1, P2, so that the occurrence of further compressive stress concentration at the rotation leading end portions P1, P1 for each shear sliding portion A1, A2 can be suppressed.

[0065] <Third embodiment> Next, a third embodiment will be described in detail with reference to FIGS.

[0066] [Drive slippage prevention structure] This embodiment differs from the above-mentioned embodiments in the structure of the "driving deviation suppression structure". FIG. 11 shows a part of the upper valve seal member 81A provided on a part of the upper surface 41a of the rotary disk 40 and a part of the upper housing 11A in a plan view similar to FIG. 8, which is related to the comparison of this embodiment. In the above-mentioned embodiments, the first groove inner convex portion 44 is provided in the valve seal member 81 at the boundary between each shear sliding portion A1, A2 and the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2, that is, at the "inflection point" where adjacent curved portions are connected to each other. However, as shown in FIG. 11, when the first shear sliding portion A1 crosses the opening 20a of the inflow passage 20, the crossing portion is opened to the opening 20a, so that the crossing portion receives the tensile stress F1 due to the sliding resistance of the portion other than the crossing portion, and the open portion tries to move to the sliding portion. However, there is a concern that the movement is suppressed by the first groove inner convex portion 44, and the compressive stress F2 acts. Therefore, in this embodiment, the drive deviation suppression structure 10 is configured as follows.

[0067] FIG. 12 shows a plan view of one upper valve seal member 81A provided on the upper surface 41a of the rotary disk 40 according to this embodiment. As shown in FIG. 12, in this embodiment, it is assumed that the sliding resistance (friction coefficient) of the valve seal member 81 is large. The valve seal member 81 includes a plurality of curved portions and a plurality of inflection points where adjacent curved portions are connected to each other. The first groove inner convex portion 44 abuts against the inflection point vicinity portion except for the inflection points. That is, the valve seal member 81 includes the shear sliding portions A1 and A2, the inner peripheral sliding portion B1, and the outer peripheral sliding portion B2 as the curved portions, and includes a plurality of boundaries K1 as the inflection points. The first groove inner convex portion 44 abuts against the boundary vicinity portion (inflection point vicinity portion) M1 except for some of the boundaries K1. In particular, in this embodiment, the first groove inner convex portion 44 is provided in the boundary vicinity region M1 between the outer peripheral sliding portion B2 and each of the shear sliding portions A1, A2, and the first groove inner convex portion 44 is provided in the boundary K1 between the inner peripheral sliding portion B1 and each of the shear sliding portions A1, A2. In this embodiment, the first groove inner convex portion 44 is provided in the boundary K1 between the inner peripheral sliding portion B1 and each of the shear sliding portions A1, A2, but the first groove inner convex portion 44 can also be provided in the boundary vicinity region M1 away from these boundaries K1.

[0068] Although not shown and not described, the lower valve seal member 81B provided on the lower surface 41b of the rotary disk 40 is also provided with a drive deviation suppression structure similar to that of the upper valve seal member 81A.

[0069] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the second embodiment, the following actions and effects are obtained. That is, in the valve seal member 81, the first groove inner convex portion 44 abuts on the boundary vicinity portion M1 (inflection point vicinity portion) that is off the boundary K1 (inflection point) where the adjacent curved portions (the first shear sliding portion A1, the second shear sliding portion A2, the inner peripheral sliding portion B1, and the outer peripheral sliding portion B2) are connected to each other. Therefore, when the valve seal member 81 passes through the opening 20a of the inflow flow path 20 and the opening 70a of the fixed flow path 70 with the rotation of the rotary disk 40, stress concentration by the first groove inner convex portion 44 at the boundary K1 of the valve seal member 81 is suppressed. Therefore, the stress concentration of the valve seal member 81 can be reduced.

[0070] <Fourth embodiment> Next, the fourth embodiment will be described in detail with reference to FIG.

[0071] [Drive slippage prevention structure] This embodiment differs from the above-mentioned embodiments in terms of the "drive deviation suppression structure." Fig. 13 is an enlarged plan view of the first to third in-groove protrusions 44-46 provided as the drive deviation suppression structure 10 in a part of the assembly groove 41c (41d) of the rotary disk 40 in this embodiment. In this embodiment, the valve seal member 81 is pressed into the assembly groove 41c (41d) so that the valve seal member 81 is brought into contact with the outer circumferential side wall 41ca (41da) of the assembly groove 41c (41d) and is not brought into contact with the inner circumferential side wall 41cb (41db). Here, as shown in FIG. 13, for each groove protrusion 44-46, of the protrusion amount J1 of the outer peripheral side wall 41ca (41da) and the protrusion amount J2 of the inner peripheral side wall 41cb (41db), which does not come into contact with the valve seal member 81, the protrusion amount J2 of the inner peripheral side wall 41cb (41db) is greater than the protrusion amount J1 of the outer peripheral side wall 41ca (41da).

[0072] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of each of the above-mentioned embodiments, the following actions and effects can be obtained. That is, when the valve seal member 81 is assembled into the assembly groove 41c (41d), as shown in FIG. 13, the valve seal member 81 is in contact with the outer peripheral side wall 41ca (41da) of the assembly groove 41c (41d), so the surface pressure has already increased. For this reason, if the convex amount J1 of each groove inner convex portion 44-46 of the contacting outer peripheral side wall 41ca (41da) is set to be the same as the convex amount J2 of each groove inner convex portion 44-46 of the non-contacting inner peripheral side wall 41cb (41db), the surface pressure of the convex portion on the outer peripheral side wall 41ca (41da) side becomes excessive, which may lead to stress concentration. In this embodiment, by making the convex amount J2 on the non-contact side larger than the convex amount J1 on the contact side, the surface pressure can be made uniform between the outer peripheral side wall 41ca (41da) and the inner peripheral side wall 41cb (41db) of each groove inner convex portion 44-46.

[0073] <Fifth embodiment> Next, the fifth embodiment will be described in detail with reference to FIG.

[0074] [Drive slippage prevention structure] This embodiment differs from the fourth embodiment in the "drive deviation suppression structure." Fig. 14 is an enlarged plan view equivalent to Fig. 13 showing the first to third in-groove protrusions 44-46 provided as the drive deviation suppression structure 10 in the assembly groove 41c (41d) of the rotating disk 40 in this embodiment. In this embodiment, the valve seal member 81 is press-fitted into the assembly groove 41c (41d) so that the valve seal member 81 does not contact the outer circumferential side wall 41ca (41da) of the assembly groove 41c (41d) but contacts the inner circumferential side wall 41cb (41db). Here, as shown in FIG. 14, for each groove protrusion 44-46, of the protrusion amount J1 of the outer peripheral side wall 41ca (41da) and the protrusion amount J2 of the inner peripheral side wall 41cb (41db), the protrusion amount J1 of the outer peripheral side wall 41ca (41da), which does not come into contact with the valve seal member 81, is greater than the protrusion amount J2 of the inner peripheral side wall 41cb (41db).

[0075] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the above-mentioned embodiments, the following actions and effects can be obtained. That is, when the valve seal member 81 is assembled into the assembly groove 41c (41d), as shown in Fig. 14, the valve seal member 81 is in contact with the inner circumferential side wall 41cb (41db) of the assembly groove 41c, so that the surface pressure has already increased. Therefore, if the convex amount J2 of each of the groove inner convex portions 44-46 of the contacting inner circumferential side wall 41cb (41db) is set to be the same as the convex amount J1 of each of the groove inner convex portions 44-46 of the non-contacting outer circumferential side wall 41ca (41da), the surface pressure of the convex portion on the inner circumferential side wall 41cb (41db) side becomes excessive, which may lead to stress concentration. In this embodiment, by making the convex amount J1 on the non-contact side larger than the convex amount J2 on the contact side, it is possible to achieve uniform surface pressure between the outer circumferential side wall 41ca (41da) and the inner circumferential side wall 41cb (41db) of each groove convex portion 44-46.

[0076] Sixth Embodiment Next, the sixth embodiment will be described in detail with reference to FIGS.

[0077] [Drive slippage prevention structure] This embodiment differs from the third embodiment in the structure of the "driving deviation suppression structure." In each of the above-mentioned embodiments, when the valve seal member 81 is crushed by the groove inner protrusions 44-46, the outer periphery side of the valve seal member 81 escapes (expands) outward and the inner periphery side escapes (expands) inward. As a result, tensile stress acts on the outer periphery side and compressive stress acts on the inner periphery side. The groove inner protrusions 44-46 of the assembly grooves 41c, 41d press against the inner periphery side and the outer periphery side of the valve seal member 81, so that compressive stress acts on the inner periphery side. Therefore, on the inner periphery side of the valve seal member 81, the compressive stress by the groove inner protrusions 44-46 is added to the part where the compressive stress acts, so that the compressive stress is larger on the inner periphery side than on the outer periphery side. Therefore, in this embodiment, the "driving deviation suppression structure" is configured as follows.

[0078] Fig. 15 shows a bottom view of one lower valve seal member 81B provided on a part of the lower surface 41b of the rotary disc 40 according to this embodiment. Fig. 16 shows a cross-sectional view of the second groove protrusion 45 according to this embodiment taken along line CC in Fig. 15. Fig. 17 shows an enlarged bottom view of each of the groove protrusions 44-46 of the assembly groove 41d according to this embodiment.

[0079] In this embodiment, as shown in FIG. 15, the assembly groove 41d includes a plurality (four in this embodiment) of groove arc portions 41d1, 41d2, 41d3, 41d4 with different arc radii. Further, as shown in FIG. 17, each of the groove arc portions 41d1 to 41d4 includes an outer peripheral side wall 41da and an inner peripheral side wall 41db. The lower valve seal member 81B includes a first shear sliding portion A1, a second shear sliding portion A2, an inner peripheral sliding portion B1, and an outer peripheral sliding portion B2 that are fitted into the respective groove arc portions 41d1 to 41d4. These sliding portions A1, A2, B1, B2 correspond to an example of the "sealing arc portion" of this disclosed technology. As shown in FIGS. 16 and 17, each of the groove inner convex portions 44 to 46 includes an outer peripheral side convex portion 47 provided on the outer peripheral side wall 41da and an inner peripheral side convex portion 48 provided on the inner peripheral side wall 41db. And, as shown in FIG. 17, with respect to each of the groove inner convex portions 44 to 46, the lower valve seal member 81B is in contact with both the convex amount J1 of the outer peripheral side wall 41da and the convex amount J2 of the inner peripheral side wall 41db. The outer peripheral side convex portion 47 and the inner peripheral side convex portion 48 are such that the smaller the radii of the respective groove arc portions 41d1, 41d2, 41d3, 41d4 and the respective sliding portions A1, A2, B1, B2, the larger the convex amount J1 of the outer peripheral side convex portion 47 is than the convex amount J2 of the inner peripheral side convex portion 48. In this embodiment, each of the convex amounts J1 and J2 corresponds to an example of the "extra amount" of this disclosed technology.

[0080] Also, in this embodiment, the smaller the arc radii of the respective sliding portions A1, A2, B1, B2 of the lower valve seal member 81B, the greater the difference between the convex amount J1 of the outer peripheral side wall 41da and the convex amount J2 of the inner peripheral side wall 41db is set. That is, in FIG. 15, the outer peripheral sliding portion B2 is the "large diameter portion", the inner peripheral sliding portion B1 is the "medium diameter portion", and each of the shear sliding portions A1, A2 is the "small diameter portion". As shown in FIG. 17, the relationship between the convex amount J1 of the outer peripheral side convex portion 47 and the convex amount J2 of the inner peripheral side convex portion 48 provided thereon is as follows in "Equation 1" and "Equation 2".

[0081] Equation 1: J1 (small diameter portion) > J1 (medium diameter portion) > J1 (large diameter portion), J2 (small diameter portion) < J2 (medium diameter portion) < J2 (large diameter portion) Equation 2: J1 (small diameter portion) - J2 (small diameter portion) > J1 (medium diameter portion) - J2 (medium diameter portion) > J1 (large diameter portion) - J2 (large diameter portion)

[0082] Although not shown and not described, the assembly groove 41c and the upper valve seal member 81A provided on the upper surface 41a of the rotating disk 40 may also be provided with a drive deviation suppression structure similar to the assembly groove 41d and the lower valve seal member 81B.

[0083] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the third embodiment, the following actions and effects can be obtained. That is, each groove inner convex portion 44-46 includes an outer circumferential convex portion 47 and an inner circumferential convex portion 48, and the outer circumferential convex portion 47 and the inner circumferential convex portion 48 have a larger convex amount J1 of the outer circumferential convex portion 47 than a convex amount J2 of the inner circumferential convex portion 48 as the radius of the groove arc portions 41d1-41d4 and each sliding portion A1, A2, B1, B2 (seal arc portions) becomes smaller. Therefore, the valve seal member 81 is corrected for an imbalance between the compressive stress due to the inner circumferential convex portion 48 and the compressive stress due to the outer circumferential convex portion 47. Therefore, it is possible to further suppress the deviation (deviation) of the attitude of the valve seal member 81 due to the sliding when the rotating disk 40 rotates, and it is possible to ensure more uniform sealing performance and wear resistance over the entire circumference of the valve seal member 81.

[0084] Seventh embodiment Next, the seventh embodiment will be described in detail with reference to FIGS.

[0085] [Drive slippage prevention structure] This embodiment differs from the above-described embodiments in terms of the "drive slippage suppression structure." Fig. 18 shows an enlarged plan view or bottom view of the groove inner convex portions 44-46 of the assembly groove 41c (41d) as the drive slippage suppression structure in comparison with this embodiment. In the above-described embodiments, the drive slippage suppression structure 10 is configured as shown in Fig. 18 in order to suppress movement of the valve seal member 81 when it slides. That is, the groove inner convex portions 44-46 are provided in the assembly groove 41c (41d), and both side surfaces of the valve seal member 81 are sandwiched between the outer circumferential convex portion 47 and the inner circumferential convex portion 48. However, in the drive slippage suppression structure 10 of each of the above-described embodiments, in order to suppress movement due to sliding of the valve seal member 81 when the rotating disk 40 rotates, it is necessary to provide a large tightening margin by each of the protrusions 47, 48, and stress concentration cannot be avoided at all times in the portion surrounded by the dash-dotted circle S1 in FIG. 18, and the stress remains even when the rotating disk 40 is stopped. As a result, there was a concern that the valve seal member 81 would "sag." Therefore, in this embodiment, the "drive slippage suppression structure" is configured as follows.

[0086] Fig. 19 shows the seal side protrusions of the seal member as the drive slippage suppression structure in this embodiment in a plan view or bottom view equivalent to Fig. 18. In this embodiment, the drive slippage suppression structure 10 is configured with the seal side protrusions 81b provided on the side surface of the valve seal member 81 so as to press the side walls of the assembly groove 41c (41d), i.e., the outer circumferential side wall 41ca (41da) and the inner circumferential side wall 41cb (41db), as shown in Fig. 19. In addition, in this embodiment, the side walls of the assembly groove 41c (41d) are provided with groove side recesses 41g corresponding to the seal side protrusions 81b.

[0087] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the above-mentioned embodiments, the following actions and effects can be obtained. That is, the drive deviation suppression structure 10 is composed of the seal side protrusion 81b provided so as to press the side walls of the assembly grooves 41c, 41d on the side surface of the valve seal member 81. Therefore, the drive deviation suppression structure 10 can be realized with an extremely simple structure, and the deviation (deviation) of the attitude of the valve seal member 81 can be suppressed, and when the rotating disk 40 rotates in one direction, the stress concentration on the other direction side of the seal side protrusion 81b can be suppressed.

[0088] 18, the valve seal member 81 is sandwiched between the outer circumferential convex portion 47 and the inner circumferential convex portion 48, so that stress concentration occurs constantly in the valve seal member 81. That is, when the rotating disc 40 rotates in the counterclockwise direction Y1, when it rotates in the clockwise direction Y2, and even when it is stopped, stress concentration occurs in the portion of the valve seal member 81 sandwiched between the two convex portions 47, 48.

[0089] In contrast, in this embodiment, the seal side convex portion 81b and the groove side concave portion 41g are provided as the drive deviation suppression structure 10, so that when the rotating disk 40 rotates in the counterclockwise direction Y1 or the clockwise direction Y2, stress concentration occurs only on the side in the rotation direction, and no stress concentration occurs on the side opposite to the rotation direction, and no stress concentration occurs even when the rotating disk 40 is stopped. For example, as shown in Fig. 19, when the rotating disk 40 rotates in the counterclockwise direction Y1, stress concentration occurs in the portion surrounded by the dashed dotted circle S3 on the rotation direction side, but no stress concentration occurs in the portion surrounded by the dashed dotted circle S2 on the opposite side to the rotation direction.

[0090] Eighth embodiment Next, the eighth embodiment will be described in detail with reference to FIGS.

[0091] [Drive slippage prevention structure] This embodiment differs from the second embodiment in the "drive deviation suppression structure." In the second embodiment, as shown in Fig. 10, the third groove convex portion 46 is provided between each rotation tip portion P1, P2 and the first groove convex portion 44 at each shear sliding portion A1, A2, but this configuration alone cannot completely suppress the movement of the valve seal member 81 at each shear sliding portion A1, A2. Therefore, in this embodiment, the third groove convex portion 46 is configured as follows.

[0092] Fig. 20 is a schematic diagram showing a part of the mounting groove 41c provided on the upper surface 41a of the rotary disk 40 and a part of the upper valve seal member 81A to be mounted therein. Fig. 21 is a cross-sectional view of the mounting groove 41c taken along line DD in Fig. 20 according to this embodiment. Fig. 22 is a cross-sectional view of the mounting groove 41c taken along line EE in Fig. 20 according to this embodiment. Fig. 23 is a cross-sectional view of the mounting groove 41c taken along line FF in Fig. 20.

[0093] In this embodiment, in each of the shear sliding regions A1 and A2, a gap g1 is provided between the upper valve seal member 81A and the assembly groove 41c only on the outer peripheral side wall 41ca side of the assembly groove 41c, and no gap is provided on the inner peripheral side wall 41cb. In FIG. 20, the thick line indicates the inner shape of the assembly groove 41c, and the solid line indicates the inner shape of the assembly groove 41c when it has a certain width "L1". This width L1 is the reference width of the width of the assembly groove 41c, and is the same as the width of the assembly groove 41c of the outer peripheral sliding region B2. "L2" indicates the width of the part of the first shear sliding region A1 other than the third groove inner convex portion 46. That is, in this embodiment, the width L2 of the assembly groove 41c corresponding to each of the shear sliding regions A1 and A2 is enlarged more than the width L1 of the assembly groove 41c corresponding to the outer peripheral sliding region B2, and the enlarged portion is provided on the outer peripheral side wall 41ca side of the assembly groove 41c. Here, by providing the groove protrusions 44, 46 at the shear sliding sites A1, A2, the escape area of ​​the upper valve seal member 81A is further reduced when compressive stress acts on the upper valve seal member 81A. Therefore, the expansion margin of the width L2 of the outer peripheral side wall 41ca of the assembly groove 41c (which is also the size of the gap g1) is set to increase as the distance between the first groove protrusion 44 and the third groove protrusion 46 decreases.

[0094] Here, when the rotary disk 40 rotates clockwise Y2 (see FIG. 20), the compressive stress of the upper valve seal member 81A is concentrated on the left side (the side of the outer peripheral side wall 41ca of the assembly groove 41c) in FIG. 21 to FIG. 23. Therefore, by providing the gaps g1 and g2 on the side of the outer peripheral side wall 41ca, the compressed upper valve seal member 81A can be provided with an escape route, and the stress concentration of the upper valve seal member 81A can be suppressed. Furthermore, by providing the groove protrusions 44 and 46 in the assembly groove 41c, the escape route of the upper valve seal member 81A is further reduced, so that, as shown in FIG. 22 and FIG. 23, the gap g1 between the groove protrusions 44 and 46 with a shorter distance to the adjacent protrusions is larger than the gap g2 between the groove protrusions 44 and 46 with a longer distance to the adjacent protrusions.

[0095] Although not shown and not described, the lower valve seal member 81B provided on the lower surface 41b of the rotary disk 40 is also provided with a drive deviation suppression structure similar to that of the upper valve seal member 81A.

[0096] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the second embodiment, the following actions and effects can be obtained. That is, gaps g1 and g2 are provided between the valve seal member 81 and the assembly grooves 41c and 41d, and the gaps g1 and g2 on the outer periphery side are larger than the gap on the inner periphery side. Therefore, even if stress is concentrated on the outer periphery side of the assembly grooves 41c and 41d when the rotary disk 40 rotates or when the valve seal member 81 passes through the opening 20a of the inflow flow path 20 and the opening 70a of the fixed flow path 70, the gaps g1 and g2 on the outer periphery side are larger than the gap on the inner periphery side, so that the gaps g1 and g2 on the outer periphery side provide more escape routes for the valve seal member 81. As a result, when the rotating disk 40 rotates or when the valve seal member 81 passes through the opening 20a of the inlet passage 20 and the opening 70a of the fixed passage 70, the deformation caused by the groove protrusions 44-46 of the valve seal member 81 can be released to a greater extent into the gaps g1, g2 on the outer periphery, thereby suppressing stress concentration in the valve seal member 81.

[0097] In this embodiment, gaps g1, g2 are provided only in the outer peripheral side walls 41ca, 41da between the valve seal member 81 corresponding to each shear sliding portion A1, A2 and the assembly grooves 41c, 41d, but gaps can also be provided in both the outer peripheral side walls 41ca, 41da and the inner peripheral side walls 41cb, 41db between the valve seal member 81 corresponding to each shear sliding portion A1, A2 and the assembly grooves 41c, 41d.

[0098] <Ninth embodiment> Next, the ninth embodiment will be described in detail with reference to FIGS.

[0099] [Drive slippage prevention structure] This embodiment is different from the third embodiment in the structure of the "driving deviation suppression structure". Figures 24 and 25 show cross-sectional views of the first shear sliding portion A1 of the lower valve seal member 81B and the corresponding mounting groove 41d, the fixed disk 50, and a part of the opening of the fixed flow passage 70 formed therein. Figure 24 shows a case where the rotary disk 40 rotates counterclockwise Y1 and the first shear sliding portion A1 of the lower valve seal member 81B rides up from the opening of the fixed flow passage 70 onto the upper surface 51a of the fixed disk 50, and Figure 25 shows a case where the rotary disk 40 rotates clockwise Y2 and the first shear sliding portion A1 of the lower valve seal member 81B rides up from the opening of the fixed flow passage 70 onto the upper surface 51a of the fixed disk 50. FIG. 26 is a schematic diagram showing, in this embodiment, the first shear sliding portion A1 (shown by a thick two-dot chain line) moving in the counterclockwise direction Y1 and the first shear sliding portion A1 (shown by a thick solid line) moving in the clockwise direction Y2, as they each ride up from the opening of the fixed flow path 70 onto the upper surface 51a of the fixed disk 50.

[0100] In the eighth embodiment, the gaps g1, g2 are provided between the valve seal member 81 and the assembly grooves 41c, 41d at each of the shear sliding sites A1, A2 so that they are larger on the outer circumferential side than on the inner circumferential side. In contrast, in this embodiment, the edge portions 41e (shown by solid lines in Figs. 24 and 25) of the outer circumferential side walls at positions (positions corresponding to each of the shear sliding sites A1, A2) of the assembly grooves 41c, 41d that intersect with the rotation direction (driving direction) of the rotary disk 40 are formed to have a larger R shape (curved shape having a large radius) or tapered shape than the edge portions 41f (shown by two-dot chain lines in Figs. 24 and 25) at other positions of the assembly groove 41d. This configuration of the edge portions 41e of the outer circumferential side walls provides each of the shear sliding sites A1, A2 with a place to escape from stress concentration.

[0101] Fig. 27 is a schematic bottom view showing the first shear sliding portion A1 of the lower valve seal member 81B and the corresponding portion of the assembly groove 41d according to this embodiment. As shown in Fig. 27, in the portion of the assembly groove 41d corresponding to the first shear sliding portion A1, a gap g3 between the outer circumferential wall of the portion and the lower valve seal member 81B is formed so as to gradually expand toward the rotation tip TP.

[0102] Although not shown and not described, the upper valve seal member 81A provided on the upper surface 41a of the rotary disk 40 is also provided with a drive deviation suppression structure similar to that of the lower valve seal member 81B.

[0103] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the effects and advantages of the eighth embodiment, the following effects and advantages are obtained. That is, the edge 41e of the outer circumferential side wall of the assembly grooves 41c, 41d at the position intersecting the rotation direction of the rotary disk 40 has a larger R shape or tapered shape than the edge 41f at other positions. Therefore, when the valve seal member 81 rides from the opening 20a of the inflow flow path 20 and the opening 70a of the fixed flow path 70 onto the inner surface 11a of the housing and the upper surface 51a (sliding surface) of the fixed disk, the valve seal member 81 is allowed to escape more by the larger R shape or tapered shape of the edge 41e of the outer circumferential side wall of the assembly grooves 41c, 41d. Therefore, the stress concentration of the valve seal member 81 can be further suppressed.

[0104] 24, when the rotating disk 40 rotates in the counterclockwise direction Y1, the lower valve seal member 81B engages with the inner peripheral side wall 41db of the assembly groove 41d and moves in the counterclockwise direction Y1, so that a tensile stress (stress that reduces the diameter of the lower valve seal member 81B) acts on the lower valve seal member 81B. At this time, since the diameter of the lower valve seal member 81B is reduced, an escape route for the stress concentration when the lower valve seal member 81B rides up from the fixed flow path 70 onto the upper surface 51a of the fixed disk 50 is not required.

[0105] On the other hand, as shown in Fig. 25, when the rotary disk 40 rotates in the clockwise direction Y2, the lower valve seal member 81B engages with the outer peripheral side wall 41da of the assembly groove 41d and moves in the clockwise direction Y2, so that a compressive stress (stress that expands the diameter of the lower valve seal member 81B) acts on the lower valve seal member 81B. Therefore, when the lower valve seal member 81B rides up from the fixed flow path 70 onto the upper surface 51a of the fixed disk 50, the escape route of the lower valve seal member 81B is reduced, and stress concentration occurs in the lower valve seal member 81B. In this embodiment, as shown in Fig. 25, the edge portion 41e of the outer peripheral side wall of the outer peripheral side wall 41da has a larger R shape or tapered shape than the edge portion 41f at other positions, so that an escape route can be provided for the lower valve seal member 81B, and stress concentration can be suppressed.

[0106] Tenth embodiment Next, the tenth embodiment will be described in detail with reference to FIGS.

[0107] [Drive slippage prevention structure] This embodiment is different from the above-mentioned embodiments in the point of "driving deviation suppression structure". FIG. 28 shows one valve seal member 81 provided on the rotary disk 40 of each of the above-mentioned embodiments in a plan view or a bottom view as a comparison of this embodiment. For convenience, FIG. 28 shows only the shape of the valve seal member 81 in a plan view, and omits the illustration of the assembly groove 41c (41d). As shown in FIG. 28, the rotary disk 40 is configured to be rotatably driven around the rotary shaft 42. The valve seal member 81 is composed of a "rotation line portion" along the rotation direction (counterclockwise Y1, clockwise Y2) of the rotary disk 40 and a "rotation intersection portion" intersecting the rotation direction. Here, the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2 already described correspond to an example of the "rotation line portion", and the first shear sliding portion A1 and the second shear sliding portion A2 already described correspond to an example of the "rotation intersection portion". The inner peripheral sliding portion B1 corresponds to an example of an "inner rotational line portion" close to the rotation center of the rotating disc 40, and the outer peripheral sliding portion B2 corresponds to an example of an "outer rotational line portion" far from the rotation center.

[0108] In this comparison, the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2 are curved with the same curvature as the rotation locus X of the rotating disk 40. Therefore, at the inflection points Q1, Q2, Q3, and Q4, which are the connection points of the adjacent sliding portions A1, A2, B1, and B2, the locus directions of the shear sliding portions A1 and A2 are reversed, and especially at the inflection points Q1 and Q2, a stress acts in the upward direction U1 due to the curved locus H1 of the shear sliding portions A1 and A2, and a stress acts in the downward direction D1 due to the curved locus H2 of the inner peripheral sliding portion B1, and bending stress acts on the inflection points Q1 and Q2. Therefore, in this embodiment, in order to suppress the bending stress at the inflection points Q1 and Q2, the inflection points Q1 and Q2 are configured as follows.

[0109] Fig. 29 shows one valve seal member 81 provided on the rotating disc 40 according to this embodiment in a plan view or a bottom view equivalent to Fig. 28. In this embodiment, the curvature of the curved locus H3 of the inner peripheral sliding part B1 is set to be smaller than the curvature of the rotation locus of the rotating disc 40, i.e., the curvature of the curved locus H2 of the comparative example.

[0110] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of each of the above-mentioned embodiments, the following actions and effects can be obtained. That is, among the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2 and the first shear sliding portion A1 and the second shear sliding portion A2 constituting the valve seal member 81, the curvature of the inner peripheral sliding portion B1 is smaller than the curvature of the rotation trajectory of the rotating disk 40, so that the stress action at the boundary portion between the inner peripheral sliding portion B1 and each of the shear sliding portions A1 and A2 becomes almost horizontal. Therefore, it is possible to suppress the bending stress concentration at the boundary portion between the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2 of the valve seal member 81 and each of the shear sliding portions A1 and A2 that occurs when the rotating disk 40 rotates.

[0111] <Another embodiment> The disclosed technology is not limited to the above-described embodiments, and may be implemented by appropriately modifying part of the configuration without departing from the spirit of the disclosed technology.

[0112] (1) In each of the above embodiments, the valve body portion 12 of the flow path switching device 1 is provided with the rotating disk 40 that rotates about the rotation axis 42, and the fixed disk 50 that is fixed to the lower housing 11B. However, the fixed disk may be omitted from the valve body portion, and only a rotating disk that rotates about the rotation axis may be provided.

[0113] (2) In each of the above embodiments, the valve seal members 81 (upper valve seal member 81A and lower valve seal member 81B) are fixed to the upper and lower surfaces of the rotating disk 40, respectively, and are provided so as to be slidable relative to the inner surfaces of the upper housing 11A and the fixed disk 50. However, the valve seal members may be fixed to the housing and provided so as to be slidable relative to the rotating disk.

[0114] (3) In each of the above embodiments, the valve body is configured as a rotating disk that rotates relative to the housing. However, the valve body may also be configured as a moving member that moves linearly relative to the housing.

[0115] (4) In each of the above embodiments, the flow path switching device 1 is embodied as a six-way valve. However, the present invention is not limited to this and may be embodied as other multi-way valves such as a three-way valve or a four-way valve.

[0116] (5) In each of the above embodiments, a rotary flow path 60 penetrating in the thickness direction of the rotating disk 40, which is the “valve body portion,” is provided as a “communicating passage.” However, it is also possible to provide a communicating passage that does not penetrate the valve body portion in the thickness direction.

[0117] (6) In each of the above embodiments, the valve seal member 81 is an O-ring having an O-shaped cross section. However, the cross section of the valve seal member can also be configured in various shapes such as diamond, square, hollow, or mountain-shaped. [Industrial Applicability]

[0118] The disclosed technology can be utilized, for example, to switch the flow path of a liquid in a liquid circuit through which a liquid such as a coolant flows. [Explanation of symbols]

[0119] 1 Flow path switching device 10 Drive slippage prevention structure 11 Housing (stator) 20 Inlet passage (connection passage) 30 Outlet passage (connection passage) 40 Rotating disc (valve body) 41c Assembly groove 41ca Outer wall 41cb Inner side wall 41d Assembly groove 41d1 Groove arc section 41d2 Groove arc section 41d3 Groove arc section 41d4 Groove arc section 41da Outer wall 41db Inner wall 41e Edge 41f Edge (other positions) 42 Rotation axis 44 First groove inner convex portion (convex portion) 45 Convex part in second groove (convex part) 46 Third groove inner convex part (convex part) 47 Outer circumferential convex part 48 Inner circumferential convex part 50 Fixed disk (stator) 60 Rotational passage (connecting passage) 70 Fixed passage (connecting passage) 81 Valve seal member (sealing means) 81b Seal side protrusion A1 First shear sliding part (seal arc part, rotation intersection part) A2 Second shear sliding area (seal arc, rotation intersection area) B1 Inner sliding parts (seal arc, rotating line part, inner rotating line part) B2 Outer peripheral sliding parts (seal arc part, rotating line part, outer rotating line part) g1~g3 Gap J1 Outer circumference protrusion amount (extrusion allowance) J2 Inner circumference protrusion amount (extrusion allowance) K1 Boundary (Inflection Point) Area near the M1 boundary (area near the inflection point)

Claims

1. At least one stator; A valve body that moves relative to the stator; the stator and the valve body each include at least one communication passage; an annular seal means provided between the stator and the valve body, the annular seal means sliding against the stator or the valve body as the valve body is driven; Equipped with a flow passage switching device configured to selectively connect the communication passage of the valve body and the communication passage of the stator by driving the valve body, thereby switching and forming a series of flow passages, the valve body or the stator includes an assembly groove for assembling the sealing means, The sealing means is assembled into the assembly groove by fitting, and in this assembled state, a drive displacement suppression structure is provided between the sealing means and a side wall of the assembly groove for suppressing displacement of the sealing means due to sliding when the valve body is driven. A flow path switching device.

2. The flow path switching device according to claim 1 , The drive deviation suppression structure is a protrusion provided on the side wall of the assembly groove and abuts against the sealing means so as to sandwich the sealing means from the inside and outside. A flow path switching device.

3. The flow path switching device according to claim 2, The sealing means includes a plurality of curved portions and a plurality of inflection points where adjacent curved portions are connected to each other, The protruding portion comes into contact with a portion near the inflection point that is not at the inflection point. A flow path switching device.

4. The flow path switching device according to claim 3, The assembly groove includes a groove arc portion and an outer peripheral side wall and an inner peripheral side wall, the sealing means includes a seal arc portion that is fitted into the groove arc portion, the protrusion includes an outer circumferential side protrusion provided on the outer circumferential side wall and an inner circumferential side protrusion provided on the inner circumferential side wall, The smaller the radius of the groove arc portion and the seal arc portion, the larger the projection allowance of the outer circumferential convex portion and the inner circumferential convex portion is. A flow path switching device.

5. The flow path switching device according to claim 1 , The drive deviation suppression structure is a seal-side protrusion provided on a side surface of the seal means so as to press against the side wall of the assembly groove. A flow path switching device.

6. 6. The flow path switching device according to claim 1, A gap is provided between the sealing means and the assembly groove, The gap on the outer circumference is larger than the gap on the inner circumference. A flow path switching device.

7. 7. The flow path switching device according to claim 6, The edge of the assembly groove at a position intersecting the drive direction of the valve body has a larger R shape or tapered shape than the edge at other positions. A flow path switching device.

8. 6. The flow path switching device according to claim 1, The valve body is configured to be rotatably driven around a rotation axis, The sealing means includes a rotation line portion along a rotation direction of the valve body and a rotation intersection portion intersecting the rotation direction, the rotational line portion includes an inner rotational line portion close to a rotation center of the valve body and an outer rotational line portion far from the rotation center, The curvature of the inner rotational path portion is smaller than the curvature of the rotational path of the valve body. A flow path switching device.

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