Flow path switching device

Abstract

A flow path switching device (1) includes a rotary disk (40) and a fixed disk (50) inside a housing (11). The housing, the fixed disk and the rotary disk include a plurality of communication passages (20, 30, 60, 70), and an annular valve seal member (81) is provided between the rotary disk, the housing, and the fixed disk. The rotary disk is rotated, and the communication passage (60) thereof and the communication passages (20, 30, 70) of the housing and the fixed disk are connected to selectively switch and form a plurality of flow paths. The rotary disk includes assembly grooves (41c, 41d) for assembling the valve seal member. The valve seal member is provided with a drive displacement suppression structure 10, between the valve seal member and the side walls of the assembly grooves, for suppressing displacement due to sliding of the valve seal member during driving of the rotary disk in a state in which the valve seal member is assembled to the assembly grooves.

Description

Flow path switching device

[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.

[0002] A conventional flow path switching device of this type is described in, for example, Patent Document 1 below. 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 to divide the interior 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 that can close the communication passages 75a, 75b.

[0003] Japanese Patent Application Laid-Open No. 2022-21966

[0004] In the device described in Patent Document 1, it is conceivable to provide sealing members around the communicating passages 75a and 75b between the fixed disk 75 and the drive disk 74. In this case, when the drive disk 74 is rotated to switch the communication between the communicating passages 75a and 75b, the edges of the communicating passages 75a and 75b or the edges of the drive disk 74 cross the sealing members with high surface pressure. In this case, sliding wear occurs in the sealing members, or the sealing members become biased (misaligned) in the opposite direction of the sliding direction, which may cause uneven sealing surface pressure by the sealing members and deteriorate sealing performance and wear resistance.

[0005] 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 varies 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 lead to 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.

[0007] (1) In order to achieve the above object, one aspect of the technology disclosed in the present application is a flow path switching device comprising at least one stator, a valve element that moves relative to the stator, the stator and the valve element each including at least one communicating passage, and an annular sealing means that is provided between the stator and the valve element and slides against the stator or the valve element as the valve element is driven, and configured to selectively connect the communicating passage of the valve element and the communicating passage of the stator by driving the valve element, thereby switching and forming a series of flow paths, wherein the valve element 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 displacement suppression structure is provided between the sealing means and a side wall of the assembly groove to suppress displacement due to sliding of the sealing means when the valve element is driven.

[0008] According to the above configuration (1), a drive slippage prevention structure is provided between the sealing 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 prevention structure prevents slippage due to sliding of the sealing means.

[0009] (2) In order to achieve the above object, in the configuration of (1) above, it is preferable that the drive deviation suppression structure is a convex portion provided on the side wall of the assembly groove and abutting against the sealing means so as to sandwich the sealing means from the inside and outside.

[0010] According to the above configuration (2), in addition to the effect of the above configuration (1), the drive deviation suppression structure is formed by the protrusions that sandwich the sealing means from the inside and outside on the side walls of the assembly groove.

[0011] (3) In order to achieve the above object, in the configuration of (2) above, it is preferable that the sealing means includes a plurality of curved portions and a plurality of inflection points where adjacent curved portions are connected, and that the convex portion abuts against a portion near the inflection points but away from the inflection points.

[0012] According to the configuration (3) above, in addition to the effect of the configuration (2) above, the convex portion of the sealing means abuts on a portion of the sealing means near the inflection point, away from the inflection point where adjacent curved portions are connected, thereby suppressing stress concentration due to the convex portion at the inflection point of the sealing means when the sealing means passes through the opening of the communicating passage as the valve disc is driven.

[0013] (4) To achieve the above object, in the configuration of (3) above, the assembly groove includes a groove arc portion and also includes 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 convex portion provided on the outer peripheral side wall and an inner peripheral side convex portion provided on the inner peripheral side wall, and it is preferable that 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 above-mentioned configuration (4), in addition to the effect of the above-mentioned configuration (3), the convex portions include outer and inner convex portions, and the smaller the radii of the groove arc portion and the seal arc portion, the larger the projection allowance of the outer convex portion is compared to the projection allowance of the inner convex portion. Therefore, the sealing means corrects the imbalance between the compressive stress caused by the inner convex portion and the compressive stress caused by the outer convex portion.

[0015] (5) In order to achieve the above object, in the configuration of (1) above, it is preferable that the drive deviation suppression structure is a seal-side convex portion provided on the side surface of the sealing means and configured to press against the side wall of the assembly groove.

[0016] According to the configuration (5) above, in addition to the effect of the configuration (1) above, the drive deviation suppression structure is configured by a seal-side protrusion provided on the side surface of the sealing means so as to press against the side wall of the assembly groove.

[0017] (6) In order to achieve the above object, in any of the configurations (1) to (5) above, a gap is provided between the sealing means and the assembly groove, and it is preferable that the gap on the outer periphery is larger than the gap on the inner periphery.

[0018] According to the configuration (6), in addition to the effects of any of the configurations (1) to (5), a gap is provided between the sealing means and the assembly groove, and the gap on the outer periphery is larger than the gap on the inner periphery. Therefore, even if stress concentrates on the outer periphery of the assembly groove when the valve disc is driven or the sealing means passes through the opening of the communicating passage, the gap on the outer periphery is larger than the gap on the inner periphery, so the gap on the outer periphery provides more escape routes for the sealing means.

[0019] (7) In order to achieve the above object, in the configuration of (6) above, it is preferable that 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 (7) above, in addition to the effect of the configuration (6) above, 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 edge at other positions. Therefore, when the sealing means moves from the opening of the communicating passage onto the sliding surface of the valve disc, the sealing means is allowed to escape more to the extent that the edge of the assembly groove has a larger R-shape or tapered shape.

[0021] (8) In order to achieve the above object, in any of the configurations (1) to (5) above, the valve body is configured to be rotatable around a rotation axis, and the sealing means comprises a rotational line portion along the rotation direction of the valve body and a rotational intersection portion intersecting the rotation direction, and the rotational line portion includes an inner rotational line portion close to the rotation center of the valve body and an outer rotational line portion far from the rotation center, and it is preferable that the curvature of the inner rotational line portion is smaller than the curvature of the rotation trajectory of the valve body.

[0022] According to the configuration (8) above, in addition to the effect of any of the configurations (1) to (5) above, among the rotational line portions (including the inner rotational line portion and the outer rotational line portion) and the rotational intersection portion that constitute the sealing means, the curvature of the inner rotational line portion is smaller than the curvature of the rotational trajectory of the valve body, so that the stress action at the boundary between the inner rotational line portion and the rotational intersection portion becomes approximately horizontal.

[0023] According to the above configuration (1), it is possible to suppress deviation (misalignment) of the position of the sealing means due to sliding when the valve body 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 configuration (2) above, in addition to the effect of the configuration (1) above, a drive deviation suppression structure can be realized with an extremely simple structure, and deviation (deviation) of the position 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 all around the sealing means.

[0025] According to the above-mentioned configuration (3), in addition to the effect of the above-mentioned configuration (2), it is possible to reduce the stress concentration on the sealing means.

[0026] According to the configuration (4) above, in addition to the effect of the configuration (3) above, it is possible to further suppress deviation (misalignment) 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 configuration (5) above, in addition to the effect of the configuration (1) above, a drive deviation suppression structure can be realized with an extremely simple structure, and deviation (deviation) of the posture of the sealing means can be suppressed. Furthermore, when the valve body is driven in one direction, stress concentration on the other side of the seal-side convex portion can be suppressed.

[0028] According to the configuration (6) above, in addition to the effect of any of the configurations (1) to (5) above, when the valve body is driven or when 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 above configuration (7), in addition to the effect of the above configuration (6), stress concentration on the sealing means can be further suppressed.

[0030] According to the configuration (8) above, in addition to the effect of any of the configurations (1) to (5) described above, it is possible to suppress stress concentration at the boundary between the rotational line portion and the rotation tolerance portion of the sealing means that occurs when the valve body is driven.

[0031] 1 is a perspective view showing an appearance of a flow path switching device according to the first embodiment; an exploded perspective view showing a flow path switching device according to the first embodiment; a cross-sectional view showing a flow path switching device according to the first embodiment; a plan view showing an upper surface of a rotating disk according to the first embodiment; a plan view showing an upper surface of a fixed disk according to the first embodiment; an image diagram showing a flow path pattern A according to the first embodiment; an image diagram showing a flow path pattern B according to the first embodiment; a plan view showing one upper valve seal member provided on a part of the upper surface of the rotating disk and a part of an upper housing according to a comparative example of the first embodiment; a plan view equivalent to FIG. 8 showing one 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 the first embodiment; a plan view equivalent to FIG. 8 showing one 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 second embodiment; 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 the rotating disk and a part of the upper housing according to a comparative example of a third embodiment. 15A and 15B are plan views showing one valve seal member provided on a portion of the upper surface of the rotating disk according to a third embodiment; a plan view showing an enlarged view of first to third in-groove protrusions provided as a drive slippage suppression structure in a portion of the assembly groove of the rotating disk according to a fourth embodiment; a plan view similar to FIG. 13 showing an enlarged view of first to third in-groove protrusions provided as a drive slippage suppression structure in a portion of the assembly groove of the rotating disk according to a fifth embodiment; a bottom view showing one lower valve seal member provided on a portion of the lower surface of the rotating disk according to a sixth embodiment; a cross-sectional view taken along line CC in FIG. 15A showing a cutaway view of a second in-groove protrusion in the sixth embodiment; a bottom view showing an enlarged view of each in-groove protrusion in the assembly groove according to the sixth embodiment; and a plan view or bottom view showing an enlarged view of each in-groove protrusion in the assembly groove as a drive slippage suppression structure according to a comparative example of the seventh embodiment. 18 , showing the seal-side protrusions of the seal member as a drive misalignment suppression structure according to the seventh embodiment. A schematic diagram showing a part of an assembly groove provided on the upper surface of a part of a rotary disk and a part of an upper valve seal member assembled thereto according to the eighth embodiment. A cross-sectional view taken along line D-D in FIG. 20 , showing the assembly groove according to the eighth embodiment. A cross-sectional view taken along line E-E in FIG. 20 , showing the assembly groove according to the eighth embodiment. A cross-sectional view taken along line F-F in FIG. 20 , showing the assembly groove according to the eighth embodiment.11A and 11B are cross-sectional views showing the first shear sliding portion of the lower valve seal member and the corresponding assembly groove portion, and the fixed disk and a portion of the opening of the fixed flow path formed therein when the rotating disk is rotating counterclockwise, according to the ninth embodiment; 12A and 12B are cross-sectional views showing the first shear sliding portion of the lower valve seal member and the corresponding assembly groove portion, and the fixed disk and a portion of the opening of the fixed flow path formed therein when the rotating disk is rotating clockwise, according to the ninth embodiment; 13A and 13B are schematic views showing the first shear sliding portion (indicated by a thick two-dot chain line) moving counterclockwise and the first shear sliding portion (indicated by a thick solid line) moving clockwise, respectively, riding up from the opening of the fixed flow path onto the upper surface of the fixed disk, according to the ninth embodiment; 14A and 14B are bottom views showing the first shear sliding portion of the lower valve seal member and the corresponding assembly groove portion, according to the ninth embodiment; 15A and 15B are plan and bottom views showing one valve seal member provided on the rotating disk of each embodiment, as a comparative example of the tenth embodiment; FIG. 29 is a plan view or bottom view equivalent to FIG. 28 showing one valve seal member provided on the rotary disk in the tenth embodiment.

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

[0033] First Embodiment A first embodiment will be described in detail with reference to FIGS. 1 to 11. FIG.

[0034] [Overview of the flow path switching device] Fig. 1 is a perspective view showing the appearance of a flow path switching device 1 of this embodiment. Fig. 2 is an exploded perspective view of the flow path switching device 1 of this embodiment (the drive unit 13 is not shown). Fig. 3 is a cross-sectional view of the flow path switching device 1 of this embodiment (the drive unit 13 is not shown). As shown in Figs. 1 to 3, the flow path switching device 1 includes a housing 11, a valve body unit 12, and a drive unit 13.

[0035] [Regarding the Housing] As shown in FIGS. 1 to 3 , the housing 11 is formed by fastening an upper housing 11A and a lower housing 11B together with a plurality of screws 16. The housing 11 includes an inflow channel 20 through which liquid flows in and an outflow channel 30 through which liquid flows out. In this embodiment, the flow path switching device 1 is configured as a six-way valve, for example. The housing 11 has three inflow channels 20 and three outflow channels 30. As the three inflow channels 20, a first inflow channel 21, a second inflow channel 22, and a third inflow channel 23 are provided in the upper housing 11A. As shown in FIG. 3 , an opening 20a is provided at one end of the inflow channel 20 facing the rotary disk 40, which will be described later, and which can communicate with a rotary channel 60, which will be described later. As the three outflow channels 30, a first outflow channel 31, a second outflow channel 32, and a third outflow channel 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 technology disclosed herein. The inlet flow passages 20 (first inlet flow passage 21, second inlet flow passage 22, and third inlet flow passage 23) and the outlet flow passages 30 (first outlet flow passage 31, second outlet flow passage 32, and third outlet flow passage 33) correspond to an example of a "communication passage" in the technology disclosed herein.

[0037] [Regarding the Valve Disk] The valve disk 12 is provided inside the housing 11. As shown in Figures 2 and 3, the valve disk 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 rotation 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. The fixed disk 50 also constitutes a part of a "stator" in the technology disclosed herein.

[0039] [Regarding the Rotating Disk] FIG. 4 shows a plan view of the upper surface of the rotating disk 40 according to this embodiment. As shown in FIGS. 2 to 4, the rotating disk 40 is disposed between the upper housing 11A and the fixed disk 50. The rotating disk 40 includes a disk portion 41 and a rotating shaft 42. The rotating disk 40 (disk portion 41) is formed in a disk shape and includes multiple rotary flow paths 60. These rotary flow paths 60 penetrate the rotating disk 40 in the thickness direction (axial direction) and extend along the plate surface direction. The rotary flow paths 60 can also communicate with the inlet flow path 20 and the fixed flow path 70, which will be described later. In this embodiment, the rotating 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 rotating disk 40 in the shape of curved elongated holes ("cocoon-shaped") in a plan view. These rotary flow paths 60 (first rotary flow path 61, second rotary flow path 62, and third rotary flow path 63) correspond to an example of a "communication path" in the technology disclosed herein.

[0040] [Regarding the Rotating Shaft] The rotating shaft 42 is connected at one axial end to the rotating disk 40 (disk portion 41) and at the other axial end to the driving unit 13. The rotating shaft 42 is formed integrally with the disk portion 41 so 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, causing the rotating disk 40 to rotate.

[0041] [Regarding the Fixed Disk] Figure 5 shows a plan view of the upper surface of the fixed disk 50 according to this embodiment. As shown in Figures 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. Retaining springs 82 are provided between the fixed disk 50 and the lower housing 11B to urge and retain the fixed disk 50 toward the rotary disk 40. The retaining springs 82 are arranged on the lower surface of the fixed disk 50 so as to encompass each of the cylindrical portions 52.

[0042] The disk portion 51 is formed in a disk shape and includes fixed flow passages 70 that penetrate 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 arranged at equal angular intervals from one another. 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, one for each of 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 rotary disk 40.

[0044] [Regarding 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 rotary shaft 42 .

[0045] The flow path switching device 1 configured as described above forms a flow path through which a liquid flows by connecting the inflow flow path 20, the rotary flow path 60, and the fixed flow path 70 (outflow flow path 30). The flow path switching device 1 then rotates the rotary disk 40 via the rotation shaft 42 using the drive unit 13, and switches the combination of connections between the three rotary 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). By this switching, the flow path switching device 1 switches the flow path of the liquid between several patterns.

[0046] [Regarding Flow Path Pattern] For example, as shown in Fig. 6, the flow path switching device 1 has three rotary flow paths 60 (61 to 63) that 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 illustrating flow path pattern A according to this embodiment.

[0047] The flow path switching device 1 can switch from the state of flow path pattern A shown in Fig. 6 to flow path pattern B shown in Fig. 7 by rotating the rotary disk 40 clockwise by 60° using the drive unit 13. Fig. 7 is a schematic image diagram showing flow path pattern B according to this embodiment.

[0048] That is, in flow path pattern B, the flow path switching device 1 uses three rotary flow paths 60 (61 to 63) to connect the first inlet flow path 21, the third fixed flow path 73, and the third outlet flow path 33, to connect the second inlet flow path 22, the first fixed flow path 71, and the first outlet flow path 31, and to connect the third inlet flow path 23, the second fixed flow path 72, and the second outlet flow path 32.

[0049] The flow path switching device 1 can also switch from the state of flow path pattern B shown in Fig. 7 to flow path pattern A shown in Fig. 6 by rotating the rotary disk 40 counterclockwise by "60°" using the drive unit 13. Alternatively, the flow path switching device 1 can switch to a state equivalent to flow path pattern A shown in Fig. 6 by further rotating the rotary disk 40 clockwise by "60°" (in this case, the combination of rotary flow paths 60 is different).

[0050] [Regarding the Valve Seal Members] In this embodiment, as shown in FIG. 3 , in the flow path switching device 1, valve seal members 81 are provided between the upper housing 11A and the rotary disk 40 and between the rotary disk 40 and the fixed disk 50 to prevent leakage of liquid from the flow paths. 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. Furthermore, 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 portion 41 of the rotary disk 40. Furthermore, 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, 41d are formed along the outer periphery of the "cocoon-shaped" rotary flow path 60 of the rotary disk 40. The valve seal member 81 has a "cocoon" shape similar to that of the assembly grooves 41c and 41d, and is press-fitted and fixed into the assembly grooves 41c and 41d.

[0051] As shown in FIGS. 2 to 4 , the valve seal member 81 is provided on the upper surface 41a and 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" rotary 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. The upper valve seal member 81A contacts the inner surface 11a of the upper housing 11A to seal the flow passage formed between the inlet flow passage 20 and the rotary flow passage 60 communicating with the inlet 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) contacts the fixed disk 50 to seal the flow passage formed between the fixed flow passage 70 and the rotary 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 (e.g., Teflon (registered trademark)), a rubber with a fluororesin attached, or a material other than fluororesin or rubber. These valve seal members 81 correspond to an example of the "sealing means" of the disclosed technology. In Figures 2, 4, 6, and 7, the shape of the valve seal member 81 is shown schematically. Details of the shape of the valve seal member 81 and related members will be described later.

[0053] 3, a lip seal 83 is provided between the upper housing 11A and the rotary shaft 42. Another lip seal 84 is provided between each cylindrical portion 52 of the fixed disk 50 and the lower housing 11B.

[0054] [Regarding Issues with the Valve Seal Member During Rotation of the Rotating Disk] FIG. 8 shows a plan view of one upper valve seal member 81A provided on a portion of the upper surface 41a of the rotating disk 40 and a portion of the upper housing 11A, which is a comparison example of this embodiment. In FIG. 8, the curved portions indicated by arrows at both ends of the cocoon-shaped upper valve seal member 81A in its longitudinal direction (the rotational direction Y of the rotating disk 40) are defined as a "first shear sliding portion A1" and a "second shear sliding portion A2," respectively. Furthermore, the curved portion indicated by the inner arrow in the radial direction of the rotating disk 40 along the longitudinal direction is defined as an "inner circumferential sliding portion B1." Furthermore, the curved portion indicated by the outer arrow in the radial direction of the rotating disk 40 along the longitudinal direction is defined as an "outer circumferential sliding portion B2." Here, each of the shear sliding portions A1 and A2 and the corresponding portion of the assembly groove 41c corresponds to a position intersecting the rotational direction (drive direction) of the rotating disk 40. The sliding portions B1 and B2 on the inner and outer circumferences and the corresponding portions of the assembly groove 41c correspond to positions along the rotation direction (drive direction) of the rotary disk 40.

[0055] As shown in FIG. 8 , when the rotary disk 40 rotates counterclockwise Y1, as 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. As a result, at the front side of the upper valve seal member 81A's rotation (first shear sliding region A1), the region A1 is pulled, causing its diameter to shrink, resulting in a low surface pressure at one rotation tip P1, circled by a dashed line. Meanwhile, at the rear side of the upper valve seal member 81A's rotation (second shear sliding region A2), the region A2 is compressed, causing its diameter to expand, resulting in a high surface pressure at the other rotation tip P2, circled by a dashed line. Therefore, the surface pressure between the upper valve seal member 81A and the upper housing 11A varies. As a result, the sliding resistance of the upper valve seal member 81A increases, potentially resulting in uneven wear and a deterioration in sealing performance. That is, when the rotary disk 40 rotates, there is a concern that the upper valve seal member 81A may slide and slip (drive slippage), deteriorating 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, while the second shear sliding portion A2 becomes the front side of the rotation and is pulled, resulting in a similar concern. A similar concern exists 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, and C3 indicates the difference in tension and compression. Therefore, in this embodiment, the following "drive slippage suppression structure" is provided to address the issues with the "cocoon-shaped" valve seal member 81 described above.

[0056] [Regarding the Drive Slippage Suppression Structure] Figure 9 is a plan view similar to Figure 8 showing one upper valve seal member 81A provided on a portion of the upper surface 41a of the rotary disk 40 and a portion of the upper housing 11A according to this embodiment. The upper valve seal member 81A is fitted into the assembly groove 41c. In this assembled state, a drive slippage suppression structure 10 is provided between the upper valve seal member 81A and the side wall of the assembly groove 41c in an area surrounded by a dashed circle (excluding P1 and P2) in Figure 9, for suppressing slippage due to sliding of the upper valve seal member 81A during rotation of the rotary disk 40. In this embodiment, the drive slippage suppression structure 10 is provided on the side wall of the assembly groove 41c and is a first groove protrusion 44 and a second groove protrusion 45 that abut against the upper valve seal member 81A so as to sandwich the seal member 81A from both the inside and outside.

[0057] Here, the first groove convex portion 44 is provided at the boundary between each shear sliding portion A1, A2 and the inner circumferential sliding portion B1 and the outer circumferential sliding portion B2, where the sliding direction of the upper valve seal member 81A is significantly different when the rotary disk 40 rotates counterclockwise Y1. The shear sliding portions A1, A2 and the inner circumferential sliding portion B1 and the outer circumferential sliding portion B2 correspond to the multiple "curved portions" that make up the upper valve seal member 81A. The above "boundaries" correspond to "inflection points" where adjacent curved portions connect. Furthermore, the second groove convex portion 45 is provided approximately in the center of the outer circumferential sliding portion B2, where the spacing between adjacent first groove convex portions 44 is long.

[0058] Although not shown and 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] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above addresses the above-mentioned problem associated with the "cocoon-shaped" valve seal member 81 as follows. That is, a drive slippage suppression structure 10 is provided between the valve seal members 81 (upper valve seal member 81A, lower valve seal member 81B) fitted into the assembly grooves 41c, 41d of the rotary disk 40 and the side walls of the assembly grooves 41c, 41d. Therefore, when the rotary disk 40 rotates (when driven), the drive slippage suppression structure 10 suppresses slippage of the valve seal member 81 due to sliding. This makes it possible to suppress deviation (misalignment) of the position of the valve seal member 81 due to sliding when the rotary disk 40 rotates, thereby ensuring substantially uniform sealing performance and wear resistance 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. Also, it is possible to suppress deviation (misalignment) of the position of the valve seal member 81 due to sliding when the rotating disk 40 is driven. Furthermore, it is possible to ensure approximately uniform sealing performance and wear resistance around the entire circumference of the valve seal member 81.

[0061] Second Embodiment Next, a 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 denoted by the same reference numerals and description thereof will be omitted, and differences will be mainly described.

[0062] [Regarding the Drive Slip Suppression Structure] This embodiment differs 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 according to this embodiment, which is provided on a portion of the upper surface 41a of the rotary disk 40. In this embodiment, no in-groove convexities (drive slippage suppression structure) are provided at the rotational tip ends P1 and P2, where compressive stress is concentrated at each shear sliding region A1 and A2 when the upper valve seal member 81A rotates with the rotary disk 40. In other words, in each shear sliding region A1 and A2, the in-groove convexities (drive slippage suppression structure) are provided at positions that avoid the rotational tip ends P1 and P2. That is, in this embodiment, as shown in FIG. 10, a third in-groove convexity 46 (drive slippage suppression structure 10) is provided between each rotational tip end P1 and P2 and the first in-groove convexity 44.

[0063] Although not shown and 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] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to those of the first embodiment. That is, in this embodiment, the third groove convex portion 46 (drive deviation suppression structure 10) is provided at each shear sliding region A1, A2. This further suppresses deviation (misalignment) of the position of each shear sliding region A1, A2 during rotation of the rotary disk 40, thereby ensuring more uniform sealing performance and wear resistance around the entire circumference of the valve seal member 81. Furthermore, at each shear sliding region A1, A2, the third groove convex portion 46 is provided at a position that avoids the rotation leading edge portions P1, P2. Therefore, it is possible to further suppress the occurrence of compressive stress concentration at the rotation leading edge portions P1, P1 of each shear sliding region A1, A2.

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

[0066] [Regarding the Drive Misalignment Suppression Structure] This embodiment differs from the previous embodiments in terms of the "drive misalignment suppression structure." FIG. 11 , a plan view similar to FIG. 8 , shows a portion of an upper valve seal member 81A provided on a portion of the upper surface 41a of the rotary disk 40 and a portion of the upper housing 11A. In the previous embodiments, the valve seal member 81 includes first-groove convex portions 44 at the boundaries between the shear sliding regions A1 and A2 and the inner circumferential sliding region B1 and the outer circumferential sliding region B2, i.e., at the "inflection points" where adjacent curved portions connect. However, as shown in FIG. 11 , when the first shear sliding region A1 crosses the opening 20a of the inlet flow passage 20, the crossing portion is opened to the opening 20a. Therefore, the crossing portion is subjected to tensile stress F1 due to the sliding resistance of the portions other than the crossing portion, and the open portion tends to move toward the sliding location. However, this movement is suppressed by the first-groove convex portions 44, which raises concerns about the application of compressive stress F2. 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, this embodiment assumes that the sliding resistance (coefficient of friction) of the valve seal member 81 is large. The valve seal member 81 includes multiple curved portions and multiple inflection points connecting adjacent curved portions. The first-groove convex portions 44 abut against areas near the inflection points that are separate from the inflection points. That is, the valve seal member 81 includes shear sliding regions A1 and A2, an inner circumferential sliding region B1, and an outer circumferential sliding region B2 as curved portions, and multiple boundaries K1 as inflection points. The first-groove convex portions 44 abut against areas near the boundaries (areas near the inflection points) M1 that are separate from some of the boundaries K1. In particular, in this embodiment, the first-groove convex portions 44 are provided in the boundary-neighborhood regions M1 between the outer circumferential sliding region B2 and the shear sliding regions A1 and A2. Furthermore, the boundaries K1 between the inner circumferential sliding region B1 and each of the shear sliding regions A1, A2 are provided with first groove inner convex portions 44. In this embodiment, the boundaries K1 between the inner circumferential sliding region B1 and each of the shear sliding regions A1, A2 are provided with the first groove inner convex portions 44, but the first groove inner convex portions 44 may also be provided in boundary vicinity regions M1 outside these boundaries K1.

[0068] Although not shown and 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] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to those of the second embodiment. That is, the first-groove convex portion 44 abuts against the valve seal member 81 at a boundary vicinity region M1 (a region near an inflection point) that is away from the boundary K1 (inflection point) where adjacent curved portions (the first shear sliding region A1, the second shear sliding region A2, the inner circumferential sliding region B1, and the outer circumferential sliding region B2) connect. Therefore, when the valve seal member 81 passes through the opening 20a of the inlet flow channel 20 and the opening 70a of the fixed flow channel 70 as the rotary disk 40 rotates, stress concentration at the boundary K1 of the valve seal member 81 due to the first-groove convex portion 44 is suppressed. This reduces stress concentration in the valve seal member 81.

[0070] Fourth Embodiment Next, a fourth embodiment will be described in detail with reference to FIG.

[0071] [Regarding the Drive Misalignment Suppression Structure] This embodiment differs from the previous embodiments in terms of the "drive misalignment suppression structure." FIG. 13 is an enlarged plan view of the first to third in-groove protrusions 44 to 46 provided as the drive misalignment suppression structure 10 in a portion of the assembly groove 41c (41d) of the rotary disk 40. In this embodiment, the valve seal member 81 contacts the outer peripheral sidewall 41ca (41da) of the assembly groove 41c (41d). In contrast, the valve seal member 81 is press-fitted into the assembly groove 41c (41d) so as not to contact the inner peripheral sidewall 41cb (41db) of the assembly groove 41c (41d). As shown in FIG. 13, for each groove protrusion 44 to 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 J2 of the inner peripheral side wall 41cb (41db), which does not come into contact with the valve seal member 81, is greater than the protrusion amount J1 of the outer peripheral side wall 41ca (41da).

[0072] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to the functions and effects of the previous embodiments. 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 sidewall 41ca (41da) of the assembly groove 41c (41d), so the surface pressure is already elevated. Therefore, if the convexity amount J1 of each of the groove convexities 44-46 on the outer peripheral sidewall 41ca (41da) that is in contact is set to be the same as the convexity amount J2 of each of the groove convexities 44-46 on the inner peripheral sidewall 41cb (41db) that is not in contact, there is a concern that the surface pressure on the convexities on the outer peripheral sidewall 41ca (41da) side will be excessive, leading 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, it is possible to achieve uniform surface pressure between the outer side wall 41ca (41da) and the inner side wall 41cb (41db) of each groove convex portion 44 to 46.

[0073] Fifth Embodiment Next, a fifth embodiment will be described in detail with reference to FIG.

[0074] [Regarding the Drive Misalignment Suppression Structure] This embodiment differs from the fourth embodiment in terms of the "drive misalignment suppression structure." FIG. 14 is an enlarged plan view equivalent to FIG. 13 showing the first to third in-groove protrusions 44 to 46 provided as the drive misalignment suppression structure 10 in the assembly groove 41c (41d) of the rotary disk 40 according to this embodiment. In this embodiment, the valve seal member 81 does not contact the outer peripheral sidewall 41ca (41da) of the assembly groove 41c (41d). In contrast, the valve seal member 81 is press-fitted into the assembly groove 41c (41d) so that the valve seal member 81 contacts the inner peripheral sidewall 41cb (41db) of the assembly groove 41c (41d). Here, as shown in Figure 14, for each groove protrusion 44 to 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 larger than the protrusion amount J2 of the inner peripheral side wall 41cb (41db).

[0075] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to the functions and effects of the previous embodiments. 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 sidewall 41cb (41db) of the assembly groove 41c (41d), so the surface pressure is already elevated. Therefore, if the convexity amount J2 of each of the groove convexities 44-46 on the contacting inner circumferential sidewall 41cb (41db) is set to be the same as the convexity amount J1 of each of the groove convexities 44-46 on the non-contacting outer circumferential sidewall 41ca (41da), there is a concern that the surface pressure on the convexities on the inner circumferential sidewall 41cb (41db) side will be excessive, leading 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 side wall 41ca (41da) and the inner side wall 41cb (41db) of each groove convex portion 44 to 46.

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

[0077] [Regarding the Drive Slip Suppression Structure] This embodiment differs from the third embodiment in terms of the "drive slippage suppression structure." In each of the above embodiments, when the valve seal member 81 is crushed by the groove protrusions 44-46, its outer periphery recedes outward and its inner periphery recedes inward (expands). As a result, tensile stress acts on the outer periphery and compressive stress acts on the inner periphery. The groove protrusions 44-46 of the assembly grooves 41c, 41d press against the inner and outer periphery sides of the valve seal member 81, resulting in compressive stress. Therefore, on the inner periphery of the valve seal member 81, compressive stress is added by the groove protrusions 44-46 to the portion where compressive stress acts, resulting in greater compressive stress on the inner periphery than on the outer periphery. Therefore, in this embodiment, the "drive slippage suppression structure" is configured as follows.

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

[0079] In this embodiment, as shown in Fig. 15, the assembly groove 41d includes multiple (four in this embodiment) groove arc portions 41d1, 41d2, 41d3, and 41d4 with different arc radii. Also, 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 each of the groove arc portions 41d1 to 41d4. Each of these sliding portions A1, A2, B1, and B2 corresponds to an example of a "seal arc portion" in the disclosed technology. 16 and 17 , each of the groove protrusions 44-46 includes an outer circumferential protrusion 47 provided on the outer circumferential sidewall 41da and an inner circumferential protrusion 48 provided on the inner circumferential sidewall 41db. As shown in FIG. 17 , for each of the groove protrusions 44-46, the lower valve seal member 81B contacts both the protrusion amount J1 of the outer circumferential sidewall 41da and the protrusion amount J2 of the inner circumferential sidewall 41db. Furthermore, as the radii of the groove arc portions 41d1, 41d2, 41d3, and 41d4 and the sliding portions A1, A2, B1, and B2 become smaller, the protrusion amount J1 of the outer circumferential protrusion 47 becomes larger than the protrusion amount J2 of the inner circumferential protrusion 48. In this embodiment, the protrusion amounts J1 and J2 correspond to an example of the "extrusion allowance" of the disclosed technology.

[0080] In this embodiment, the difference between the amount of convexity J1 of the outer peripheral side wall 41da and the amount of convexity J2 of the inner peripheral side wall 41db is set to increase as the arc radii of the sliding portions A1, A2, B1, and B2 of the lower valve seal member 81B decrease. 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 the shear sliding portions A1 and A2 are the "small diameter portions." As shown in Fig. 17, the relationship between the amount of convexity J1 of the outer peripheral convex portion 47 and the amount of convexity J2 of the inner peripheral convex portion 48 provided thereon is expressed by the following "Equation 1" and "Equation 2."

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

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

[0083] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to those of the third embodiment. That is, each of the groove protrusions 44-46 includes an outer circumferential protrusion 47 and an inner circumferential protrusion 48. The smaller the radius of the groove arc portions 41d1-41d4 and each sliding portion A1, A2, B1, B2 (seal arc portions), the larger the protrusion amount J1 of the outer circumferential protrusion 47 is compared with the protrusion amount J2 of the inner circumferential protrusion 48. Therefore, the valve seal member 81 corrects the imbalance between the compressive stress caused by the inner circumferential protrusion 48 and the compressive stress caused by the outer circumferential protrusion 47. This further reduces deviation (misalignment) of the valve seal member 81 due to sliding during rotation of the rotary disk 40, ensuring more uniform sealing performance and wear resistance around the entire circumference of the valve seal member 81.

[0084] Seventh Embodiment Next, a seventh embodiment will be described in detail with reference to FIGS. 18 and 19. FIG.

[0085] [Regarding the Drive Slip Suppression Structure] This embodiment differs from the previous embodiments in terms of the "drive slippage suppression structure." FIG. 18 shows an enlarged plan view and bottom view of the in-groove convex portions 44-46 of the assembly groove 41c (41d) as a drive slippage suppression structure, in comparison with this embodiment. In the previous embodiments, the drive slippage suppression structure 10 was configured as shown in FIG. 18 to suppress movement of the valve seal member 81 during sliding. That is, the assembly groove 41c (41d) is provided with the in-groove convex portions 44-46, 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 the previous embodiments, a large interference between the convex portions 47, 48 was required to suppress movement of the valve seal member 81 due to sliding during rotation of the rotary disk 40. Therefore, stress concentration was unavoidable in the area surrounded by the dashed-dotted circle S1 in Figure 18, and stress remained even when the rotary disk 40 was stopped. As a result, there was a concern that the valve seal member 81 would "sag." Therefore, in this embodiment, the "drive deviation suppression structure" is configured as follows.

[0086] Fig. 19 shows, in a plan view or bottom view equivalent to Fig. 18, the seal-side protrusions of the seal member serving as the drive slippage suppression structure according to this embodiment. In this embodiment, as shown in Fig. 19, the drive slippage suppression structure 10 is configured with seal-side protrusions 81b provided on the side surface of the valve seal member 81 and arranged to press against 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)). In addition, in this embodiment, groove-side recesses 41g corresponding to the seal-side protrusions 81b are provided on the side walls of the assembly groove 41c (41d).

[0087] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to the functions and effects of the previous embodiments. That is, the drive deviation suppression structure 10 is configured with the seal-side convex portion 81b provided on the side surface of the valve seal member 81 so as to press against the side walls of the assembly grooves 41c, 41d. This allows the drive deviation suppression structure 10 to be realized with an extremely simple structure. Furthermore, it is possible to suppress deviation (misalignment) of the position of the valve seal member 81, and to suppress stress concentration on the other side of the seal-side convex portion 81b when the rotating disk 40 rotates in one direction.

[0088] 18, in each of the above-described embodiments, the valve seal member 81 is sandwiched between the outer circumferential convex portion 47 and the inner circumferential convex portion 48, and therefore stress concentration occurs constantly in the valve seal member 81. That is, when the rotary disk 40 rotates counterclockwise Y1, when it rotates clockwise 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. Therefore, when the rotating disk 40 rotates counterclockwise Y1 or clockwise 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 Figure 19, when the rotating disk 40 rotates counterclockwise Y1, stress concentration occurs in the part surrounded by the dash-dotted circle S3 on the side in the rotation direction, but no stress concentration occurs in the part surrounded by the dash-dotted circle S2 on the side opposite to the rotation direction.

[0090] Eighth Embodiment Next, an eighth embodiment will be described in detail with reference to FIGS. 20 to 23. FIG.

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

[0092] Figure 20 is a schematic diagram showing a portion of the assembly groove 41c provided on the upper surface 41a of the rotary disk 40 and a portion of the upper valve seal member 81A assembled thereto, according to this embodiment. Figure 21 is a cross-sectional view of the assembly groove 41c taken along line D-D in Figure 20 according to this embodiment. Figure 22 is a cross-sectional view of the assembly groove 41c taken along line E-E in Figure 20 according to this embodiment. Figure 23 is a cross-sectional view of the assembly groove 41c taken along line F-F in Figure 20.

[0093] In this embodiment, at each shear sliding portion A1, A2, a gap g1 is provided between the upper valve seal member 81A and the assembly groove 41c only on the outer peripheral sidewall 41ca side of the assembly groove 41c, and no gap is provided on the inner peripheral sidewall 41cb side. In Figure 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 constant width "L1." This width L1 is the reference width of the assembly groove 41c and is the same as the width of the assembly groove 41c at the outer peripheral sliding portion B2. "L2" indicates the width of the portion of the first shear sliding portion 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 shear sliding region A1, A2 is wider than the width L1 of the assembly groove 41c corresponding to the outer peripheral sliding region B2, and the widened portion is located on the outer peripheral side wall 41ca side of the assembly groove 41c. The provision of the groove protrusions 44, 46 at each of the shear sliding regions A1, A2 further reduces the escape route for the upper valve seal member 81A when compressive stress is applied. Therefore, the widened portion 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] When the rotary disk 40 rotates clockwise Y2 (see FIG. 20), compressive stress of the upper valve seal member 81A is concentrated on the left side (the side of the outer peripheral wall 41ca of the assembly groove 41c) in FIGS. 21 to 23. Therefore, by providing gaps g1 and g2 on the side of the outer peripheral wall 41ca, a relief area for the compressed upper valve seal member 81A can be provided, thereby suppressing stress concentration on the upper valve seal member 81A. Furthermore, by providing each of the groove protrusions 44 and 46 in the assembly groove 41c, the relief area for the upper valve seal member 81A is further reduced. As a result, as shown in FIGS. 22 and 23, the gap g1 at the portion of each groove protrusion 44 and 46 where the distance to the adjacent protrusion is short is larger than the gap g2 at the portion where the distance to the adjacent protrusion is long.

[0095] Although not shown and 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] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to the functions and effects of the second embodiment. Specifically, gaps g1 and g2 are provided between the valve seal member 81 and the assembly grooves 41c and 41d, and the outer peripheral gaps g1 and g2 are larger than the inner peripheral gap. Therefore, when the rotary disk 40 rotates or when the valve seal member 81 passes through the opening 20a of the inlet flow channel 20 and the opening 70a of the fixed flow channel 70, stress may concentrate on the outer peripheral sides of the assembly grooves 41c and 41d. Even in this case, because the outer peripheral gaps g1 and g2 are larger than the inner peripheral gap, the outer peripheral gaps g1 and g2 provide more escape routes for the valve seal member 81. Therefore, when the rotating disk 40 rotates, or when the valve seal member 81 passes through the opening 20a of the inlet flow path 20 and the opening 70a of the fixed flow path 70, the deformation caused by the protrusions 44 to 46 within the grooves of the valve seal member 81 can be released to a greater extent into the gaps g1 and 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 region A1, A2 and the assembly grooves 41c, 41d. Alternatively, gaps may 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 region A1, A2 and the assembly grooves 41c, 41d.

[0098] Ninth Embodiment Next, a ninth embodiment will be described in detail with reference to FIGS.

[0099] [Regarding the Drive Slip Suppression Structure] This embodiment differs from the third embodiment in terms of the "drive slippage 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 assembly groove 41d, as well as the fixed disk 50 and a portion of the opening of the fixed flow path 70 formed therein. Figure 24 shows the case where the rotating disk 40 rotates counterclockwise Y1 and the first shear sliding portion A1 of the lower valve seal member 81B rides from the opening of the fixed flow path 70 onto the upper surface 51a of the fixed disk 50. Figure 25 shows the case where the rotating disk 40 rotates clockwise Y2 and the first shear sliding portion A1 of the lower valve seal member 81B rides from the opening of the fixed flow path 70 onto the upper surface 51a of the fixed disk 50. Figure 26 is a schematic diagram showing, in this embodiment, the first shear sliding portion A1 (shown by a thick two-dot chain line) moving counterclockwise Y1 and the first shear sliding portion A1 (shown by a thick solid line) moving clockwise Y2, as they each climb 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 shear sliding region A1, A2 so that they are larger on the outer periphery than on the inner periphery. In contrast, in this embodiment, the outer peripheral wall edges 41e (shown by solid lines in FIGS. 24 and 25 ) of the assembly grooves 41c, 41d at positions intersecting the rotation direction (drive direction) of the rotary disk 40 (positions corresponding to each shear sliding region A1, A2) are formed to have a larger R-shape (a curved shape with a larger radius) or tapered shape than the edges 41f (shown by two-dot chain lines in FIGS. 24 and 25 ) at other positions of the assembly groove 41d. This configuration of the outer peripheral wall edges 41e provides each shear sliding region A1, A2 with a relief for stress concentration.

[0101] 27 is a schematic bottom view showing the first shear sliding region 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 region A1, a gap g3 between the outer peripheral wall of the assembly groove 41d and the lower valve seal member 81B is formed so as to gradually widen toward the rotation tip TP.

[0102] Although not shown and 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] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to those of the eighth embodiment. That is, the edge 41e of the outer peripheral sidewall of the assembly grooves 41c, 41d at a position intersecting the rotation direction of the rotary disk 40 has a larger rounded or tapered shape than the edge 41f at other positions. Therefore, the valve seal member 81 may run from the opening 20a of the inlet flow channel 20 or the opening 70a of the fixed flow channel 70 onto the inner surface 11a of the housing or the upper surface 51a (sliding surface) of the fixed disk. In this case, the larger rounded or tapered shape of the edge 41e of the outer peripheral sidewall of the assembly grooves 41c, 41d allows the valve seal member 81 to escape more. This further reduces stress concentration on the valve seal member 81.

[0104] 24, when the rotary disk 40 rotates counterclockwise Y1, the lower valve seal member 81B engages with the inner circumferential side wall 41db of the assembly groove 41d and moves counterclockwise Y1. As a result, 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, because the diameter of the lower valve seal member 81B is reduced, no escape route is required for the stress concentration when the lower valve seal member 81B moves from the fixed flow path 70 onto the upper surface 51a of the fixed disk 50.

[0105] On the other hand, as shown in FIG. 25 , when the rotary disk 40 rotates clockwise Y2, the lower valve seal member 81B engages with the outer peripheral side wall 41da of the assembly groove 41d and moves clockwise Y2. This causes compressive stress (stress that expands the diameter of the lower valve seal member 81B) to act on the lower valve seal member 81B. This reduces the escape route for the lower valve seal member 81B when it climbs from the fixed flow path 70 onto the upper surface 51a of the fixed disk 50, resulting in stress concentration on the lower valve seal member 81B. In this embodiment, as shown in FIG. 25 , the edge 41e of the outer peripheral side wall 41da has a larger R-shape or tapered shape than the edge 41f at other positions. This provides an escape route for the lower valve seal member 81B, thereby suppressing stress concentration.

[0106] Tenth Embodiment Next, a tenth embodiment will be described in detail with reference to FIGS. 28 and 29. FIG.

[0107] [Regarding the Drive Misalignment Suppression Structure] This embodiment differs from the above-described embodiments in terms of the "drive misalignment suppression structure." FIG. 28 shows, in plan and bottom views, one valve seal member 81 provided on the rotary disk 40 of each of the above-described embodiments, as a comparative example of this embodiment. For convenience, FIG. 28 only shows the planar shape of the valve seal member 81, and omits the assembly grooves 41c (41d). As shown in FIG. 28 , the rotary disk 40 is configured to be rotatable about the rotation shaft 42. The valve seal member 81 is composed of a "rotation line portion" that runs along the rotation direction (counterclockwise Y1, clockwise Y2) of the rotary disk 40 and a "rotation intersection portion" that intersects with the rotation direction. Here, the inner peripheral sliding portion B1 and the outer peripheral sliding portion B2, which have already been described, are examples of "rotation line portion," and the first shear sliding portion A1 and the second shear sliding portion A2, which have already been described, are examples of "rotation intersection portions." The inner sliding portion B1 is an example of an "inner rotational axis portion" that is close to the rotation center of the rotating disk 40, and the outer sliding portion B2 is an example of an "outer rotational axis portion" that is far from the rotation center.

[0108] In this comparative example, 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 portions of 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. In particular, at the portions of the inflection points Q1 and Q2, stress acts in the upward direction U1 due to the curved locus H1 of the shear sliding portions A1 and A2, and 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 portions of the inflection points Q1 and Q2 are configured as follows.

[0109] 29 shows one valve seal member 81 according to this embodiment, which is provided on the rotary disc 40, 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 portion B1 is set smaller than the curvature of the rotation locus of the rotary disc 40, i.e., the curvature of the curved locus H2 of the comparative example.

[0110] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to the functions and effects of the previous embodiments. That is, among the inner circumferential sliding portion B1, the outer circumferential sliding portion B2, and the first shear sliding portion A1 and second shear sliding portion A2 that constitute the valve seal member 81, the curvature of the inner circumferential sliding portion B1 is smaller than the curvature of the rotation trajectory of the rotary disk 40. As a result, stress acts at the boundaries between the inner circumferential sliding portion B1 and each of the shear sliding portions A1 and A2, making it possible to suppress bending stress concentration at the boundaries between the inner circumferential sliding portion B1 and each of the outer circumferential sliding portions B2 of the valve seal member 81 and each of the shear sliding portions A1 and A2 that occurs during rotation of the rotary disk 40.

[0111] <Other Embodiments> The disclosed technology is not limited to the above-described embodiments, and can be implemented by appropriately modifying part of the configuration within the scope 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 rotary 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 the rotary 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 rotary 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 rotary disk.

[0114] (3) In the above embodiments, the valve body is configured as a rotary 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 the above-described 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 that penetrates the rotating disk 40, which is the “valve body portion,” in the thickness direction 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 configured as an O-ring with an O-shaped cross section. However, the cross section of the valve seal member can also be configured in various shapes such as a diamond shape, a square shape, a hollow shape, a mountain shape, etc.

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

[0119] REFERENCE SIGNS LIST 1 flow path switching device 10 drive deviation suppression structure 11 housing (stator) 20 inflow flow path (communication path) 30 outflow flow path (communication path) 40 rotating disk (valve body) 41c assembly groove 41ca outer peripheral side wall 41cb inner peripheral side wall 41d assembly groove 41d1 groove arc portion 41d2 groove arc portion 41d3 groove arc portion 41d4 groove arc portion 41da outer peripheral side wall 41db inner peripheral side wall 41e edge portion 41f edge portion (other position) 42 rotating shaft 44 first groove inner convex portion (convex portion) 45 second groove inner convex portion (convex portion) 46 third groove inner convex portion (convex portion) 47 outer peripheral side convex portion 48 inner peripheral side convex portion 50 fixed disk (stator) 60 DESCRIPTION OF THE REFERENCE NUMERALS Rotational flow path (communicating path) 70 Fixed flow path (communicating path) 81 Valve seal member (sealing means) 81b Seal-side convex portion A1 First shear sliding portion (seal arc portion, rotation intersection portion) A2 Second shear sliding portion (seal arc portion, rotation intersection portion) B1 Inner peripheral sliding portion (seal arc portion, rotation line portion, inner rotation line portion) B2 Outer peripheral sliding portion (seal arc portion, rotation line portion, outer rotation line portion) g1 to g3 Clearances J1 Amount of convexity on outer peripheral side (extension) J2 Amount of convexity on inner peripheral side (extension) K1 Boundary (inflection point) M1 Boundary vicinity portion (inflection point vicinity portion)

Claims

1. A flow path switching device comprising: at least one stator; a valve disc driven relatively to the stator; the stator and the valve disc each including at least one communication passage; and an annular sealing means provided between the stator and the valve disc and adapted to slide against the stator or the valve disc as the valve disc is driven, wherein the valve disc is driven to selectively connect the communication passage of the valve disc to the communication passage of the stator, thereby switching and forming a series of flow paths, wherein the valve disc 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 the assembled state, a drive slippage suppression structure is provided between the sealing means and a side wall of the assembly groove for suppressing slippage caused by sliding of the sealing means when the valve disc is driven.

2. A flow path switching device as claimed in claim 1, characterized in that the drive deviation prevention structure is a convex portion 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.

3. A flow path switching device as claimed in claim 2, characterized in that 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 but not including the inflection points.

4. A flow path switching device as described in claim 3, wherein the assembly groove includes a groove arc portion and also includes 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 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.

5. A flow path switching device as claimed in claim 1, characterized in that the drive deviation suppression structure is a seal side convex portion provided on a side surface of the sealing means and arranged to press against the side wall of the assembly groove.

6. A flow path switching device as claimed in any one of claims 1 to 5, characterized in that 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.

7. A flow path switching device as claimed in claim 6, characterized in that 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.

8. A flow path switching device as claimed in any one of claims 1 to 5, characterized in that the valve body is configured to be rotatably driven around a rotation axis, the sealing means comprises a rotational line portion along the rotation direction of the valve body and a rotational intersection portion intersecting the rotation direction, the rotational line portion includes an inner rotational line portion close to the rotation center of the valve body and an outer rotational line portion far from the rotation center, and the curvature of the inner rotational line portion is smaller than the curvature of the rotational trajectory of the valve body.

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