Flow passage switching device

Abstract

To suppress increase in a manufacturing cost, and to secure sealing performance of seal means.SOLUTION: A flow passage switching device includes a stator 11, a valve element 13 relatively driven with the stator, a communication passage provided in the stator and the valve element, and annular seal means 17 sliding with respect to the stator in accordance with driving of the valve element. The communication passage of the valve element and the communication passage of the stator are selectively connected by driving of the valve element, and thereby, a series of flow passages is switched and formed. The seal means includes an inner circular portion arranged in a center side of the valve element, an outer circular portion arranged in an outer peripheral side of the valve element, and a partition portion connecting the inner circular portion and the outer circular portion at plural portions and partitioning between the plurality of communication passages. The valve element includes an attachment groove 13e for attaching the seal means, and the partition portion of the seal means is engaged with the attachment groove in a pulled state and is attached.SELECTED DRAWING: Figure 24

Description

[Technical field]

[0001] The technology disclosed in this specification relates to a flow path switching device that switches a flow path of a fluid, and in particular to an assembly structure of a seal means used in a sliding portion between a stator and a valve body. [Background technology]

[0002] The applicant of the present application is currently developing a flow path switching device for switching liquid flow paths, which comprises a stator, a valve body that moves relative to the stator, a communicating passage provided in the stator and the valve body, and a sealing means between the stator and the valve body that 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, thereby switching between and forming a series of flow paths.

[0003] Here, as a technique related to a sealing means, for example, Patent Document 1 below discloses a technique related to a deformed O-ring and a sealing structure that are assembled in the middle of a flow path of a fluid (lubricating oil). This sealing structure has a deformed O-ring that is fitted into an elliptical recessed portion to seal the flow path. The deformed O-ring has an outer periphery length slightly longer than the inner periphery length of the recessed portion, and is provided with a first portion that is easily deformed so as to be recessed inward away from the inner periphery wall of the recessed portion when fitted into the recessed portion, a second portion that is less easily deformed than the first portion, and a deformation prevention means that prevents the deformation of the first portion. According to this sealing structure, when the deformed O-ring is fitted into the recessed portion, an external force acting on the second portion that is less easily deformed concentrates stress on the first portion that is more easily deformed, and tries to recess the first portion inward. At this time, the first portion functions as a deformation prevention means to prevent the first portion from being recessed. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2011-106485 A Summary of the Invention [Problem to be solved by the invention]

[0005] According to the seal structure described in Patent Document 1, the outer periphery of the deformed O-ring is in close contact with the inner periphery of the recessed fitting portion, so that deformation due to stress concentration in the first portion can be prevented, and the desired sealing performance can be achieved. In addition, when the deformed O-ring is assembled into the recessed fitting portion, even if the recessed fitting portion faces downward, the deformed O-ring can be prevented from falling off. However, it is necessary to provide a deformation prevention means in the first portion, and special processing is required for the deformed O-ring, which raises concerns about increased manufacturing costs.

[0006] This disclosed technology has been made in consideration of the above-mentioned circumstances, and its purpose is to provide a flow path switching device that makes it possible to ensure the sealing performance of the sealing means without significantly increasing manufacturing costs. [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 including at least one stator, a valve body that moves relative to the stator, at least one communication passage provided in each of the stator and the valve body, 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 communication passage of the valve body and the communication passage of the stator by driving the valve body, and to switch and form a series of flow paths, wherein the sealing means includes an inner circular portion located on the center side of the valve body, an outer circular portion located on the outer periphery of the valve body, and partition portions that connect the inner circular portion and the outer circular portion at multiple points and separate the multiple communication passages, the valve body or the stator includes an assembly groove for assembling the sealing means, and the partition portion of the sealing means is fitted into the assembly groove in a tensioned state and assembled.

[0008] According to the configuration of the above technology, at least one communication passage is provided in each of the stator and the valve body, and a seal means is assembled in an assembly groove provided in the valve body or the stator. The seal means includes an inner circular portion arranged on the center side of the valve body, an outer circular portion arranged on the outer periphery side of the valve body, and a partition portion that connects the inner circular portion and the outer circular portion and separates the multiple communication passages, and the partition portion is fitted into the assembly groove in a tensioned state and assembled. Therefore, a tensile force acts on the partition portion, and deformation of the partition portion against an external force is suppressed. In addition, when the valve body is driven to switch the flow path and the partition portion crosses an opening of the communication passage, the partition portion is prevented from getting caught on the opening or from jumping out into the opening.

[0009] In order to achieve the above object, the technology described in claim 2 is a flow path switching device comprising at least one stator, a valve body that moves relative to the stator, at least one communication passage provided in each of the stator and the valve body, 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 communication passage of the valve body and the communication passage of the stator by driving the valve body, and to switch and form a series of flow paths, wherein the sealing means includes an inner circular portion located on the center side of the valve body, an outer circular portion located on the outer periphery of the valve body, and partition portions that connect the inner circular portion and the outer circular portion at multiple points and separate the multiple communication passages, the valve body or the stator includes an assembly groove for assembling the sealing means, and the sealing means is assembled by fitting into the assembly groove, and the inner wall of the assembly groove at a portion where the partition portion is fitted has multiple protrusions that abut against the partition portion and are arranged at different positions on both sides of the partition portion.

[0010] According to the configuration of the above technology, unlike the technology described in claim 1, the inner wall of the assembly groove where the partition is fitted has multiple protrusions that abut against the partition, which are arranged at different positions on both sides of the partition. Therefore, a pressing force acts on the partition when the protrusions on the inner wall of the assembly groove abut against it, so that deformation of the partition against an external force is suppressed. In addition, when the valve body is driven to switch the flow path and the partition crosses the opening of the communication passage, the partition is prevented from getting caught on the opening or from jumping out into the opening.

[0011] In order to achieve the above object, the technology described in claim 3 is a flow path switching device including at least one stator, a valve body that moves relative to the stator, at least one communication path provided in each of the stator and the valve body, and an annular seal 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 the valve body is selectively connected to the communication path of the valve body and the communication path of the stator by driving the valve body, and a series of flow paths are switched and formed. In this flow path switching device, the seal means is disposed on an inner circular portion disposed on the center side of the valve body, and a seal means is disposed on an inner circular portion disposed on the center side of the valve body. and a valve body including an outer circular portion arranged on the outer periphery of the stator, and partition portions connecting the inner circular portion and the outer circular portion at multiple points and separating a plurality of communicating passages, the valve body including an assembly groove for assembling the sealing means, the sealing means having a mountain-shaped cross section spreading toward the valve body side and including a recessed portion recessed on the stator side and a hollow portion which is divided into at least two portions toward the valve body side and has an internal cavity, the assembly groove including an inner-groove ridge arranged in the hollow portion, and a side wall of the inner-groove ridge continuously changes from a curved surface with a small curvature to a curved surface with a large curvature from the bottom of the assembly groove to the top of the inner-groove ridge.

[0012] According to the configuration of the above technology, unlike the technology described in claims 1 and 2, the sealing means has a mountain-shaped cross section that expands toward the valve body, and includes a recess that is recessed on the stator side and a cavity that is divided into at least two parts toward the valve body side and has a hollow on the inside. In the assembly groove, the side wall of the groove protrusion placed in the cavity continuously changes from a curved surface with a small curvature to a curved surface with a large curvature from the bottom of the assembly groove to the top of the groove protrusion. Therefore, when the sealing means starts to slide against the stator or the valve body as the valve body is driven, the inner surface of the cavity of the sealing means continuously contacts the curved surface with a small curvature to a curved surface with a large curvature from the bottom of the assembly groove to the top of the groove protrusion, and the contact area of ​​the inner surface of the cavity with the side wall of the groove protrusion expands. This distributes the stress acting on the inner surface of the cavity, suppressing twisting of the sealing means.

[0013] In order to achieve the above object, the technology described in claim 4 provides a flow path switching device including at least one stator, a valve body that moves relative to the stator, at least one communication path provided in each of the stator and the valve body, and an annular seal 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 communication path of the valve body and the communication path of the stator by driving the valve body, and to switch and form a series of flow paths, the seal means having an inner circular portion disposed on the center side of the valve body, an outer circular portion disposed on the outer periphery side of the valve body, and a seal means that is formed by sealing the inner circular portion and the outer circular portion. at a plurality of locations and partition portions which separate the plurality of communicating passages, the valve body includes an assembly groove into which the sealing means is assembled, the sealing means having a mountain-shaped cross section spreading toward the valve body side and including a recessed portion which is recessed on the stator side and a hollow portion which is divided into at least two portions toward the valve body side and has an internal cavity, the assembly groove includes an intra-groove ridge which is disposed in the hollow portion, and the inner side wall of the assembly groove and the side wall of the intra-groove ridge each have a vertical surface which extends vertically near the bottom of the assembly groove, and the side wall of the intra-groove ridge continuously changes from a curved surface with a smaller curvature to a curved surface with a larger curvature from the vertical surface toward the top of the intra-groove ridge.

[0014] According to the configuration of the above technology, unlike the technology described in claim 3, the inner side wall of the assembly groove and the side wall of the groove protrusion placed in the cavity each have a vertical surface that extends vertically near the bottom of the assembly groove, and the side wall of the groove protrusion continuously changes from a curved surface with a smaller curvature to a curved surface with a larger curvature from the bottom of the assembly groove to the top of the groove protrusion. Therefore, when the sealing means begins to slide against the stator or the valve body as the valve body is driven, the inner surface of the cavity of the sealing means continuously contacts a curved surface with a smaller curvature to a curved surface with a larger curvature from the bottom of the assembly groove to the top of the groove protrusion, and the contact area of ​​the inner surface of the cavity with the side wall of the groove protrusion expands. This distributes the stress acting on the inner surface of the cavity, and suppresses twisting of the sealing means. On the other hand, the side wall of the inner-groove protrusion has a vertical surface that extends vertically near the bottom of the assembly groove, so even if the sealing means contracts inward along the curved surface of the side wall of the inner-groove protrusion, the surface pressure of the sealing means against the inner-groove protrusion is maintained by that vertical surface.

[0015] In order to achieve the above object, the technology described in claim 5 is the technology described in claim 2, wherein one of the stator and the valve body is a retaining member that retains the sealing means, and the other is a slidable member against which the sealing means slides, the sealing means has a mountain-shaped cross section that widens toward the retaining member side and includes a concave portion that is recessed on the slidable member side and a hollow portion that is branched into at least two portions toward the retaining member side and has a hollow interior, the assembly groove includes an inner-groove ridge that is disposed in the hollow portion, and an inner-groove ridge convex portion that abuts against the inner wall of the hollow portion is provided on a side wall of the inner-groove ridge that corresponds to the partition portion.

[0016] According to the configuration of the above technique, in addition to the function of the technique described in claim 2, the sealing means has a mountain-shaped cross section that expands toward the holding member side, and includes a recess that is recessed on the side of the slidable member, and a hollow portion that branches into at least two parts toward the holding member side and has a hollow inside. Also, the assembly groove includes an in-groove protrusion that is arranged in the hollow portion, and an in-groove protrusion convex portion that abuts against the inner wall of the hollow portion is provided on the side wall of the in-groove protrusion that corresponds to the partition portion. Therefore, the in-groove protrusion is arranged in the hollow portion of the partition portion, and a pressing force acts on the inner wall of the hollow portion by abutting against the in-groove protrusion convex portion, so that deformation of the partition portion against an external force is suppressed.

[0017] In order to achieve the above object, the technology described in claim 6 is the technology described in claim 5, wherein the convex portion of the assembly groove and the inner-groove protrusion convex portion are configured to abut perpendicularly against the outer surface and the inner surface of the hollow portion at the partition portion of the sealing means.

[0018] According to the configuration of the above technology, in addition to the effect of the technology described in claim 5, the convex portion of the assembly groove and the inner-groove protrusion convex portion perpendicularly abut against the outer surface and the inner surface of the hollow portion at the partition portion, thereby expanding the range over which the outer surface and inner surface of the partition portion are subjected to high surface pressure.

[0019] In order to achieve the above object, the technology described in claim 7 is the technology described in any one of claims 1 to 6, wherein the sealing means further includes an outer branch portion where the partition portion branches off to an outer circular portion, and an inner branch portion where the partition portion branches off to an inner circular portion, and the outer branch portion and the inner branch portion are positioned outside the distribution area of ​​the openings of the communicating passage that the sealing means crosses while sliding.

[0020] According to the configuration of the above technology, in addition to the effect of the technology described in any one of claims 1 to 6, the outer branch portion and the inner branch portion of the sealing means, which are subject to particularly high surface pressure, are positioned outside the distribution area of ​​the opening across which the sealing means slides.

[0021] In order to achieve the above object, the technology described in claim 8 is directed to the technology described in any one of claims 1 to 6, wherein, among the openings of the communicating passage, the opening across which the partition portion of the sealing means slides has an intersecting opening edge extending in a direction intersecting the sliding direction, the intersecting opening edge has a curved surface that curves toward the inside of the opening, and the diameter of the curved surface is larger toward the center than at both ends of the intersecting opening edge.

[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 6, the opening of the communication passage of the stator is more likely to protrude when the partition of the sealing means crosses it, as it is opened. However, the crossing opening edge of this opening has a larger diameter at the inner curved surface than at both ends. Therefore, even if the partition protrudes significantly at the inner side of the opening when it is opened, the large-diameter curved surface of the crossing opening edge allows the partition to pass smoothly.

[0023] In order to achieve the above object, the technology described in claim 9 is based on any one of the technologies described in claims 1 to 6, and is characterized in that an auxiliary seat portion that extends along the sliding direction and comes into contact with the partition portion is provided on the inside of the opening of the communicating passage, which opening is crossed by the partition portion of the sealing means while sliding.

[0024] According to the configuration of the above technology, in addition to the effect of the technology described in any one of claims 1 to 6, an auxiliary seat with which the partition part of the seal means comes into contact is provided on the inside of the opening of the stator through which the partition part of the seal means slides across. Therefore, when the partition part crosses the opening, it comes into contact with the auxiliary seat part.

[0025] In order to achieve the above-mentioned object, the technology described in claim 10 is directed to the technology described in any one of claims 1 to 6, in which a protrusion prevention means is provided to prevent the partition portion of the sealing means from protruding from the assembly groove.

[0026] According to the configuration of the above technique, in addition to the effect of the technique of any one of claims 1 to 6, the protrusion of the partition portion of the seal means from the assembly groove is restricted by the protrusion restriction means.

[0027] In order to achieve the above object, the technology described in claim 11 is the technology described in claim 1 or 2, wherein one of the stator and the valve body is a retaining member that retains the sealing means, and the other is a slidable member against which the sealing means slides, the sealing means has a mountain-shaped cross section that expands toward the retaining member side, and includes a recess that is recessed on the slidable member side, and a hollow portion that is branched into at least two toward the retaining member side and has a hollow inside, and the sealing means has a smaller compression allowance on the inner diameter side than on the outer diameter side.

[0028] According to the configuration of the above technology, in addition to the function of the technology described in claim 1 or 2, the sealing means has a mountain-shaped cross section that expands toward the holding member side, and includes a recessed portion that is recessed toward the sliding member side, and a hollow portion that branches into at least two toward the holding member side and has a hollow inside. The compression allowance of this sealing means is smaller on the inner diameter side than on the outer diameter side. The surface pressure of the sealing means becomes smaller as the compression allowance becomes smaller.

[0029] In order to achieve the above object, the technology described in claim 12 is the technology described in claim 11, wherein the compression allowance of the partition portion is smaller than the compression allowance on the inner diameter side of the outer circular portion.

[0030] According to the configuration of the above technology, in addition to the effect of the technology described in claim 11, when the valve body is driven, the partition and the outer circular part are compressed by the sliding of the sealing means, but the compression allowance of the partition is smaller than the compression allowance of the inner diameter side of the outer circular part. The smaller the compression allowance, the smaller the surface pressure becomes.

[0031] In order to achieve the above object, the technology described in claim 13 is the technology described in claim 11, wherein the compression allowance on the inner diameter side of the outer circular portion is smaller in the vicinity of the partition portion.

[0032] According to the configuration of the above technology, in addition to the effect of the technology described in claim 11, when the valve body is driven, the partition and the outer circular part are compressed by the sliding of the sealing means, but the compression allowance on the inner diameter side of the outer circular part is smaller closer to the partition. The smaller the compression allowance, the smaller the surface pressure becomes.

[0033] In order to achieve the above object, the technology described in claim 14 is the technology described in claim 11, wherein the compression allowance on the inner diameter side of the inner circular portion is smaller in the vicinity of the partition portion.

[0034] According to the configuration of the above technology, in addition to the effect of the technology described in claim 11, when the valve body is driven, the partition part and the inner circular part are compressed by the sliding of the sealing means, but the compression allowance on the inner diameter side of the inner circular part is smaller closer to the partition part. The smaller the compression allowance, the smaller the surface pressure becomes.

[0035] In order to achieve the above object, the technology described in claim 15 is based on the technology described in claim 11, and is further characterized in that the sealing means further includes an outer branch portion where the partition portion branches off to an outer circular portion, and an inner branch portion where the partition portion branches off to an inner circular portion, and the outer branch portion and the inner branch portion include a seal surface pressure dispersion portion for dispersing the seal surface pressure.

[0036] According to the configuration of the above technology, in addition to the effect of the technology described in claim 11, the outer branch portion and the inner branch portion of the sealing means contract due to compression during assembly, and the sealing surface pressure increases. However, since the sealing surface pressure dispersing portion is included, the sealing surface pressure is dispersed by the dispersing portion.

[0037] In order to achieve the above object, the technology described in claim 16 is the technology described in claim 15, in which reinforcing legs are provided in the hollow portion to reinforcingly support the sealing means in the assembly groove.

[0038] According to the configuration of the above technology, in addition to the effect of the technology described in claim 15, even if the area of ​​the sealing means on the side of the sliding member is widened, the reinforcing legs are provided in the hollow portion on the opposite side, so that the sealing means is supported and reinforced by the assembly groove.

[0039] In order to achieve the above object, the technology recited in claim 17 is characterized in that in the technology recited in any one of claims 1 to 6, the flow path switching device is used in a cooling system for an electric vehicle.

[0040] According to the configuration of the above technology, the flow path switching device used in the cooling system of an electric vehicle can achieve the same effect as the technology described in any one of claims 1 to 6. Effect of the Invention

[0041] According to the technique recited in claim 1, the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0042] According to the technique recited in claim 2, the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0043] According to the technique recited in claim 3, the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0044] According to the technique recited in claim 4, the sealing performance of the sealing means can be ensured without any significant increase in manufacturing costs, and the sealing means can be prevented from falling off from the assembly groove.

[0045] According to the technology described in claim 5, in addition to the effect of the technology described in claim 2, it is possible to suppress the displacement of the partition of the sealing means and suppress the repulsive force while ensuring the surface pressure required for sealing. Also, when the fluid is a liquid, the recess of the partition becomes a liquid pool, and the lubricating effect of the liquid can reduce the sliding resistance of the partition against the sliding member.

[0046] According to the technique recited in claim 6, in addition to the effect of the technique recited in claim 5, it is possible to reduce stress concentration on the outer and inner surfaces of the partition of the seal means.

[0047] According to the technology described in claim 7, in addition to the effects of the technology described in any one of claims 1 to 6, when the sealing means crosses the opening of the communicating passage, the outer branch portion and the inner branch portion, which are subjected to high surface pressure, can be prevented from jumping into the opening, getting caught on the periphery of the opening, and having poor sliding properties.

[0048] According to the technology described in claim 8, in addition to the effects of the technology described in any one of claims 1 to 6, even if the partition portion protrudes into the opening of the communicating passage when crossing the opening, the sealing means can reduce the risk of getting caught on the intersecting opening edge or deterioration of sliding properties when riding over the intersecting opening edge.

[0049] According to the technology described in claim 9, in addition to the effects of the technology described in any one of claims 1 to 6, when the partition portion of the sealing means crosses the opening of the communicating passage, it is possible to suppress the partition portion from protruding into the opening, thereby reducing the partition portion from getting caught on the periphery of the opening and the deterioration of sliding properties.

[0050] According to the technology described in claim 10, in addition to the effects of the technology described in any one of claims 1 to 6, the posture of the partition of the sealing means can be maintained and the partition can be prevented from protruding into the opening of the communicating passage when the partition crosses the opening, thereby reducing the partition getting caught on the periphery of the opening and the deterioration of sliding properties.

[0051] According to the technology described in claim 11, in addition to the effects of the technology described in claim 1 or 2, the sealing surface pressure of the sealing means can be made to act uniformly between the outer diameter side and the inner diameter side of the sealing means.

[0052] According to the technique recited in claim 12, in addition to the effect of the technique recited in claim 11, it is possible to apply an appropriate seal surface pressure between the partition portion and the outer circular portion of the seal means.

[0053] According to the technology recited in claim 13, in addition to the effect of the technology recited in claim 11, it is possible to apply an appropriate sealing surface pressure to the outer circular portion of the sealing means depending on the portion.

[0054] According to the technique recited in claim 14, in addition to the effect of the technique recited in claim 11, it is possible to apply an appropriate sealing surface pressure to the inner circular portion of the sealing means depending on the portion.

[0055] According to the technique recited in claim 15, in addition to the effect of the technique recited in claim 11, it is possible to apply an appropriate seal surface pressure to the outer branch portion and the inner branch portion of the seal means.

[0056] According to the technology recited in claim 16, in addition to the effect of the technology recited in claim 15, a reaction force against the pressing force during sliding can be secured on the side of the hollow portion of the sealing means, and an appropriate sealing surface pressure can be applied to the sealing means.

[0057] According to the technology recited in claim 17, it is possible to obtain an effect equivalent to that of the technology recited in any one of claims 1 to 6 with respect to a flow path switching device used in a cooling system of an electric vehicle. [Brief description of the drawings]

[0058] [Figure 1] FIG. 2 is a perspective view showing a flow path switching device in the first embodiment. [Diagram 2] FIG. 2 is a front view showing the flow path switching device in the first embodiment. [Diagram 3] FIG. 2 is a plan view showing the flow path switching device in the first embodiment. [Figure 4] FIG. 3 is a bottom view showing the flow path switching device in the first embodiment. [Diagram 5] FIG. 2 is an exploded perspective view showing the flow path switching device in the first embodiment. [Figure 6] 3 is a cross-sectional view taken along line AA in FIG. 2 showing the flow path switching device according to the first embodiment. [Figure 7] 4 is a cross-sectional view of the flow path switching device taken along line BB in FIG. 3 according to the first embodiment. [Figure 8] FIG. 3 is a perspective view showing the inside of an upper housing in the first embodiment. [Figure 9] FIG. 3 is a perspective view showing a first rotating disk in the first embodiment. [Figure 10] FIG. 3 is a plan view showing a first rotating disk in the first embodiment. [Figure 11] FIG. 4 is a bottom view showing the first rotating disk in the first embodiment. [Figure 12] FIG. 4 is a plan view showing a second rotating disk in the first embodiment. [Figure 13] FIG. 4 is a bottom view showing the second rotating disk in the first embodiment. [Figure 14] FIG. 3 is a perspective view showing a rotation shaft in the first embodiment. [Figure 15] 15 is a cross-sectional view taken along line EE in FIG. 14, showing a rotation shaft in the first embodiment. [Figure 16] 3 is a cross-sectional view taken along line FF in FIG. 2, showing the flow path switching device 1 according to the first embodiment. [Figure 17] 3 is a schematic cross-sectional view taken along line GG in FIG. 2, illustrating the rotational position of a first rotating disk with respect to an upper housing for a "first pattern" of a flow path switching pattern in the first embodiment. [Figure 18] 3 is a schematic cross-sectional view of the first embodiment taken along line HH in FIG. 2, showing the rotational position of the second rotating disk relative to the lower housing for the "first pattern." FIG. [Figure 19] 18 is a schematic diagram equivalent to FIG. 17 showing the rotational position of the first rotating disk with respect to the upper housing in the "second pattern" of the flow path switching pattern in the first embodiment. FIG. [Figure 20] FIG. 19 is a schematic diagram equivalent to FIG. 18 showing the rotational position of the second rotating disk with respect to the lower housing for the "second pattern" in the first embodiment. [Figure 21] FIG. 2 is a circuit diagram showing an example of use of the flow path switching device in the first embodiment. [Figure 22] 4A and 4B are plan and bottom views respectively showing the side of a first rotating disk in contact with an upper housing and the side of a second rotating disk in contact with a lower housing in the first embodiment. [Diagram 23] 23 is an enlarged cross-sectional view showing the first rotating disk and the upper housing taken along line II in FIG. 22 at the portion of the assembly groove to which the upper seal member is attached in the first embodiment; FIG. [Figure 24] 24 is an enlarged cross-sectional view equivalent to FIG. 23 showing a deformation state of the upper seal member when a rotational force acts in a direction perpendicular to the upper seal member in the first embodiment. FIG. [Diagram 25] 23 is a plan view equivalent to FIG. 22 showing a state in which each rotary disk rotates and the partition portion of each seal member crosses the entrance and exit of each inlet / outlet passage in the first embodiment. FIG. [Figure 26] FIG. 4 is a plan view illustrating a simplified state in which each seal member is assembled into an assembly groove in the first embodiment. [Figure 27] FIG. 3 is a plan view illustrating only an assembly groove in the first embodiment. [Figure 28] FIG. 3 is a plan view illustrating only the sealing members in a simplified manner in the first embodiment. [Figure 29] 24 is an enlarged cross-sectional view equivalent to FIG. 23 showing a state in which a partition portion of a first seal member is assembled into an assembly groove in the second embodiment. [Diagram 30] 29 according to the second embodiment, showing a state in which the partition portion is assembled into the assembly groove. FIG. [Diagram 31] 29 according to the third embodiment, showing a state in which the partition portion of the first seal member is assembled into the assembly groove. FIG. [Diagram 32] 32 is a cross-sectional view taken along line KK in FIG. 31 , showing a state in which the partition portion is assembled into the assembly groove according to the third embodiment. [Diagram 33] 33 is a cross-sectional view taken along line NN in FIG. 32, illustrating a state in which the partition portion is assembled into the assembly groove according to the third embodiment. [Diagram 34] FIG. 33 is a cross-sectional view corresponding to FIG. 32 showing a state in which the partition portion is assembled into the assembly groove according to a comparative example of the third embodiment. [Diagram 35] 34 is an enlarged cross-sectional view equivalent to FIG. 33 showing a state in which the partition portion of the first seal member is assembled into the assembly groove in the fourth embodiment. [Diagram 36] 34 is an enlarged cross-sectional view equivalent to FIG. 33 showing a state in which the partition portion of the first seal member is assembled into the assembly groove in the fifth embodiment. [Figure 37] FIG. 23 is an enlarged plan view showing the vicinity of a partition portion of a first seal member assembled in an assembly groove of a first rotating disk, according to a comparative example of the sixth embodiment. [Figure 38] FIG. 23 is a cross-sectional view illustrating a state in which a partition portion crosses an entrance / exit according to a comparative example of the sixth embodiment. [Figure 39]FIG. 38 is an enlarged plan view equivalent to FIG. 37 showing the vicinity of a partition portion of a first seal member assembled in an assembly groove of a first rotating disk in the sixth embodiment. [Diagram 40] FIG. 23 is a bottom view showing one of the openings of the first to fourth inlet / outlet passages that opens to the inner surface of the upper housing in the seventh embodiment. [Diagram 41] 41 is a cross-sectional view showing the entrance of the seventh embodiment taken along line C1-C1 or line C2-C2 in FIG. 40. [Diagram 42] FIG. 41 is a cross-sectional view showing the entrance taken along line DD in FIG. 40 according to the seventh embodiment. [Diagram 43] FIG. 23 is a bottom view showing one of the openings of the first to fourth inlet / outlet passages opening to the inner surface of the upper housing in the eighth embodiment. [Diagram 44] 44 is a cross-sectional view showing the entrance of the eighth embodiment taken along line QQ in FIG. 43. [Diagram 45] FIG. 23 is a bottom view illustrating simply only the assembly groove in the second rotating disc in the ninth embodiment. [Figure 46] 46 is an enlarged cross-sectional view taken along lines S1-S1 and S2-S2 in FIG. 45 (centers of the partitions) showing a state in which the partitions of the second seal member are assembled into the assembly grooves in the ninth embodiment. [Figure 47] FIG. 47 is an enlarged exploded cross-sectional view showing an assembly structure of the portion shown in FIG. 46 according to the ninth embodiment. [Figure 48] FIG. 49 is a bottom view showing the part shown in FIG. 48 as viewed from below in FIG. 46 according to the ninth embodiment. [Figure 49] 46 is an enlarged cross-sectional view illustrating the state in which the partition portion of the second seal member is assembled into the assembly groove, taken along lines T1-T1 and T2-T2 in FIG. 45 (portions other than the center of the partition portion) in the ninth embodiment. [Figure 50] FIG. 23 is a plan view showing a side where a first rotating disk contacts an upper housing, according to a comparative example of the tenth embodiment. [Figure 51]51 is an enlarged cross-sectional view showing a first rotating disk and an upper housing, taken along line UU in FIG. 50, at a portion of an assembly groove in which an outer circular portion of a first seal member is assembled, according to a comparative example of the tenth embodiment. [Figure 52] FIG. 23 is a plan view showing the side where the first rotating disk contacts the upper housing in the tenth embodiment. [Diagram 53] 53 is an enlarged cross-sectional view showing the first seal member and the assembly groove of the first rotating disc in the tenth embodiment, taken along line V1-V1 (outer circle portion) and line V2-V2 (inner circle portion) in FIG. 52. [Figure 54] FIG. 54 is an enlarged cross-sectional view equivalent to FIG. 53 showing a portion of a first seal member and an assembly groove of a first rotating disc in the eleventh embodiment. [Figure 55] FIG. 23 is a plan view showing the side where the first rotating disk contacts the upper housing in the twelfth embodiment. [Figure 56] 58 is an enlarged cross-sectional view showing the first seal member and the assembly groove of the first rotating disk taken along line WW (partition portion) in FIG. 57 according to the twelfth embodiment. FIG. [Figure 57] FIG. 57 is an enlarged cross-sectional view equivalent to FIG. 56 showing the first seal member and the assembly groove of the first rotating disc in the thirteenth embodiment. [Figure 58] FIG. 23 is a plan view showing the side where the first rotating disk contacts the upper housing in the fourteenth embodiment. [Figure 59] 59 is an enlarged cross-sectional view showing the first seal member and the assembly groove of the first rotating disc taken along line Z1-Z1 in FIG. 58 (the outer branch portion near the partition portion) in the fourteenth embodiment. [Figure 60] 59 is an enlarged cross-sectional view showing the first seal member and the assembly groove of the first rotating disc taken along line Z2-Z2 in FIG. 58 (the inner branch portion near the partition portion) in the fifteenth embodiment. [Figure 61] FIG. 39 is an enlarged plan view showing a portion of a partition of a first seal member assembled in an assembly groove of a first rotating disc in the sixteenth embodiment. [Figure 62]FIG. 23 is an enlarged plan view showing a portion of an outer branch portion of a first seal member assembled in an assembly groove of a first rotating disc in a sixteenth embodiment. [Figure 63] FIG. 63 is a cross-sectional view taken along line PP in FIG. 62 showing a portion of the outer branching portion according to the sixteenth embodiment. [Figure 64] FIG. 63 is a cross-sectional view equivalent to FIG. 62 showing a portion of an outer branching portion according to a modified example of the sixteenth embodiment. [Figure 65] 31 , showing a comparative example of the seventeenth embodiment in which the partition portion of the first seal member is assembled into the assembly groove and before the first seal member is crushed without contacting the inner surface of the upper housing. FIG. [Figure 66] FIG. 67 is an enlarged cross-sectional view equivalent to FIG. 65 showing a comparative example of the seventeenth embodiment, in which the partition portion is similarly assembled into the assembly groove and the first seal member is in contact with the inner surface of the upper housing and crushed. [Figure 67] This is an enlarged cross-sectional view similar to Figure 65 showing a comparative example of the 17th embodiment in which the partition portion is similarly assembled into the assembly groove, the first rotating disk is rotating, and the first seal member is sliding on the inner surface of the upper housing. [Figure 68] 31 in the seventeenth embodiment, showing a state in which the partition portion of the first seal member is assembled into the assembly groove and before the first seal member is crushed without contacting the inner surface of the upper housing. FIG. [Figure 69] FIG. 69 is an enlarged cross-sectional view similar to FIG. 68 showing the partition portion assembled into the assembly groove and the first seal member in contact with the inner surface of the upper housing and crushed in the seventeenth embodiment. [Figure 70] This is an enlarged cross-sectional view similar to Figure 68 showing the state in which the partition portion is assembled into the assembly groove, the first rotating disk is rotating, and the first seal member is sliding against the inner surface of the upper housing in the 17th embodiment. [Figure 71] FIG. 71 is an enlarged cross-sectional view equivalent to FIG. 70 showing a state in which a partition portion of a second seal member slides against an inner surface of a lower housing in the seventeenth embodiment. [Figure 72]FIG. 72 is an enlarged cross-sectional view similar to FIG. 71 showing the state in which the partition portion has just started to pass through the entrance of the lower housing in the seventeenth embodiment. [Figure 73] FIG. 72 is an enlarged cross-sectional view similar to FIG. 71 showing the partition portion passing through the entrance / exit according to the seventeenth embodiment. [Figure 74] 23 is an enlarged cross-sectional view showing the bottom of the mounting groove of the second rotating disc, one of the grooves split into two by an inner-groove protrusion, and the end of one of the legs assembled into the groove in the 18th embodiment. FIG. [Figure 75] FIG. 33 is a cross-sectional view corresponding to FIG. 32 showing a second seal member and an assembly groove in which the second seal member is assembled in the nineteenth embodiment. [Figure 76] 76 is an enlarged cross-sectional view showing the bottom of the assembly groove, one of the grooves, and an end of one of the legs assembled in the groove, taken along line K1-K1 in FIG. 75, in the 19th embodiment. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0059] Hereinafter, several embodiments of the flow path switching device will be described in detail with reference to the drawings.

[0060] First Embodiment The first embodiment will be described in detail with reference to FIGS.

[0061] [Outline of flow switching device] FIG. 1 shows a perspective view of the flow path switching device 1 of this embodiment. FIG. 2 shows a front view of the flow path switching device 1. FIG. 3 shows a plan view of the flow path switching device 1. FIG. 4 shows a bottom view of the flow path switching device 1. FIG. 5 shows an exploded perspective view of the flow path switching device 1. FIG. 6 shows a cross-sectional view of the flow path switching device 1 taken along line AA in FIG. 2. FIG. 7 shows a cross-sectional view of the flow path switching device 1 taken along line BB in FIG. 3. As shown in FIGS. 1 to 7, the flow path switching device 1 includes a housing 2, a valve body portion 3 arranged inside the housing 2, and a drive portion 4 that drives the valve body portion 3.

[0062] [About housing] As shown in Figs. 1 to 7, the housing 2 includes an upper housing 11 and a lower housing 12, and is configured by fastening the two housings 11, 12 with a plurality of screws 6. The housing 2 corresponds to an example of a "stator" in this disclosed technology. The housing 2 includes an inflow / outflow passage 20 through which a fluid flows in and out. The flow path switching device 1 of this embodiment is configured as an eight-way valve as an example, and the housing 2 has eight inflow / outflow passages 20. As the eight inflow / outflow passages 20, the upper housing 11 is provided with a first inflow / outflow passage 21, a second inflow / outflow passage 22, a third inflow / outflow passage 23, and a fourth inflow / outflow passage 24, and the lower housing 12 is provided with a fifth inflow / outflow passage 25, a sixth inflow / outflow passage 26, a seventh inflow / outflow passage 27, and an eighth inflow / outflow passage 28. Fig. 8 shows the inside of the upper housing 11 in a perspective view. As shown in FIG. 8, the entrance 21a of the first inflow / outflow passage 21, the entrance 22a of the second inflow / outflow passage 22, the entrance 23a of the third inflow / outflow passage 23, and the entrance 24a of the fourth inflow / outflow passage 24 are opened on the inside of the upper housing 11. Similarly, as shown in FIG. 5, the entrances 25a, 26a, 27a, and 28a of the fifth inflow / outflow passage 25 to the eighth inflow / outflow passage 28 are opened on the inside of the lower housing 12. The inflow / outflow passage 20 corresponds to an example of a "communication passage" provided in the "stator" of this disclosed technology. Also, each of the entrances 21a to 28a corresponds to an example of an "opening" of the "communication passage" of this disclosed technology. In this embodiment, the housing 2 is formed of, for example, resin.

[0063] [About the valve body] As shown in Figs. 5 to 7, the valve body portion 3 includes a first rotating disk 13 and a second rotating disk 14 that rotate in the housing 2 and are stacked adjacent to each other vertically, and a rotating shaft 15 that drives and rotates both rotating disks 13, 14. Both rotating disks 13, 14 are stacked in the axial direction X. The first rotating disk 13 and the second rotating disk 14 correspond to an example of a "valve body" in this disclosed technology. Both rotating disks 13, 14 and the rotating shaft 15 are formed of, for example, resin.

[0064] [About the first rotating disk] FIG. 9 shows the first rotating disk 13 in a perspective view. FIG. 10 shows the first rotating disk 13 in a plan view. FIG. 11 shows the first rotating disk 13 in a bottom view. As shown in FIG. 5 to FIG. 7, the first rotating disk 13 is accommodated in the housing 2 together with the second rotating disk 14. As shown in FIG. 9 to FIG. 11, the first rotating disk 13 is formed in a substantially cylindrical shape with a bottom, and includes two rotation passages 30 that open upward in the axial direction X. As the two rotation passages 30, a first rotation passage 31 and a second rotation passage 32 are provided. The rotation passage 30 is semicircular in plan view. The rotation passage 30 corresponds to an example of a "communication passage" provided in the "valve body" of this disclosed technology. A first shaft hole 13a through which the rotating shaft 15 passes is formed in the center of the first rotating disk 13. A first boss 13b is formed in the first rotating disk 13, centered on the first shaft hole 13a.

[0065] [About the second rotating disk] FIG. 12 shows the second rotating disk 14 in a plan view. FIG. 13 shows the second rotating disk 14 in a bottom view. As shown in FIG. 13, the second rotating disk 14 is formed in a substantially cylindrical shape with a bottom like the first rotating disk 13, and includes two rotation passages 40 that open downward in the axial direction X. As the two rotation passages 40, a third rotation passage 43 and a fourth rotation passage 44 are provided. This rotation passage 40 is semicircular in shape when viewed from the bottom. This rotation passage 40 corresponds to an example of a "communication passage" provided in the "valve body" of this disclosed technology. A second shaft hole 14a through which the rotating shaft 15 penetrates is also formed in the center of the second rotating disk 14. As shown in FIG. 12, a second boss 14b is formed on the upper surface side of the second rotating disk 14, centered on the second shaft hole 14a.

[0066] [About the rotation axis] FIG. 14 shows the rotating shaft 15 in a perspective view. FIG. 15 shows the rotating shaft 15 in a cross-sectional view taken along the line EE in FIG. 14. As shown in FIGS. 14 and 15, the rotating shaft 15 of this embodiment is formed in multiple stages with different outer diameters in parts. The upper end 15a of the rotating shaft 15, which is connected to the driving unit 4, is a gear having multiple teeth. The lower end 15b of the rotating shaft 15, which is fitted into the shaft hole 12a of the lower housing 12, has a small diameter and an irregular shape. A pair of first and second protrusions 15c and 15d are arranged on the same circumference on the outer periphery of the middle part of the rotating shaft 15. As shown in FIG. 15, the protrusions 15c and 15d protrude in an arc shape on the outer periphery of the rotating shaft 15 and are arranged at an interval of 180 degrees. The first protrusion 15c has a longer circumferential length than the second protrusion 15d. Here, it is preferable that the protrusions 15c, 15d are arranged in two or more locations to ensure stable engagement with the first rotating disk 13 and the second rotating disk 14, and it is also preferable that they are arranged and shaped asymmetrically to prevent incorrect assembly.

[0067] 5 to 7, the rotating shaft 15 is provided penetrating the upper housing 11 and both rotating disks 13, 14. An upper end 15a of the rotating shaft 15 passes through a through hole 11a of the upper housing 11 and is connected to the driving unit 4, and a lower end 15b is rotatably supported by a shaft hole 12a of the lower housing 12.

[0068] As shown in FIG. 6 and FIG. 7, a bearing 51 that rotatably supports the rotating shaft 15 is provided in the through hole 11a of the upper housing 11. A washer 52 is provided at the upper end opening of the through hole 11a, centering on the rotating shaft 15. The washer 52 is held by an E-ring 53 fixed on the rotating shaft 15. A compression spring 54 is provided on the rotating shaft 15 between the bearing 51 and the washer 52. The compression spring 54 biases the rotating shaft 15 upward in the axial direction X, thereby preventing rattling due to vibration of the rotating shaft 15. The bearing 51 supports the rotating shaft 15 with an inner ring to smooth the rotation of the rotating shaft 15. The bearing 51 also supports the compression spring 54 with an inner ring to smooth the rotation of the compression spring 54. Furthermore, a lip seal 55 that prevents leakage of fluid is provided between the upper housing 11 and the rotating shaft 15 in the through hole 11a. The rotating shaft 15 may be made of metal.

[0069] 6 and 7, a torsion spring 56 is provided inside the shaft hole 12a of the lower housing 12, centered on the lower end 15b of the rotating shaft 15. The torsion spring 56 is interposed between the bottom of the shaft hole 12a and the middle part of the rotating shaft 15, and biases the rotating shaft 15 in the rotation direction Y, thereby eliminating rattling between the rotating shaft 15 and the drive unit 4.

[0070] [Rotation transmission mechanism] The flow path switching device 1 of this embodiment includes a rotation transmission mechanism for transmitting the rotational force of the rotating shaft 15 to the first rotating disk 13 and the second rotating disk 14. Fig. 16 shows the flow path switching device 1 in a cross-sectional view taken along line FF in Fig. 2. The rotation transmission mechanism of this embodiment is provided between the first rotating disk 13 and the second rotating disk 14 and the rotating shaft 15, and is configured to allow relative movement of the first rotating disk 13 and the second rotating disk 14 in the axial direction X of the rotating shaft 15, and to be able to partially release the transmission of the rotational force of the rotating shaft 15 to the first rotating disk 13 and the second rotating disk 14 as the rotating shaft 15 rotates.

[0071] In this embodiment, both rotating disks 13, 14 and a rotating shaft 15 are connected to be relatively movable in the rotation direction Y and the axial direction X. That is, as shown in FIG. 16, the rotating shaft 15 is assembled to the first boss 13b so as to coincide with the center of the first boss 13b of the first rotating disk 13. As shown in FIG. 11, FIG. 12 and FIG. 16, the first boss 13b has a pair of first notches 13c, 13d in which a part of the circumferential direction is missing. As shown in FIG. 16, the first protrusion 15c and the second protrusion 15d are fitted into the first notches 13c, 13d. A gap 16 is provided in the circumferential direction between the first notches 13c, 13d and the first protrusion 15c and the second protrusion 15d. Therefore, the rotating shaft 15 and the first rotating disk 13 are allowed to move relatively in the axial direction X along the first cutouts 13c, 13d and the protrusions 15c, 15d, and are allowed to move relatively in the rotational direction Y within the range of the gaps 16 between the first cutouts 13c, 13d and the protrusions 15c, 15d. In this manner, the rotating shaft 15 is connected to the first rotating disk 13 so as to be movable relatively in the rotational direction Y and the axial direction X.

[0072] On the other hand, like the first rotating disk 13, the rotating shaft 15 is assembled to the second boss 14b so as to coincide with the center of the second boss 14b of the second rotating disk 14. Like the first boss 13b, the second boss 14b has a pair of second notches 14c, 14d that are missing a part in the circumferential direction, as shown in FIG. 12. The first protrusion 15c and the second protrusion 15d are fitted into these second notches 14c, 14d. A gap is also provided in the circumferential direction between the second notches 14c, 14d and each of the protrusions 15c, 15d. Therefore, the rotating shaft 15 and the second rotating disk 14 are allowed to move relatively in the axial direction X along the second notches 14c, 14d and each of the protrusions 15c, 15d, and are allowed to move relatively in the rotation direction Y within the range of the gap between the second notches 14c, 14d and each of the protrusions 15c, 15d. In this manner, the rotating shaft 15 is connected to the second rotating disk 14 so as to be movable in the rotational direction Y and the axial direction X relative to the second rotating disk 14 .

[0073] The rotating shaft 15 rotates by receiving a driving force from the drive unit 4, and rotates relatively within the gap 16 at each boss 13b, 14b, and rotates integrally with both rotating disks 13, 14 by engaging with the circumferential inner surfaces of each notch 13c, 13d and each notch 14c, 14d.

[0074] [About sealing materials] As shown in Figs. 5 to 7, 9, 10 and 13, in this embodiment, a first seal member 17 and a second seal member 18 of a circumferential type having a substantially annular shape are provided between the first rotating disk 13 and the second rotating disk 14 and the housing 2 (the upper housing 11 and the lower housing 12) to suppress leakage of fluid. The first seal member 17 is provided on the first rotating disk 13, and the second seal member 18 is provided on the second rotating disk 14. That is, as shown in Figs. 9 and 10, a circumferential assembly groove 13e for assembling the first seal member 17 is formed on the upper surface of the first rotating disk 13 so as to surround the periphery of the openings of the two rotation passages 30 (the first rotation passage 31 and the second rotation passage 32). The first seal member 17 is fitted and fixed in the assembly groove 13e, and is provided so as to protrude from the upper surface of the first rotating disk 13. As shown in FIG. 13, a circumferential type assembly groove 14e for assembling the second seal member 18 is formed on the lower surface of the second rotating disk 14 so as to surround the openings of the two rotating passages 40 (the third rotating passage 43 and the fourth rotating passage 44). The second seal member 18 is fitted and fixed in the assembly groove 14e, and is provided so as to protrude from the lower surface of the second rotating disk 14. In this embodiment, the seal members 17, 18 are formed only from rubber. The seal members 17, 18 may be formed from fluororesin (e.g., Teflon (registered trademark)) or from rubber to which fluororesin is attached. In addition, the seal members 17, 18 in this embodiment have a cross section cut in a direction perpendicular to the longitudinal direction of each part (hereinafter referred to as a "vertical cross section") that forms a mountain shape (M-shape).

[0075] [About the drive unit] The drive unit 4 includes a motor or the like (not shown) for applying a rotational driving force to the rotary shaft 15. The flow path switching device 1 is configured to selectively combine and connect the rotation passages 30, 40 of both rotary disks 13, 14 and the inflow / outflow passages 20 (the first inflow / outflow passage 21 to the eighth inflow / outflow passage 28) of the housing 2 by driving the rotary disks 13, 14 to rotate via the rotary shaft 15 by the drive unit 4, thereby switching and forming a series of flow paths. In other words, a plurality of "flow path switching patterns" described later are formed.

[0076] [About flow path switching patterns] Here, an example of the flow path switching pattern will be described. FIG. 17 shows the rotational position of the first rotating disk 13 relative to the upper housing 11 in a schematic cross-sectional view taken along line GG in FIG. 2, which relates to the "first pattern" of the flow path switching pattern. In FIG. 17, the contour of the upper housing 11, which does not appear in the cross-sectional view, is shown by a two-dot chain line. FIG. 18 shows the rotational position of the second rotating disk 14 relative to the lower housing 12 in a schematic cross-sectional view taken along line HH in FIG. 2, which relates to the "first pattern". In FIG. 18, the contour of the lower housing 12, which does not appear in the cross-sectional view, is shown by a two-dot chain line. FIG. 19 shows the rotational position of the first rotating disk 13 relative to the upper housing 11 in a schematic cross-sectional view similar to FIG. 17, which relates to the "second pattern" of the flow path switching pattern. In FIG. 20, the rotational position of the second rotating disk 14 relative to the lower housing 12 in a schematic cross-sectional view similar to FIG. 18, which relates to the "second pattern".

[0077] In the first pattern, as shown in Fig. 17 and Fig. 18, depending on the rotational positions of the first rotating disk 13 and the second rotating disk 14, the first rotation passage 31 of the first rotating disk 13 communicates with the first inflow / outflow passage 21 and the second inflow / outflow passage 22, and the second rotation passage 32 communicates with the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24. In addition, the third rotation passage 43 of the second rotating disk 14 communicates with the fifth inflow / outflow passage 25 and the sixth inflow / outflow passage 26, and the fourth rotation passage 44 communicates with the seventh inflow / outflow passage 27 and the eighth inflow / outflow passage 28. In this state, as shown by the arrows in Fig. 17, the fluid that has flowed into the first inflow / outflow passage 21 flows out from the second inflow / outflow passage 22 via the first rotation passage 31, and the fluid that has flowed into the fourth inflow / outflow passage 24 flows out from the third inflow / outflow passage 23 via the second rotation passage 32. Furthermore, as shown by the arrows in Figure 18, the fluid that flows into the sixth inflow / outflow passage 26 flows out from the fifth inflow / outflow passage 25 via the third rotation passage 43, and the fluid that flows into the seventh inflow / outflow passage 27 flows out from the eighth inflow / outflow passage 28 via the fourth rotation passage 44.

[0078] In the second pattern, as shown in Fig. 19 and Fig. 20, the first rotating disk 13 and the second rotating disk 14 rotate about 60° counterclockwise from the state of the first pattern, and the first rotation passage 31 of the first rotating disk 13 communicates with the first inflow / outflow passage 21 and the third inflow / outflow passage 23, and the second rotation passage 32 communicates with the second inflow / outflow passage 22 and the fourth inflow / outflow passage 24. In addition, the third rotation passage 43 of the second rotating disk 14 communicates with the fifth inflow / outflow passage 25 and the sixth inflow / outflow passage 26, and the fourth rotation passage 44 communicates with the seventh inflow / outflow passage 27 and the eighth inflow / outflow passage 28. In this state, as shown by the arrows in Fig. 19, the fluid that has flowed into the first inflow / outflow passage 21 flows out from the third inflow / outflow passage 23 via the first rotation passage 31, and the fluid that has flowed into the fourth inflow / outflow passage 24 flows out from the second inflow / outflow passage 22 via the second rotation passage 32. As shown by the arrows in Figure 20, the fluid that flows into the seventh inflow / outflow passage 27 flows out from the eighth inflow / outflow passage 28 via the fourth rotation passage 44, and the fluid that flows into the sixth inflow / outflow passage 26 flows out from the fifth inflow / outflow passage 25 via the third rotation passage 43.

[0079] In this embodiment, as shown in Figures 5, 7 and 16, a plurality of compression springs 61 are provided between the first rotating disk 13 and the second rotating disk 14 to separate the first rotating disk 13 and the second rotating disk 14 from each other and to bias them in a direction toward the upper housing 11 and the lower housing 12 in order to adjust the contact surface pressure of each seal member 17, 18 against the upper housing 11 and the lower housing 12. The plurality of compression springs 61 have the same shape and biasing force. In this embodiment, three compression springs 61 are disposed at equal angular intervals between the two rotating disks 13, 14. In this embodiment, the above-mentioned "rotation transmission mechanism" and the compression springs 61 constitute a "surface pressure adjustment mechanism."

[0080] As shown in Figs. 7, 11 and 12, three receiving holes 13f for receiving the upper parts of the compression springs 61 are provided at equal angular intervals on the bottom surface of the first rotating disk 13. As shown in Figs. 5, 7 and 12, three receiving holes 14f for receiving the lower parts of the compression springs 61 are provided at equal angular intervals on the top surface of the second rotating disk 14. Cylindrical portions 13g and 14g are provided at the centers of the receiving holes 13f and 14f, respectively, and the compression springs 61 are assembled and held around the cylindrical portions 13g and 14g. By assembling the compression springs 61 into the receiving holes 13f and 14f between the two rotating disks 13 and 14, the urging force of the compression springs 61 causes the two rotating disks 13 and 14 to be separated from each other and to approach the upper housing 11 and the lower housing 12, and the seal members 17 and 18 are urged in a direction to contact the inner surfaces of the upper housing 11 and the lower housing 12. In this embodiment, the above-mentioned rotation transmission mechanism connects each of the rotating disks 13, 14 to the rotating shaft 15 so that they can move relatively in the axial direction X. Therefore, each of the rotating disks 13, 14 is allowed to move in the axial direction X within a predetermined range by the biasing force of each of the compression springs 61.

[0081] [Examples of using the flow switching device] FIG. 21 shows a circuit diagram of an example of use of the flow path switching device 1. As shown in FIG. 21, in this embodiment, the flow path switching device 1 is used in a cooling system 91 mounted on an electric vehicle 90. In addition to the flow path switching device 1, the cooling system 91 includes a radiator 92, a PCU 93, a battery 94, and a chiller 95. A first pipe 96A is connected to the radiator 92, a second pipe 96B is connected to the PCU 93, a third pipe 96C is connected to the battery 94, and a fourth pipe 96D is connected to the chiller 95. In addition to the PCU 93, a first electric pump 97 is provided in the second pipe 96B, and in addition to the chiller 95, a second electric pump 98 is provided in the fourth pipe 96D. Both ends of the first pipe 96A are connected to the second inflow / outflow passage 22 and the sixth inflow / outflow passage 26 of the flow path switching device 1, and both ends of the second pipe 96B are connected to the third inflow / outflow passage 23 and the seventh inflow / outflow passage 27 of the flow path switching device 1. Both ends of the third pipe 96C are connected to the fourth inflow / outflow passage 24 and the eighth inflow / outflow passage 28 of the flow path switching device 1, and both ends of the fourth pipe 96D are connected to the first inflow / outflow passage 21 and the fifth inflow / outflow passage 25 of the flow path switching device 1. The flow of the refrigerant to each of the parts 92 to 95 is controlled by driving the flow path switching device 1 to switch the flow paths.

[0082] [Issues regarding sealing materials] 22 shows the side of the first rotating disk 13 that contacts the upper housing 11 and the side of the second rotating disk 14 that contacts the lower housing 12 in the same plan view (bottom view). In FIG. 22, what is shown by two-dot chain lines in each rotating disk 13 (14) is the inlet / outlet ports 21a, 22a, 23a, 24a (25a, 26a, 27a, 28a) of each inlet / outlet passage 21-24 (25-28) provided in each housing 11 (12). As shown in Fig. 22, each seal member 17 (18) includes an inner circular portion 17a (18a) arranged near the rotation axis 15 on the center side of each rotary disk 13 (14), an outer circular portion 17b (18b) arranged on the outer periphery side of each rotary disk 13 (14), and partition portions 17c (18c), 17d (18d) that connect the inner circular portion 17a (18a) and the outer circular portion 17b (18b) at least two points (two points in this embodiment) and separate the first rotation passage 31 (third rotation passage 43) and the second rotation passage 32 (fourth rotation passage 44). In Fig. 22, each seal member 17 (18) is shown with gauze (dots) to distinguish it from the others.

[0083] Fig. 23 shows an enlarged cross-sectional view of the first rotating disk 13 and the upper housing 11 taken along line II in Fig. 22 at the portion of the assembly groove 13e in which the first seal member 17 is assembled. Fig. 24 shows an enlarged cross-sectional view equivalent to Fig. 23 showing a deformation state of the first seal member 17 when a rotational force acts in a direction perpendicular to the first seal member 17. In this embodiment, of the housings 11, 12 and the rotating disks 13, 14, the rotating disks 13, 14 are holding members that hold the seal members 17, 18, and the housings 11, 12 are sliding members on which the seal members 17, 18 slide. As shown in Figs. 23 and 24, the first seal member 17 has a mountain-shaped cross section that expands toward the first rotating disk 13 side, and includes a top 19a that contacts the inner surface of the upper housing 11, a leg portion 19b that branches into at least two parts (two parts in this embodiment) from the top 19a toward the holding member side, a recess 19c that is recessed toward the upper housing 11 side, and a hollow portion 19d that is a hollow inside the bifurcated leg portion 19b. The top 19a includes two left and right protrusions 82a and 82b that have the same height. The lower ends of the two left and right leg portions 19b extend to the same length. The second seal member 18 also has a mountain-shaped cross section like the first seal member 17, and includes the top 19a, the leg portion 19b, the recess 19c, and the hollow portion 19d.

[0084] In this embodiment, the seal members 17, 18 provided on the rotating disks 13, 14 contact the inner surface of the upper housing 11 and the inner surface of the lower housing 12, respectively. Therefore, when the rotating disks 13, 14 rotate, sliding resistance is generated between the seal members 17, 18 and the upper housing 11 and the lower housing 12. In particular, the sliding resistance increases when the rotating disks 13, 14 start to rotate. In this embodiment, the seal members 17, 18 have a mountain-shaped vertical cross section, so that their legs 19b contact the bottom walls of the assembly grooves 13e, 14e and their tops 19a contact the inner surfaces of the housings 11, 12. Since there is a hollow portion 19d between the bifurcated legs 19b, when each rotating disk 13, 14 starts to rotate, the reaction force (strength) of each sealing member 17, 18 in the orthogonal direction decreases, and the Young's modulus in the orthogonal direction decreases. As shown in Figure 24, as the legs 19b slide, they may twist significantly, raising the concern that the sealing performance of each sealing member 17, 18 may not be ensured.

[0085] On the other hand, Fig. 25 is a plan view (bottom view) equivalent to Fig. 22 showing a state in which the partitions 17c (18c), 17d (18d) of the seal members 17 (18) pass (cross) through the inlets 23a, 22a (27a, 26a) of the inlet / outlet passages 23, 24 (27, 26) as the rotary disks 13 (14) rotate. As shown in Fig. 25, when the partitions 17c (18c), 17d (18d) of the seal members 17 (18) cross the inlets 21a-24a (25a-28a) of the inlet / outlet passages 21-24 (25-28), that is, when they are opened to the inlet / outlet passages 21-24 (25-28), the following changes occur in the seal members 17 (18). That is, in each seal member 17 (18), as shown by the arrow in Fig. 25, at the connection between the outer circular portion 17b (18b) and the partitions 17c (18c), 17d (18d), a part of the rubber material of the outer circular portion 17b (18b) is crushed and moves to the partitions 17c (18c), 17d (18d), and at the connection between the inner circular portion 17a (18a) and the partitions 17c (18c), 17d (18d), a part of the rubber material of the inner circular portion 17a (18a) is crushed and moves to the partitions 17c (18c), 17d (18d). As a result, at the partitions 17c (18c), 17d (18d), a part of the rubber material may be displaced toward each of the entrances 21a to 24a (25a to 28a) when opened, and may try to jump out. In order to ensure that the sealing members 17 (18) smoothly move from the inlet / outlet passages onto the inner surfaces of the housings 11 (12) and provide a good seal, it is necessary to prevent the partitions 17c (18c), 17d (18d) from protruding.

[0086] Therefore, in the flow path switching device 1 of this embodiment, in order to prevent the seal members 17, 18 from twisting or popping out, the assembly structure of the seal members 17, 18 into the assembly grooves 13e, 14e is configured as follows.

[0087] [Assembly structure of each sealing component] Fig. 26 shows a simplified plan view of the seal members 17 (18) of this embodiment assembled into the assembly grooves 13e (14e). Fig. 27 shows a simplified plan view of only the assembly grooves 13e (14e). Fig. 28 shows a simplified plan view of only the seal members 17 (18). In this embodiment, as shown in Figs. 27 and 28, the seal members 17 (18) and the assembly grooves 13e (14e) have substantially the same size and shape in a plan view, but the length (partition length) L2 of the partitions 17c (18c), 17d (18d) of each seal member 17 (18) is set to be slightly smaller than the length (partition groove length) L1 of a portion of the assembly groove 13e (14e) to which the partitions 17c (18c), 17d (18d) of each seal member 17 (18) are assembled. With this setting, the partition portions 17c (18c), 17d (18d) of the respective seal members 17 (18) are fitted in the assembly grooves 13e (14e) under tension and assembled.

[0088] [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 first seal member 17 and the second seal member 18 are provided between the first rotating disk 13 and the second rotating disk 14 and the housing 2 (the upper housing 11 and the lower housing 12), and a plurality of compression springs 61 are provided between the first rotating disk 13 and the second rotating disk 14 to bias the rotating disks 13 and 14 in a direction to separate the rotating disks 13 and 14 from each other and to approach the housing 2. Therefore, even if there is a variation in the parts constituting the flow path switching device 1 and the tightening margin of each seal member 17 and 18 varies due to the variation, the variation is adjusted by the biasing force of the compression spring 61, and the contact surface pressure of each seal member 17 and 18 against the housing 2 is adjusted. Therefore, the seal members 17 and 18 provided between the housing 2 and both rotating disks 13 and 14 can be maintained at an appropriate surface pressure, and the sealing performance of each seal member 17 and 18 can be ensured. That is, the influence of the interference caused by hardening, settling, wear, etc. of the seal members 17, 18 can be eliminated, and the robustness of the seal members 17, 18 can be improved.

[0089] In this embodiment, the valve body portion 3 is composed of a first rotating disk 13 and a second rotating disk 14 separated vertically, and a rotating shaft 15, and a plurality of compression springs 61 (three in this embodiment) are provided between the two rotating disks 13, 14 to urge the two rotating disks 13, 14 in directions separating them from each other. Therefore, the compression springs 61 can absorb variations in the components, and variations in the tightening margins of the seal members 17, 18 can be reduced.

[0090] According to the configuration of the flow path switching device 1 of this embodiment, the urging force of the compression spring 61 acts on the first rotating disk 13 and the second rotating disk 14, and the rotation transmission mechanism allows the two rotating disks 13 and 14 to move relative to each other in the axial direction X of the rotating shaft 15, and this relative movement adjusts the contact surface pressure of each of the seal members 17 and 18. In addition, as the rotating shaft 15 rotates, the rotation force is transmitted to the first rotating disk 13 and the second rotating disk 14 by the rotation transmission mechanism, so that both rotating disks 13 and 14 rotate, and the transmission of the rotation force is partially released by the rotation transmission mechanism, so that the rotation of both rotating disks 13 and 14 stops. Therefore, even if both rotating disks 13 and 14 rotate relative to the housing 2, the seal members 17 and 18 provided between the housing 2 and both rotating disks 13 and 14 can be maintained at an appropriate surface pressure, and the sealing performance of each seal member 17 and 18 can be ensured.

[0091] According to the configuration of the flow path switching device 1 of this embodiment, the upper housing 11 is provided with four inflow / outflow passages 20 (first to fourth inflow / outflow passages 21-24), and the lower housing 12 is provided with four inflow / outflow passages 20 (fifth to eighth inflow / outflow passages 25-28). The first rotating disk 13 is provided with two rotational passages 30 (first rotational passage 31 and second rotational passage 32), and the second rotating disk 14 is provided with two rotational passages 40 (third rotational passage 43 and fourth rotational passage 44). Furthermore, a first seal member 17 is assembled into an assembly groove 13e provided in the first rotating disk 13, and a second seal member 18 is assembled into an assembly groove 14e of the second rotating disk 14. Each seal member 17, 18 includes an inner circular portion 17a, 18a arranged on the center side of each rotary disk 13, 14, an outer circular portion 17b, 18b arranged on the outer periphery side of each rotary disk 13, 14, and a partition portion 17c, 17d, 18c, 18d that connects the inner circular portion 17a, 18a and the outer circular portion 17b, 18b and partitions between the two rotary passages 31, 32, 43, 44, respectively, and the partition portions 17c, 17d, 18c, 18d are fitted and assembled in the assembly grooves 13e, 14e in a tensioned state. Therefore, a tension force acts on the partition portions 17c, 17d, 18c, 18d, so that deformation of the partition portions 17c, 17d, 18c, 18d against an external force is suppressed. In addition, when the rotary disks 13 and 14 are rotated to switch the flow paths and the partitions 17c, 17d, 18c, and 18d cross the inlets 21a to 28a of the inflow passages 21 to 28, the partitions 17c, 17d, 18c, and 18d are prevented from getting caught in the inlets 21a to 28a and from protruding into the inlets 21a to 28a. This ensures the sealing performance of the seal members 17 and 18 without significantly increasing the manufacturing cost.

[0092] According to the configuration of the flow path switching device 1 of this embodiment, the flow path switching device 1 used in the cooling system 91 of the electric vehicle 90 can achieve an effect equivalent to that of the technology described in any one of claims 1 to 6. Therefore, the flow path switching device 1 used in the cooling system 91 of the electric vehicle 90 can achieve an effect equivalent to that of the technology described in any one of claims 1 to 6.

[0093] According to the configuration of this embodiment, elastic seal members 17, 18 are provided between the housing 2 and both rotating disks 13, 14, so that both rotating disks 13, 14 are supported in a floating state by the seal members 17, 18. Therefore, when both rotating disks 13, 14 rotate, the floating effect of the seal members 17, 18 can prevent uneven wear of the seal members 17, 18. Therefore, the seal members 17, 18 can ensure the sealing of the flow paths, and can reliably prevent leakage of fluid from the flow paths.

[0094] According to the configuration of the flow path switching device 1 of this embodiment, the seal members 17, 18 can also be used as elastic members for maintaining the orientation of both rotating disks 13, 14 with respect to the housing 2. Therefore, there is no need to provide separate elastic members for maintaining the orientation of both rotating disks 13, 14, and an increase in the number of parts can be suppressed, allowing the flow path switching device 1 to be made smaller and simpler.

[0095] <Second embodiment> The second embodiment will be described in detail with reference to Figures 29 and 30. In the following description, the same components as 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.

[0096] [Assembly structure of each sealing component] In this embodiment, the configuration is different from the first embodiment in terms of the contents of the assembly structure of each seal member 17, 18. FIG. 29 shows a state in which the partition portion 17c of the first seal member 17 is assembled into the assembly groove 13e in an enlarged sectional view equivalent to FIG. 23. FIG. 30 shows a state in which the partition portion 17c is assembled into the assembly groove 13e in a sectional view taken along the line JJ in FIG. 29. In this embodiment, each seal member 17, 18 is assembled by fitting into the assembly grooves 13e, 14e. Also, as shown in FIG. 30, a plurality of protrusions 71 that abut against the partition portion 17c are provided along the side wall of the partition portion 17c on the inner side wall of the assembly groove 13e at a portion where the partition portion 17c is fitted. These plurality of protrusions 71 are arranged at different positions alternately so as not to face each other on both sides of the partition portion 17c. As a result, the portion of the assembly groove 13e into which the partition 17c is fitted meanders slightly in the longitudinal direction in a plan view. The legs 19b on both sides of the partition 17c are alternately pressed inward by the multiple protrusions 71 and are alternately deformed. In this embodiment, the partition length L2 is set slightly longer than the partition groove length L1, taking into account the deformation caused by the protrusions 71 of the partition 17c. In Figs. 29 and 30, the assembly groove 13e into which the first seal member 17 is assembled is illustrated and described, but the assembly groove 14e into which the second seal member 18 is assembled has a similar configuration, although illustration and description are omitted (the same applies in the following description).

[0097] [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, unlike the configuration of the first embodiment, on the inner side walls of the parts of the assembly grooves 13e and 14e where the partitions 17c, 17d, 18c, and 18d are fitted, a plurality of protrusions 71 that abut against the partitions 17c, 17d, 18c, and 18d are arranged at different positions on both sides of the partitions 17c, 17d, 18c, and 18d. Therefore, a pressing force acts on the partitions 17c, 17d, 18c, and 18d by abutting against the protrusions 71 on the inner side walls of the assembly grooves 13e and 14e, so that deformation of the partitions 17c, 17d, 18c, and 18d against an external force is suppressed. In addition, when the rotary disks 13 and 14 are rotated to switch the flow paths and the partitions 17c, 17d, 18c, and 18d cross the inlets 21a to 28a of the inlet / outlet passages 20, the partitions 17c, 17d, 18c, and 18d are prevented from getting caught in the inlets 21a to 28a and from protruding into the inlets 21a to 28a. This ensures the sealing performance of the seal members 17 and 18 without significantly increasing the manufacturing cost.

[0098] In this embodiment, a bifurcated mountain-shaped cross section is used for each of the seal members 17 and 18, but instead of the bifurcated mountain-shaped cross section, a shape without a cavity in the center of the cross section, such as an O-ring, may also be used.

[0099] <Third embodiment> The third embodiment will be described in detail with reference to FIGS.

[0100] [Assembly structure of each sealing component] This embodiment differs from the second embodiment in the details of the assembly structure of the seal members 17, 18. Fig. 31 shows an enlarged cross-sectional view equivalent to Fig. 29 of the partition portion 17c of the first seal member 17 assembled into the assembly groove 13e. Fig. 32 shows a cross-sectional view taken along line KK in Fig. 31 of the partition portion 17c assembled into the assembly groove 13e. Fig. 33 shows a cross-sectional view taken along line NN in Fig. 32 of the partition portion 17c assembled into the assembly groove 13e.

[0101] As shown in FIG. 31 and FIG. 32, in this embodiment, in addition to the configuration equivalent to the second embodiment, the assembly groove 13e of the first rotating disk 13 is provided with an in-groove ridge 72 disposed in the hollow portion 19d of the first seal member 17. In this embodiment, the in-groove ridge 72 is provided in all parts of the assembly groove 13e, but the in-groove ridge 72 may be provided only in parts of the assembly groove 13e corresponding to the partition portions 17c and 17d. In addition, in this embodiment, a plurality of in-groove ridge protrusions 73 that abut on the inner wall of the hollow portion 19d are provided on both side walls of the in-groove ridge 72. These in-groove ridge protrusions 73 are disposed on both sides of the in-groove ridge 72 and are disposed offset from the protrusions 71 provided on the side walls of the assembly groove 13e so as not to face them. Although illustration and description are omitted, the same applies to the assembly groove 14e of the second rotating disk 14 and the second seal member 18. In this embodiment, the in-groove ribs 72 are provided in all portions of each of the assembly grooves 13e, 14e, but it is also possible to provide the in-groove ribs 72 only in the portions of each of the assembly grooves 13e, 14e that correspond to the partitions 17c, 17d, 18c, and 18d. In this embodiment, as shown in Fig. 33, the side walls of each of the protrusions 71, 73 are formed perpendicular to the bottom wall of the assembly groove 13e.

[0102] [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, each seal member 17, 18 has a mountain-shaped cross section that spreads toward each rotating disk 13, 14, and includes a recess 19c that is recessed toward each housing 11, 12, and a hollow portion 19d that is bifurcated toward each rotating disk 13, 14 and has a hollow inside. Also, each assembly groove 13e, 14e includes an in-groove protrusion 72 arranged in the hollow portion 19d, and an in-groove protrusion convex portion 73 that abuts against the inner wall of the hollow portion 19d is provided on the side wall of the in-groove protrusion 72 corresponding to the partition portions 17c, 17d, 18c, 18d. Therefore, the groove protrusions 72 are arranged in the hollows 19d of the partitions 17c, 17d, 18c, 18d, and a pressing force acts on the inner walls of the hollows 19d by contacting with the groove protrusions 73, so that deformation of the partitions 17c, 17d, 18c, 18d against external forces is suppressed. Therefore, it is possible to suppress the displacement of the partitions 17c, 17d, 18c, 18d of the seal members 17, 18, and suppress the repulsive force while ensuring the surface pressure required for sealing. Also, as in this embodiment, when the fluid is liquid, the recesses 19c of the partitions 17c, 17d, 18c, 18d become liquid pools, and the lubricating effect of the liquid can reduce the sliding resistance of the partitions 17c, 17d, 18c, 18d against the housings 11, 12.

[0103] In this embodiment, a plurality of protrusions 71 are provided on both side walls of the assembly grooves 13e, 14e, and a plurality of in-groove protrusions 73 are provided on both side walls of the in-groove protrusions 72, so that the spaces into which the seal members 17, 18 of the assembly grooves 13e, 14e are fitted form a corrugated shape in a plan view. By assembling the non-corrugated seal members 17, 18 into the corrugated spaces of the assembly grooves 13e, 14e, a holding surface pressure is formed alternately on the side surfaces of the seal members 17, 18 by the protrusions 71, 73 without imposing a large burden on the seal members 17, 18, and the non-corrugated seal members 17, 18 are inevitably deformed into a corrugated shape. Since the holding surface pressure at this time is a surface pressure due to bending stress, even if a part of the rubber material moves to the partitions 17c, 17d, 18c, 18d due to crushing from the inner circular parts 17a, 18a and the outer circular parts 17b, 18b when the partitions 17c, 17d, 18c, 18d pass through the entrances 21a-214a, 25a-28a, the bending stress can prevent the seal members 17, 18 from falling out of the assembly grooves 13e, 14e. At this time, the bending stress of the seal members 17, 18 is accompanied by a pulling action, so the seal members 17, 18 do not pop out due to assembly. Furthermore, as shown in FIG. 32, even at the upper limit of the component tolerance, by ensuring the clearance CL between each of the sealing members 17, 18 and the in-groove protrusion 72, it is possible to avoid excessive press-fit stress when assembling each of the sealing members 17, 18 into the assembly grooves 13e, 14e.

[0104] Here, as a comparative example, as shown in Fig. 34, it is assumed that the inner wall of the cavity 19d abuts against the side wall of the inner groove protrusion 72 without providing the inner groove protrusion 73 on both side walls of the inner groove protrusion 72. In this case, in order to increase the side holding force of each seal member 17, 18 in each assembly groove 13e, 14e, it is necessary to make the protrusions 71 provided on both side walls of each assembly groove 13e, 14e tall. However, if the protrusions 71 are made tall, there is a concern that the press-fitting stress becomes excessive when the seal members 17, 18 are assembled into the assembly grooves 13e, 14e, which may cause the seal members 17, 18 to sag. In addition, the volume of each seal member 17, 18 moves in the vertical direction and the sliding direction in Fig. 33 due to the press-fitting, which may cause the rubber material to pop out during assembly. Furthermore, there is a concern that wear of the seal members 17, 18 may worsen when the partition portions 17c, 17d, 18c, 18d at the entrances 21a-24a, 25a-28a are opened and run onto the inner surfaces of the housings 11, 12. In contrast, the configuration of this embodiment can eliminate the above concerns regarding the seal members 17, 18. Figure 34 is a cross-sectional view equivalent to Figure 32, showing a state in which the partition portion 17c is assembled into the assembly groove 13e.

[0105] <Fourth embodiment> The fourth embodiment will be described in detail with reference to FIG.

[0106] [Regarding the problem of the third embodiment] In the third embodiment, as shown in Fig. 33, the side walls of the protrusions 71, 73 are formed perpendicular to the bottom wall of the assembly groove 13e, and the pair of legs 19b constituting the partitions 17c, 17d of the first seal member 17 open outwardly. For this reason, when the protrusions 71, 73 are provided in the assembly groove 13e, there is a concern that the high surface pressure area shown by the chain ellipse in Fig. 33 will have a difference in height between the protrusion 71 and the outside of the leg 19b and between the groove protrusion 73 and the inside of the leg 19, which may cause unstable side support. Therefore, in this fourth embodiment, the assembly structure of the seal members 17, 18 is configured as follows.

[0107] [Assembly structure of each sealing component] Fig. 35 is an enlarged cross-sectional view equivalent to Fig. 33 showing a state in which the partition portion 17c of the first seal member 17 is assembled into the assembly groove 13e. In this embodiment, as shown in Fig. 35, the side surface of the groove protrusion 73 is formed to widen in a tapered manner toward the bottom wall in accordance with the leg portion 19b of the first seal member 17 that opens outwardly. Although not shown and not described, the same applies to the assembly groove 14e of the second rotating disk 14 and the second seal member 18.

[0108] [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 contrast to the third embodiment, the groove protrusions 73 are formed so that their sides taper toward the bottom wall in accordance with the flared shape of the legs 19b of each of the seal members 17, 18. Therefore, the high surface pressure points shown by the chain ovals in Fig. 35 are the same height between the protrusions 71 and the outside of the legs 19b and between the groove protrusions 73 and the inside of the legs 19, and the side holding of each of the seal members 17, 18 can be stabilized.

[0109] <Fifth embodiment> The fifth embodiment will be described in detail with reference to FIG.

[0110] [Regarding the problem of the fourth embodiment] In the fourth embodiment, in order to stabilize the side holding of each seal member 17, 18, the groove protrusion 73 is formed as shown in Fig. 35, so that the height of the high surface pressure portion formed by the protrusion 71 and the groove protrusion 73 is made the same, but the area of ​​the high surface pressure portion becomes narrow. In response to this, it is conceivable to increase the height of the lower portion of the groove protrusion 73 in order to increase the side holding force, but this may lead to stress concentration (sagging) in that portion. Therefore, in this fifth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0111] [Assembly structure of each sealing component] Fig. 36 shows a state in which the partition portion 17c of the first seal member 17 is assembled into the assembly groove 13e, in an enlarged cross-sectional view equivalent to Fig. 33. In this embodiment, as shown in Fig. 36, the convex portion 71 and the groove protruding portion 73 of the assembly groove 13e are configured to vertically abut against the outer surface and inner surface of the leg portion 19b of the first seal member 17. That is, the lower portions of both leg portions 19b of the first seal member 17 are formed to be perpendicular to the bottom wall of the assembly groove 13e, and the outer surfaces of the convex portion 71 and the groove protruding portion 73 are formed to be perpendicular to the bottom wall of the assembly groove 13e. Although illustration and description are omitted, the same applies to the assembly groove 14e of the second rotating disk 14 and the second seal member 18.

[0112] [About the action and effect of the flow switching device] The above-described configuration of the flow path switching device 1 of this embodiment provides the following actions and effects in comparison with the fourth embodiment. That is, the convex portions 71 and the groove protrusions 73 of the mounting grooves 13e and 14e are in contact with the outer surfaces of the legs 19b and the inner surfaces of the hollow portions 19d at the partition portions 17c, 17d, 18c, and 18d of the sealing members 17 and 18 perpendicularly. Therefore, as shown by the chain ellipse in FIG. 36, the range in which the outer and inner surfaces of the partition portions 17c, 17d, 18c, and 18d are high expands along the legs 19b. Therefore, stress concentration on the outer and inner surfaces of the partition portions 17c, 17d, 18c, and 18d of the sealing members 17 and 18 can be alleviated.

[0113] In addition, since both leg portions 19b of each of the seal members 17, 18 are formed so as to be perpendicular to the bottom wall of the assembly grooves 13e, 14e, the seal members 17, 18 can be molded so as to be removable from a die when manufactured. Furthermore, since the convex portions 71 and the in-groove ridge convex portions 73 of the assembly grooves 13e, 14e are formed so as to be perpendicular to the bottom wall of the assembly grooves 13e, 14e, the rotary disks 13, 14 can be molded so as to be removable from a die when manufactured.

[0114] Sixth embodiment The sixth embodiment will be described in detail with reference to FIGS.

[0115] [Regarding the problems of the above embodiments] FIG. 37 is a plan view showing an enlarged view of the partition portion 17c of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13, as a comparison with this embodiment. As shown in FIG. 37, the first seal member 17 further includes an outer branch portion 17e (a portion surrounded by an upper broken-line ellipse) where the partition portion 17c branches off to the outer circular portion 17b, and an inner branch portion 17f (a portion surrounded by a lower broken-line ellipse) where the partition portion 17c branches off to the inner circular portion 17a. These branch portions 17e and 17f have a high density of rubber material, and the movement of the rubber material due to squeezing is concentrated, so that the sliding relationship with the upper housing 11 results in a high surface pressure. On the other hand, on the inner surface of the upper housing 11 on which the first seal member 17 slides, the openings 21a to 24a of the first inflow / outflow passage 21 to the fourth inflow / outflow passage 24 are opened opposite to each other, as shown by the two-dot chain line in FIG. 37. In FIG. 37, the area surrounded by thick two-dot chain lines L3 and L4 indicates an entrance distribution area DA of each of the entrances 21a to 24a across which the first seal member 17 slides.

[0116] As shown in Fig. 37, the outer branch 17e and the inner branch 17f of the partition 17c of the first seal member 17 overlap the inlet / outlet distribution area DA, so that these branches 17e, 17f cross the inlet / outlet distribution area DA when the first rotating disk 13 rotates to switch the flow path. At this time, there is a concern that a difference in surface pressure will occur between these branches 17e, 17f and the partitions 17c, 17d other than the branches 17e, 17f, and that a wear step will occur. Fig. 38 is a schematic cross-sectional view showing the state in which the partition 17c crosses the inlets 21a to 24a. 38, when the high surface pressure branch portions 17e, 17f are opened into the entrances 21a to 24a, the partition portion 17c protrudes more into the entrances 21a to 24a, so that the partition portion 17c is more likely to be caught when it rides up onto the opening edge of the entrances 21a to 24a. Although not shown and described, the same applies to the partition portion 17d and the second seal member 18. Therefore, in this sixth embodiment, the assembly structure of the seal members 17, 18 is configured as follows.

[0117] [Assembly structure of each sealing component] Fig. 39 is an enlarged plan view equivalent to Fig. 37 showing the vicinity of the partition portion 17c of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13 according to this embodiment. In this embodiment, as shown in Fig. 39, the outer branch portion 17e and the inner branch portion 17f of the partition portion 17c of the first seal member 17 are disposed outside the entrance / exit distribution area DA without overlapping with the entrance / exit distribution area DA. Although illustration and description are omitted, the same is true for the partition portion 17d and the second seal member 18.

[0118] [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 outer branch portion 17e and the inner branch portion 17f of each of the seal members 17, 18, which are particularly subjected to high surface pressure, are arranged outside the inlet / outlet distribution area DA of the inlets 21a to 28a of each of the inlet / outlet passages 20, which the seal members 17, 18 cross while sliding. Therefore, when each of the seal members 17, 18 crosses the inlets 21a to 28a of the inlet / outlet passages 20, it is possible to reduce the outer branch portion 17e and the inner branch portion 17f, which are subjected to high surface pressure, from jumping out into the inlets 21a to 28a, getting caught on the periphery of the inlets 21a to 28a, and deteriorating the sliding properties.

[0119] Seventh embodiment The seventh embodiment will be described in detail with reference to FIGS.

[0120] [Assembly structure of each sealing component] This embodiment is different from the sixth embodiment in terms of the configuration for the same problem as the sixth embodiment. Fig. 40 shows in a plan view one of the inlets 21a-24a of the first inlet / outlet passage 21-fourth inlet / outlet passage 24 that opens on the inner surface of the upper housing 11 according to this embodiment. Fig. 41 shows the inlets 21a-24a in a cross-sectional view cut along the line C1-C1 or C2-C2 in Fig. 40. Fig. 42 shows the inlets 21a-24a in a cross-sectional view cut along the line DD in Fig. 40. The positions of the lines C1-C1 and C2-C2 in Fig. 40 indicate the vicinity of both ends of the inlets 21a-24a in the radial direction of the upper housing 11, respectively, and the position of the line DD indicates the vicinity of the center of the inlets 21a-24a in the radial direction of the upper housing 11.

[0121] As shown in Fig. 40 and Fig. 41, among the entrances 21a to 24a, the entrances 21a to 24a across which the partitions 17c and 17d of the first seal member 17 slide have an intersecting opening edge 29 (shown with gauze in Fig. 40) extending in a direction intersecting the sliding direction (shown by arrow M in Fig. 40). As shown in Fig. 41 and Fig. 42, the intersecting opening edge 29 has curved surfaces R1 and R2 curved toward the inside of the entrances 21a to 24a, and is set so that the diameter of the curved surface R2 is larger toward the center shown in Fig. 42 than the curved surface R1 on both ends of the intersecting opening edge 29 shown in Fig. 41. Although illustration and description are omitted, the same is true for the entrances 25a to 28a of the fifth inflow / outflow passage 25 to the eighth inflow / outflow passage 28 that open to the inner surface of the lower housing 12.

[0122] [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 partitions 17c, 17d, 18c, and 18d protrude more when opening the inlets 21a to 28a of the inlet / outlet passages 20 of the housings 11 and 12 toward the center. However, the crossing opening edge 29 of the inlets 21a to 28a has a larger diameter at the center curved surface R2 than at the curved surfaces R1 at both ends. Therefore, even if the partitions 17c, 17d, 18c, and 18d protrude more when opening the inlets 21a to 28a, the larger diameter curved surface R2 of the crossing opening edge 29 allows the partitions 17c, 17d, 18c, and 18d to pass through smoothly. Therefore, even if the partition portions 17c, 17d, 18c, 18d of each sealing member 17, 18 protrude into the entrances 21a-28a of the inflow / outflow passage 20 when crossing the entrances 21a-28a, it is possible to reduce the risk of the partition portions 17c, 17d, 18c, 18d getting caught on the intersecting opening edge 29 or the deterioration of sliding properties when riding up onto the intersecting opening edge 29.

[0123] Eighth embodiment The eighth embodiment will be described in detail with reference to FIGS.

[0124] [Assembly structure of each sealing component] This embodiment differs from the sixth and seventh embodiments in terms of the configuration for solving the same problems as those of the sixth and seventh embodiments. Fig. 43 shows in a plan view one of the openings 21a-24a of the first inflow / outflow passage 21-fourth inflow / outflow passage 24 that open to the inner surface of the upper housing 11 according to this embodiment. Fig. 44 shows the openings 21a-24a in a cross-sectional view taken along line QQ in Fig. 43. The position of line QQ in Fig. 43 indicates the vicinity of the center of the openings 21a-24a in the radial direction of the upper housing 11.

[0125] As shown in Fig. 43, an auxiliary seat 76 that extends thinly along the sliding direction (indicated by arrow M) and contacts the partitions 17c and 17d is provided at the center of the inside of the entrances 21a to 24a through which the partitions 17c and 17d of the first seal member 17 slide. Since it is not necessary to ensure the sealing performance of the first seal member 17 at the auxiliary seat 76, the seat surface 76a of the auxiliary seat 76 is not flush with the inner surface 11b of the upper housing 11 and is lowered into the entrances 21a to 24a as shown in Fig. 44 in order to avoid wear of the auxiliary seat 76 when the partitions 17c and 17d cross each of the entrances 21a to 24a. Although illustration and description are omitted, the same is true for the entrances 25a to 28a of the fifth to eighth inlet / outlet passages 25 to 28 that open to the inner surface of the lower housing 12.

[0126] [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 auxiliary seats 76 with which the partitions 17c, 17d, 18c, 18d come into contact are provided inside the entrances 21a to 28a of the inflow / outflow passage 20, which the partitions 17c, 17d, 18c, 18d of the seal members 17, 18 slide across. Therefore, the partitions 17c, 17d, 18c, 18d come into contact with the auxiliary seats 76 when they cross the entrances 21a to 28a. As a result, when the partition portions 17c, 17d, 18c, 18d of each sealing member 17, 18 cross the entrances 21a-28a of the inflow / outflow passage 20, the partition portions 17c, 17d, 18c, 18d can be prevented from protruding into the entrances 21a-28a, thereby reducing the occurrence of the partition portions 17c, 17d, 18c, 18d getting caught on the periphery of the entrances 21a-28a and deterioration of their sliding properties.

[0127] <Ninth embodiment> The ninth embodiment will be described in detail with reference to FIGS.

[0128] [Assembly structure of each sealing component] This embodiment differs from the sixth to eighth embodiments in terms of the configuration for solving the same problems as those of the sixth to eighth embodiments. Fig. 45 shows only the mounting groove 14e in the second rotating disk 14 in a simplified plan view. Fig. 46 shows an enlarged cross-sectional view taken along lines S1-S1 and S2-S2 in Fig. 45 (central parts of the partitions 18c and 18d) showing a state in which the partitions 18c and 18d of the second seal member 18 are mounted in the mounting groove 14e. Fig. 47 shows an exploded enlarged cross-sectional view of the mounting structure of the part shown in Fig. 46. Fig. 48 shows a plan view of the part shown in Fig. 46 as viewed from below. FIG. 49 is an enlarged cross-sectional view taken along lines T1-T1 and T2-T2 in FIG. 45 (parts other than the central parts of the partitions 18c and 18d) showing a state in which the partitions 18c and 18d of the second seal member 18 are assembled into the assembly groove 14e. In the second rotating disk 14, the second seal member 18 is assembled downward into the assembly groove 14e, and therefore, after assembly, the second seal member 18 may fall off, which may cause a problem. In addition, there is a concern that the partitions 18c and 18d of the second seal member 18 may get caught when they move from the entrances 25a to 28a onto the inner surface of the lower housing 12. Therefore, in the ninth embodiment, the assembly structure of the second seal member 18 is configured as follows.

[0129] As shown in Figs. 46 and 48, in this embodiment, in order to prevent the partitions 18c and 18d of the second seal member 18 from popping out of the assembly groove 14e, a pair of seal stoppers 79 are provided in the assembly groove 14e so as to sandwich both sides of the partitions 18c and 18d in correspondence with the central portions of the partitions 18c and 18d in order to prevent the partitions 18c and 18d from popping out of the assembly groove 14e. As shown in Fig. 47, these seal stoppers 79 are fixed to the second rotating disk 14 by being inserted into recesses 80 formed in the opening edge of the assembly groove 14e. As shown in Fig. 48, the fixed side corners of the seal stoppers 79 and the corners of the recesses 80 are wedge-shaped in a bottom view, so that the seal stoppers 79 engage with the recesses 80 to prevent them from falling out of the recesses 80. Here, the seal stoppers 79 can be fixed to the recesses 80 by adhesive or welding. Alternatively, the seal stopper 79 can be fixed by weak press-fitting into the recess 80 by using a material with a large swelling difference in water compared to the second rotating disk 14. In this case, the second rotating disk 14 can be made of "PPS" which swells very little, and the seal stopper 79 can be made of "PA66" which is a nylon-based material with a large swelling. The seal stopper 79 corresponds to an example of the "protrusion prevention means" of this disclosed technology. Although illustration and description are omitted, the assembly groove 13e of the first rotating disk 13 can be configured in the same manner. Also, the seal stopper can be provided in a portion other than the center of the partition portion 17c, 17d, 18c, 18d of each seal member 17, 18.

[0130] [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 seal stoppers 79 are provided for the partitions 17c, 17d, 18c, and 18d of the seal members 17 and 18 to prevent them from popping out of the assembly grooves 13e and 14e. Therefore, the seal stoppers 79 prevent the seal members 17 and 18 from popping out of the assembly grooves 13e and 14e. For this reason, even if the seal members 17 and 18 face downward during component transport of the rotary disks 13 and 14, the drop of the central parts of the partitions 17c, 17d, 18c, and 18d from the assembly grooves 13e and 14e can be suppressed to a small drop f1 as shown by the two-dot chain line in FIG. 46. On the other hand, the drop of the parts other than the central parts of the partitions 17c, 17d, 18c, and 18d becomes a large drop f2 as shown by the two-dot chain line in FIG. 49.

[0131] During operation of the flow path switching device 1, the partitions 17c, 17d, 18c, 18d of the seal members 17, 18 are restricted from popping out of the assembly grooves 13e, 14e by the seal stoppers 79. This maintains the orientation of the partitions 17c, 17d, 18c, 18d of the seal members 17, 18, and prevents the partitions 17c, 17d, 18c, 18d from popping out of the entrances 21a-28a when the partitions 17c, 17d, 18c, 18d cross the entrances 21a-28a of the inflow / outflow passages 20 of the housings 11, 12. This reduces the partitions 17c, 17d, 18c, 18d from getting caught on the periphery of the entrances 21a-28a and the deterioration of the sliding properties.

[0132] Tenth embodiment The tenth embodiment will be described in detail with reference to FIGS.

[0133] [Regarding the problems of the above embodiments] FIG. 50 shows a plan view of the side where the first rotating disk 13 contacts the upper housing 11 in a comparative example of this embodiment. FIG. 51 shows an enlarged cross-sectional view of the first rotating disk 13 and the upper housing 11 taken along line UU in FIG. 50 at the portion of the mounting groove 13e where the outer circular portion 17b of the first seal member 17 is mounted, also in a comparative example. As shown in FIG. 51, the first seal member 17 in this embodiment is designed to exert a sealing function by securing a surface pressure by being crushed by contact with the inner surface of the upper housing 11, which is the mating member. In this embodiment, as shown by the chain ellipse in FIG. 51, the first seal member 17 has two seal surfaces at the top 19a and the leg 19b, and it is desirable that the surface pressure of these seal surfaces is uniform. Here, the top 19a and the leg 19b of the first seal member 17 are crushed, and the rubber material escapes in the left-right and circumferential directions as shown by the arrows. In this case, the outer circular portion 17b can be crushed to the outside (right side in the figure), but cannot be crushed to the inside (left side in the figure). Therefore, the inside of the first seal member 17 has a high surface pressure, and the outside has a lower surface pressure than the inside. As a result, a surface pressure difference occurs between the inside and outside of the outer circular portion 17b of the first seal member 17, and there is a concern that the sealing performance will decrease due to uneven wear. The same applies to the inner circular portion 17a. The same applies to the second seal member 18 that is assembled into the assembly groove 14e of the second rotating disk 14. Therefore, in this tenth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0134] [Assembly structure of each sealing component] FIG. 52 shows a plan view of the first rotating disk 13 in contact with the upper housing 11 according to the tenth embodiment. FIG. 53 shows an enlarged cross-sectional view of the first seal member 17 and the assembly groove 13e of the first rotating disk 13, cut along the V1-V1 line (outer circle portion 17b) and the V2-V2 line (inner circle portion 17a) in FIG. 52 according to the tenth embodiment. As shown in FIG. 53, in this embodiment, the heights of the two convex portions 82a, 82b of the top portion 19a of the first seal member 17 are the same, and the lengths to the lower ends of the two leg portions 19b are the same. In addition, the assembly groove 13e is divided into two by the groove inner protrusion 72, that is, the left inner groove 81a and the right outer groove 81b, with the inner groove 81a being set slightly deeper than the outer groove 81b. As a result, the compression allowance of the inner diameter side of the first seal member 17 is set smaller than the compression allowance of the outer diameter side. Here, the groove depth difference α1 is set larger in the inner circular portion 17a having a smaller inner diameter than in the outer circular portion 17b having a larger inner diameter. By setting it in this way, the compression allowance (squeezing allowance) on the inner diameter side of the first seal member 17 is smaller than the compression allowance (squeezing allowance) on the outer diameter side. Although not shown and not described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can be configured in a similar manner.

[0135] [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, each seal member 17, 18 has a mountain-shaped cross section that spreads toward each rotary disk 13, 14 side, and includes a recess 19c that is recessed toward each housing 11, 12 side, and a hollow portion 19d that is bifurcated toward each rotary disk 13, 14 side and has a hollow inside. Each seal member 17, 18 is set so that the compression allowance on the inner diameter side is smaller than the compression allowance on the outer diameter side. The surface pressure of each seal member 17, 18 becomes smaller as the compression allowance is smaller. Therefore, in addition to the actions and effects of each of the above-mentioned embodiments, the seal surface pressure of each seal member 17, 18 can be made to act uniformly between the outer diameter side and the inner diameter side of each seal member 17, 18.

[0136] <Eleventh embodiment> The eleventh embodiment will be described in detail with reference to FIG.

[0137] [Assembly structure of each sealing component] The eleventh embodiment differs from the tenth embodiment in the assembly structure of the seal members 17, 18. In FIG. 54, the first seal member 17 of the first rotating disk 13 and the assembly groove 13e are shown in an enlarged cross-sectional view similar to FIG. 53 according to the eleventh embodiment. In this embodiment, the length to the lower end of the two legs 19b of the first seal member 17 is set to be the same, and the inner convex portion 82a of the top portion 19a is set to be slightly lower than the outer convex portion 82b. Here, the difference in height (height difference) β1 between the two convex portions 82a, 82b is set to be larger for the inner circular portion 17a having a smaller inner diameter than for the outer circular portion 17b having a larger inner diameter. By setting in this way, the compression allowance of the inner diameter side of the first seal member 17 is smaller than the compression allowance of the outer diameter side. Although illustration and description are omitted, the mounting groove 14e of the second rotating disk 14 and the second seal member 18 mounted thereto can be configured in a similar manner.

[0138] [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 contrast to the tenth embodiment, each seal member 17, 18 has a mountain-shaped cross section that expands toward each rotary disk 13, 14, and includes a recess 19c that is recessed toward each housing 11, 12, and a hollow portion 19d that is divided into at least two toward each housing 11, 12 and has a hollow inside. Each seal member 17, 18 has a smaller compression allowance on the inner diameter side than on the outer diameter side. The surface pressure of each seal member 17, 18 decreases as the compression allowance decreases. Therefore, the seal surface pressure of each seal member 17, 18 can be made to act uniformly between the outer diameter side and the inner diameter side of each seal member 17, 18.

[0139] In this embodiment, the compression allowance on the inner diameter side of each seal member 17, 18 is made smaller than the compression allowance on the outer diameter side thereof (adjustment of the convex height difference) by the height difference β1 of the convex parts 82a, 82b of the apex 19a of each seal member 17, 18. In contrast to this, it is also possible to make the length to the bottom end of the inner leg part 19b shorter than the length to the bottom end of the outer leg part 19b (adjustment of the leg length), or to adjust both the convex height difference and the leg length.

[0140] <Twelfth embodiment> The twelfth embodiment will be described in detail with reference to FIGS.

[0141] [Issues regarding the partitions of each sealing material] In Fig. 50, the rubber material moves from the inner circular portion 17a and the outer circular portion 17b to the partition portions 17c and 17d of the first seal member 17 due to contact with the inner surface of the upper housing 11 (rubber material crushing), and the surface pressure of both the sliding surface of the top portion 19a and the non-sliding surface of the lower end of the leg portion 19b becomes high, as shown by the dashed ellipse in Fig. 51. At this time, it is desired to move the rubber material from the partition portions 17c and 17d to the inner circular portion 17a and the outer circular portion 17b, but since the rubber material moves from the inner circular portion 17a and the outer circular portion 17b to the partition portions 17c and 17d, the average surface pressure of the two convex portions 82a and 82b of the top portions 19a of the partition portions 17c and 17d is inevitably higher than other portions. In addition, the branching portions of the partitions 17c, 17d and the inner and outer circular portions 17a, 17b are subject to high surface pressure because the rubber material is crushed and moved in a concentrated manner. Although not shown in the figures and description, the same applies to the second seal member 18. Therefore, in the twelfth embodiment, the assembly structure of the seal members 17, 18 is configured as follows.

[0142] [Assembly structure of each sealing component] FIG. 55 shows a plan view of the side of the first rotating disk 13 that contacts the upper housing 11 according to the twelfth embodiment. FIG. 56 shows an enlarged cross-sectional view of the first seal member 17 and the assembly groove 13e of the first rotating disk 13 cut along the line WW (partition 17c) in FIG. 55 according to the twelfth embodiment. As shown in FIG. 56, in this embodiment, the heights of the two convex parts 82a, 82b of the top 19a of the partition 17c of the first seal member 17 are set to be the same, and the lengths to the lower ends of the two legs 19b are set to be the same, and both the inner groove 81a on the left side and the outer groove 81b on the right side of the assembly groove 13e are set slightly deeper than the comparative example shown in FIG. 51, which is the reference. Here, the groove depth difference α3 is set deeper than the groove depth difference α1 of FIG. 53 of the tenth embodiment. Although not shown, the same is true for the partition 17d. By setting it in this way, the compression allowance of the partition portions 17c, 17d of the first seal member 17 is smaller than the compression allowance on the inner diameter side of the outer circular portion 17b. Although not shown and described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can be configured in a similar manner.

[0143] [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, when the rotary disks 13 and 14 are driven to rotate, the partitions 17c, 17d, 18c, and 18d and the outer circular parts 17b and 18b are compressed by the sliding of the seal members 17 and 18, but the compression allowance of the partitions 17c, 17d, 18c, and 18d is smaller than the compression allowance of the inner diameter side of the outer circular parts 17b and 18b. The smaller the compression allowance, the smaller the surface pressure. Therefore, an appropriate seal surface pressure can be applied between the partitions 17c, 17d, 18c, and 18d of the seal members 17 and 18 and the outer circular parts 17b and 18b.

[0144] <Thirteenth embodiment> The thirteenth embodiment will be described in detail with reference to FIG.

[0145] [Assembly structure of each sealing component] This embodiment differs from the twelfth embodiment in the configuration of the assembly structure of each seal member. Fig. 57 shows the first seal member 17 of the first rotating disk 13 and the assembly groove 13e in an enlarged cross-sectional view equivalent to Fig. 56 according to the thirteenth embodiment. As shown in Fig. 57, in this embodiment, the heights of the two convex parts 82a, 82b of the top 19a of the partition part 17c of the first seal member 17 are set to be the same, and the lengths to the lower ends of the two legs 19b are set to be the same, and the heights of both the two convex parts 82a, 82b of the top 19a are set to be slightly lower than the comparative example shown in Fig. 51, which is the reference. Here, the height difference β2 of the convex parts 82a, 82b is set to be larger than the height difference β1 of Fig. 54 of the eleventh embodiment. Although not shown, the same is true for the partition part 17d. By setting it in this way, the compression allowance of the partition portions 17c, 17d of the first seal member 17 is smaller than the compression allowance on the inner diameter side of the outer circular portion 17b. Although not shown and described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can be configured in a similar manner.

[0146] [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, it is possible to obtain the same functions and effects as those of the twelfth embodiment.

[0147] <Fourteenth embodiment> The fourteenth embodiment will be described in detail with reference to FIGS.

[0148] [Assembly structure of each sealing component] This embodiment differs from the tenth to thirteenth embodiments in terms of the configuration of the assembly structure of each seal member. Fig. 58 shows a plan view of the side of the first rotating disk 13 that contacts the upper housing 11 according to this fourteenth embodiment. Fig. 59 shows an enlarged cross-sectional view of the first seal member 17 of the first rotating disk 13 and the assembly groove 13e along the Z1-Z1 line (the outer branch portion 17e near the partition portion 17c) in Fig. 58 according to this fourteenth embodiment. As shown in Fig. 59, in this embodiment, for the outer branch portion 17e near the partition portion 17c, the heights of the two protrusions 82a, 82b of the top 19a are set to be the same, the lengths to the lower ends of the two legs 19b are set to be the same, and the heights of both the two protrusions 82a, 82b of the top 19a are set to be the same as the reference height in Fig. 51. Here, the inner groove 81a of the outer branch portion 17e is set deeper than the reference depth in FIG. 51 by a groove depth difference α4, and the outer groove 81b is set deeper than the reference depth by a groove depth difference α5.

[0149] The groove depth difference α4 of the inner groove 81a of the outer branch portion 17e is set to increase smoothly from the groove depth difference α1 of the inner groove 81a of the outer circular portion 17b. Also, the groove depth difference α5 of the outer groove 81b of the outer branch portion 17e is set to increase smoothly from the reference depth. Here, the groove depth differences α1, α3, α4 of the inner groove 81a of the outer branch portion 17e described above are "α1≦α4≦α3". Also, when there is a slight difference between the groove depth differences α1, α3, α4, they are changed smoothly between them, and when the groove depth difference α5 is slight, they are changed smoothly from the reference depth.

[0150] Although not shown in the figures, the same is true for the outer branch portion 17e near the partition portion 17d. By setting in this manner, the compression allowance on the inner diameter side of the outer circular portion 17b of the first seal member 17 becomes smaller toward the partition portions 17c, 17d. Although not shown and not described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can be configured in the same manner.

[0151] [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 following actions and effects can be obtained compared to the tenth to thirteenth embodiments. That is, in this fourteenth embodiment, when the rotary disks 13, 14 are driven to rotate, the partitions 17c, 17d, 18c, 18d and the outer circular parts 17b, 18b are compressed by the sliding of the seal members 17, 18, but the compression margin on the inner diameter side of the outer circular parts 17b, 18b is smaller in the vicinity of the partitions 17c, 17d, 18c, 18d. The smaller the compression margin, the smaller the surface pressure. Therefore, it is possible to apply an appropriate seal surface pressure to the outer circular parts 17b, 18b of the seal members 17, 18 according to their locations.

[0152] In this embodiment, the outer branch portion 17e of each seal member 17, 18 is configured to adjust the depth of the inner groove 81a and the outer groove 81b of the assembly grooves 13e, 14e, but it can also be configured to adjust the height of the convex portions 82a, 82b of the tops 19a of each seal member 17, 18.

[0153] <Fifteenth embodiment> The fifteenth embodiment will be described in detail with reference to FIG.

[0154] [Assembly structure of each sealing component] This embodiment differs from the tenth to fourteenth embodiments in terms of the configuration of the assembly structure of each seal member. Fig. 60 shows an enlarged cross-sectional view of the first seal member 17 of the first rotating disk 13 and the assembly groove 13e according to the fifteenth embodiment, cut along the Z2-Z2 line (the inner branch portion 17f near the partition portion 17c) in Fig. 58. As shown in Fig. 60, in this embodiment, for the inner branch portion 17f near the partition portion 17c, the heights of the two convex portions 82a, 82b of the top portion 19a are set to be the same, the lengths to the lower ends of the two legs 19b are set to be the same, and the heights of both the two convex portions 82a, 82b of the top portion 19a are set to be the same as the reference height in Fig. 51. Here, the inner groove 81a of the inner branch portion 17f is set to be deeper than the reference depth in Fig. 51 by a groove depth difference α6, and the outer groove 81b is set to be deeper than the reference depth by a groove depth difference α7.

[0155] The groove depth difference α6 of the inner groove 81a of the inner branch portion 17f is set to increase smoothly from the groove depth difference α2 (not shown) of the inner groove 81a of the inner circular portion 17a. The groove depth difference α7 of the outer groove 81b of the inner branch portion 17f is set to increase smoothly from the reference depth. Here, the groove depth differences α2, α3, α6 of the inner groove 81a of the inner branch portion 17f described above are "α2≦α6≦α3". When there is a slight difference between the groove depth differences α2, α3, α6, they are changed smoothly between them, and when the groove depth difference α7 is slight, they are changed smoothly from the reference depth.

[0156] Although not shown in the figures, the same is true for the inner branch portion 17f near the partition portion 17d. By setting in this manner, the compression allowance on the inner diameter side of the inner circular portion 17a of the first seal member 17 becomes smaller toward the partition portions 17c, 17d. Although not shown and not described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can be configured in the same manner.

[0157] [About the action and effect of the flow switching device] The above-described configuration of the flow path switching device 1 of this embodiment provides the following actions and effects compared to the tenth to fourteenth embodiments. That is, in this fifteenth embodiment, when the rotary disks 13, 14 are driven to rotate, the partitions 17c, 17d, 18c, 18d and the inner circular parts 17a, 18a are compressed by the sliding of the seal members 17, 18, but the compression margin on the inner diameter side of the inner circular parts 17a, 18a is smaller in the vicinity of the partitions 17c, 17d, 18c, 18d. The smaller the compression margin, the smaller the surface pressure. Therefore, it is possible to apply an appropriate seal surface pressure to the inner circular parts 17a, 18a of the seal members 17, 18 according to their locations.

[0158] In this embodiment, the inner branch portion 17f of each sealing member 17, 18 is configured to adjust the depth of the inner groove 81a and the outer groove 81b of the assembly grooves 13e, 14e, but it can also be configured to adjust the height of the convex portions 82a, 82b of the tops 19a of each sealing member 17, 18.

[0159] <16th embodiment> The sixteenth embodiment will be described in detail with reference to FIGS.

[0160] [Regarding the problem addressed in the sixth embodiment] In the sixth embodiment, referring to Figs. 37 and 38, when the outer branch portion 17e and the inner branch portion 17f of the first seal member 17 cross the entrance distribution area DA, a difference in surface pressure occurs between these branch portions 17e, 17f and the partition portions 17c, 17d other than the branch portions 17e, 17f, and a wear step occurs. In addition, since the high surface pressure branch portions 17e, 17f are opened into the entrances 21a to 24a, and the protrusion of the partition portion 17c into the entrances 21a to 24a increases, it is concerned that the partition portion 17c is likely to be caught when the partition portion 17c rides up on the opening edge of each of the entrances 21a to 24a. The same concern was also raised about the second seal member 18. Therefore, in the sixth embodiment, in order to address the above problem, the outer branch portion 17e and the inner branch portion 17f of the first seal member 17 are arranged outside the entrance distribution area DA without overlapping with the entrance distribution area DA. The same measures were taken for the second seal member 18.

[0161] [Assembly structure of each sealing component] In this embodiment, in order to address the issues raised in the sixth embodiment, the following configuration is added to the configuration of the sixth embodiment. Fig. 61 shows an enlarged plan view equivalent to Fig. 39 of the partition portion 17c of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13 according to the sixteenth embodiment. Fig. 62 shows an enlarged plan view of the outer branch portion 17e of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13 according to this embodiment. Fig. 63 shows the outer branch portion 17e in a cross section taken along line PP in Fig. 62.

[0162] In this embodiment, as shown in FIG. 61, a dummy seal surface 82c for dispersing the seal surface pressure is additionally provided in the outer branch portion 17e and the inner branch portion 17f arranged outside the entrance / exit distribution area DA. As shown in FIG. 63, in this embodiment, a substantially triangular convex portion is provided on each of the branches 17e and 17f as the dummy seal surface 82c. Since the cavity portion 19d of each of the branches 17e and 17f is larger than other portions, the groove protrusion 72 provided in the cavity portion 19d protrudes over a wider range than other portions. This dummy seal surface 82c corresponds to an example of the "seal surface pressure dispersing portion" of this disclosed technology. Although illustration and description are omitted, the same is true for the partition portion 17d and the second seal member 18.

[0163] [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 outer branch portion 17e and the inner branch portion 17f of the seal members 17, 18 contract due to compression during assembly, and the seal surface pressure increases, but since the dummy seal surface 82c is included, the seal surface pressure is dispersed by the seal surface 82c. Therefore, an appropriate seal surface pressure can be applied to the outer branch portion 17e and the inner branch portion 17f of the seal members 17, 18.

[0164] [Modification of the 16th embodiment] Fig. 64 shows a cross-sectional view of the outer branch portion 17e according to this modification, which is similar to Fig. 62. In this modification, a middle groove 81c is formed on the inside of the groove protrusion 72 provided in the hollow portion 19d. In addition to the two legs 19b of the outer branch portion 17e, a reinforcing leg 19f that reinforcingly supports the outer branch portion 17e of the first seal member 17 is provided in the middle groove 81c in the hollow portion 19d of the first seal member 17. Although illustration and description are omitted, the same applies to the inner branch portion 17f and the second seal member 18.

[0165] [About the action and effect of the modified version] According to the configuration of this modified example described above, the area of ​​the top 19a of each seal member 17, 18 on the side of each housing 11, 12 is increased, but since the reinforcing legs 19f are provided in the cavity 19d on the opposite side, each seal member 17, 18 is supported by the reinforcing legs 19f in the assembly grooves 13e, 14e. Therefore, a reaction force against the pressing force during sliding can be secured on the cavity 19d side of each seal member 17, 18, and an appropriate seal surface pressure can be applied to each seal member 17, 18.

[0166] <Seventeenth embodiment> The seventeenth embodiment will be described in detail with reference to FIGS.

[0167] In the third embodiment, as shown in Figures 31 and 32, in-groove protrusions 72 are provided in the assembly grooves 13e, 14e to be disposed in the hollow portions 19d of the seal members 17, 18, and a plurality of in-groove protrusions 73 that abut on the inner walls of the hollow portions 19d are provided on both side walls of the in-groove protrusions 72. In contrast to this, a case may be considered in which in-groove protrusions 72 are provided in the assembly grooves 13e, 14e, but in-groove protrusions 73 are not provided on both side walls of the in-groove protrusions 72.

[0168] 65 to 67 show a comparative example assuming that the in-groove protrusion 73 is not provided on the in-groove protrusion 72. FIG. 65 shows, in an enlarged cross-sectional view equivalent to FIG. 31, a state in which the partitioning portions 17c and 17d of the first seal member 17 are assembled into the assembly groove 13e, and the first seal member 17 is not in contact with the inner surface of the upper housing 11 and is not yet crushed. FIG. 66 shows, in an enlarged cross-sectional view equivalent to FIG. 65, a state in which the partitioning portions 17c and 17d are assembled into the assembly groove 13e, and the first seal member 17 is in contact with the inner surface of the upper housing 11 and is crushed. FIG. 67 shows, in an enlarged cross-sectional view equivalent to FIG. 65, a state in which the partitioning portions 17c and 17d are assembled into the assembly groove 13e, and the first rotating disk 13 rotates and the first seal member 17 slides on the inner surface of the upper housing 11.

[0169] As shown in Figures 65 to 67, the groove protrusion 72 and the inner wall of the assembly groove 13e in this case have a vertical portion extending vertically near the bottom of the assembly groove 13e. Therefore, as shown in Figure 67, when the first seal member 17 slides on the inner surface of the upper housing 11, the first seal member 17 is displaced in the direction opposite to the sliding direction, and the inner wall of one leg portion 19b is pressed against the top of the groove protrusion 72 and the outer wall of the other leg portion 19b is pressed against the vertical portion of the inner wall of the assembly groove 13e, which may cause stress concentration at these pressed portions. Therefore, in this seventeenth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0170] [Assembly structure of each sealing component] Fig. 68 shows the cross-sectional shape of the partitions 17c and 17d of the first seal member 17 in a free state and the state where the partitions 17c and 17d are overlapped with the assembly groove 13e in the 17th embodiment, in an enlarged cross-sectional view equivalent to Fig. 31. The assembly groove 13e is divided into one groove 81d and the other groove 81e by the groove protrusion 72, and one leg 19b is assembled into the one groove 81d, and the other leg 19b is assembled into the other groove 81e. Fig. 69 shows the first seal member 17 in a state where the partitions 17c and 17d are assembled into the assembly groove 13e and where the first seal member 17 is crushed by contacting the inner surface of the upper housing 11, in an enlarged cross-sectional view equivalent to Fig. 68. Figure 70 is an enlarged cross-sectional view similar to Figure 68 showing the state in which partitions 17c, 17d are assembled into assembly groove 13e, the first rotating disk 13 is rotating, and the first seal member 17 is sliding against the inner surface of the upper housing 11.

[0171] 68 to 70, in this embodiment, unlike the comparative example, the side wall of the in-groove protrusion 72 is formed so as to continuously change from a curved surface with a small curvature (large R) to a curved surface with a large curvature (small R) from the bottom of the assembly groove 13e to the top of the in-groove protrusion 72. Although not shown and not described, the same is true for the in-groove protrusion 72 of the assembly groove 14e of the second rotating disk 14.

[0172] [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, unlike the configurations of the first and second embodiments, each seal member 17, 18 has a mountain-shaped cross section that widens toward each rotating disk 13, 14, and includes a recess 19c that is recessed toward each housing 11, 12, and a hollow portion 19d that is bifurcated toward each rotating disk 13, 14 and has a hollow inside. In each assembly groove 13e, 14e, the side wall of the groove protrusion 72 arranged in the hollow portion 19d changes continuously from a curved surface with a small curvature (large R) to a curved surface with a large curvature (small R) from the bottom of each assembly groove 13e, 14e toward the top of the groove protrusion 72. Therefore, when the seal members 17, 18 start to slide against the housings 11, 12 as the rotary disks 13, 14 rotate, the inner surface of the cavity 19d of each seal member 17, 18 contacts successively from the bottom of the mounting groove 13e, 14e to the top of the groove protrusion 72, from the small curvature surface (large R) to the large curvature surface (small R), and the contact area of ​​the inner surface of the cavity 19d against the side wall of the groove protrusion 72 expands. This distributes the stress acting on the inner surface of the cavity 19d, and suppresses twisting of the seal members 17, 18. This ensures the sealing performance of the seal members 17, 18 without significantly increasing the manufacturing cost.

[0173] <Eighteenth embodiment> The eighteenth embodiment will be described in detail with reference to FIGS.

[0174] [Regarding the problem of the 17th embodiment] 71 to 73 relate to a seventeenth embodiment which is to be compared with this embodiment, and assume a state in which the second rotating disk 14 rotates and the second seal member 18 slides on the inner surface of the lower housing 12. FIG. 71 shows, in an enlarged cross-sectional view equivalent to FIG. 69, a state in which the partitions 18c, 18d of the second seal member 18 slide on the inner surface of the lower housing 12. FIG. 72 shows, in an enlarged cross-sectional view equivalent to FIG. 71, a state in which the partitions 18c, 18d have begun to pass through the entrances 25a to 28a of the lower housing 12. FIG. 73 shows, in an enlarged cross-sectional view equivalent to FIG. 71, a state in which the partitions 18c, 18d have passed through the entrances 25a to 28a.

[0175] In the seventeenth embodiment, the side walls of the groove ridges 72 of the assembly grooves 14e corresponding to the partitions 18c, 18d have curved surfaces whose curvature changes from the bottom of the assembly grooves 14e to the top of the groove ridges 72. Therefore, as shown in Fig. 73, when the partitions 18c, 18d pass through the entrances 25a to 28a, stress acts in the direction in which the second seal member 18 falls, so that the legs 19b contract inward along the curved surfaces of the side walls of the groove ridges 72, and the legs 19b cannot maintain the surface pressure, which may cause the partitions 18c, 18d to fall into the entrances 25a to 28a. Therefore, in the eighteenth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0176] [Assembly structure of each sealing component] Fig. 74 shows an enlarged cross-sectional view of one groove 81d divided into two by the groove protrusion 72 at the bottom of the mounting groove 14e of the second rotating disk 14 according to the 18th embodiment, and an end of one leg 19b mounted in the groove 81d. In this embodiment, the inner wall of the mounting groove 14e and the side wall of the groove protrusion 72 each have vertical surfaces 86a, 87a extending vertically near the bottom of the groove 81d of the mounting groove 14e, and the side wall of the groove protrusion 72 changes continuously from a curved surface with a small curvature to a curved surface with a large curvature from the vertical surface 87a toward the top of the groove protrusion 72. That is, as shown in Fig. 74, the inner peripheral wall of the mounting groove 14e has a curved surface 86b and a vertical surface 86a from the bottom toward the opening edge. On the other hand, the side wall of the groove protrusion 72 has a curved surface 87b and a vertical surface 87a from the bottom to the top, and a curved surface 87c that changes from the end of the vertical surface 87a continues. Although not shown and not described, the same is true for the other groove 81e of the assembly groove 14e.

[0177] [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, unlike the configuration of the 17th embodiment, the inner side walls of each assembly groove 13e, 14e and the side walls of the intra-groove protrusion 72 arranged in the hollow portion 19d each have vertical surfaces 86a, 87a extending vertically near the bottom of each assembly groove 13e, 14e, and the side walls of the intra-groove protrusion 72 continuously change from a curved surface with a small curvature (large R) to a curved surface with a large curvature (small R) from the bottom of each assembly groove 13e, 14e toward the top of the intra-groove protrusion 72. Therefore, when the seal members 17, 18 start to slide against the housings 11, 12 as the rotary disks 13, 14 rotate, the inner surface of the cavity 19d of each seal member 17, 18 contacts successively from the bottom of the mounting groove 13e, 14e to the top of the groove protrusion 72, from the small curvature surface (large R) to the large curvature surface (small R), and the contact area of ​​the inner surface of the cavity 19d against the side wall of the groove protrusion 72 expands. This distributes the stress acting on the inner surface of the cavity 19d, and suppresses twisting of the seal members 17, 18. This ensures the sealing performance of the seal members 17, 18 without significantly increasing the manufacturing cost. Meanwhile, since the side walls of the in-groove ridges 72 have vertical surfaces extending vertically near the bottoms of the assembly grooves 13e, 14e, even if the seal members 17, 18 contract inward along the curved surfaces of the side walls of the in-groove ridges 72, the surface pressure of the seal members 17, 18 against the in-groove ridges 72 is maintained by the vertical surfaces. This makes it possible to prevent the seal members 17, 18 from falling off the assembly grooves 13e, 14e.

[0178] <Nineteenth embodiment> The nineteenth embodiment will be described in detail with reference to FIGS.

[0179] [Assembly structure of each sealing component] The 19th embodiment differs in configuration from the 18th embodiment in the following respects: Fig. 75 shows the second seal member 18 and the assembly groove 14e to which it is attached in this embodiment in a cross-sectional view equivalent to Fig. 32. Fig. 76 shows an enlarged cross-sectional view taken along line K1-K1 in Fig. 75, which shows the bottom of the assembly groove 14e, one groove 81d, and the end of one leg 19b attached to the groove 81d.

[0180] In this embodiment, as shown in Figures 75 and 76, a plurality of convex portions 14i extending vertically from the bottom of one groove 81d are formed at equal intervals along the longitudinal direction of the groove 81d on the side wall of the assembly groove 14e into which the second seal member 18 is fitted, that is, on the outer side wall of one groove 81d. Here, as shown in Figure 76, the total width W1 of the bottom of one groove 81d is larger than the partial width W2 of the bottom of the part of the convex portions 14i, but the open width of the leg portion 19b of the second seal member 18 before assembly into the groove 81d is set to be smaller than the total width W1 and larger than the partial width W2. Although illustration and description are omitted, the same is true for the other groove 81e of the assembly groove 14e.

[0181] [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, unlike the configuration of the 18th embodiment, the side wall of the assembly groove 14e into which the second seal member 18 is fitted, that is, the outer side wall of both grooves 81d, 81e, is provided with a plurality of protrusions 14i extending vertically from the bottoms of those grooves 81d, 81e. Therefore, in addition to the action and effect of the 18th embodiment, it is possible to increase the surface pressure of each leg portion 19b which contributes to preventing the second seal member 18 from falling.

[0182] <Another embodiment> The disclosed technology is not limited to the above-described embodiments, and may be implemented by modifying part of the configuration as appropriate without departing from the spirit of the disclosed technology.

[0183] (1) In each of the above embodiments, the flow path switching device 1 is configured as an 8-way valve, but is not limited to this, and may be configured as other multi-way valves such as a 3-way valve, a 4-way valve, or a 6-way valve.

[0184] (2) In each of the above embodiments, the "valve body" of the disclosed technology is configured to be composed of a first rotating disk 13 and a second rotating disk 14, which are configured to rotate integrally on a rotating shaft 15. In contrast, the "valve body" can also be configured to be composed of a first sliding plate and a second sliding plate that move linearly.

[0185] (3) In each of the above embodiments, the first seal member 17 is fixed to the first rotating disk 13, and the second seal member 18 is fixed to the second rotating disk 14. However, it is also possible to fix the first seal member to an upper housing facing the first rotating disk, and fix the second seal member to a lower housing facing the second rotating disk.

[0186] (4) In each of the above-described embodiments, the cross section of the sealing members 17, 18 is formed into a bifurcated mountain shape. However, in terms of matters related only to the external shape of the sealing members, the cross section may be formed into a shape such as a solid O-ring without a cavity. [Industrial Applicability]

[0187] The disclosed technology can be utilized to switch the flow path of a fluid in a fluid circuit through which a fluid flows. [Explanation of symbols]

[0188] 1 Flow path switching device 2 Housing (stator) 11 Upper housing (stator) 12 Lower housing (stator) 13 First rotating disk (valve body) 13e Assembly groove 14 Second rotating disk (valve body) 14e Assembly groove 14i Convex 17 First seal member (sealing means) 17a Inner circle 17b Outer circle 17c Partition 17d Partition 17e Outer branch 17f Inner branch 18 Second seal member (sealing means) 18a Inner circle 18b Outer circle 18c Partition 18d Partition 19c Recess 19d Cavity 19f Reinforcement leg 20 Inflow / outflow passage (communicating passage) 21 1st inlet / outlet passage 21a Entrance / exit (opening) 22 2nd inlet / outlet passage 22a Entrance / exit (opening) 23 3rd inlet / outlet passage 23a Entrance / exit (opening) 24 4th inlet / outlet passage 24a Entrance / exit (opening) 25 5th inlet / outlet passage 25a Entrance / exit (opening) 26 No. 6 inlet / outlet passage 26a Entrance / exit (opening) 27 7th inlet / outlet passage 27a Entrance / exit (opening) 28 No. 8 inlet / outlet passage 28a Entrance / exit (opening) 29 Cross opening edge 30 Rotating passage (connecting passage) 31 First rotating passage (connecting passage) 32 Second rotating passage (connecting passage) 40 Rotating passage (connecting passage) 43 Third Turn Passage 44 4th Turn Passage 71 Convex 72 Groove ridge 73 Groove protrusion 76 Auxiliary seat 79 Seal stopper (means for preventing popping out) 84 Dummy seal surface (seal surface pressure distribution part) 90 Electric vehicle 91 Cooling System

Claims

1. At least one stator; A valve body that moves relative to the stator; At least one communication passage is provided in each of the stator and the valve body; 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 sealing means includes an inner circular portion disposed on a central side of the valve body or the stator, an outer circular portion disposed on an outer peripheral side of the valve body or the stator, and partition portions that connect the inner circular portion and the outer circular portion at a plurality of points and separate the plurality of communication passages provided in the valve body or the stator, The valve body or the stator includes an assembly groove into which the sealing means is assembled, and the partition portion of the sealing means is fitted into the assembly groove in a tensioned state and assembled. A flow path switching device.

2. At least one stator; A valve body that moves relative to the stator; At least one communication passage is provided in each of the stator and the valve body; 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 sealing means includes an inner circular portion disposed on a central side of the valve body or the stator, an outer circular portion disposed on an outer peripheral side of the valve body or the stator, and partition portions that connect the inner circular portion and the outer circular portion at a plurality of points and separate the plurality of communication passages provided in the valve body or the stator, the valve body or the stator includes an assembly groove into which the sealing means is assembled, and the sealing means is assembled by being fitted into the assembly groove; A plurality of protrusions that come into contact with the partition portion are disposed at different positions on both sides of the partition portion on an inner wall of the assembly groove at a portion where the partition portion is fitted. A flow path switching device.

3. At least one stator; A valve body that moves relative to the stator; At least one communication passage is provided in each of the stator and the valve body; 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 sealing means includes an inner circular portion disposed on a central side of the valve body or the stator, an outer circular portion disposed on an outer peripheral side of the valve body or the stator, and partition portions that connect the inner circular portion and the outer circular portion at a plurality of points and separate the plurality of communication passages provided in the valve body or the stator, The valve body includes an assembly groove into which the sealing means is assembled, the sealing means has a mountain-shaped cross section expanding toward the valve body or the stator, and includes a recessed portion recessed toward the stator or the valve body, and a hollow portion which is branched into at least two portions toward the valve body or the stator and has a hollow inside, The assembly groove includes a groove protrusion disposed in the cavity portion, The side wall of the groove protrusion changes continuously from a curved surface with a small curvature to a curved surface with a large curvature from the bottom of the assembly groove to the top of the groove protrusion. A flow path switching device.

4. At least one stator; A valve body that moves relative to the stator; At least one communication passage is provided in each of the stator and the valve body; 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 sealing means includes an inner circular portion disposed on a central side of the valve body or the stator, an outer circular portion disposed on an outer peripheral side of the valve body or the stator, and partition portions that connect the inner circular portion and the outer circular portion at a plurality of points and separate the plurality of communication passages provided in the valve body or the stator, The valve body includes an assembly groove into which the sealing means is assembled, the sealing means has a mountain-shaped cross section expanding toward the valve body or the stator, and includes a recessed portion recessed toward the stator or the valve body, and a hollow portion which is branched into at least two portions toward the valve body or the stator and has a hollow inside, The assembly groove includes a groove protrusion disposed in the cavity portion, The inner side wall of the assembly groove and the side wall of the groove protrusion each have a vertical surface extending vertically near the bottom of the assembly groove, and the side wall of the groove protrusion continuously changes from a curved surface with a small curvature to a curved surface with a large curvature from the vertical surface toward the top of the groove protrusion. A flow path switching device.

5. The flow path switching device according to claim 2, one of the stator and the valve body is a holding member that holds the sealing means, and the other is a sliding member on which the sealing means slides, the sealing means has a mountain-shaped cross section expanding toward the holding member, and includes a recessed portion recessed toward the sliding member, and a hollow portion branching into at least two portions toward the holding member, the hollow portion being hollow on the inside; The assembly groove includes a groove protrusion disposed in the cavity portion, A groove protrusion convex portion that abuts against an inner wall of the cavity portion is provided on a side wall of the groove protrusion corresponding to the partition portion. A flow path switching device.

6. The flow path switching device according to claim 5 , The convex portion of the assembly groove and the inner-groove rib convex portion are configured to vertically abut against an outer surface of the partition portion of the sealing means and an inner surface of the cavity portion. A flow path switching device.

7. 7. The flow path switching device according to claim 1, the sealing means further includes an outer branch portion where the partition portion branches to the outer circular portion, and an inner branch portion where the partition portion branches to the inner circular portion, The outer branch portion and the inner branch portion are disposed outside a distribution area of ​​the openings of the communication passage that the sealing means crosses while sliding. A flow path switching device.

8. 7. The flow path switching device according to claim 1, the opening of the communication passage, across which the partition portion of the seal means slides, has an intersecting opening edge extending in a direction intersecting the sliding direction; The intersecting opening edge has a curved surface that curves toward the inside of the opening, and the diameter of the curved surface is larger toward the center than toward both ends of the intersecting opening edge. A flow path switching device.

9. 7. The flow path switching device according to claim 1, An auxiliary seat that extends along the sliding direction and comes into contact with the partition portion of the sealing means is provided on the inside of the opening of the communication passage, the opening being crossed by the partition portion of the sealing means while sliding. A flow path switching device.

10. 7. The flow path switching device according to claim 1, A protrusion prevention means is provided for preventing the partition portion of the sealing means from protruding from the assembly groove. A flow path switching device.

11. The flow path switching device according to claim 1 or 2, one of the stator and the valve body is a holding member that holds the sealing means, and the other is a sliding member on which the sealing means slides, the sealing means has a mountain-shaped cross section expanding toward the holding member, and includes a recessed portion recessed toward the sliding member, and a hollow portion branching into at least two portions toward the holding member, the hollow portion being hollow on the inside; The sealing means has a smaller compression allowance on the inner diameter side than on the outer diameter side. A flow path switching device.

12. The flow path switching device according to claim 11, The compression allowance of the partition portion is smaller than the compression allowance on the inner diameter side of the outer circular portion. A flow path switching device.

13. The flow path switching device according to claim 11, The compression allowance on the inner diameter side of the outer circular portion is smaller in the vicinity of the partition portion. A flow path switching device.

14. The flow path switching device according to claim 11, The compression allowance on the inner diameter side of the inner circular portion is smaller in the vicinity of the partition portion. A flow path switching device.

15. The flow path switching device according to claim 11, the sealing means further includes an outer branch portion where the partition portion branches to the outer circular portion, and an inner branch portion where the partition portion branches to the inner circular portion, The outer branch portion and the inner branch portion each include a seal surface pressure dispersion portion for dispersing a seal surface pressure. A flow path switching device.

16. The flow path switching device according to claim 15, The hollow portion is provided with a reinforcing leg for reinforcingly supporting the sealing means in the assembly groove. A flow path switching device.

17. 7. The flow path switching device according to claim 1, The flow path switching device is used in the cooling system of an electric vehicle. A flow path switching device.

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