Flow path switching device

Abstract

This flow passage switching device is provided with: a stator 11(12); a valve body (13(14)) that is driven relative to the stator; a communication passage that is provided to the stator and the valve body; and an annular sealing means (17(18)) that slides relative to the stator as the valve body is driven. The communication passages (31(43), 32(44)) of the valve body and the communication passages (21a to 24a (25a to 28a)) of the stator are selectively connected by driving the valve body, thereby switching a series of flow passages. The sealing means (17(18)) includes: an inner circular part (17a(18a)) disposed on the center side of the valve body; an outer circular part (17b(18b)) disposed on the outer peripheral side of the valve body; and partition parts (17c(18c), 17d(18d)) that connect the inner circular part and the outer circular part at a plurality of positions and partition the plurality of communication passages (31(43), 32(44)). The valve body (13(14)) includes an assembling groove (13e(14e)) for assembling the sealing means (17(18)), and the partition parts of the sealing means are assembled by being fitted into the assembling groove in a pulled / expanded state.

Description

Flow path switching device

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

[0002] The applicant of the present application is currently developing a flow path switching device for switching the flow paths of liquid, which includes a stator, a valve body that moves relative to the stator, a connecting 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 connecting passage of the valve body with the connecting passage of the stator by driving the valve body, thereby switching and forming a series of flow paths.

[0003] As a technology related to sealing means, for example, Patent Document 1 below discloses a technology related to a deformable O-ring and a seal structure to be installed in the middle of a fluid (lubricant) flow path. This seal structure includes a deformable O-ring that is fitted into an oval recessed fitting portion to seal the flow path. The deformable O-ring has an outer periphery slightly longer than the inner periphery of the recessed fitting portion. The deformable O-ring includes a first portion that is easily deformed so as to move away from the inner periphery of the recessed fitting portion and recess inward when fitted into the recessed fitting portion, a second portion that is less easily deformed than the first portion, and a deformation prevention means for preventing deformation of the first portion. According to this seal structure, when the deformable O-ring is fitted into the recessed fitting 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, tending to recess the first portion inward. At this time, the first portion functions as a deformation prevention means, preventing the first portion from recessing.

[0004] JP 2011-106485 A

[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 circumferential wall of the recessed fitting portion, preventing deformation due to stress concentration in the first portion and achieving the desired sealing performance. Furthermore, when assembling the deformed O-ring into the recessed fitting portion, even if the recessed fitting portion is facing downward, the deformed O-ring is prevented from falling off. However, it is necessary to provide a means for preventing deformation in the first portion, which requires special processing of the deformed O-ring, raising concerns about increased manufacturing costs.

[0006] This disclosed technology has been made in consideration of the above 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.

[0007] (1) In order to achieve the above object, one aspect of the technology disclosed in the present application is a flow path switching device comprising at least one stator, a valve element that moves relative to the stator, at least one communication passage provided in each of the stator and the valve element, and an annular sealing means that is provided between the stator and the valve element and slides against the stator or the valve element as the valve element is driven, wherein the valve element is driven to selectively connect the communication passage of the valve element to the communication passage of the stator, and switching between and forming a series of flow paths, the sealing means including an inner circular portion located on the center side of the valve element, an outer circular portion located on the outer periphery of the valve element, and partition portions that connect the inner circular portion and the outer circular portion at multiple locations and separate the multiple communication passages, the valve element or the stator including an assembly groove for assembling the sealing means, and the partition portion of the sealing means being fitted into the assembly groove in a tensioned state and assembled.

[0008] According to the configuration (1) above, the stator and the valve disc each have at least one communication passage, and a sealing means is assembled in an assembly groove provided in the valve disc or the stator. The sealing means includes an inner circular portion disposed toward the center of the valve disc, an outer circular portion disposed toward the outer periphery of the valve disc, and a partition portion connecting the inner circular portion and the outer circular portion and separating the multiple communication passages. The partition portion is fitted into the assembly groove and assembled in a tensioned state. Therefore, a tensile force acts on the partition portion, which prevents deformation of the partition portion against external forces. Furthermore, when the valve disc is actuated 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] (2) In order to achieve the above object, a flow path switching device is provided which includes at least one stator, a valve element which moves relative to the stator, at least one communication passage provided in each of the stator and the valve element, and an annular sealing means which is provided between the stator and the valve element and slides against the stator or the valve element as the valve element is driven, and which is configured to selectively connect the communication passage of the valve element and the communication passage of the stator by driving the valve element, thereby switching and forming a series of flow paths, wherein the sealing means includes an inner circular portion located on the center side of the valve element, an outer circular portion located on the outer periphery of the valve element, and partition portions which connect the inner circular portion and the outer circular portion at multiple locations and separate the multiple communication passages, the valve element or the stator includes an assembly groove in which the sealing means is assembled, and the sealing means is assembled by fitting into the assembly groove, and the inner wall of the assembly groove at the portion where the partition portion is fitted has multiple protrusions which abut against the partition portion and are arranged at different positions on both sides of the partition portion.

[0010] According to the configuration (2), unlike the configuration (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, so deformation of the partition against external forces is suppressed. Furthermore, when the valve body is actuated to switch the flow path and the partition crosses an opening of the communication passage, the partition is prevented from getting caught on the opening or from jumping out into the opening.

[0011] (3) In order to achieve the above object, the flow path switching device comprises at least one stator, a valve element that moves relative to the stator, at least one communication path provided in each of the stator and the valve element, and an annular sealing means that is provided between the stator and the valve element and slides against the stator or the valve element as the valve element is driven, and is configured to selectively connect the communication path of the valve element and the communication path of the stator by driving the valve element, and to switch and form a series of flow paths, the sealing means having an inner circular portion located on the center side of the valve element and an annular portion located on the outer periphery of the valve element. The valve body includes an outer circular portion in which the stator is disposed, and partition portions that connect the inner circular portion and the outer circular portion at multiple locations and separate the multiple communicating passages, the valve body includes an assembly groove in which the sealing means is assembled, the sealing means having a mountain-shaped cross section that widens toward the valve body side and including a recessed portion that is recessed on the stator side and a hollow portion that branches into at least two portions toward the valve body side and has a hollow interior, the assembly groove includes an in-groove ridge that is disposed in the hollow portion, and the side wall of the in-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 in-groove ridge.

[0012] According to the configuration (3), unlike the configurations (1) and (2), the sealing means has a mountain-shaped cross section that widens toward the valve disc, including a recessed portion that is recessed toward the stator, and a hollow portion that branches into at least two portions toward the valve disc and has an internal cavity. The side walls of the groove-mounted ridges disposed in the hollow portions of the assembly groove continuously change from a small curvature surface to a large curvature surface from the bottom of the assembly groove to the top of the groove-mounted ridges. Therefore, when the sealing means begins to slide relative to the stator or valve disc as the valve disc is driven, the inner surface of the hollow portion of the sealing means continuously contacts the curved surface from a small curvature surface to a large curvature surface from the bottom of the assembly groove to the top of the groove-mounted ridges, expanding the contact area of ​​the inner surface of the cavity with the side walls of the groove-mounted ridges. This distributes stress acting on the inner surface of the hollow portion and suppresses twisting of the sealing means.

[0013] (4) In order to achieve the above object, a flow path switching device is provided with at least one stator, a valve element that moves relative to the stator, at least one communication path provided in each of the stator and the valve element, and an annular sealing means that is provided between the stator and the valve element and slides against the stator or the valve element as the valve element is driven, and is configured to selectively connect the communication path of the valve element and the communication path of the stator by driving the valve element, and to switch and form a series of flow paths, the sealing means having an inner circular portion located on the center side of the valve element, an outer circular portion located on the outer periphery of the valve element, and a plurality of sealing portions that are formed between the inner circular portion and the outer circular portion. the valve body includes an assembly groove into which the sealing means is assembled, the sealing means having a mountain-shaped cross section widening towards the valve body side, and including a recessed portion recessed on the stator side and a hollow portion which is forked into at least two portions towards the valve body side and has an interior hollow, the assembly groove includes an in-groove ridge disposed in the hollow portion, the inner side wall of the assembly groove and the side wall of the in-groove ridge each have a vertical surface extending vertically near the bottom of the assembly groove, and the side wall of the in-groove ridge continuously changes from a curved surface with a smaller curvature to a curved surface with a larger curvature from the vertical surface towards the top of the in-groove ridge.

[0014] According to the configuration (4), unlike the configuration (3), the inner wall of the assembly groove and the side wall of the in-groove ridge disposed in the cavity each have a vertical surface extending perpendicularly near the bottom of the assembly groove, and the side wall of the in-groove ridge continuously changes in curvature from a smaller curvature to a larger curvature from the bottom of the assembly groove to the top of the in-groove ridge. Therefore, when the sealing means begins to slide against the stator or the valve disc as the valve disc is driven, the inner surface of the cavity of the sealing means continuously contacts a curved surface from a smaller curvature to a larger curvature from the bottom of the assembly groove to the top of the in-groove ridge, expanding the contact area of ​​the inner surface of the cavity with the side wall of the in-groove ridge. This distributes stress acting on the inner surface of the cavity and suppresses twisting of the sealing means. On the other hand, the side walls of the intra-groove ridges have vertical surfaces that extend vertically near the bottom of the assembly groove. Therefore, even if the sealing means contracts inward along the curved surfaces of the side walls of the intra-groove ridges, the surface pressure of the sealing means against the intra-groove ridges is maintained by the vertical surfaces.

[0015] (5) To achieve the above object, in the configuration of (2) above, it is preferable that one of the stator and the valve body is a retaining member that retains 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 that widens toward the retaining member side, and includes a recess that is recessed on the sliding member side, and a hollow portion that branches into at least two toward the retaining member side and has a hollow interior, the assembly groove includes an in-groove ridge that is arranged in the hollow portion, and the side wall of the in-groove ridge that corresponds to the partition portion is provided with an in-groove ridge convex portion that abuts against the inner wall of the hollow portion.

[0016] According to the configuration (5) above, in addition to the effects of the configuration (2) above, the sealing means has a mountain-shaped cross section that widens toward the holding member, and includes a recessed portion that is recessed toward the sliding member, and a hollow portion that branches into at least two portions toward the holding member and has an internal cavity. The assembly groove also includes an in-groove ridge disposed in the hollow portion, and an in-groove ridge convex portion that abuts against the inner wall of the hollow portion is provided on the side wall of the in-groove ridge corresponding to the partition portion. Therefore, the in-groove ridge is disposed 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 ridge convex portion, thereby suppressing deformation of the partition portion against external forces.

[0017] (6) In order to achieve the above object, in the configuration of (5) above, it is preferable that the convex portion of the assembly groove and the convex ridge portion in the groove 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 (6) above, in addition to the effect of the configuration (5) above, the convex portion of the assembly groove and the convex portion of the groove protrusion perpendicularly contact the outer surface and the inner surface of the hollow portion at the partition portion, thereby expanding the range in which the outer surface and inner surface of the partition portion are subjected to high surface pressure.

[0019] (7) In order to achieve the above object, in any of the configurations (1) to (6) above, it is preferable that 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, and that the outer branch portion and the inner branch portion are positioned outside the distribution area of ​​the openings of the communication passage that the sealing means slides across.

[0020] According to the configuration (7) above, in addition to the effect of any of the configurations (1) to (6) above, the outer branch portion and the inner branch portion of the sealing means, which are subject to particularly high surface pressure, are arranged outside the distribution area of ​​the opening across which the sealing means slides.

[0021] (8) In order to achieve the above object, in any of the configurations (1) to (6) above, it is preferable that, 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 of the intersecting opening edge than at both ends.

[0022] According to the configuration (8), in addition to the effects of any of the configurations (1) to (6), the opening of the stator communication passage is more likely to protrude when the partition of the sealing means crosses it toward the center. However, the diameter of the intersecting opening edge of this opening is larger at the inner curved surface than at the both end surfaces. Therefore, even if the partition protrudes significantly toward the center of the opening when it is opened, the larger-diameter curved surface of the intersecting opening edge allows the partition to pass smoothly.

[0023] (9) In order to achieve the above object, in any of the configurations (1) to (6) above, it is preferable that an auxiliary seat portion that extends along the sliding direction and contacts the partition portion is provided on the inside of the opening of the communicating passage that is crossed by the partition portion of the sealing means while sliding.

[0024] According to the configuration (9) above, in addition to the effects of any of the configurations (1) to (6) above, an auxiliary seat with which the partition of the sealing means comes into contact is provided inside the opening of the stator through which the partition slides. Therefore, the partition comes into contact with the auxiliary seat when crossing the opening.

[0025] (10) In order to achieve the above object, in any of the configurations (1) to (6) above, it is preferable to provide a protrusion prevention means for preventing the partition portion of the sealing means from protruding from the assembly groove.

[0026] According to the configuration (10) above, in addition to the effect of any one of the configurations (1) to (6) above, the protrusion of the partition portion of the sealing means from the assembly groove is restricted by the protrusion restriction means.

[0027] (11) In order to achieve the above object, in the configuration of (1) or (2) above, 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, and the sealing means has a mountain-shaped cross section that widens toward the holding member side, and includes a recess that is recessed on the sliding member side, and a hollow portion that branches into at least two toward the holding member side and has a hollow inside, and it is preferable that the compression allowance of the sealing means on the inner diameter side is smaller than the compression allowance on the outer diameter side.

[0028] According to the configuration (11) above, in addition to the effects of the configurations (1) and (2) above, the sealing means has a mountain-shaped cross section that widens toward the holding member, and includes a recessed portion that is recessed toward the sliding member, and a hollow portion that branches into at least two portions toward the holding member and has a hollow interior. This sealing means has a smaller compression allowance on its inner diameter side than on its outer diameter side. The smaller the compression allowance, the smaller the surface pressure of the sealing means.

[0029] (12) To achieve the above object, in the configuration of (11) above, it is preferable that 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 (12) above, in addition to the effect of the configuration (11) above, when the valve disc is driven, the partition and the outer circular portion 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 portion. The smaller the compression allowance, the smaller the surface pressure.

[0031] (13) To achieve the above object, in the configuration of (11) above, it is preferable that 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 (13) above, in addition to the effect of the configuration (11) above, when the valve disc is driven, the partition portion and the outer circular portion are compressed by the sliding of the sealing means, but the compression allowance on the inner diameter side of the outer circular portion is smaller closer to the partition portion. The smaller the compression allowance, the smaller the surface pressure.

[0033] (14) To achieve the above object, in the configuration of (11) above, it is preferable that the compression allowance on the inner diameter side of the inner circular portion is smaller the closer to the partition portion.

[0034] According to the configuration of (14) above, in addition to the effect of the configuration of (11) above, when the valve disc is driven, the partition portion and the inner circular portion are compressed by the sliding of the sealing means, but the compression allowance on the inner diameter side of the inner circular portion is smaller closer to the partition portion. The smaller the compression allowance, the smaller the surface pressure.

[0035] (15) In order to achieve the above object, in the configuration of (11) above, it is preferable that 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, and that 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 (15) above, in addition to the effect of the configuration (11) above, 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, but since the configuration includes a sealing surface pressure dispersion portion, the sealing surface pressure is dispersed by the dispersion portion.

[0037] (16) To achieve the above object, in the configuration of (15) above, it is preferable that the cavity be provided with reinforcing legs that reinforcingly support the sealing means in the assembly groove.

[0038] According to the configuration (16) above, in addition to the effect of the configuration (15) above, even if the area of ​​the sealing means on the side of the sliding member is increased, the reinforcing legs are provided in the hollow portion on the opposite side, so that the sealing means is supported in a reinforcing manner by the assembly groove.

[0039] (17) To achieve the above object, in any one of the configurations (1) to (6), the flow path switching device is preferably used in a cooling system for an electric vehicle.

[0040] According to the configuration (17) above, the flow path switching device used in the cooling system of an electric vehicle can achieve the same effect as any one of the configurations (1) to (6) above.

[0041] According to the above configuration (1), the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0042] According to the above configuration (2), the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0043] According to the above configuration (3), the sealing performance of the sealing means can be ensured without any particular increase in manufacturing costs.

[0044] According to the above configuration (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 configuration (5) above, in addition to the effect of the configuration (2) above, 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. Furthermore, when the fluid is a liquid, the recess of the partition becomes a pool of liquid, and the lubricating effect of the liquid reduces the sliding resistance of the partition against the sliding member.

[0046] According to the above-mentioned configuration (6), in addition to the effect of the above-mentioned configuration (5), it is possible to reduce the concentration of stress on the outer and inner surfaces of the partition portion of the sealing means.

[0047] According to the configuration (7), in addition to the effect of any of the configurations (1) to (6) above, 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 configuration (8) above, in addition to the effect of any of the configurations (1) to (6) above, even if the partition portion protrudes into the opening of the communicating passage when crossing the opening, the sealing means can reduce the possibility of getting caught on the edge of the intersecting opening or deterioration of sliding properties when riding over the edge of the intersecting opening.

[0049] According to the configuration (9) above, in addition to the effect of any of the configurations (1) to (6) above, when the partition portion of the sealing means crosses the opening of the communicating passage, it is possible to prevent the partition portion from protruding into the opening, thereby reducing the possibility of the partition portion getting caught on the periphery of the opening and deterioration of sliding properties.

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

[0051] According to the configuration (11) above, in addition to the effects of the configurations (1) and (2) above, 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 configuration (12) above, in addition to the effect of the configuration (11) above, it is possible to apply an appropriate sealing surface pressure between the partition portion and the outer circular portion of the sealing means.

[0053] According to the configuration (13) above, in addition to the effect of the configuration (11) above, it is possible to apply an appropriate sealing surface pressure to the outer circular portion of the sealing means depending on the location.

[0054] According to the configuration (14) above, in addition to the effect of the configuration (11) above, it is possible to apply an appropriate sealing surface pressure to the inner circular portion of the sealing means depending on the location.

[0055] According to the configuration (15) above, in addition to the effect of the configuration (11) above, it is possible to apply an appropriate sealing surface pressure to the outer branch portion and the inner branch portion of the sealing means.

[0056] According to the configuration (16) above, in addition to the effect of the configuration (15) above, 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 configuration (17) above, it is possible to obtain the same effect as any one of the configurations (1) to (6) above for a flow path switching device used in a cooling system for an electric vehicle.

[0058] Perspective view showing the flow path switching device according to the first embodiment. Front view showing the flow path switching device according to the first embodiment. Plan view showing the flow path switching device according to the first embodiment. Bottom view showing the flow path switching device according to the first embodiment. Exploded perspective view showing the flow path switching device according to the first embodiment. Cross-sectional view taken along line A-A of FIG. 2 showing the flow path switching device according to the first embodiment. Cross-sectional view taken along line B-B of FIG. 3 showing the flow path switching device according to the first embodiment. Perspective view showing the inside of the upper housing according to the first embodiment. Perspective view showing the first rotating disk according to the first embodiment. Plan view showing the first rotating disk according to the first embodiment. Bottom view showing the first rotating disk according to the first embodiment. Plan view showing the second rotating disk according to the first embodiment. Bottom view showing the second rotating disk according to the first embodiment. Perspective view showing the rotating shaft according to the first embodiment. Cross-sectional view taken along line E-E of FIG. 14 showing the rotating shaft according to the first embodiment. Cross-sectional view taken along line F-F of FIG. 2 showing the flow path switching device 1 according to the first embodiment. Schematic diagram of a cross-sectional view taken along line G-G of FIG. 2 showing the rotational position of the first rotating disk with respect to the upper housing for the "first pattern" of the flow path switching pattern according to the first embodiment. Schematic diagram of a cross-sectional view taken along line H-H of FIG. 2 showing the rotational position of the second rotating disk with respect to the lower housing for the same "first pattern" according to the first embodiment. Schematic diagram similar to FIG. 17 showing the rotational position of the first rotating disk with respect to the upper housing for the "second pattern" of the flow path switching pattern according to the first embodiment. Schematic diagram similar to FIG. 18 showing the rotational position of the second rotating disk with respect to the lower housing for the same "second pattern" according to the first embodiment. Circuit diagram showing an example of use of the flow path switching device. Plan view or bottom view showing the side where the first rotating disk contacts the upper housing and the side where the second rotating disk contacts the lower housing according to the first embodiment. Enlarged cross-sectional view showing the first rotating disk and the upper housing cut along line I-I of FIG. 22 at the portion of the assembly groove where the upper seal member is assembled. Enlarged cross-sectional view similar to FIG. 23 showing the deformed state of the upper seal member when a rotational force acts in the orthogonal direction of the upper seal member according to the first embodiment. Plan view similar to FIG. 22 showing the state where each rotating disk rotates and the partition portion of each seal member crosses the entrances and exits of each inflow / outflow passage. Plan view simply showing the assembly state of each seal member in the assembly groove.A plan view schematically showing only the assembly groove according to the first embodiment. A plan view schematically showing only each sealing member according to the first embodiment. An enlarged cross-sectional view corresponding to FIG. 23 showing a state where the partition portion of the first sealing member is assembled to the assembly groove according to the second embodiment. A cross-sectional view taken along line J-J of FIG. 29 showing a state where the partition portion is similarly assembled to the assembly groove according to the second embodiment. An enlarged cross-sectional view corresponding to FIG. 29 showing a state where the partition portion of the first sealing member is assembled to the assembly groove according to the third embodiment. A cross-sectional view taken along line K-K of FIG. 31 showing a state where the partition portion is similarly assembled to the assembly groove according to the third embodiment. A cross-sectional view taken along line N-N of FIG. 32 showing a state where the partition portion is similarly assembled to the assembly groove according to the third embodiment. A cross-sectional view corresponding to FIG. 32 showing a state where the partition portion is similarly assembled to the assembly groove according to the proportionality of the third embodiment. An enlarged cross-sectional view corresponding to FIG. 33 showing a state where the partition portion of the first sealing member is assembled to the assembly groove according to the fourth embodiment. An enlarged cross-sectional view corresponding to FIG. 33 showing a state where the partition portion of the first sealing member is assembled to the assembly groove according to the fifth embodiment. A plan view showing an enlarged view of the vicinity of the partition portion of the first sealing member assembled to the assembly groove of the first rotating disk according to the proportionality of the sixth embodiment. A cross-sectional view schematically showing a state where the partition portion crosses the entrance and exit according to the proportionality of the sixth embodiment. An enlarged plan view corresponding to FIG. 37 showing the vicinity of the partition portion of the first sealing member assembled to the assembly groove of the first rotating disk according to the sixth embodiment. A bottom view showing one of the entrances and exits of the first to fourth inflow / outflow passages opening on the inner surface of the upper housing according to the seventh embodiment. A cross-sectional view showing the entrance and exit cut along line C1-C1 or C2-C2 of FIG. 40 according to the seventh embodiment. A cross-sectional view showing the entrance and exit similarly cut along line D-D of FIG. 40 according to the seventh embodiment. A bottom view showing one of the entrances and exits of the first to fourth inflow / outflow passages opening on the inner surface of the upper housing according to the eighth embodiment. A cross-sectional view showing the entrance and exit cut along line Q-Q of FIG. 43 according to the eighth embodiment. A bottom view schematically showing only the assembly groove in the second rotating disk according to the ninth embodiment. An enlarged cross-sectional view showing a state where the partition portion of the second sealing member is assembled to the assembly groove cut at the portions of lines S1-S1 and S2-S2 (the central portion of the partition portion) of FIG. 45 according to the ninth embodiment. An enlarged cross-sectional view showing the assembly structure of the portion shown in FIG. 46 disassembled according to the ninth embodiment.Bottom view showing the part shown in Fig. 48 as viewed from below the part shown in Fig. 46, according to the 9th embodiment. Enlarged cross-sectional view showing the state where the partition portion of the second seal member is assembled in the assembly groove, cut at the portions of lines T1 - T1 and T2 - T2 in Fig. 45 (portions other than the central portion of the partition portion). Planar view showing the side of the first rotating disk that contacts the upper housing, according to the proportionality of the 10th embodiment. Enlarged cross-sectional view showing the first rotating disk and the upper housing cut along line U - U in Fig. 50 at the portion of the assembly groove where the outer circular portion of the first seal member is assembled. Planar view showing the side of the first rotating disk that contacts the upper housing, according to the 10th embodiment. Enlarged cross-sectional view showing the portion of the first seal member of the first rotating disk and the assembly groove cut along lines V1 - V1 (outer circular portion) and V2 - V2 (inner circular portion) in Fig. 52. Enlarged cross-sectional view similar to Fig. 53 showing the portion of the first seal member of the first rotating disk and the assembly groove, according to the 11th embodiment. Planar view showing the side of the first rotating disk that contacts the upper housing, according to the 12th embodiment. Enlarged cross-sectional view showing the portion of the first seal member of the first rotating disk and the assembly groove cut along line W - W in Fig. 57 (partition portion). Enlarged cross-sectional view similar to Fig. 56 showing the portion of the first seal member of the first rotating disk and the assembly groove, according to the 13th embodiment. Planar view showing the side of the first rotating disk that contacts the upper housing, according to the 14th embodiment. Enlarged cross-sectional view showing the portion of the first seal member of the first rotating disk and the assembly groove cut along line Z1 - Z1 in Fig. 58 (outer branch portion near the partition portion). Enlarged cross-sectional view showing the portion of the first seal member of the first rotating disk and the assembly groove cut along line Z2 - Z2 in Fig. 58 (inner branch portion near the partition portion), according to the 15th embodiment. Enlarged planer view similar to Fig. 39 showing the portion of the partition portion of the first seal member assembled in the assembly groove of the first rotating disk, according to the 16th embodiment. Enlarged planer view showing the portion of the outer branch portion of the first seal member assembled in the assembly groove of the first rotating disk, according to the 16th embodiment. Cross-sectional view along line P - P in Fig. 62 showing the portion of the outer branch portion, according to the 16th embodiment. Cross-sectional view similar to Fig. 62 showing the portion of the outer branch portion, according to the modified example of the 16th embodiment.31 according to a comparative example of the seventeenth embodiment, showing a state in which a 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. An enlarged cross-sectional view equivalent to FIG. 65 according to a comparative example of the seventeenth embodiment, showing a state in which a partition portion is assembled into the assembly groove and the first seal member is crushed by contacting the inner surface of the upper housing. An enlarged cross-sectional view equivalent to FIG. 65 according to a comparative example of the seventeenth embodiment, showing a state in which a partition portion is assembled into the assembly groove and the first seal member is crushed by contacting the inner surface of the upper housing. An enlarged cross-sectional view equivalent to FIG. 31 according to a comparative example of the seventeenth embodiment, showing a state in which a 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. 68 , showing a state in which the partition is assembled into the assembly groove and the first seal member is in contact with the inner surface of the upper housing and crushed, according to the seventeenth embodiment. FIG. 68 , showing a state in which the partition is assembled into the assembly groove and the first rotating disk is rotating, causing the first seal member to slide against the inner surface of the upper housing, according to the seventeenth embodiment. FIG. 70 , showing a state in which the partition of the second seal member slides against the inner surface of the lower housing, according to the seventeenth embodiment. FIG. 71 , showing a state in which the partition has started to pass through the opening of the lower housing, according to the seventeenth embodiment. FIG. 72 , showing a state in which the partition has passed through the opening of the lower housing, according to the seventeenth embodiment. 75. An enlarged cross-sectional view showing the bottom of the assembly groove of the second rotating disk, one of the grooves divided into two by an intra-groove protrusion, and an end of one of the legs assembled in the groove, according to the 18th embodiment. A cross-sectional view equivalent to FIG. 32 showing the second seal member and the assembly groove in which it is assembled, according to the 19th embodiment. An enlarged cross-sectional view showing the bottom of the assembly groove, one of the grooves, and the end of one of the legs assembled in the groove, taken along the K1-K1 line in FIG. 75, according to the 19th embodiment.

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

[0060] First Embodiment A first embodiment will be described in detail with reference to FIGS. 1 to 34. FIG.

[0061] [Overview of Flow Path 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 A-A in FIG. 2. FIG. 7 shows a cross-sectional view of the flow path switching device 1 taken along line B-B 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] [Regarding the 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 housings 11, 12 together with a plurality of screws 6. The housing 2 corresponds to an example of a "stator" in the disclosed technology. The housing 2 includes inlet / outlet passages 20 through which fluid flows in and out. The flow path switching device 1 of this embodiment is configured as an eight-way valve, for example. The housing 2 has eight inlet / outlet passages 20. As the eight inlet / outlet passages 20, the upper housing 11 is provided with a first inlet / outlet passage 21, a second inlet / outlet passage 22, a third inlet / outlet passage 23, and a fourth inlet / outlet passage 24. The lower housing 12 is provided with a fifth inlet / outlet passage 25, a sixth inlet / outlet passage 26, a seventh inlet / outlet passage 27, and an eighth inlet / outlet passage 28. FIG. 8 is a perspective view showing the inside of the upper housing 11. As shown in FIG. 8 , an inlet / outlet 21 a of the first inlet / outlet passage 21, an inlet / outlet 22 a of the second inlet / outlet passage 22, an inlet / outlet 23 a of the third inlet / outlet passage 23, and an inlet / outlet 24 a of the fourth inlet / outlet passage 24 are respectively opened on the inside of the upper housing 11. Similarly, as shown in FIG. 5 , inlet / outlet 25 a, 26 a, 27 a, and 28 a of the fifth inlet / outlet passage 25 to the eighth inlet / outlet passage 28 are respectively opened on the inside of the lower housing 12. Note that the inlet / outlet passage 20 corresponds to an example of a "communicating passage" provided in a "stator" of the disclosed technology. Furthermore, the inlets / outlets 21 a to 28 a correspond to an example of an "opening" of the "communicating passage" of the disclosed technology. In this embodiment, the housing 2 is formed, for example, from resin.

[0063] [Regarding the Valve Disk] As shown in Figures 5 to 7, the valve disk 3 rotates in the housing 2 and includes a first rotating disk 13 and a second rotating disk 14 that are stacked adjacent to each other vertically, and a rotating shaft 15 that rotates the rotating disks 13, 14. The 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" in the technology disclosed herein. The rotating disks 13, 14 and the rotating shaft 15 are formed, for example, from resin.

[0064] [Regarding the First Rotating Disk] FIG. 9 shows a perspective view of the first rotating disk 13. FIG. 10 shows a plan view of the first rotating disk 13. FIG. 11 shows a bottom view of the first rotating disk 13. As shown in FIGS. 5 to 7, the first rotating disk 13 is housed inside the housing 2 together with the second rotating disk 14. As shown in FIGS. 9 to 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. The two rotation passages 30 include a first rotation passage 31 and a second rotation passage 32. The rotation passages 30 are semicircular arc-shaped in a plan view. The rotation passages 30 correspond to an example of a "communication passage" provided in a "valve body" of the technology disclosed herein. A first shaft hole 13a through which the rotation shaft 15 passes is formed at the center of the first rotating disk 13. A first boss 13b is formed on the first rotating disk 13, centered on the first shaft hole 13a.

[0065] [Regarding the Second Rotating Disk] FIG. 12 shows a plan view of the second rotating disk 14. FIG. 13 shows a bottom view of the second rotating disk 14. As shown in FIG. 13, the second rotating disk 14 is formed in a substantially cylindrical shape with a bottom, similar to the first rotating disk 13, and includes two rotation passages 40 that open downward in the axial direction X. The two rotation passages 40 include a third rotation passage 43 and a fourth rotation passage 44. The rotation passages 40 are semicircular arc-shaped in bottom view. The rotation passages 40 correspond to an example of a "communication passage" provided in a "valve body" of the technology disclosed herein. A second axial hole 14a through which the rotation shaft 15 passes 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 of the second rotating disk 14, centered on the second axial hole 14a.

[0066] [Regarding the Rotating Shaft] FIG. 14 shows a perspective view of the rotating shaft 15. FIG. 15 shows a cross-sectional view of the rotating shaft 15 taken along line E-E 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. The upper end 15a of the rotating shaft 15, which is connected to the drive unit 4, is a gear with 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 provided on the outer periphery of the middle portion of the rotating shaft 15. As shown in FIG. 15, the protrusions 15c and 15d protrude in an arc shape from the outer periphery of the rotating shaft 15 and are spaced 180 degrees apart. 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 desirable that they be arranged and shaped asymmetrically to prevent incorrect assembly.

[0067] 5 to 7, the rotating shaft 15 is provided to penetrate the upper housing 11 and both rotating disks 13, 14. The upper end 15a of the rotating shaft 15 penetrates the through-hole 11a of the upper housing 11 and is connected to the drive unit 4. The lower end 15b of the rotating shaft 15 is rotatably supported in the shaft hole 12a of the lower housing 12.

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

[0069] 6 and 7, a torsion spring 56 is provided inside the shaft hole 12a of the lower housing 12, with the lower end 15b of the rotary shaft 15 as its center. The torsion spring 56 is interposed between the bottom of the shaft hole 12a and the middle part of the rotary shaft 15, and urges the rotary shaft 15 in the rotational direction Y, thereby eliminating rattle between the rotary shaft 15 and the drive unit 4.

[0070] [Regarding the Rotational Transmission Mechanism] The flow path switching device 1 of this embodiment includes a rotational transmission mechanism for transmitting the rotational force of the rotating shaft 15 to the first rotating disk 13 and the second rotating disk 14. Figure 16 shows the flow path switching device 1 in a cross-sectional view taken along line F-F in Figure 2. The rotational transmission mechanism of this embodiment is provided between the first rotating disk 13 and the second rotating disk 14 and the rotating shaft 15. The rotational transmission mechanism allows 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 is configured 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 the rotating shaft 15 are connected to be relatively movable in the rotational 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 of the first rotating disk 13 so as to coincide with the center of the first boss 13b. As shown in FIGS. 11 , 12 , and 16 , the first boss 13b has a pair of first notches 13c, 13d, which are missing portions of the first boss 13b in the circumferential direction. As shown in FIG. 16 , a first protrusion 15c and a second protrusion 15d are fitted into these 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 notches 13c, 13d and the protrusions 15c, 15d. Furthermore, the rotating shaft 15 and the first rotating disk 13 are allowed to move relatively in the rotation direction Y within the range of gaps 16 between the first cutouts 13c, 13d and the protrusions 15c, 15d. In this way, the rotating shaft 15 is connected to the first rotating disk 13 so as to be able to move relatively in the rotation direction Y and the axial direction X.

[0072] On the other hand, similar to the first rotating disk 13, the rotating shaft 15 is assembled to the second boss 14b of the second rotating disk 14 so as to coincide with the center of the second boss 14b. Similar to the first boss 13b, the second boss 14b has a pair of second notches 14c, 14d, which are missing portions of its circumferential surface, as shown in FIG. 12 . The first protrusion 15c and the second protrusion 15d are fitted into these second notches 14c, 14d. Circumferential gaps are also provided between the second notches 14c, 14d and the protrusions 15c, 15d. Therefore, the rotating shaft 15 and the second rotating disk 14 are allowed to move relative to each other in the axial direction X along the second notches 14c, 14d and the protrusions 15c, 15d. Furthermore, the rotation shaft 15 and the second rotating disk 14 are allowed to move relatively in the rotation direction Y within the range of the gaps between the second cutouts 14c, 14d and the protrusions 15c, 15d. In this way, the rotation shaft 15 is connected to the second rotating disk 14 so as to be able to move relatively in the rotation direction Y and the axial direction X.

[0073] The rotating shaft 15 rotates by receiving driving force from the drive unit 4, and rotates relative to each other 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] [Regarding the Seal Members] As shown in Figures 5 to 7, 9, 10, and 13, in this embodiment, a first seal member 17 and a second seal member 18 having a substantially annular shape are provided between the first rotating disk 13 and the housing 2 (the upper housing 11 and the lower housing 12) to prevent fluid leakage. 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 Figures 9 and 10, a circumferential assembly groove 13e for assembling the first seal member 17 is formed on the top surface of the first rotating disk 13 so as to surround the peripheries of the openings of the two rotational passages 30 (the first rotational passage 31 and the second rotational 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 top surface of the first rotating disk 13. As shown in FIG. 13 , a circumferential assembly groove 14e for assembling the second seal member 18 is formed on the underside of the second rotating disk 14, surrounding the openings of the two rotational passages 40 (the third rotational passage 43 and the fourth rotational 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 underside of the second rotating disk 14. In this embodiment, the seal members 17, 18 are formed solely from rubber. The seal members 17, 18 may also be formed from a fluororesin (e.g., Teflon (registered trademark)) or rubber coated with a fluororesin. In this embodiment, the cross section of each seal member 17, 18 taken perpendicular to the longitudinal direction of each portion (hereinafter referred to as the "vertical cross section") is mountain-shaped (M-shaped).

[0075] [Regarding 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 rotates both rotary disks 13, 14 via the rotary shaft 15 using the drive unit 4. The flow path switching device 1 is configured to selectively combine and connect the rotary passages 30, 40 of both rotary disks 13, 14 with the inflow / outflow passages 20 (first inflow / outflow passage 21 to eighth inflow / outflow passage 28) of the housing 2 through this rotational drive, thereby switching between and forming a series of flow paths. In other words, the flow path switching device 1 is configured to form a plurality of "flow path switching patterns" described below.

[0076] [Regarding the Flow Path Switching Pattern] An example of a flow path switching pattern will now 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 G-G in FIG. 2, relating to a "first pattern" of the flow path switching pattern. In FIG. 17, the outline of the upper housing 11, which is not shown in the cross-section, is shown by a two-dot chain line. FIG. 18 also 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 H-H in FIG. 2, relating to the "first pattern." In FIG. 18, the outline of the lower housing 12, which is not shown in the cross-section, is shown by a two-dot chain line. FIG. 19 also shows the rotational position of the first rotating disk 13 relative to the upper housing 11 in a schematic view similar to FIG. 17, relating to a "second pattern" of the flow path switching pattern. FIG. 20 also shows the rotational position of the second rotating disk 14 relative to the lower housing 12 in a schematic view similar to FIG. 18, relating to the "second pattern."

[0077] 17 and 18 , depending on the rotational positions of the first rotating disk 13 and the second rotating disk 14, the first rotational 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 rotational passage 32 communicates with the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24. Furthermore, the third rotational 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 rotational 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 rotational 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 rotational 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] 19 and 20 , in the second pattern, the first rotating disk 13 and the second rotating disk 14 rotate counterclockwise by approximately 60° from the state of the first pattern, and the first rotational 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 rotational passage 32 communicates with the second inflow / outflow passage 22 and the fourth inflow / outflow passage 24. In addition, the third rotational 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 rotational 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 rotational 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 rotational 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. The plurality of compression springs 61 urge the first rotating disk 13 and the second rotating disk 14 in directions that separate them from each other and bring them closer to 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 urging force. In this embodiment, three compression springs 61 are arranged 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 Figures 7, 11, and 12, three receiving holes 13f are provided at equal angular intervals on the bottom surface of the first rotating disk 13 to receive the upper portions of the compression springs 61. As shown in Figures 5, 7, and 12, three receiving holes 14f are provided at equal angular intervals on the top surface of the second rotating disk 14 to receive the lower portions of the compression springs 61. A cylindrical portion 13g is provided at the center of each receiving hole 13f, 14f. The compression springs 61 are assembled and held around the cylindrical portions 13g, 14g. The compression springs 61 are assembled into the receiving holes 13f, 14f between the rotating disks 13, 14. As a result, the biasing force of each compression spring 61 separates the rotating disks 13, 14 from each other and brings them closer to the upper housing 11 and the lower housing 12, biasing the seal members 17, 18 in directions that bring them into contact with the inner surfaces of the upper housing 11 and the lower housing 12. In this embodiment, the above-described rotation transmission mechanism connects the rotary disks 13, 14 to the rotary shaft 15 so as to be movable relative to the rotary shaft 15 in the axial direction X. Therefore, the biasing force of each compression spring 61 allows the rotary disks 13, 14 to move in the axial direction X within a predetermined range.

[0081] [Use Example of Flow Channel Switching Device] FIG. 21 is a circuit diagram illustrating a use example of the flow channel switching device 1 described above. As shown in FIG. 21 , in this embodiment, the flow channel switching device 1 is used in a cooling system 91 mounted on an electric vehicle 90. In addition to the flow channel 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. A fourth pipe 96D is connected to the chiller 95. A first electric pump 97 is provided to the second pipe 96B in addition to the PCU 93. A second electric pump 98 is provided to the fourth pipe 96D in addition to the chiller 95. 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 channel switching device 1. Both ends of the second pipe 96B are connected to the third inlet / outlet passage 23 and the seventh inlet / outlet passage 27 of the flow path switching device 1. Both ends of the third pipe 96C are connected to the fourth inlet / outlet passage 24 and the eighth inlet / outlet passage 28 of the flow path switching device 1. Both ends of the fourth pipe 96D are connected to the first inlet / outlet passage 21 and the fifth inlet / outlet passage 25 of the flow path switching device 1. The flow of refrigerant to each of the sections 92 to 95 is controlled by driving the flow path switching device 1 to switch the flow paths.

[0082] [Regarding issues with sealing members] Figure 22 shows the same plan view (bottom view) of 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 Figure 22, dashed two-dot lines in each rotating disk 13 (14) indicate the inlets and outlets 21a, 22a, 23a, 24a (25a, 26a, 27a, 28a) of each inlet / outlet passage 21 to 24 (25 to 28) provided in each housing 11 (12). As shown in Figure 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 peripheral 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 locations (two locations 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 Figure 22, each seal member 17 (18) is shown with dots to distinguish it from the others.

[0083] Figure 23 is an enlarged cross-sectional view of the first rotating disk 13 and the upper housing 11, taken along line II in Figure 22 at the assembly groove 13e where the first seal member 17 is assembled. Figure 24 is an enlarged cross-sectional view equivalent to Figure 23, showing the deformation 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 against which the seal members 17, 18 slide. As shown in Figures 23 and 24, the first seal member 17 has a mountain-shaped cross section that widens toward the first rotating disk 13. The first seal member 17 includes a top 19a that contacts the inner surface of the upper housing 11, leg portions 19b that branch from the top 19a toward the retaining member (two branches in this embodiment), a recess 19c that is recessed toward the upper housing 11, and a hollow portion 19d that is hollow inside the bifurcated leg portions 19b. The top 19a includes two left and right protrusions 82a, 82b that have the same height. The lower ends of the two left and right leg portions 19b extend the same length. Like the first seal member 17, the second seal member 18 also has a mountain-shaped cross section and includes the top 19a, leg portions 19b, recesses 19c, and hollow portion 19d.

[0084] In this embodiment, the seal members 17, 18 provided on each rotary disk 13, 14 contact the inner surface of the upper housing 11 and the inner surface of the lower housing 12, respectively. Therefore, when each rotary disk 13, 14 rotates, sliding resistance is generated between each seal member 17, 18 and the upper housing 11 and the lower housing 12. In particular, the sliding resistance increases when each rotary disk 13, 14 begins to rotate. In this embodiment, since the vertical cross section of each seal member 17, 18 is mountain-shaped, the legs 19b of each seal member 17, 18 contact the bottom walls of the assembly grooves 13e, 14e, and the tops 19a of each seal member 17, 18 contact the inner surfaces of each housing 11, 12. A cavity 19d is defined between the bifurcated legs 19b. For this reason, when the rotating disks 13, 14 start 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 twist significantly, raising the concern that the sealing properties of each sealing member 17, 18 may no longer be ensured.

[0085] On the other hand, Figure 25 is a plan view (bottom view) equivalent to Figure 22 showing the state in which the partitions 17c (18c), 17d (18d) of each seal member 17 (18) pass (cross) through the inlets 23a, 22a (27a, 26a) of each inlet / outlet passage 23, 24 (27, 26) as each rotary disk 13 (14) rotates. As shown in Figure 25, when the partitions 17c (18c), 17d (18d) of each seal member 17 (18) cross the inlets 21a to 24a (25a to 28a) of each inlet / outlet passage 21 to 24 (25 to 28), that is, when they are opened to each inlet / outlet passage 21 to 24 (25 to 28), the following changes occur in each seal member 17 (18). That is, in each seal member 17 (18), as shown by the arrows in Figure 25, at the connection between the outer circular portion 17b (18b) and the partitions 17c (18c), 17d (18d), a portion of the rubber material of the outer circular portion 17b (18b) is crushed and moves toward the partitions 17c (18c), 17d (18d). Also, at the connection between the inner circular portion 17a (18a) and the partitions 17c (18c), 17d (18d), a portion of the rubber material of the inner circular portion 17a (18a) is crushed and moves toward the partitions 17c (18c), 17d (18d). As a result, at the partitions 17c (18c), 17d (18d), a portion of the rubber material may be displaced toward each of the entrances 21a to 24a (25a to 28a) when the partitions 17c (18c), 17d (18d) are opened, and may try to protrude. In order to ensure that each sealing member 17 (18) smoothly moves from each inlet / outlet passage onto the inner surface of each housing 11 (12) and ensure sealing performance, it is necessary to prevent this partition portion 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] [Regarding the assembly structure of each seal member] Figure 26 is a simplified plan view showing the assembly state of each seal member 17 (18) into the assembly groove 13e (14e) of this embodiment. Figure 27 is a simplified plan view showing only the assembly grooves 13e (14e). Figure 28 is a simplified plan view showing only the seal members 17 (18). In this embodiment, as shown in Figures 27 and 28, each seal member 17 (18) and each assembly groove 13e (14e) have approximately the same size and shape in plan view. However, 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 the portion of the assembly groove 13e (14e) where the partitions 17c (18c), 17d (18d) of each seal member 17 (18) are assembled. With this setting, the partitions 17c (18c), 17d (18d) of each seal member 17 (18) are fitted into the assembly groove 13e (14e) in a tensioned state and assembled.

[0088] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel 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). Furthermore, a plurality of compression springs 61 are provided between the first rotating disk 13 and the second rotating disk 14 to separate the rotating disks 13, 14 from each other and to bias the rotating disks 13, 14 in a direction toward the housing 2. Therefore, even if there is variation in the components constituting the flow channel switching device 1 and the interference of the seal members 17, 18 varies due to the variation, the variation is adjusted by the biasing force of the compression springs 61, and the contact surface pressure of the seal members 17, 18 against the housing 2 is adjusted. Therefore, the seal members 17, 18 provided between the housing 2 and the rotating disks 13, 14 can be maintained at an appropriate surface pressure, ensuring the sealing performance of the seal members 17, 18. That is, the influence of interference due to 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 3 is composed of a first rotating disk 13 and a second rotating disk 14 separated into upper and lower parts, 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 interference of the sealing members 17, 18 can be reduced.

[0090] According to the configuration of the flow path switching device 1 of this embodiment, the biasing force of the compression spring 61 acts on the first rotating disk 13 and the second rotating disk 14. This action allows the rotation transmission mechanism to move the two rotating disks 13, 14 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, 18. Furthermore, as the rotating shaft 15 rotates, the rotational force is transmitted to the first rotating disk 13 and the second rotating disk 14 by the rotation transmission mechanism, causing both rotating disks 13, 14 to rotate. Furthermore, the transmission of the rotational force is partially released by the rotation transmission mechanism, causing both rotating disks 13, 14 to stop rotating. Therefore, even when the two rotating disks 13, 14 rotate relative to the housing 2, the seal members 17, 18 provided between the housing 2 and both rotating disks 13, 14 can be maintained at an appropriate surface pressure, ensuring the sealing performance of each seal member 17, 18.

[0091] According to the configuration of the flow path switching device 1 of this embodiment, the upper housing 11 is provided with four inlet / outlet passages 20 (first to fourth inlet / outlet passages 21 to 24). The lower housing 12 is provided with four inlet / outlet passages 20 (fifth to eighth inlet / outlet passages 25 to 28). The first rotating disk 13 is provided with two rotational passages 30 (first rotational passage 31 and second rotational passage 32). The second rotating disk 14 is provided with two rotational passages 40 (third rotational passage 43 and fourth rotational passage 44). A first seal member 17 is assembled into an assembly groove 13e formed in the first rotating disk 13. 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 disposed on the center side of each rotary disk 13, 14, an outer circular portion 17b, 18b disposed on the outer periphery side of each rotary disk 13, 14, and partition portions 17c, 17d, 18c, 18d that connect the inner circular portion 17a, 18a and the outer circular portion 17b, 18b and separate the two rotational passages 31, 32, 43, 44. These partition portions 17c, 17d, 18c, 18d are fitted into the assembly grooves 13e, 14e in a tensioned state and assembled. Therefore, a tension force acts on the partition portions 17c, 17d, 18c, 18d, which prevents deformation of the partition portions 17c, 17d, 18c, 18d against external forces. Furthermore, in order to switch the flow paths, the rotary disks 13 and 14 are rotated, and the partitions 17c, 17d, 18c, and 18d cross the inlets 21a to 28a of the inlet passages 21 to 28. At this time, the partitions 17c, 17d, 18c, and 18d are prevented from getting caught on 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 manufacturing costs.

[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 rotary disks 13, 14, so that both rotary disks 13, 14 are supported in a floating state by the seal members 17, 18. Therefore, when both rotary disks 13, 14 rotate, the floating effect of the seal members 17, 18 can prevent uneven wear of the seal members 17, 18. As a result, the seal members 17, 18 can ensure the sealing of the flow paths, and can reliably prevent fluid leakage 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 rotary disks 13, 14 relative to the housing 2. Therefore, there is no need to provide separate elastic members for maintaining the orientation of both rotary disks 13, 14, which makes it possible to suppress an increase in the number of parts and to achieve a reduction in size and simplification of the flow path switching device 1.

[0095] Second Embodiment A second embodiment will be described in detail with reference to Figures 29 and 30. In the following description, components equivalent to those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted, and differences will be mainly described.

[0096] [Assembly Structure of Each Seal Member] This embodiment differs from the first embodiment in the assembly structure of each seal member 17, 18. Figure 29 is an enlarged cross-sectional view equivalent to Figure 23 showing the partition portion 17c of the first seal member 17 assembled into the assembly groove 13e. Figure 30 is a cross-sectional view taken along line J-J in Figure 29 showing the partition portion 17c assembled into the assembly groove 13e. In this embodiment, the seal members 17, 18 are assembled by fitting into the assembly grooves 13e, 14e. Also, as shown in Figure 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 wall of the assembly groove 13e, where the partition portion 17c fits. These protrusions 71 are arranged alternately on both sides of the partition portion 17c so as not to face each other. As a result, the portion of the assembly groove 13e into which the partition 17c is fitted meanders slightly along 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, causing them to deform alternately. In this embodiment, the partition length L2 is set slightly longer than the partition groove length L1 to account for deformation caused by the protrusions 71 of the partition 17c. Figures 29 and 30 illustrate and describe the assembly groove 13e into which the first seal member 17 is assembled. In contrast, although not shown or described, the assembly groove 14e into which the second seal member 18 is assembled is assumed to have a similar configuration (the same applies in the following description).

[0097] [Regarding Functions and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, unlike the configuration of the first embodiment, the inner walls of the assembly grooves 13 e, 14 e at the portions where the partitions 17 c, 17 d, 18 c, and 18 d are fitted have a plurality of protrusions 71 that abut against the partitions 17 c, 17 d, 18 c, and 18 d, and are arranged at different positions on both sides of the partitions 17 c, 17 d, 18 c, and 18 d. Therefore, a pressing force acts on the partitions 17 c, 17 d, 18 c, and 18 d when the protrusions 71 on the inner walls of the assembly grooves 13 e, 14 e abut, thereby suppressing deformation of the partitions 17 c, 17 d, 18 c, and 18 d against external forces. Furthermore, in order to switch the flow paths, the rotary disks 13 and 14 are rotated, and the partitions 17c, 17d, 18c, and 18d cross the inlets 21a to 28a of the inlet / outlet passages 20. At this time, the partitions 17c, 17d, 18c, and 18d are prevented from getting caught on 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 manufacturing costs.

[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, can also be used.

[0099] Third Embodiment A third embodiment will be described in detail with reference to FIGS.

[0100] [Regarding the assembly structure of each seal member] This embodiment differs from the second embodiment in the details of the assembly structure of each seal member 17, 18. Figure 31 is an enlarged cross-sectional view equivalent to Figure 29 showing the state in which the partition portion 17c of the first seal member 17 is assembled into the assembly groove 13e. Figure 32 is a cross-sectional view taken along line K-K in Figure 31 showing the state in which the partition portion 17c is assembled into the assembly groove 13e. Figure 33 is a cross-sectional view taken along line N-N in Figure 32 showing the state in which the partition portion 17c is assembled into the assembly groove 13e.

[0101] As shown in Figures 31 and 32, in this embodiment, in addition to the same configuration as the second embodiment, the assembly groove 13e of the first rotating disk 13 is provided with an in-groove ridge 72 that is disposed within the hollow portion 19d of the first seal member 17. In this embodiment, the in-groove ridge 72 is disposed throughout the entire assembly groove 13e, but it is also possible to provide the in-groove ridge 72 only in the portion of the assembly groove 13e that corresponds to the partition portions 17c and 17d. Also, in this embodiment, a plurality of in-groove ridge protrusions 73 that abut against 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 offset from the protrusions 71 disposed on the side walls of the assembly groove 13e so as not to face them. Although not shown or described, 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 Figure 33, the side walls of each of the protrusions 71, 73 are formed perpendicular to the bottom wall of the assembly groove 13e.

[0102] [Regarding Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects in addition to those of the second embodiment. That is, each seal member 17, 18 has a mountain-shaped cross section that widens 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 branches toward each rotary disk 13, 14. Furthermore, each assembly groove 13e, 14e includes an intra-groove ridge 72 disposed in the hollow portion 19d, and an intra-groove ridge convex portion 73 that abuts against the inner wall of the hollow portion 19d is provided on the side wall of the intra-groove ridge 72 corresponding to the partition portions 17c, 17d, 18c, 18d. Therefore, the groove protrusions 72 are disposed in the hollow portions 19d of the partitions 17c, 17d, 18c, and 18d, and a pressing force acts on the inner walls of the hollow portions 19d by contacting the groove protrusions 73. This prevents the partitions 17c, 17d, 18c, and 18d from deforming against external forces. This prevents the partitions 17c, 17d, 18c, and 18d of the seal members 17 and 18 from shifting, thereby suppressing repulsive forces while ensuring the necessary surface pressure for sealing. Furthermore, when the fluid is a liquid, as in this embodiment, the recesses 19c of the partitions 17c, 17d, 18c, and 18d become liquid reservoirs. This allows the lubricating effect of the liquid to reduce the sliding resistance of the partitions 17c, 17d, 18c, and 18d against the housings 11 and 12.

[0103] In this embodiment, multiple protrusions 71 are provided on both side walls of the assembly grooves 13e, 14e, and multiple in-groove protrusions 73 are provided on both side walls of the in-groove protrusions 72. This creates a corrugated shape in plan view for the spaces in the assembly grooves 13e, 14e into which the seal members 17, 18 fit. The non-corrugated seal members 17, 18 are assembled into the corrugated spaces of the assembly grooves 13e, 14e. This creates a holding surface pressure on the side surfaces of the seal members 17, 18, alternating with the protrusions 71, 73, without placing a large burden on the seal members 17, 18, which inevitably causes the non-corrugated seal members 17, 18 to deform into a corrugated shape. This holding surface pressure is a surface pressure due to bending stress. Therefore, even if a portion of the rubber material moves from the inner circular portion 17a, 18a and the outer circular portion 17b, 18b to the partitions 17c, 17d, 18c, 18d due to crushing when the partitions 17c, 17d, 18c, 18d pass through the entrances 21a-214a, 25a-28a, the resulting bending stress prevents the seal members 17, 18 from falling out of the assembly grooves 13e, 14e. The bending stress of the seal members 17, 18 also acts as a tension force, preventing the seal members 17, 18 from popping out during assembly. Furthermore, as shown in FIG. 32 , even at the upper limit of the part tolerances, a clearance CL is maintained between the seal members 17, 18 and the groove ridges 72. This prevents excessive press-fit stress when the seal members 17, 18 are assembled into the assembly grooves 13e, 14e.

[0104] As a comparative example, consider a case in which no groove-protruding ridges 73 are provided on either side of the groove-protruding ridges 72, and the inner wall of the cavity 19d abuts against the side walls of the groove-protruding ridges 72, as shown in Figure 34. In this case, the protruding ridges 71 on either side of the assembly grooves 13e, 14e must be raised to increase the lateral holding force of the seal members 17, 18 in the assembly grooves 13e, 14e. However, raising the protruding ridges 71 increases the pressure-fitting stress during assembly of the seal members 17, 18 into the assembly grooves 13e, 14e, potentially causing wear and tear on the seal members 17, 18. Furthermore, because the pressure-fitting causes the volume of the seal members 17, 18 to move in the vertical and sliding directions in Figure 33, there is a risk of the rubber material popping out during assembly. Furthermore, there is a concern that wear of the seal members 17, 18 may worsen when the partitions 17c, 17d, 18c, and 18d at the entrances 21a to 24a, 25a to 28a are opened and ride up onto the inner surfaces of the housings 11 and 12. In contrast, the configuration of this embodiment can eliminate the above concerns regarding the seal members 17 and 18. Figure 34 is a cross-sectional view equivalent to Figure 32, showing the state in which the partition 17c is assembled into the assembly groove 13e.

[0105] Fourth Embodiment A fourth embodiment will be described in detail with reference to FIG.

[0106] [Problems of the Third Embodiment] In the third 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, and the pair of legs 19b constituting the partitions 17c, 17d of the first seal member 17 open outward. Therefore, if each of the protrusions 71, 73 is provided in the assembly groove 13e, there will be a height difference between the high surface pressure area indicated by the chain ellipse in Fig. 33 between the protrusion 71 and the outer side of the leg 19b and the inner side of the groove protrusion 73 and the leg 19b, which could cause unstable lateral support. Therefore, in the fourth embodiment, the assembly structure of each of the seal members 17, 18 is configured as follows.

[0107] [Assembly Structure of Each Seal Member] Figure 35 is an enlarged cross-sectional view equivalent to Figure 33 showing the partition portion 17c of the first seal member 17 assembled into the assembly groove 13e. In this embodiment, as shown in Figure 35, the side surfaces of the in-groove protrusions 73 are formed to taper toward the bottom wall in accordance with the fact that the leg portions 19b of the first seal member 17 open outward. Although not shown or described, the same applies to the assembly groove 14e of the second rotating disk 14 and the second seal member 18.

[0108] [Operation and Effects of the Flow Channel Switching Device] In contrast to the third embodiment, the configuration of the flow channel switching device 1 of this embodiment described above has the in-groove protrusions 73 formed so that their sides taper toward the bottom wall to match the flared shape of the legs 19 b of each seal member 17, 18. Therefore, the high surface pressure areas shown by the chain ellipses in Figure 35 are the same height between the protrusions 71 and the outside of the legs 19 b and between the in-groove protrusions 73 and the inside of the legs 19 b, allowing for stable lateral support of each seal member 17, 18.

[0109] Fifth Embodiment A fifth embodiment will be described in detail with reference to FIG.

[0110] [Regarding the Issues of the Fourth Embodiment] In the fourth embodiment, in order to stabilize the side support of each seal member 17, 18, the groove protrusions 73 were formed as shown in Figure 35, and the heights of the high surface pressure areas formed by the protrusions 71 and the groove protrusions 73 were made the same, but the area of ​​the high surface pressure areas was narrowed. In response to this, it was possible to increase the height of the lower parts of the groove protrusions 73 in order to increase the side support force, but this could lead to stress concentration (sagging) in those areas. Therefore, in the fifth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0111] [Assembly Structure of Each Seal Member] Figure 36 is an enlarged cross-sectional view equivalent to Figure 33 showing the partition portion 17c of the first seal member 17 assembled into the assembly groove 13e. In this embodiment, as shown in Figure 36, the convex portion 71 and the in-groove protrusion 73 of the assembly groove 13e are configured to perpendicularly abut the outer and inner surfaces of the legs 19b of the first seal member 17. That is, the lower portions of both legs 19b of the first seal member 17 are formed perpendicular to the bottom wall of the assembly groove 13e, and the outer surfaces of the convex portion 71 and the in-groove protrusion 73 are formed perpendicular to the bottom wall of the assembly groove 13e. Although not shown or described, the same applies to the assembly groove 14e of the second rotating disk 14 and the second seal member 18.

[0112] [Operations and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following operations and effects compared to the fourth embodiment. That is, the convex portions 71 and the in-groove ridges 73 of the assembly grooves 13e and 14e perpendicularly abut the outer surfaces of the leg portions 19b and the inner surfaces of the hollow portions 19d at the partition portions 17c, 17d, 18c, and 18d of each seal member 17 and 18. Therefore, as shown by the chain oval in FIG. 36 , the ranges where the outer and inner surfaces of the partition portions 17c, 17d, 18c, and 18d are high expand along the leg portions 19b. This reduces stress concentration on the outer and inner surfaces of the partition portions 17c, 17d, 18c, and 18d of each seal member 17 and 18.

[0113] Furthermore, since both leg portions 19b of each seal member 17, 18 are formed perpendicular to the bottom wall of the assembly groove 13e, 14e, the seal members 17, 18 can be molded 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 perpendicular to the bottom wall of the assembly groove 13e, 14e, the rotary disks 13, 14 can be molded to be removable from a die when manufactured.

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

[0115] [Regarding the Issues of the Previous Embodiments] Figure 37 is an enlarged plan view showing, as a comparison with this embodiment, 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. As shown in Figure 37, the first seal member 17 further includes an outer branch portion 17e (the portion surrounded by the upper dashed ellipse) where the partition portion 17c branches off to the outer circular portion 17b, and an inner branch portion 17f (the portion surrounded by the lower dashed ellipse) where the partition portion 17c branches off to the inner circular portion 17a. These branch portions 17e, 17f are made of a rubber material with a high density, and the movement of the rubber material due to crushing is concentrated therein, resulting in high surface pressure when sliding with the upper housing 11. Meanwhile, on the inner surface of the upper housing 11 along which the first seal member 17 slides, the openings 21a to 24a of the first to fourth inflow / outflow passages 21 to 24 open opposite to each other, as shown by the two-dot chain lines in Fig. 37. In Fig. 37, the area surrounded by the thick two-dot chain lines L3 and L4 indicates the opening distribution area DA of the openings 21a to 24a across which the first seal member 17 slides.

[0116] As shown in Figure 37, the outer branch 17e and inner branch 17f of the partition 17c of the first seal member 17 partially overlap the inlet / outlet distribution area DA. Therefore, when the first rotating disk 13 rotates to switch the flow path, these branches 17e and 17f cross the inlet / outlet distribution area DA. This creates a surface pressure difference between these branches 17e and 17f and the partitions 17c and 17d other than the branches 17e and 17f, potentially resulting in wear steps. Figure 38 shows a schematic cross-sectional view of the partition 17c crossing the inlets 21a to 24a. As shown in Figure 38, the high-surface-pressure branches 17e and 17f open into the inlets 21a to 24a. As a result, the partition 17c protrudes more into the opening, making it easier for the partition 17c to get caught when riding over the opening edge of each of the entrances 21a to 24a. Although not shown and described, the same applies to the partition 17d and the second seal member 18. Therefore, in this sixth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0117] [Regarding the assembly structure of each seal member] Figure 39 is an enlarged plan view equivalent to Figure 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 Figure 39, the outer branch portion 17e and the inner branch portion 17f of the partition portion 17c of the first seal member 17 are arranged outside the entrance / exit distribution area DA without overlapping with the entrance / exit distribution area DA. Although not shown or described, the same applies to the partition portion 17d and the second seal member 18.

[0118] [Regarding the Functions and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, the outer branch portion 17e and the inner branch portion 17f of each seal member 17, 18, which are subject to particularly high surface pressure, are arranged outside the inlet / outlet distribution area DA of the inlets 21a to 28a of each inlet / outlet passage 20, which each seal member 17, 18 slides across. Therefore, when each seal member 17, 18 crosses the inlets 21a to 28a of the inlet / outlet passage 20, the outer branch portion 17e and the inner branch portion 17f, which are subject to high surface pressure, can be reduced from protruding into the inlets 21a to 28a, getting caught on the periphery of the inlets 21a to 28a, or causing deterioration in sliding properties.

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

[0120] [Regarding the assembly structure of each seal member] This embodiment differs from the sixth embodiment in terms of the configuration for addressing the same problem as in the sixth embodiment. Figure 40 shows a plan view of one of the openings 21a to 24a of the first through fourth inlet / outlet passages 21 to 24, which open to the inner surface of the upper housing 11 according to this embodiment. Figure 41 shows the opening 21a to 24a in a cross-sectional view taken along line C1-C1 or line C2-C2 in Figure 40. Figure 42 shows the opening 21a to 24a in a cross-sectional view taken along line D-D in Figure 40. The positions of lines C1-C1 and C2-C2 in Figure 40 indicate the vicinity of both ends of the openings 21a to 24a in the radial direction of the upper housing 11, respectively, and the position of line D-D indicates the vicinity of the center of the openings 21a to 24a in the radial direction of the upper housing 11.

[0121] As shown in Figures 40 and 41, among the openings 21a to 24a, the openings 21a to 24a across which the partitions 17c, 17d of the first seal member 17 slide have intersecting opening edges 29 (shown with a gauze pattern in Figure 40) extending in a direction intersecting the sliding direction (indicated by arrow M in Figure 40). As shown in Figures 41 and 42, the intersecting opening edges 29 have curved surfaces R1, R2 that curve toward the inside of the openings 21a to 24a, and the diameter of the curved surface R2 is set to be larger toward the center as shown in Figure 42 than the curved surface R1 on both ends of the intersecting opening edges 29 shown in Figure 41. Although not shown or described, the same applies to the openings 25a to 28a of the fifth inflow / outflow passages 25 to the eighth inflow / outflow passages 28 that open to the inner surface of the lower housing 12.

[0122] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, the partitions 17c, 17d, 18c, and 18d protrude more toward the center of the inlets 21a to 28a of the inlet / outlet passages 20 of each housing 11, 12 when the inlets are opened. However, the curved surfaces R2 of the intersecting opening edges 29 of the inlets 21a to 28a are larger in diameter toward the center than the curved surfaces R1 at both ends. Therefore, even if the partitions 17c, 17d, 18c, and 18d protrude significantly toward the center of the inlets 21a to 28a when the inlets are opened, the larger-diameter curved surfaces R2 of the intersecting opening edges 29 allow the partitions 17c, 17d, 18c, and 18d to pass through smoothly. Therefore, even if the partition portions 17c, 17d, 18c, and 18d of each sealing member 17 and 18 jump out into the entrances 21a to 28a of the inflow / outflow passage 20 when crossing the entrances 21a to 28a, it is possible to reduce the possibility of the seal members 17 and 18 getting caught on the intersecting opening edge 29 or deterioration of sliding properties when riding up onto the intersecting opening edge 29.

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

[0124] [Regarding the assembly structure of each seal member] This embodiment differs from the sixth and seventh embodiments in terms of the configuration for addressing the same issues as those of the sixth and seventh embodiments. Figure 43 shows a plan view of one of the openings 21a to 24a of the first through fourth inlet / outlet passages 21 to 24, which open to the inner surface of the upper housing 11, according to this embodiment. Figure 44 shows a cross-sectional view of the opening 21a to 24a taken along line Q-Q in Figure 43. The position of line Q-Q in Figure 43 indicates the vicinity of the center of the openings 21a to 24a in the radial direction of the upper housing 11.

[0125] As shown in FIG. 43 , among the entrances 21a to 24a, the entrances 21a to 24a through which the partitions 17c and 17d of the first seal member 17 slide are provided at the center of their inner surfaces with auxiliary seats 76 that extend narrowly along the sliding direction (indicated by arrow M) and contact the partitions 17c and 17d. The auxiliary seats 76 do not need to ensure the sealing performance of the first seal member 17. Furthermore, to prevent wear on the auxiliary seats 76 when the partitions 17c and 17d cross the entrances 21a to 24a, the seat surfaces 76a of the auxiliary seats 76 are not flush with the inner surface 11b of the upper housing 11 but are recessed toward the entrances 21a to 24a, as shown in FIG. 44 . Although not shown or described, the same applies to 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] [Regarding Functions and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, auxiliary seats 76 that contact the partitions 17c, 17d, 18c, and 18d are provided inside the entrances 21a to 28a of the inlet / outlet passage 20, which the partitions 17c, 17d, 18c, and 18d of the seal members 17, 18 slide across. Therefore, the partitions 17c, 17d, 18c, and 18d contact the auxiliary seats 76 when they cross the entrances 21a to 28a. Therefore, when the partition portions 17c, 17d, 18c, 18d of each sealing member 17, 18 cross the entrances and exits 21a to 28a of the inflow and outflow passage 20, the partition portions 17c, 17d, 18c, 18d can be prevented from protruding into the entrances and exits 21a to 28a, thereby reducing the chance of the partition portions 17c, 17d, 18c, 18d getting caught on the periphery of the entrances and exits 21a to 28a and the deterioration of sliding properties.

[0127] Ninth Embodiment A ninth embodiment will be described in detail with reference to FIGS.

[0128] [Regarding the assembly structure of each seal member] This embodiment differs from the sixth to eighth embodiments in terms of the configuration for addressing the same issues as those of the sixth to eighth embodiments. Figure 45 shows a simplified plan view of only the assembly groove 14e in the second rotating disk 14. Figure 46 shows an enlarged cross-sectional view taken along lines S1-S1 and S2-S2 in Figure 45 (the central portions of the partitions 18c and 18d) showing the state in which the partitions 18c and 18d of the second seal member 18 are assembled into the assembly groove 14e. Figure 47 shows an exploded enlarged cross-sectional view of the assembly structure of the portion shown in Figure 46. Figure 48 shows a plan view of the portion shown in Figure 46 as viewed from below. Figure 49 is an enlarged cross-sectional view taken along lines T1-T1 and T2-T2 in Figure 45 (parts other than the center of the partitions 18c and 18d) showing the 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 facing downward into the assembly groove 14e, which can cause the second seal member 18 to fall off after assembly. Furthermore, there is a concern that the partitions 18c and 18d of the second seal member 18 may get caught when they move from the openings 25a to 28a onto the inner surface of the lower housing 12. Therefore, in this ninth embodiment, the assembly structure of the second seal member 18 is configured as follows.

[0129] As shown in Figures 46 and 48, in this embodiment, in order to prevent the partitions 18c and 18d of the second seal member 18 from jumping out of the assembly groove 14e, a pair of seal stoppers 79 are provided in the assembly groove 14e, corresponding to the centers of the partitions 18c and 18d, so as to sandwich the partitions 18c and 18d. As shown in Figure 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 Figure 48, the fixed side corners of the seal stoppers 79 and the corners of the recesses 80 form a wedge shape in a bottom view, so that the seal stoppers 79 engage with the recesses 80 and 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 difference in swelling in water compared to the second rotating disk 14. In this case, the second rotating disk 14 can be formed from "PPS," which swells very little, and the seal stopper 79 can be formed from "PA66," 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 not shown and described, the assembly groove 13e of the first rotating disk 13 can be configured in a similar manner. Furthermore, seal stoppers can be provided in portions other than the centers of the partitions 17c, 17d, 18c, and 18d of each seal member 17, 18.

[0130] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, the partition portions 17c, 17d, 18c, and 18d of each seal member 17, 18 are provided with seal stoppers 79 to prevent each seal member 17, 18 from protruding from the assembly grooves 13e, 14e. Therefore, the seal stoppers 79 prevent each seal member 17, 18 from protruding from the assembly grooves 13e, 14e. Therefore, for example, even if each seal member 17, 18 faces downward during component transport of each rotary disk 13, 14, the falling of the central portions of the partition portions 17c, 17d, 18c, and 18d from the assembly grooves 13e, 14e can be limited to a small fall f1, as indicated by the two-dot chain line in FIG. 46 . In contrast, the falling of portions other than the central portions of the partition portions 17c, 17d, 18c, and 18d becomes a large fall f2, as indicated by the two-dot chain line in FIG. 49 .

[0131] Furthermore, during operation of the flow path switching device 1, the seal stoppers 79 prevent the partitions 17c, 17d, 18c, and 18d of the seal members 17 and 18 from protruding from the assembly grooves 13e and 14e. This allows the partitions 17c, 17d, 18c, and 18d of the seal members 17 and 18 to maintain their proper positions. Furthermore, when the partitions 17c, 17d, 18c, and 18d cross the inlets 21a to 28a of the inlet / outlet passages 20 of the housings 11 and 12, the partitions 17c, 17d, 18c, and 18d are prevented from protruding into the inlets 21a to 28a. Furthermore, this reduces the likelihood of the partitions 17c, 17d, 18c, and 18d getting caught on the peripheries of the inlets 21a to 28a and reducing deterioration of their sliding properties.

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

[0133] [Problems of the Previous Embodiments] Figure 50 shows a plan view of the side of the first rotating disk 13 that contacts the upper housing 11 in a comparative example of this embodiment. Figure 51 also shows an enlarged cross-sectional view of the first rotating disk 13 and the upper housing 11 taken along line U-U in Figure 50 at the assembly groove 13e where the outer circular portion 17b of the first seal member 17 is assembled. As shown in Figure 51, the first seal member 17 of this comparative example is designed to provide a sealing function by ensuring surface pressure through crushing upon contact with the inner surface of the upper housing 11, which is the mating member. In this comparative example, as shown by the chain oval in Figure 51, the first seal member 17 has two sealing surfaces, the top 19a and the leg 19b, and it is desirable that the surface pressure of these sealing surfaces be uniform. Here, as the top 19a and the leg 19b of the first seal member 17 are crushed, the rubber material escapes in the left-right and circumferential directions, as indicated 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). As a result, 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 difference in surface pressure occurs between the inside and outside of the outer circular portion 17b of the first seal member 17, which may cause uneven wear and reduce sealing performance. 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] [Regarding the assembly structure of each seal member] Figure 52 shows a plan view of the side of the first rotating disk 13 that contacts the upper housing 11 according to the tenth embodiment. Figure 53 shows an enlarged cross-sectional view of the first seal member 17 and assembly groove 13e of the first rotating disk 13 taken along line V1-V1 (outer circular portion 17b) and line V2-V2 (inner circular portion 17a) in Figure 52 according to the tenth embodiment. As shown in Figure 53, in this embodiment, the heights of the two protrusions 82a, 82b on the top 19a of the first seal member 17 are the same, and the lengths to the bottom ends of the two legs 19b are the same. Furthermore, the assembly groove 13e is divided into two by the groove rib 72, that is, the left inner groove 81a and the right outer groove 81b, with the inner groove 81a being slightly deeper than the outer groove 81b. As a result, the compression allowance on the inner diameter side of the first seal member 17 is set smaller than the compression allowance on the outer diameter side. Here, the groove depth difference α1 is set larger for the inner circular portion 17a, which has a smaller inner diameter, than for the outer circular portion 17b, which has a larger inner diameter. By setting it in this manner, the compression allowance (crush allowance) on the inner diameter side of the first seal member 17 is smaller than the compression allowance (crush allowance) on the outer diameter side. Although not shown and described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can also be configured in a similar manner.

[0135] [Operations and Effects 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 widens toward the rotating disks 13, 14, and includes a recess 19c that is recessed toward the housings 11, 12, and a hollow portion 19d that branches toward the rotating disks 13, 14 and has an internal cavity. Each seal member 17, 18 has a smaller compression allowance on its inner diameter side than on its outer diameter side. The smaller the compression allowance, the smaller the surface pressure of each seal member 17, 18. Therefore, in addition to the operations and effects of the previous embodiments, the seal surface pressure of each seal member 17, 18 can be uniformly applied between the outer diameter side and the inner diameter side of each seal member 17, 18.

[0136] Eleventh Embodiment An eleventh embodiment will be described in detail with reference to FIG.

[0137] [Regarding the Assembly Structure of Each Seal Member] The eleventh embodiment differs from the tenth embodiment in the assembly structure of each seal member 17, 18. Figure 54 is an enlarged cross-sectional view equivalent to Figure 53 showing the first seal member 17 and the assembly groove 13e of the first rotating disk 13 according to the eleventh embodiment. As shown in Figure 54, in this embodiment, the lengths to the bottom ends of the two legs 19b of the first seal member 17 are the same, and of the two convex portions 82a, 82b on the top 19a, the inner convex portion 82a is slightly lower than the outer convex portion 82b. The height difference (height difference) β1 between the two convex portions 82a, 82b is set larger for the inner circular portion 17a, which has a smaller inner diameter, than for the outer circular portion 17b, which has a larger inner diameter. This setting results in a smaller compression allowance on the inner diameter side of the first seal member 17 than on the outer diameter side. Although not shown and described, the assembly groove 14e of the second rotary disk 14 and the second seal member 18 assembled thereto can be configured in a similar manner.

[0138] [Operation and Effects of the Flow Switching Device] According to the configuration of the flow switching device 1 of this embodiment described above, compared to the tenth embodiment, each seal member 17, 18 has a mountain-shaped cross section that widens toward the rotary disks 13, 14, and includes a recess 19c that is recessed toward the housings 11, 12, and a hollow portion 19d that branches into at least two parts toward the housings 11, 12 and has an internal cavity. Each seal member 17, 18 has a smaller compression allowance on its inner diameter side than on its outer diameter side. The smaller the compression allowance, the smaller the surface pressure of each seal member 17, 18. This allows the seal surface pressure of each seal member 17, 18 to be uniformly applied 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 convexity height difference) by the height difference β1 between the convexities 82a, 82b of the apex 19a of each seal member 17, 18. On the other hand, it is also possible to make the length to the bottom end of the inner leg 19b shorter than the length to the bottom end of the outer leg 19b (adjustment of the leg length), or to adjust both the convexity height difference and the leg length.

[0140] Twelfth Embodiment A twelfth embodiment will be described in detail with reference to FIGS. 55 and 56. FIG.

[0141] [Issues with the Partitions of Each Seal Member] In Fig. 50, when the partitions 17c and 17d of the first seal member 17 come into contact with the inner surface of the upper housing 11 (rubber crushing), rubber material moves from the inner circular portion 17a and the outer circular portion 17b, and as shown by the dashed oval in Fig. 51, the surface pressure increases on the sliding surface of the top 19a and the non-sliding surface at the lower end of the leg 19b. At this time, while it is desired to move the rubber material from the partitions 17c and 17d to the inner circular portion 17a and the outer circular portion 17b, the rubber material moves from the inner circular portion 17a and the outer circular portion 17b to the partitions 17c and 17d. As a result, the average surface pressure of the two protrusions 82a and 82b on the top 19a of the partitions 17c and 17d is necessarily higher than that of other portions. Furthermore, 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 compressed and moved intensively. Although not shown or described, the same applies to the second seal member 18. Therefore, in this twelfth embodiment, the assembly structure of the seal members 17, 18 is configured as follows.

[0142] [Regarding the assembly structure of each seal member] Figure 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. Figure 56 shows an enlarged cross-sectional view of the first seal member 17 and assembly groove 13e of the first rotating disk 13 taken along line W-W (partition 17c) in Figure 55 according to the twelfth embodiment. As shown in Figure 56, in this embodiment, for the partition 17c of the first seal member 17, the heights of the two protrusions 82a, 82b on the top 19a are the same, and the lengths to the bottom ends of the two legs 19b are the same. Furthermore, both the inner groove 81a on the left side and the outer groove 81b on the right side of the assembly groove 13e are slightly deeper than the reference groove shown in Figure 51. Here, the groove depth difference α3 is set deeper than the groove depth difference α1 of the tenth embodiment shown in Figure 53. Although not shown in the figures, the same applies to the partition portion 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 the same way.

[0143] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, when the rotary disks 13 and 14 are rotated, the partitions 17c, 17d, 18c, and 18d and the outer circular portions 17b and 18b are compressed due to the sliding of the seal members 17 and 18. However, the compression margin of the partitions 17c, 17d, 18c, and 18d is smaller than the compression margin on the inner diameter side of the outer circular portions 17b and 18b. The smaller the compression margin, 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 portions 17b and 18b.

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

[0145] [Regarding the Assembly Structure of Each Seal Member] This embodiment differs from the twelfth embodiment in the configuration of the assembly structure of each seal member. Figure 57 is an enlarged cross-sectional view equivalent to Figure 56 showing the first seal member 17 and the assembly groove 13e of the first rotating disk 13 according to the thirteenth embodiment. As shown in Figure 57, in this embodiment, for the partition portion 17c of the first seal member 17, the heights of the two convex portions 82a, 82b on the top portion 19a are the same, and the lengths to the bottom ends of the two leg portions 19b are the same. The heights of both of the two convex portions 82a, 82b on the top portion 19a are set slightly lower than the reference height shown in Figure 51. Here, the height difference β2 between the convex portions 82a, 82b is set larger than the height difference β1 of Figure 54 for the eleventh embodiment. Although not shown, the same applies to the partition portion 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] [Operations and Effects of Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, it is possible to obtain operations and effects equivalent to those of the twelfth embodiment.

[0147] <Fourteenth Embodiment> A fourteenth embodiment will be described in detail with reference to Figs.

[0148] [Regarding the assembly structure of each seal member] This embodiment differs from the tenth to thirteenth embodiments in 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 taken along line Z1-Z1 in Fig. 58 (the outer branch portion 17e near the partition portion 17c). 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 on the top portion 19a are the same, the lengths to the bottom ends of the two legs 19b are the same, and the heights of both protrusions 82a, 82b on the top portion 19a are set to 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 smoothly increase from the groove depth difference α1 of the inner groove 81a of the outer circular portion 17b. The groove depth difference α5 of the outer groove 81b of the outer branch portion 17e is set to smoothly increase from a reference depth. The groove depth differences α1, α3, and α4 of the inner groove 81a of the outer branch portion 17e satisfy the relationship "α1≦α4≦α3." When there is a slight difference between the groove depth differences α1, α3, and α4, the groove depth difference α4 is smoothly varied between them. When the groove depth difference α5 is slight, the groove depth difference α5 is smoothly varied from the reference depth.

[0150] Although not shown in the drawings, the same applies to the outer branch portion 17e near the partition portion 17d. By setting it 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 as it approaches the partition portions 17c and 17d. Although not shown and described, the assembly groove 14e of the second rotating disk 14 and the second seal member 18 assembled thereto can also be configured in the same way.

[0151] [Operations and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following operations and effects compared to the tenth to thirteenth embodiments. That is, in this fourteenth embodiment, when the rotary disks 13 and 14 are driven to rotate, the partitions 17c, 17d, 18c, and 18d and the outer circular portions 17b and 18b are compressed due to the sliding of the seal members 17 and 18. However, the compression margin on the inner diameter side of the outer circular portions 17b and 18b is smaller in the vicinity of the partitions 17c, 17d, 18c, and 18d. The smaller the compression margin, the smaller the surface pressure. Therefore, an appropriate seal surface pressure can be applied to the outer circular portions 17b and 18b of the seal members 17 and 18 according to their locations.

[0152] In this embodiment, the depths of the inner grooves 81a and outer grooves 81b of the assembly grooves 13e and 14e are adjustable for the outer branch portions 17e of the seal members 17 and 18. Alternatively, the heights of the protrusions 82a and 82b on the tops 19a of the seal members 17 and 18 can be adjusted.

[0153] Fifteenth Embodiment A fifteenth embodiment will be described in detail with reference to FIG.

[0154] [Regarding the assembly structure of each seal member] This embodiment differs from the tenth to fourteenth embodiments in the configuration of the assembly structure of each seal member. Figure 60 is 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, taken along line Z2-Z2 in Figure 58 (the inner branch portion 17f near the partition portion 17c). As shown in Figure 60, in this embodiment, for the inner branch portion 17f near the partition portion 17c, the heights of the two protrusions 82a, 82b on the top 19a are the same, the lengths to the bottom ends of the two leg portions 19b are the same, and the heights of both of the two protrusions 82a, 82b on the top 19a are set to the same as the reference height in Figure 51. Here, the inner groove 81a of the inner branch portion 17f is set deeper than the reference depth in FIG. 51 by a groove depth difference α6, and the outer groove 81b is set 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 smoothly increase 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 smoothly increase from a reference depth. The groove depth differences α2, α3, and α6 of the inner groove 81a of the inner branch portion 17f satisfy the relationship "α2≦α6≦α3." When there is a slight difference between the groove depth differences α2, α3, and α6, the groove depth difference α6 is smoothly varied between them. When the groove depth difference α7 is slight, the groove depth difference α7 is smoothly varied from the reference depth.

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

[0157] [Regarding the Functions and Effects of the Flow Channel Switching Device] The configuration of the flow channel switching device 1 of this embodiment described above provides the following functions and effects compared to the tenth to fourteenth embodiments. That is, in the fifteenth embodiment, when the rotary disks 13 and 14 are driven to rotate, the partitions 17c, 17d, 18c, and 18d and the inner circular portions 17a and 18a are compressed due to the sliding of the seal members 17 and 18. However, the compression margin on the inner diameter side of the inner circular portions 17a and 18a is smaller in the vicinity of the partitions 17c, 17d, 18c, and 18d. The smaller the compression margin, the smaller the surface pressure. Therefore, an appropriate seal surface pressure can be applied to the inner circular portions 17a and 18a of the seal members 17 and 18 according to their locations.

[0158] In this embodiment, the depths of the inner grooves 81a and outer grooves 81b of the assembly grooves 13e and 14e are adjustable for the inner branch portions 17f of each of the seal members 17 and 18. Alternatively, the heights of the protrusions 82a and 82b on the tops 19a of each of the seal members 17 and 18 can be adjusted.

[0159] Sixteenth Embodiment A sixteenth embodiment will be described in detail with reference to FIGS.

[0160] [Regarding the Issues Addressed in the Sixth Embodiment] In the sixth embodiment, as shown in Figures 37 and 38, when the outer branch portion 17e and the inner branch portion 17f of the first seal member 17 cross the entrance / exit distribution area DA, a difference in surface pressure occurs between these branches 17e, 17f and the partition portions 17c, 17d other than the branches 17e, 17f, potentially resulting in wear steps. Furthermore, the high surface pressure of each branch portion 17e, 17f opens into each of the entrances 21a to 24a, increasing the likelihood of the partition portion 17c protruding into the entrances. Therefore, there was concern that the partition portion 17c would be easily caught when it climbed over the opening edge of each of the entrances 21a to 24a. The same concern was raised for the second seal member 18. Therefore, in the sixth embodiment, in order to address the above-mentioned problem, the outer branch portion 17e and the inner branch portion 17f of the first seal member 17 are arranged outside the entrance / exit distribution area DA without overlapping with the entrance / exit distribution area DA. A similar measure is taken for the second seal member 18.

[0161] [Regarding the assembly structure of each seal member] 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. Figure 61 relates to this sixteenth embodiment and shows, in an enlarged plan view equivalent to Figure 39, a portion of the partition portion 17c of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13. Figure 62 relates to this embodiment and shows, in an enlarged plan view, a portion of the outer branch portion 17e of the first seal member 17 assembled in the assembly groove 13e of the first rotating disk 13. Figure 63 shows the portion of the outer branch portion 17e in a cross-sectional view taken along line P-P in Figure 62.

[0162] In this embodiment, as shown in FIG. 61 , dummy seal surfaces 82c are additionally provided in the outer branch 17e and inner branch 17f located outside the entrance / exit distribution area DA to distribute the seal surface pressure. As shown in FIG. 63 , in this embodiment, approximately triangular convex portions are provided on each branch 17e, 17f as the dummy seal surfaces 82c. Because the cavity 19d of each branch 17e, 17f is larger than the other portions, the groove protrusions 72 provided within the cavity 19d protrude over a wider area than the other portions. This dummy seal surface 82c corresponds to an example of the "seal surface pressure distribution portion" of this disclosed technology. Although not shown or described, the same applies to the partition 17d and the second seal member 18.

[0163] [Operation and Effects of the Flow Switching Device] According to the configuration of the flow switching device 1 of this embodiment described above, the outer branch portion 17 e and the inner branch portion 17 f of the seal members 17, 18 contract due to compression during assembly, and the sealing surface pressure increases, but because the dummy sealing surface 82 c is included, the sealing surface pressure is dispersed by the sealing surface 82 c. Therefore, an appropriate sealing surface pressure can be applied to the outer branch portion 17 e and the inner branch portion 17 f of the seal members 17, 18.

[0164] [Regarding a Modification of the Sixteenth Embodiment] Figure 64 shows a cross-sectional view of the outer branch portion 17e according to this modification, similar to Figure 62. In this modification, an inner groove 81c is formed inside the groove rib 72 provided in the hollow portion 19d. In addition to the two legs 19b of the outer branch portion 17e, a reinforcing leg 19f is provided in the hollow portion 19d of the first seal member 17 to reinforcingly support the outer branch portion 17e of the first seal member 17. Although not shown or described, the same applies to the inner branch portion 17f and the second seal member 18.

[0165] [Operation and Effects of the Modified Example] According to the configuration of this modified example described above, the area of ​​the side of each seal member 17, 18 facing the housings 11, 12, i.e., the area of ​​the top portion 19a, is increased, but since the reinforcing legs 19f are provided in the hollow portion 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 hollow portion 19d side of each seal member 17, 18, and an appropriate sealing surface pressure can be applied to each seal member 17, 18.

[0166] Seventeenth Embodiment A seventeenth embodiment will be described in detail with reference to FIGS.

[0167] 31 and 32 , in the third embodiment, in-groove ridges 72 are provided in the assembly grooves 13e, 14e to be placed in the hollow portions 19d of the seal members 17, 18, and a plurality of in-groove ridge protrusions 73 that abut on the inner walls of the hollow portions 19d are provided on both side walls of the in-groove ridges 72. Alternatively, it is also possible to provide in-groove ridges 72 in the assembly grooves 13e, 14e without providing in-groove ridge protrusions 73 on both side walls of the in-groove ridges 72.

[0168] Figures 65 to 67 show a comparative example assuming that the above-described groove ridge 72 does not have the groove ridge convex portion 73. Figure 65 is an enlarged cross-sectional view equivalent to Figure 31 showing the state in which the partition portions 17c and 17d of the first seal member 17 are assembled into the assembly groove 13e and the first seal member 17 has not yet been crushed without contacting the inner surface of the upper housing 11. Figure 66 is an enlarged cross-sectional view equivalent to Figure 65 showing the state in which the partition portions 17c and 17d are assembled into the assembly groove 13e and the first seal member 17 has come into contact with the inner surface of the upper housing 11 and been crushed. Figure 67 is an enlarged cross-sectional view equivalent to Figure 65 showing the state in which the partition portions 17c and 17d are assembled into the assembly groove 13e and the first rotating disk 13 is rotating and the first seal member 17 is sliding on the inner surface of the upper housing 11.

[0169] As shown in Figures 65 to 67, the groove ridge 72 and the inner wall of the assembly groove 13e in this case have vertical portions 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, with the inner wall of one leg 19b pressed against the top of the groove ridge 72 and the outer wall of the other leg 19b pressed against the vertical portion of the inner wall of the assembly groove 13e. This raises the concern that stress may be concentrated at these pressing portions. Therefore, in this seventeenth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0170] [Regarding the assembly structure of each seal member] Figure 68, according to the seventeenth embodiment, is an enlarged cross-sectional view equivalent to Figure 31 showing the cross-sectional shapes of the partition portions 17c, 17d of the first seal member 17 in a free state and the state in which they are overlapped with the assembly groove 13e. Here, the assembly groove 13e is divided into one groove 81d and the other groove 81e by the intra-groove rib 72, and one leg portion 19b is assembled into one groove 81d, and the other leg portion 19b is assembled into the other groove 81e. Figure 69, similarly, is an enlarged cross-sectional view equivalent to Figure 68 showing the partition portions 17c, 17d assembled into the assembly groove 13e, with the first seal member 17 in contact with the inner surface of the upper housing 11 and crushed. Figure 70 shows an enlarged cross-sectional view similar to Figure 68 in which the partitions 17c and 17d are assembled into the 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 ridge 72 is formed so that the curved surface changes continuously from a small curvature (large R) to a large curvature (small R) from the bottom of the assembly groove 13e to the top of the in-groove ridge 72. Although not shown and not described, the same applies to the in-groove ridge 72 of the assembly groove 14e of the second rotating disk 14.

[0172] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel 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 the corresponding rotary disk 13, 14, and includes a recess 19c that is recessed toward the corresponding housing 11, 12, and a hollow portion 19d that branches toward the corresponding rotary disk 13, 14. In each of the assembly grooves 13e, 14e, the side wall of the groove protrusion 72 disposed in the hollow portion 19d continuously changes from a small curvature (large R) to a large curvature (small R) from the bottom of the assembly groove 13e, 14e to the top of the groove protrusion 72. Therefore, as the rotary disks 13, 14 rotate, each seal member 17, 18 begins to slide against each housing 11, 12. At this time, the inner surface of the cavity 19d of each seal member 17, 18 contacts successively from the small curvature (large R) to the large curvature (small R) from the bottom of each assembly groove 13e, 14e toward the top of the groove protrusion 72, expanding the contact area of ​​the inner surface of the cavity 19d with the side wall of the groove protrusion 72. This distributes 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 each seal member 17, 18 without significantly increasing manufacturing costs.

[0173] Eighteenth Embodiment An eighteenth embodiment will be described in detail with reference to FIGS.

[0174] 71 to 73 relate to the seventeenth embodiment, which is compared to this embodiment, and illustrate 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 is an enlarged cross-sectional view equivalent to FIG. 69 showing the state in which the partitions 18c and 18d of the second seal member 18 slide on the inner surface of the lower housing 12. FIG. 72 is an enlarged cross-sectional view equivalent to FIG. 71 showing the state in which the partitions 18c and 18d have begun to pass through the openings 25a to 28a of the lower housing 12. FIG. 73 is an enlarged cross-sectional view equivalent to FIG. 71 showing the state in which the partitions 18c and 18d have passed through the openings 25a to 28a.

[0175] In the seventeenth embodiment, the side walls of the groove ridges 72 for the assembly grooves 14e corresponding to the partitions 18c, 18d also 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 Figure 73, when the partitions 18c, 18d pass through the openings 25a to 28a, stress acts in the direction in which the second seal member 18 falls, causing the legs 19b to contract inward along the curved surfaces of the side walls of the groove ridges 72, making it impossible for the legs 19b to maintain surface pressure, which could cause the partitions 18c, 18d to fall into the openings 25a to 28a. Therefore, in the eighteenth embodiment, the assembly structure of each seal member 17, 18 is configured as follows.

[0176] [Regarding the assembly structure of each seal member] Figure 74 is an enlarged cross-sectional view of the bottom of the assembly groove 14e of the second rotating disk 14, showing one groove 81d divided into two by the intra-groove ridge 72, and the end of one leg 19b assembled to the groove 81d, according to the eighteenth embodiment. In this embodiment, the inner wall of the assembly groove 14e and the side wall of the intra-groove ridge 72 each have vertical surfaces 86a, 87a extending vertically near the bottom of one groove 81d of the assembly groove 14e, and the side wall of the intra-groove ridge 72 continuously changes from a curved surface with a smaller curvature to a curved surface with a larger curvature from the vertical surface 87a toward the top of the intra-groove ridge 72. That is, as shown in Figure 74, the inner peripheral wall of the assembly 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 ridge 72 has a curved surface 87b and a vertical surface 87a from the bottom to the top, and a curved surface 87c that changes shape continues from the end of the vertical surface 87a. Although not shown and described, the same applies to the other groove 81e of the assembly groove 14e.

[0177] [Operation and Effects of the Flow Channel Switching Device] According to the configuration of the flow channel switching device 1 of this embodiment described above, unlike the configuration of the seventeenth embodiment, the inner walls of the assembly grooves 13 e, 14 e and the side walls of the groove protrusions 72 disposed in the hollow portions 19 d have vertical surfaces 86 a, 87 a extending perpendicularly near the bottoms of the assembly grooves 13 e, 14 e, respectively. Furthermore, the side walls of the groove protrusions 72 continuously change in curvature from a small curvature (large R) to a large curvature (small R) from the bottoms of the assembly grooves 13 e, 14 e toward the tops of the groove protrusions 72. Therefore, as the rotary disks 13, 14 rotate, the seal members 17, 18 begin to slide relative to the housings 11, 12. In this case, the inner surfaces of the hollow portions 19d of the seal members 17, 18 contact successively from the small curvature (large R) to the large curvature (small R) from the bottom of each assembly groove 13e, 14e toward the top of the groove ridge 72, expanding the contact area of ​​the inner surfaces of the hollow portions 19d with the side walls of the groove ridge 72. This distributes stress acting on the inner surfaces of the hollow portions 19d and suppresses twisting of the seal members 17, 18. This ensures the sealing performance of the seal members 17, 18 without significantly increasing manufacturing costs. Meanwhile, the side walls of the groove ridge 72 have vertical surfaces extending vertically near the bottoms of the assembly grooves 13e, 14e. As a result, even if the seal members 17, 18 contract inward along the curved surfaces of the side walls of the groove ridges 72, the surface pressure of the seal members 17, 18 against the groove ridges 72 is maintained on the vertical surfaces, thereby preventing the seal members 17, 18 from falling out of the assembly grooves 13e, 14e.

[0178] <19th Embodiment> The 19th embodiment will be described in detail with reference to Figs.

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

[0180] In this embodiment, as shown in Figures 75 and 76, a plurality of protrusions 14i extending perpendicularly from the bottom of one groove 81d are formed at equal intervals along the longitudinal direction of the groove 81d on the outer side wall of the assembly groove 14e into which the second seal member 18 is fitted. Here, as shown in Figure 76, the overall width W1 of the bottom of one groove 81d is greater than the partial width W2 of the bottom of the protrusions 14i, but the open width of the leg portions 19b of the second seal member 18 before assembly into the groove 81d is set to be smaller than the overall width W1 but larger than the partial width W2. Although not shown or described, the same applies to the other groove 81e of the assembly groove 14e.

[0181] [Regarding the action and effect of the flow path 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 walls of the assembly groove 14e into which the second seal member 18 is fitted, that is, the outer side walls of both grooves 81d, 81e, are 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] <Other Embodiments> The disclosed technology is not limited to the above-described embodiments, and can be implemented by appropriately modifying part of the configuration within the scope of the disclosed technology.

[0183] (1) In each of the above embodiments, the flow path switching device 1 is configured as an eight-way valve. However, the present invention is not limited to this, and other multi-way valves such as a three-way valve, a four-way valve, and a six-way valve may also be used.

[0184] (2) In each of the above embodiments, the "valve body" of the disclosed technology is configured to be composed of the first rotating disk 13 and the second rotating disk 14, which are configured to rotate integrally on the rotating shaft 15. However, the "valve body" may also be configured to be composed of the first sliding plate and the second sliding plate which 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 embodiments, the cross section of the sealing members 17, 18 is formed into a bifurcated mountain shape. However, in regard to matters related only to the external shape of the sealing members, the cross section may be formed into the shape of a solid O-ring or the like without a cavity.

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

[0188] REFERENCE SIGNS LIST 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 portion 17 first seal member (sealing means) 17a inner circular portion 17b outer circular portion 17c partition portion 17d partition portion 17e outer branch portion 17f inner branch portion 18 second seal member (sealing means) 18a inner circular portion 18b outer circular portion 18c partition portion 18d partition portion 19c recessed portion 19d hollow portion 19f reinforcing leg 20 inflow / outflow passage (communicating passage) 21 first inflow / outflow passage 21a entrance / exit (opening) 22 second inflow / outflow passage 22a Entrance / exit (opening) 23 Third inflow / outflow passage 23a Entrance / exit (opening) 24 Fourth inflow / outflow passage 24a Entrance / exit (opening) 25 Fifth inflow / outflow passage 25a Entrance / exit (opening) 26 Sixth inflow / outflow passage 26a Entrance / exit (opening) 27 Seventh inflow / outflow passage 27a Entrance / exit (opening) 28 Eighth inflow / outflow passage 28a Entrance / exit (opening) 29 Intersecting opening edge 30 Rotation passage (communicating passage) 31 First rotation passage (communicating passage) 32 Second rotation passage (communicating passage) 40 Rotation passage (communicating passage) 43 Third rotation passage 44 Fourth rotation passage 71 Convex portion 72 In-groove ridge 73 In-groove ridge ridge convex portion 76 Auxiliary seat portion 79 Seal stopper (jump-out prevention means) 84 Dummy seal surface (seal surface pressure distribution portion) 90 Electric car 91 Cooling system

Claims

1. A flow path switching device comprising: at least one stator; a valve disc driven relatively to the stator; at least one communication passage provided in each of the stator and the valve disc; and an annular sealing means provided between the stator and the valve disc and adapted to slide against the stator or the valve disc as the valve disc is driven, wherein the valve disc is driven to selectively connect the communication passage of the valve disc to the communication passage of the stator, thereby switching and forming a series of flow paths; wherein the sealing means comprises an inner circular portion disposed on the center side of the valve disc or the stator, an outer circular portion disposed on the outer periphery of the valve disc or the stator, and partition portions which 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 disc or the stator; the valve disc 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 under tension and assembled.

2. A flow path switching device comprising: 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 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, wherein the valve body is driven to selectively connect the communication path of the valve body and the communication path of the stator to switch and form a series of flow paths, wherein the sealing means includes an inner circular portion that is arranged on the center side of the valve body or the stator, an outer circular portion that is arranged on the outer periphery 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 paths provided in the valve body or the stator, 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, the assembly groove has an inner wall of a portion where the partition is fitted, and a plurality of protrusions that abut against the partition are arranged at different positions on both sides of the partition.

3. A flow path switching device comprising at least one stator, a valve body driven relatively to the stator, at least one communication path provided in each of the stator and the valve body, and an annular sealing means provided between the stator and the valve body and sliding against the stator or the valve body as the valve body is driven, wherein the valve body is driven to selectively connect the communication path of the valve body to the communication path of the stator, and switch between and form a series of flow paths, wherein the sealing means comprises an inner circular portion disposed on the center side of the valve body or the stator, an outer circular portion disposed on the outer periphery of the valve body or the stator, and partition portions connecting the inner circular portion and the outer circular portion at a plurality of points and partitioning between the plurality of communication paths provided in the valve body or the stator, and the valve body includes an assembly groove for assembling the sealing means, the sealing means has a mountain-shaped cross section spreading toward the valve body or the stator, and includes a recess that is recessed on the side of the stator or the valve body, and a hollow portion that is branched into at least two portions toward the valve body or the stator and has a hollow inside, the assembly groove includes an inner-groove protrusion that is disposed in the hollow portion, and a side wall of the inner-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 inner-groove protrusion.

4. A flow path switching device comprising at least one stator, a valve body driven relatively to the stator, at least one communication path provided in each of the stator and the valve body, and an annular sealing means provided between the stator and the valve body and sliding against the stator or the valve body as the valve body is driven, wherein the valve body is driven to selectively connect the communication path of the valve body to the communication path of the stator, and a series of flow paths is switched and formed, wherein the sealing means comprises an inner circular portion disposed on the center side of the valve body or the stator, an outer circular portion disposed on the outer periphery of the valve body or the stator, and partition portions connecting the inner circular portion and the outer circular portion at a plurality of points and separating the plurality of communication paths provided in the valve body or the stator, and the valve body includes an assembly groove for assembling the sealing means, the sealing means has a mountain-shaped cross section expanding toward the valve body or the stator, and includes a recess that is recessed on the side of the stator or the valve body, and a hollow portion that is branched into at least two portions toward the valve body or the stator and has a hollow inside, the assembly groove includes an intra-groove protrusion disposed in the hollow portion, an inner wall of the assembly groove and a side wall of the intra-groove protrusion each have a vertical surface that extends vertically near a bottom of the assembly groove, and the side wall of the intra-groove protrusion 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 protrusion.

5. A flow path switching device as claimed in claim 2, wherein one of the stator and the valve body is a retaining member which retains the sealing means, and the other is a sliding member against which the sealing means slides, the sealing means has a mountain-shaped cross section which widens towards the retaining member and includes a recess which is recessed towards the sliding member and a hollow portion which is branched into at least two towards the retaining member and has an internal cavity, the assembly groove includes an inner-groove ridge which is arranged in the hollow portion, and a side wall of the inner-groove ridge which corresponds to the partition portion is provided with an inner-groove ridge convex portion which abuts against the inner wall of the hollow portion.

6. A flow path switching device as claimed in claim 5, characterized in that the convex portion of the assembly groove and the inner groove protrusion 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.

7. A flow path switching device as claimed in any one of claims 1 to 6, characterized in that the sealing means further includes an outer branch portion where the partition portion branches off to the outer circular portion, and an inner branch portion where the partition portion branches off to the inner circular portion, and the outer branch portion and the inner branch portion are positioned outside the distribution area of ​​the openings of the communication passage that the sealing means slides across.

8. A flow path switching device as claimed in any one of claims 1 to 6, characterized in that, among the openings of the communication 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 having a curved surface that curves towards the inside of the opening, and the diameter of the curved surface is larger towards the centre of the intersecting opening edge than at both ends.

9. A flow path switching device as claimed in any one of claims 1 to 6, characterized in that an auxiliary seat 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, and which extends along the sliding direction and with which the partition portion comes into contact.

10. A flow path switching device according to any one of claims 1 to 6, characterized in that a protrusion prevention means is provided for preventing the partition portion of the sealing means from protruding from the assembly groove.

11. A flow path switching device as claimed in claim 1 or 2, wherein one of the stator and the valve body is a retaining member which retains the sealing means, and the other is a sliding member against which the sealing means slides, the sealing means has a mountain-shaped cross section which expands towards the retaining member and includes a recess which is recessed towards the sliding member and a hollow portion which branches into at least two towards the retaining member and has a hollow interior, and the sealing means has a smaller compression allowance on the inner diameter side than on the outer diameter side.

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

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

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

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

16. A flow path switching device as claimed in claim 15, characterized in that the hollow portion is provided with a reinforcing leg for reinforcingly supporting the sealing means in the assembly groove.

17. A flow path switching device according to any one of claims 1 to 6, characterized in that the flow path switching device is used in a cooling system for an electric vehicle.

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