Flow path switching device and fluid circuit system including the same

Abstract

To reduce an excessive load applied to a seal member by a residual pressure in an in-housing space.SOLUTION: A flow path switching device 1 is provided with: a housing 2; two rotating discs 13, 14 located adjacent to each other; communication channels 20, 30, 40 provided at the housing 2 and the rotating discs 13, 14; sealing members 17, 18 provided between the surrounding areas of the communication channels 30, 40 of the rotating discs 13, 14 and the housing 2; and a compression spring 61 for causing the rotating discs 13, 14 to separate from each other and urging the rotating discs 13, 14 in a direction toward the housing 2. The flow path switching device 1 causes the rotating discs 13, 14 to rotate to connect the communication channels 30, 40 of the rotating discs 13, 14 with the communication channel 20 of the housing 2, thus switching a flow path. An in-housing space 7 excluding the communication channels 20 to 40 is provided between the housing 2 and the rotating discs 13, 14, and a pressure regulation hole 8 which communicates with one 20 of the communication channels to regulate the pressure in the in-housing space 7 is provided at the housing 2.SELECTED DRAWING: Figure 8

Description

[Technical field]

[0001] The technology disclosed in this specification relates to a flow path switching device that switches a flow path of a fluid, and a fluid circuit system including the flow path switching device. [Background technology]

[0002] Conventionally, as this type of technology, for example, a technology "flow path switching valve" described in the following Patent Document 1 is known. The flow path switching valve of this technology includes a main valve housing (housing), a main valve body (valve body portion) rotatably arranged in the housing, and a fluid pressure actuator (drive portion) for rotating the valve body portion, and is configured so that the flow path can be switched by rotating the valve body portion. Here, the valve body portion includes a first layer member (first drive member) and a second layer member (second drive member), and the first drive member, the second drive member, and the housing each have a plurality of communication passages, and a plurality of flow paths are formed by rotating each drive member and combining the connections of the communication passages. Packings (sealing members) are provided between the housing and each drive member that form the communication passages. This flow path switching valve is used, for example, as a four-way switching valve in a heat pump type heating and cooling system including a pump. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2016-98968 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the flow path switching valve described in Patent Document 1, when the internal pressure of the flow path drops when the pump is stopped in a heat pump type heating and cooling system, the pressure (residual pressure) remaining outside each drive member (the space inside the housing excluding the communication passage between each drive member and the housing) may press each drive member toward the housing, causing an excessive load to be applied to the seal member. As a result, there is a concern that the seal member may be excessively crushed, or may become worn or unevenly worn.

[0005] This disclosed technology has been made in consideration of the above-mentioned circumstances, and its purpose is to provide a flow path switching device and a fluid circuit system equipped with a flow path switching device that make it possible to suppress excessive load on a sealing member due to residual pressure in the space within the housing. [Means for solving the problem]

[0006] In order to achieve the above object, the flow path switching device according to claim 1 includes a housing and a valve body portion arranged inside the housing, the valve body portion including a first drive member and a second drive member arranged adjacent to each other, the housing and at least one of the first drive member and the second drive member each include a plurality of communication passages, a seal member for suppressing leakage of fluid is provided between the housing and a periphery of the communication passage in at least one of the first drive member and the second drive member, and a seal member for suppressing leakage of fluid is provided between the first drive member and the second drive member in order to adjust a contact surface pressure of the seal member against the housing or the first drive member and the second drive member. The flow path switching device is configured such that an elastic member is provided which biases the first drive member and the second drive member in a direction separating them from each other and bringing them closer to the housing, and by driving the first drive member and the second drive member, a communication passage in at least one of the first drive member and the second drive member and a communication passage in the housing are combined and connected to selectively switch between multiple flow paths, and the purpose of the device is that an internal housing space excluding the communication passages is provided between the housing and the first drive member and the second drive member, and the housing is provided with a pressure adjustment hole which communicates with at least one of the communication passages in order to adjust the pressure in the internal housing space.

[0007] According to the configuration of the above technology, when the fluid is not pumped to the communication passages of the housing, the pressure in the housing space between the housing and the first and second drive members is released to at least one of the communication passages through the pressure adjustment hole, and the pressure in the housing space is reduced. Therefore, the drive members are no longer pressed toward the housing by the residual pressure in the housing space.

[0008] In order to achieve the above-mentioned object, the flow path switching device described in claim 2 is a flow path switching device described in claim 1, wherein at least one of the first driving member and the second driving member or the housing is provided with a regulating means for regulating the reduction of the gap between at least one of the first driving member and the second driving member and the housing.

[0009] According to the configuration of the above technology, in addition to the action of the flow path switching device described in claim 1, even if at least one of the first drive member and the second drive member tilts due to an imbalance in fluid pressure in the connecting passage of at least one of the first drive member and the second drive member, the reduction of the gap between at least one of the first drive member and the second drive member and the housing is regulated by the regulating means.

[0010] In order to achieve the above object, the flow path switching device of claim 3 is the flow path switching device of claim 1, further comprising a rotating shaft for rotating each drive member, the rotating shaft is inserted into each drive member so as to be movable relative to the drive member in the rotational and axial directions, the rotating shaft is provided with an enlarged diameter portion for transmitting driving force to each drive member, each drive member is formed with a plurality of long hole-shaped rotation passages as communicating passages extending in an arc along the rotation locus of each drive member around the rotating shaft, and the enlarged diameter portion is arranged toward the center of the arc of the rotation passage.

[0011] According to the configuration of the above technology, in addition to the action of the flow path switching device described in claim 1, the driving force of the rotating shaft is transmitted to each driving member by the enlarged diameter portion, and each driving member rotates. The enlarged diameter portion of the rotating shaft is disposed toward the center of the arc of the multiple rotation passages that extend in an arc shape around the rotating shaft in each driving member. Therefore, each driving member is engaged with and supported by the enlarged diameter portion toward the center of the arc of the rotation passage.

[0012] In order to achieve the above-mentioned object, the flow path switching device described in claim 4 is a flow path switching device described in claim 3, in which the rotation passages of each driving member are arranged linearly symmetrically with respect to the axis of symmetry, and each driving member has an abutment portion that is parallel to the axis of symmetry and can abut against the enlarged diameter portion.

[0013] According to the configuration of the above technology, in addition to the action of the flow path switching device described in claim 3, the rotation passages of each drive member are arranged symmetrically with respect to the axis of symmetry, and each drive member has a contact portion that is parallel to the axis of symmetry and can contact the enlarged diameter portion. Therefore, when the rotation shaft stops rotating, the enlarged diameter portion of the rotation shaft contacts the contact portion of each drive member, and the contact provides resistance to the inclination of each drive member in a direction perpendicular to the axis of symmetry of the rotation passage.

[0014] In order to achieve the above-mentioned object, the flow path switching device described in claim 5 is a flow path switching device described in claim 3, wherein the enlarged diameter portion is arranged between each driving member and extends outside the outer diameter of the rotation passage of each driving member.

[0015] According to the configuration of the above technology, in addition to the effect of the flow path switching device described in claim 3, the expanded diameter portion extends beyond the outer diameter of the rotation passage of each drive member, so that the outer diameter of the expanded diameter portion is larger than the outer diameter of the rotation passage.

[0016] In order to achieve the above-mentioned object, the flow path switching device described in claim 6 is a flow path switching device described in claim 3, wherein the first drive member and the second drive member each have an axial hole through which a rotating shaft is inserted, and the hole length of the axial hole of one of the first drive member and the second drive member, which includes a rotating passage that forms a higher pressure flow path, is longer than the hole length of the axial hole of the other drive member.

[0017] According to the configuration of the above technology, in addition to the action of the flow path switching device described in claim 3, of the first and second drive members, one of the drive members including a rotation passage forming a higher pressure flow path is more likely to tilt than the other drive member. With this configuration, the length of the shaft hole of one drive member is longer than the length of the shaft hole of the other drive member, so the angle at which the shaft hole of one drive member is allowed to tilt relative to the rotation axis is smaller than that of the shaft hole of the other drive member.

[0018] In order to achieve the above-mentioned object, the flow path switching device described in claim 7 is a flow path switching device described in claim 3, wherein the first drive member and the second drive member each have an axial hole through which a rotating shaft is inserted, and the radial clearance between the axial hole and the rotating shaft of one of the first drive member and the second drive member, which includes a rotating passage that forms a higher pressure flow path, is smaller than the radial clearance between the axial hole and the rotating shaft of the other drive member.

[0019] According to the configuration of the above technology, in addition to the action of the flow path switching device described in claim 3, of the first and second drive members, one of the drive members including a rotation passage forming a higher pressure flow path is more likely to tilt than the other drive member. With this configuration, the radial clearance between the shaft hole of one drive member and the rotating shaft is smaller than the radial clearance between the shaft hole of the other drive member and the rotating shaft, so the angle at which the shaft hole of one drive member is allowed to tilt relative to the rotating shaft is smaller than the shaft hole of the other drive member.

[0020] In order to achieve the above object, the fluid circuit system described in claim 8 is a fluid circuit system equipped with a flow path switching device described in any one of claims 1 to 7, further comprising a pump for pressurizing and pumping a fluid, and the pressure adjustment hole is provided corresponding to a specific communication passage, among a plurality of communication passages, to which an outlet of the pump is connected.

[0021] According to the configuration of the above technology, in addition to the action of the flow path switching device according to any one of claims 1 to 7, in a flow path circuit system equipped with a pump, a pressure adjustment hole is provided corresponding to a specific communication path, among a plurality of communication paths, to which an outlet of the pump is connected. Therefore, when the pump is driven, the pressure in the space within the housing is not released by the pressure adjustment hole, and when the pump is stopped, the pressure in the space within the housing is reliably released by the pressure adjustment hole.

[0022] In order to achieve the above object, the fluid circuit system according to claim 9 is the fluid circuit system according to claim 8, wherein a pump having an outlet communicating with a specific communication passage is configured to be constantly driven.

[0023] According to the configuration of the above technology, in addition to the action of the fluid circuit system described in claim 8, the pump, whose outlet is connected to a specific communication passage, is constantly driven, so that pressure from the pump always acts on the space within the housing via the pressure adjustment hole.

[0024] In order to achieve the above object, the fluid circuit system according to claim 10 is a fluid circuit system including a flow path switching device according to any one of claims 1 to 7, further including a pump for pumping a fluid, the flow path switching device including, as housings, an upper housing for accommodating a first drive member and a lower housing for accommodating a second drive member, a predetermined communication passage is arranged in one of the upper housing and the lower housing, and a communication passage is arranged in the other housing, and at least a part of the predetermined communication passage is provided so as to be capable of communicating with an inlet of the pump. The purpose of this document is to

[0025] According to the configuration of the above technology, in addition to the function of the flow path switching device according to any one of claims 1 to 7, in a flow path circuit system including a pump, the flow path switching device is provided such that at least a part of a predetermined communication passage disposed in one of the upper housing accommodating the first drive member or the lower housing accommodating the second drive member can communicate with an inlet of the pump. Therefore, in one of the first drive member or the second drive member, which includes a communication passage leading to the predetermined communication passage, bias in the fluid pressure in the communication passage is reduced.

[0026] In order to achieve the above object, the fluid circuit system described in claim 11 is the fluid circuit system described in claim 10, wherein the flow path switching device includes a first seal member arranged between the upper housing and the first drive member, and a second seal member arranged between the lower housing and the second drive member, and the first seal member or the second seal member provided in the upper housing or the lower housing in which at least a part of a specified communication passage is arranged has a hardness or spring constant higher than that of the second seal member or the first seal member provided in the lower housing or the upper housing in which other communication passages are arranged.

[0027] According to the configuration of the above technology, in addition to the action of the fluid circuit system described in claim 10, in the flow path switching device, the housing space of the upper housing or the lower housing in which at least a part of the predetermined communication passage that can communicate with the inlet of the pump is disposed is at a low pressure close to atmospheric pressure. Therefore, the pressing load of the first seal member or the second seal member on the upper housing or the lower housing due to the pressure of this low-pressure housing space becomes large. According to this configuration, the first seal member or the second seal member corresponding to the upper housing or the lower housing in which the housing space is at a low pressure has a higher hardness or spring constant than the second seal member or the first seal member corresponding to the lower housing or the upper housing, so that the first seal member or the second seal member corresponding to the upper housing or the lower housing in which the housing space is at a low pressure is less likely to be displaced by the load.

[0028] In order to achieve the above object, the fluid circuit system described in claim 12 is the fluid circuit system described in claim 10, wherein the flow path switching device comprises a partition plate fixed on a rotating shaft and arranged between a first drive member and a second drive member, a first elastic member that urges the partition plate and the first drive member in a direction separating them from each other, and a second elastic member that urges the partition plate and the second drive member in a direction separating them from each other, and the first elastic member or the second elastic member provided corresponding to the upper housing or the lower housing in which at least a part of a specified communication passage is arranged has a smaller spring constant than the second elastic member or the first elastic member provided corresponding to the lower housing or the upper housing in which another communication passage is arranged.

[0029] According to the configuration of the above technology, in addition to the action of the fluid circuit system described in claim 10, in the flow path switching device, a first elastic member is arranged on the rotating shaft between the first driving member and the partition plate, which urges them in the direction separating them, and a second elastic member is arranged between the second driving member and the partition plate, which urges them in the direction separating them. Here, the housing space in the upper housing or the lower housing in which at least a part of a predetermined communication passage that can communicate with the inlet of the pump is arranged is at a low pressure close to atmospheric pressure. Therefore, the pressing load by the first elastic member or the second elastic member on the first seal member or the second seal member corresponding to the upper housing or the lower housing in which the housing space is at a low pressure becomes large. According to this configuration, the first elastic member or second elastic member corresponding to the upper housing or lower housing where the space inside the housing is at low pressure has a smaller spring constant than the second elastic member or first elastic member corresponding to the other lower housing or upper housing, so that the first sealing member or second sealing member provided corresponding to the upper housing or lower housing where the space inside the housing is at low pressure is less likely to be displaced by the load of the first elastic member or second elastic member.

[0030] In order to achieve the above object, the fluid circuit system described in claim 13 is a fluid circuit system equipped with a flow path switching device described in any one of claims 1 to 7, comprising a plurality of small circuits whose communication is switched by the flow path switching device, a pump provided in each of at least two of the plurality of small circuits, and a control means for controlling the operation of the flow path switching device and the pump, wherein the control means is intended to stop driving the pump after the communication switching is completed when the flow path switching device switches the communication state of the plurality of small circuits.

[0031] According to the configuration of the above technology, in addition to the function of the flow path switching device according to any one of claims 1 to 7, in the fluid circuit system, when the flow path switching device switches the communication state of the multiple small circuits, the control means stops driving the pump after the switching is completed. Therefore, when each driving member is driven to switch the communication state of the multiple small circuits, the pump is driven against the biasing force of the elastic member, and the pressure of the fluid acts on the communication passage of each driving member.

[0032] In order to achieve the above object, a flow path switching device according to a fourteenth aspect of the present invention is a flow path switching device according to any one of the first to seventh aspects, wherein the flow path switching device is used in a cooling system of an electric vehicle.

[0033] According to the configuration of the above technology, in addition to the action of the flow path switching device described in any one of claims 1 to 7, an action equivalent to that of the flow path switching device described in any one of claims 1 to 7 can be obtained for a flow path switching device used in the cooling system of an electric vehicle. Effect of the Invention

[0034] According to the flow path switching device of claim 1, it is possible to prevent the seal member from being subjected to an excessive load due to the residual pressure in the space within the housing.

[0035] According to the flow path switching device described in claim 2, in addition to the effects of the flow path switching device described in claim 1, even if at least one of the first drive member and the second drive member is tilted, excessive crushing of the sealing member between the housing can be suppressed, and sagging and uneven wear of the sealing member can be suppressed.

[0036] According to the flow path switching device of claim 3, in addition to the effects of the flow path switching device of claim 1, even if an imbalance occurs in the fluid pressure in the rotating passage and each driving member tends to tilt, the tilt of each driving member can be suppressed, and sagging and uneven wear of the sealing members can be suppressed.

[0037] According to the flow path switching device described in claim 4, in addition to the effects of the flow path switching device described in claim 3, the inclination of each driving member in a direction perpendicular to the axis of symmetry of the rotating passage can be suppressed, and sagging and uneven wear of the sealing members can be suppressed.

[0038] According to the flow path switching device described in claim 5, in addition to the effects of the flow path switching device described in claim 3, the effect of suppressing the inclination of each drive member by the expanded diameter portion can be improved, and the variation in the rotation angle of each drive member due to component tolerances can be suppressed.

[0039] According to the flow path switching device described in claim 6, in addition to the effects of the flow path switching device described in claim 3, the tilt of one of the drive members, which is prone to tilt, can be suppressed, and the wear and uneven wear of the sealing member can be suppressed.

[0040] According to the flow path switching device described in claim 7, in addition to the effects of the flow path switching device described in claim 3, the tilt of one of the drive members, which is prone to tilt, can be suppressed, and wear and uneven wear of the sealing member can be suppressed.

[0041] According to the fluid circuit system of claim 8, in addition to the effect of the flow path switching device of any one of claims 1 to 7, when the pump is stopped, it is possible to reliably prevent excessive load from being placed on the sealing member due to residual pressure in the space within the housing.

[0042] According to the fluid circuit system of claim 9, in addition to the effect of the fluid circuit system of claim 8, the pressure in the space within the housing can be constantly maintained at the pressure generated by the pump.

[0043] According to the fluid circuit system of claim 10, in addition to the effect of the flow path switching device of any one of claims 1 to 7, the inclination of one of the drive members including the communication passage leading to the predetermined communication passage can be suppressed.

[0044] According to the fluid circuit system of claim 11, in addition to the effect of the fluid circuit system of claim 10, it is possible to suppress wear and uneven wear of the first seal member or the second seal member corresponding to the upper housing or the lower housing in which a specified communication passage that can communicate with the pump inlet is arranged.

[0045] According to the fluid circuit system of claim 12, in addition to the effect of the fluid circuit system of claim 10, it is possible to suppress wear and uneven wear of the first seal member or the second seal member corresponding to the upper housing or the lower housing on the low pressure side in which a predetermined communication passage that can communicate with the inlet of the pump is arranged.

[0046] According to the flow path switching device of claim 13, in addition to the effects of the flow path switching device of any one of claims 1 to 7, when each drive member is driven, the surface pressure applied to the sealing member can be reduced, the drive torque of each drive member can be reduced, and uneven wear of the sealing member can be reduced.

[0047] According to the flow path switching device described in claim 14, in addition to the effects of the flow path switching device described in any one of claims 1 to 7, it is possible to obtain effects equivalent to those of the flow path switching device described in any one of claims 1 to 7 when used in the cooling system of an electric vehicle. [Brief description of the drawings]

[0048] [Figure 1] FIG. 2 is a perspective view showing a flow path switching device in the first embodiment. [Diagram 2]FIG. 2 is a front view showing the flow path switching device in the first embodiment. [Diagram 3] FIG. 2 is a plan view showing the flow path switching device in the first embodiment. [Figure 4] FIG. 3 is a bottom view showing the flow path switching device in the first embodiment. [Diagram 5] FIG. 2 is an exploded perspective view showing the flow path switching device in the first embodiment. [Figure 6] 3 is a cross-sectional view taken along line AA in FIG. 2 showing the flow path switching device according to the first embodiment. [Figure 7] 4 is a cross-sectional view of the flow path switching device taken along line BB in FIG. 3 according to the first embodiment. [Figure 8] FIG. 3 is a perspective view showing the inside of an upper housing in the first embodiment. [Figure 9] FIG. 3 is a perspective view showing a first rotating disk in the first embodiment. [Figure 10] FIG. 3 is a plan view showing a first rotating disk in the first embodiment. [Figure 11] FIG. 4 is a bottom view showing the first rotating disk in the first embodiment. [Figure 12] FIG. 4 is a plan view showing a second rotating disk in the first embodiment. [Figure 13] FIG. 4 is a bottom view showing the second rotating disk in the first embodiment. [Figure 14] FIG. 3 is a perspective view showing a rotation shaft in the first embodiment. [Figure 15] 15 is a cross-sectional view taken along line CC in FIG. 14 and showing a rotation shaft in the first embodiment. [Figure 16] 3 is a cross-sectional view taken along line DD in FIG. 2 showing the flow path switching device according to the first embodiment. [Figure 17] 11 is an enlarged cross-sectional view taken along line EE in FIG. 10 , showing a first rotating disk and a first seal member in the first embodiment. [Figure 18] FIG. 2 is a circuit diagram showing an example of use of the flow path switching device in the first embodiment. [Figure 19] FIG. 4 is a circuit diagram showing a first switching pattern of the cooling system in the first embodiment. [Figure 20] FIG. 4 is a circuit diagram showing a second switching pattern of the cooling system in the first embodiment. [Figure 21] FIG. 4 is a circuit diagram showing a third switching pattern of the cooling system in the first embodiment. [Figure 22] FIG. 4 is a circuit diagram showing a fourth switching pattern of the cooling system in the first embodiment. [Diagram 23] FIG. 11 is a circuit diagram showing a fifth switching pattern of the cooling system in the first embodiment. [Figure 24] 4 is a schematic diagram illustrating the rotational position of the first rotating disk relative to the upper housing and the flow of the refrigerant in a cross section taken along line FF in FIG. 2 in a second switching pattern in the first embodiment. FIG. [Diagram 25] 5 is a schematic diagram illustrating the rotational position of the second rotating disk relative to the lower housing and the flow of the refrigerant in a cross section taken along line GG in FIG. 2 in the first embodiment, in a second switching pattern. [Figure 26] 25 is a schematic diagram equivalent to FIG. 24 showing the rotational position of the first rotating disk with respect to the upper housing and the flow of the refrigerant in the third switching pattern in the first embodiment. FIG. [Figure 27] 26 is a schematic diagram equivalent to FIG. 25 showing the rotational position of the second rotating disk relative to the lower housing and the flow of the refrigerant in the third switching pattern in the first embodiment. FIG. [Figure 28] 25 is a schematic diagram equivalent to FIG. 24 showing the rotational position of the first rotating disk with respect to the upper housing and the flow of the refrigerant in a fourth switching pattern in the first embodiment. FIG. [Figure 29] 26 is a schematic diagram equivalent to FIG. 25 showing the rotational position of the second rotating disk relative to the lower housing and the flow of the refrigerant in the fourth switching pattern in the first embodiment. FIG. [Diagram 30] 5 is a flowchart showing the flow path switching control executed by a control unit in the first embodiment. [Diagram 31] FIG. 2 is a cross-sectional view illustrating a flow path switching device according to the first embodiment, and is a schematic view of a housing and a part of a valve body portion thereof. [Diagram 32] FIG. 11 is a plan view showing a first rotating disk in a second embodiment. [Diagram 33] 33 is an enlarged cross-sectional view taken along line HH in FIG. 32, showing a first rotating disk and a part of the upper housing in the second embodiment. [Diagram 34] This relates to the second embodiment and is shown in a cross-sectional view taken along line II in FIG. 33 showing a part of the first rotating disk (in a non-tilted state). [Diagram 35] 34 is an enlarged cross-sectional view equivalent to FIG. 33 showing the first rotating disk and a part of the upper housing (in a tilted state) in the second embodiment. FIG. [Diagram 36] FIG. 11 is a plan view showing a first rotating disk in a third embodiment. [Figure 37] 17 is a cross-sectional view showing a flow path switching device according to a fourth embodiment, which is equivalent to FIG. 16. [Figure 38] 13 is a cross-sectional view showing a flow path switching device according to a fifth embodiment, which is equivalent to FIG. 7. [Figure 39] 13 is a cross-sectional view showing a flow path switching device according to a sixth embodiment, which is equivalent to FIG. 7. [Diagram 40] 13 shows the relationship between the hardness of the seal member and the load required to achieve zero leakage according to the seventh embodiment. [Diagram 41] 18 is a cross-sectional view showing a second seal member and the like according to the seventh embodiment, which is equivalent to FIG. 17. [Diagram 42] 18 is a cross-sectional view showing a first seal member and the like according to the seventh embodiment, which is equivalent to FIG. 17. [Diagram 43] 13 is a cross-sectional view showing a flow path switching device according to an eighth embodiment, which is equivalent to FIG. 7. [Diagram 44] FIG. 13 is a cross-sectional view showing a bearing structure provided at the lower end of a rotating shaft in a ninth embodiment. [Diagram 45] FIG. 33 is a plan view showing a first rotating disk according to the tenth embodiment, which corresponds to FIG. 32. [Diagram 46] FIG. 23 is a plan view showing a first rotating disk in the eleventh embodiment. [Figure 47] FIG. 23 is a plan view showing a first rotating disk provided with two rotation paths etc. in the twelfth embodiment. [Figure 48] FIG. 23 is a plan view showing a first rotating disk provided with three rotation paths etc. in the twelfth embodiment. [Figure 49] FIG. 23 is a plan view showing the first rotating disk when stopped in a counterclockwise direction in the thirteenth embodiment. [Figure 50]FIG. 22 is an enlarged plan view showing a portion including a first shaft hole 13a in FIG. 49 according to the thirteenth embodiment. [Figure 51] FIG. 23 is a plan view showing the first rotating disk when stopped in a clockwise direction in the thirteenth embodiment. [Figure 52] FIG. 52 is an enlarged plan view showing a portion including the first shaft hole in FIG. 51 according to the thirteenth embodiment. [Figure 53] FIG. 51 is an enlarged plan view equivalent to FIG. 50 showing a portion of the first shaft hole of the first rotating disc when stopped in a counterclockwise direction in the fourteenth embodiment. [Figure 54] FIG. 53 is an enlarged plan view equivalent to FIG. 52 showing a portion including the first shaft hole of the first rotating disc when the clockwise rotation is stopped in the fourteenth embodiment. [Figure 55] FIG. 54 is an enlarged plan view equivalent to FIG. 53 showing a portion including the first shaft hole of the first rotating disc when stopped in a counterclockwise direction in the fifteenth embodiment. [Figure 56] FIG. 56 is an enlarged plan view showing a part of the first shaft hole in FIG. 55 according to the fifteenth embodiment. [Figure 57] FIG. 55 is an enlarged plan view equivalent to FIG. 54 showing a portion including the first shaft hole of the first rotating disc when the clockwise rotation is stopped in the fifteenth embodiment. [Figure 58] FIG. 23 is an enlarged plan view showing a portion including a first shaft hole of a first rotating disk and a rotating shaft therein in an idle state in the sixteenth embodiment. [Figure 59] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the first rotating disc is stopped in a counterclockwise direction in the sixteenth embodiment. [Figure 60] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the clockwise rotation is stopped in the sixteenth embodiment. [Figure 61] FIG. 23 is an enlarged plan view showing a portion including a first shaft hole of a first rotating disk and a rotating shaft therein in an idle state in the seventeenth embodiment. [Figure 62] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the first rotating disc is stopped in a counterclockwise direction in the seventeenth embodiment. [Figure 63] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the first rotating disc is stopped in a clockwise direction in the seventeenth embodiment. [Figure 64] FIG. 23 is an enlarged plan view showing a portion including a first shaft hole of a first rotating disk and a rotating shaft therein in an idle state in the 18th embodiment. [Figure 65] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the first rotating disc is stopped in a counterclockwise direction in the 18th embodiment. [Figure 66] FIG. 23 is an enlarged plan view showing a portion including the first shaft hole of the first rotating disc and the rotating shaft therein when the clockwise rotation is stopped in the 18th embodiment. [Figure 67] FIG. 23 is a plan view showing a second rotating disk and a rotating shaft in the nineteenth embodiment. [Figure 68] The nineteenth embodiment is shown in a cross-sectional view taken along line JJ in FIG. 67, with the second rotating disk 14 and the like being shown in a schematic diagram illustrating the relationship between the second rotating disk 14 and the first rotating disk 13 and the like. [Figure 69] FIG. 68 is a plan view corresponding to FIG. 67 showing a second rotating disc and a rotating shaft in the twentieth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0049] Hereinafter, several embodiments embodying the "flow path switching device and a fluid circuit system equipped with the flow path switching device" of the disclosed technology will be described in detail with reference to the drawings.

[0050] First Embodiment The first embodiment will be described in detail with reference to FIGS.

[0051] [Outline of flow switching device] FIG. 1 shows a perspective view of the flow path switching device 1 of this embodiment. FIG. 2 shows a front view of the flow path switching device 1. FIG. 3 shows a plan view of the flow path switching device 1. FIG. 4 shows a bottom view of the flow path switching device 1. FIG. 5 shows an exploded perspective view of the flow path switching device 1. FIG. 6 shows a cross-sectional view of the flow path switching device 1 taken along line AA in FIG. 2. FIG. 7 shows a cross-sectional view of the flow path switching device 1 taken along line BB in FIG. 3. In FIGS. 2 to 7, the control unit 5 is omitted. 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, a drive portion 4 that drives the valve body portion 3, and a control portion 5 that controls the drive portion 4.

[0052] [About housing] As shown in Figs. 1 to 7, the housing 2 includes an upper housing 11 and a lower housing 12, and is configured by fastening the two housings 11, 12 with a plurality of screws 6. The housing 2 corresponds to an example of the "housing" of this disclosed technology. The housing 2 includes an inflow / outflow passage 20 through which a fluid flows in and out. The flow path switching device 1 of this embodiment is configured as an eight-way valve as an example, and the housing 2 has eight inflow / outflow passages 20. As the eight inflow / outflow passages 20, the upper housing 11 is provided with a first inflow / outflow passage 21, a second inflow / outflow passage 22, a third inflow / outflow passage 23, and a fourth inflow / outflow passage 24, and the lower housing 12 is provided with a fifth inflow / outflow passage 25, a sixth inflow / outflow passage 26, a seventh inflow / outflow passage 27, and an eighth inflow / outflow passage 28. Fig. 8 shows the inside of the upper housing 11 in a perspective view. As shown in Fig. 8, an entrance 21a of the first inflow / outflow passage 21, an entrance 22a of the second inflow / outflow passage 22, an entrance 23a of the third inflow / outflow passage 23, and an entrance 24a of the fourth inflow / outflow passage 24 are opened on the inside of the upper housing 11. Similarly, as shown in Fig. 5, entrances 25a, 26a, 27a, and 28a of the fifth inflow / outflow passage 25 to the eighth inflow / outflow passage 28 are opened on the inside of the lower housing 12. The inflow / outflow passage 20 corresponds to an example of a "communication passage" provided in a "housing" of the disclosed technology. In this embodiment, the housing 2 is formed of, for example, resin.

[0053] [About the valve body] As shown in Figs. 5 to 7, the valve body portion 3 includes a first rotating disk 13 and a second rotating disk 14 that rotate in the housing 2 and are stacked adjacent to each other vertically, and a rotating shaft 15 that drives and rotates both rotating disks 13, 14. Both rotating disks 13, 14 are stacked in the axial direction X. The first rotating disk 13 corresponds to an example of a "first driving member" in this disclosed technology. The second rotating disk 14 corresponds to an example of a "second driving member" in this disclosed technology. Both rotating disks 13, 14 and the rotating shaft 15 are formed of, for example, resin.

[0054] [About the first rotating disk] FIG. 9 shows the first rotating disk 13 in a perspective view. FIG. 10 shows the first rotating disk 13 in a plan view. FIG. 11 shows the first rotating disk 13 in a bottom view. As shown in FIG. 5 to FIG. 7, the first rotating disk 13 is accommodated in the housing 2 together with the second rotating disk 14. As shown in FIG. 9 to FIG. 11, the first rotating disk 13 is formed in a substantially cylindrical shape with a bottom, and includes two rotation passages 30 that open upward in the axial direction X. As the two rotation passages 30, a first rotation passage 31 and a second rotation passage 32 are provided. The rotation passage 30 is semicircular in plan view. The rotation passage 30 corresponds to an example of a "communication passage" provided in the "first driving member" of this disclosed technology. In the center of the first rotating disk 13, a first shaft hole 13a through which the rotating shaft 15 passes is formed. In the first rotating disk 13, a first boss 13b is formed centered on the first shaft hole 13a.

[0055] [About the second rotating disk] FIG. 12 shows the second rotating disk 14 in a plan view. FIG. 13 shows the second rotating disk 14 in a bottom view. As shown in FIG. 13, the second rotating disk 14 is formed in a substantially cylindrical shape with a bottom like the first rotating disk 13, and includes two rotation passages 40 that open downward in the axial direction X. As the two rotation passages 40, a third rotation passage 43 and a fourth rotation passage 44 are provided. This rotation passage 40 is semicircular in shape when viewed from the bottom. This rotation passage 40 corresponds to an example of a "communication passage" provided in the "valve body" of this disclosed technology. A second shaft hole 14a through which the rotating shaft 15 penetrates is also formed in the center of the second rotating disk 14. As shown in FIG. 12, a second boss 14b is formed on the upper surface side of the second rotating disk 14, centered on the second shaft hole 14a.

[0056] [About the rotation axis] FIG. 14 shows the rotating shaft 15 in a perspective view. FIG. 15 shows the rotating shaft 15 in a cross-sectional view taken along the line CC in FIG. 14. As shown in FIG. 14 and FIG. 15, the rotating shaft 15 of this embodiment is formed in multiple stages with different outer diameters in parts. The upper end 15a of the rotating shaft 15, which is connected to the driving unit 4, is a gear having multiple teeth. The lower end 15b of the rotating shaft 15, which is fitted into the shaft hole 12a of the lower housing 12, has a small diameter and an irregular shape. A pair of first protrusions 15c and second protrusions 15d arranged on the same circumference are provided on the outer periphery of the middle part of the rotating shaft 15. As shown in FIG. 15, the protrusions 15c and 15d protrude in an arc shape on the outer periphery of the rotating shaft 15 and are arranged at an interval of 180 degrees. The first protrusion 15c has a longer circumferential length than the second protrusion 15d. Here, it is preferable that the protrusions 15c, 15d are arranged in two or more locations to ensure stable engagement with the first rotating disk 13 and the second rotating disk 14, and it is also preferable that they are arranged and shaped asymmetrically to prevent incorrect assembly.

[0057] 5 to 7, the rotating shaft 15 is provided penetrating the upper housing 11 and both rotating disks 13, 14. The upper end 15a of the rotating shaft 15 passes through a through hole 11a of the upper housing 11 and is connected to the driving unit 4, and the lower end 15b is rotatably supported by a shaft hole 12a of the lower housing 12.

[0058] As shown in FIG. 6 and FIG. 7, a bearing 51 that rotatably supports the rotating shaft 15 is provided in the through hole 11a of the upper housing 11. A washer 52 is provided at the upper end opening of the through hole 11a, centering on the rotating shaft 15. The washer 52 is held by an E-ring 53 fixed on the rotating shaft 15. A compression spring 54 is provided on the rotating shaft 15 between the bearing 51 and the washer 52. The compression spring 54 biases the rotating shaft 15 upward in the axial direction X, thereby preventing rattling due to vibration of the rotating shaft 15. The bearing 51 supports the rotating shaft 15 with an inner ring to smooth the rotation of the rotating shaft 15. The bearing 51 also supports the compression spring 54 with an inner ring to smooth the rotation of the compression spring 54. Furthermore, a lip seal 55 that prevents leakage of fluid is provided between the upper housing 11 and the rotating shaft 15 in the through hole 11a. The rotating shaft 15 may be made of metal.

[0059] 6 and 7, a torsion spring 56 is provided inside the shaft hole 12a of the lower housing 12, centered on the lower end 15b of the rotating shaft 15. The torsion spring 56 is interposed between the bottom of the shaft hole 12a and the middle part of the rotating shaft 15, and biases the rotating shaft 15 in the rotation direction Y, thereby eliminating rattling between the rotating shaft 15 and the drive unit 4.

[0060] [Rotation transmission mechanism] The flow path switching device 1 of this embodiment includes a rotation transmission mechanism for transmitting the rotational force of the rotating shaft 15 to the first rotating disk 13 and the second rotating disk 14. Fig. 16 shows the flow path switching device 1 in a cross-sectional view taken along line DD in Fig. 2. The rotation transmission mechanism of this embodiment is provided between the first rotating disk 13 and the second rotating disk 14 and the rotating shaft 15, and is configured to allow relative movement of the first rotating disk 13 and the second rotating disk 14 in the axial direction X of the rotating shaft 15, and to be able to partially release the transmission of the rotational force of the rotating shaft 15 to the first rotating disk 13 and the second rotating disk 14 as the rotating shaft 15 rotates.

[0061] In this embodiment, both rotating disks 13, 14 and a rotating shaft 15 are connected to be relatively movable in the rotation direction Y and the axial direction X. That is, as shown in FIG. 16, the rotating shaft 15 is assembled to the first boss 13b so as to coincide with the center of the first boss 13b of the first rotating disk 13. As shown in FIG. 11, FIG. 12 and FIG. 16, the first boss 13b has a pair of first notches 13c, 13d in which a part of the circumferential direction is missing. As shown in FIG. 16, the first protrusion 15c and the second protrusion 15d are fitted into the first notches 13c, 13d. A gap 16 is provided in the circumferential direction between the first notches 13c, 13d and the first protrusion 15c and the second protrusion 15d. Therefore, the rotating shaft 15 and the first rotating disk 13 are allowed to move relatively in the axial direction X along the first cutouts 13c, 13d and the protrusions 15c, 15d, and are allowed to move relatively in the rotational direction Y within the range of the gaps 16 between the first cutouts 13c, 13d and the protrusions 15c, 15d. In this manner, the rotating shaft 15 is connected to the first rotating disk 13 so as to be movable relatively in the rotational direction Y and the axial direction X.

[0062] On the other hand, like the first rotating disk 13, the rotating shaft 15 is assembled to the second boss 14b so as to coincide with the center of the second boss 14b of the second rotating disk 14. Like the first boss 13b, the second boss 14b has a pair of second notches 14c, 14d with a part of its circumferential direction missing, as shown in FIG. 12. The first protrusion 15c and the second protrusion 15d are fitted into these second notches 14c, 14d. A gap is also provided in the circumferential direction between the second notches 14c, 14d and each of the protrusions 15c, 15d. Therefore, the rotating shaft 15 and the second rotating disk 14 are allowed to move relatively in the axial direction X along the second notches 14c, 14d and each of the protrusions 15c, 15d, and are allowed to move relatively in the rotational direction Y within the range of the circumferential gap between the second notches 14c, 14d and each of the protrusions 15c, 15d. In this manner, the rotating shaft 15 is connected to the second rotating disc 14 so as to be movable relative to the second rotating disc 14 in the rotational direction Y and the axial direction X. In this embodiment, the first protrusion 15c and the second protrusion 15d correspond to an example of an "enlarged diameter portion" of the disclosed technology for transmitting a driving force to the valve body portion 3 (each of the rotating discs 13, 14).

[0063] This rotating shaft 15 rotates by receiving a driving force from the drive unit 4, and rotates relatively within the gap 16 at each boss 13b, 14b, and rotates integrally with both rotating disks 13, 14 by engaging with the circumferential inner surfaces of each notch 13c, 13d and each notch 14c, 14d.

[0064] [About sealing materials] As shown in Figs. 5 to 7, 9, 10 and 13, in this embodiment, a first seal member 17 and a second seal member 18 of a circumferential type having a substantially annular shape are provided between the first rotating disk 13 and the second rotating disk 14 and the housing 2 (the upper housing 11 and the lower housing 12) to suppress leakage of fluid. The first seal member 17 is provided on the first rotating disk 13, and the second seal member 18 is provided on the second rotating disk 14. That is, as shown in Figs. 9 and 10, a circumferential assembly groove 13e for assembling the first seal member 17 is formed on the upper surface of the first rotating disk 13 so as to surround the periphery of the openings of the two rotation passages 30 (the first rotation passage 31 and the second rotation passage 32). The first seal member 17 is fitted and fixed in the assembly groove 13e, and is provided so as to protrude from the upper surface of the first rotating disk 13. As shown in FIG. 13, a circumferential type assembly groove 14e for assembling the second seal member 18 is formed on the lower surface of the second rotating disk 14 so as to surround the periphery of the openings of the two rotating passages 40 (the third rotating passage 43 and the fourth rotating passage 44). The second seal member 18 is fitted and fixed in the assembly groove 14e and provided so as to protrude from the lower surface of the second rotating disk 14. That is, between the periphery of each of the rotating passages 30, 40 of each of the rotating disks 13, 14 and each of the housings 11, 12, the respective seal members 17, 18 are provided to suppress leakage of fluid. In this embodiment, the respective seal members 17, 18 are formed only of rubber. The respective seal members 17, 18 may be formed of fluororesin (e.g., Teflon (registered trademark)) or may be formed of rubber to which fluororesin is attached.

[0065] Here, as shown in Figures 13 and 14, each of the seal members 17 and 18 has an annular shape and includes inner circular portions 17a and 18a, outer circular portions 17b and 18b, and partition portions 17c, 17d, 18c and 18d. Each of the seal members 17 and 18 has two semicircular seal regions surrounded by the partition portions 17c, 17d, 18c and 18d, the inner circular portions 17a and 18a, and the outer circular portions 17b and 18b, and the two seal regions are arranged symmetrically with respect to the partition portions 17c, 17d, 18c and 18d as the axis of symmetry. The first seal member 17 and the second seal member 18 are formed to have the same size and shape.

[0066] In this embodiment, each of the seal members 17 and 18 has a mountain-shaped (M-shaped) cross section cut in a direction perpendicular to the longitudinal direction of each part (hereinafter referred to as a "vertical cross section"). FIG. 17 shows the first rotating disk 13 and the first seal member 17 in an enlarged cross section taken along the line EE in FIG. 10. FIG. 17 shows the upper seal member 17 assembled in the assembly groove 13e of the first rotating disk 13 cut in a direction perpendicular to the longitudinal direction of the assembly groove 13e. As shown in FIG. 17, the first seal member 17 has a mountain-shaped cross section expanding toward the first rotating disk 13 side, and includes a top 19a capable of contacting the inner surface of the upper housing 11, a leg portion 19b bifurcated from the top 19a toward the assembly groove 13e side, a recess 19c recessed toward the upper housing 11 side, and a hollow portion 19d that is hollow inside the bifurcated leg portion 19b. The top 19a includes two left and right protrusions 82a, 82b having the same height. The lower ends of the two left and right leg portions 19b extend to the same length. Although not shown and described, the second seal member 18, like the first seal member 17, also has a mountain-shaped cross section and includes a top 19a, leg portions 19b, a recess 19c, and a hollow portion 19d.

[0067] In this embodiment, the mounting groove 13e of the first rotating disk 13 is provided with an in-groove ridge 72 disposed in the hollow portion 19d of the first seal member 17. In this embodiment, the in-groove ridge 72 is provided in the entire mounting groove 13e, but it is also possible to provide the in-groove ridge 72 only in a portion of the mounting groove 13e. A plurality of in-groove ridge protrusions that abut against the inner wall of the hollow portion 19d can also be provided on both side walls of the in-groove ridge 72. Although not shown and not described, the same applies to the mounting groove 14e of the second rotating disk 14 and the second seal member 18.

[0068] In this embodiment, as shown in Figs. 5, 7 and 16, a plurality of compression springs 61 are provided between the first rotating disk 13 and the second rotating disk 14 to adjust the contact surface pressure of the seal members 17, 18 against the upper housing 11 and the lower housing 12, and to bias the first rotating disk 13 and the second rotating disk 14 in a direction to move them closer to the upper housing 11 and the lower housing 12 while separating them from each other. The plurality of compression springs 61 have the same shape and biasing force. In this embodiment, three compression springs 61 are disposed at equal angular intervals between the two rotating disks 13, 14. The plurality of compression springs 61 correspond to an example of the "elastic member" of this disclosed technology. The above-mentioned "rotation transmission mechanism" and the compression springs 61 constitute a "surface pressure adjustment mechanism."

[0069] As shown in Figs. 7 and 11, three receiving holes 13f for receiving the upper parts of the compression springs 61 are provided at equal angular intervals on the bottom surface of the first rotating disk 13. As shown in Figs. 5, 7, and 12, three receiving holes 14f for receiving the lower parts of the compression springs 61 are provided at equal angular intervals on the top surface of the second rotating disk 14. Cylindrical portions 13g and 14g are provided at the centers of the receiving holes 13f and 14f, respectively, and the compression springs 61 are assembled and held around the cylindrical portions 13g and 14g. By assembling the compression springs 61 into the receiving holes 13f and 14f between the two rotating disks 13 and 14, the urging force of the compression springs 61 causes the two rotating disks 13 and 14 to be separated from each other and to approach the upper housing 11 and the lower housing 12, and the seal members 17 and 18 are urged in a direction to contact the inner surfaces of the upper housing 11 and the lower housing 12. In this embodiment, the above-mentioned rotation transmission mechanism connects each of the rotating disks 13, 14 to the rotating shaft 15 so that they can move relatively in the axial direction X. Therefore, each of the rotating disks 13, 14 is allowed to move in the axial direction X within a predetermined range by the biasing force of each of the compression springs 61.

[0070] [About the drive unit] The drive unit 4 includes a motor or the like (not shown) for applying a rotational driving force to the rotary shaft 15. The flow path switching device 1 is configured to selectively combine and connect the rotation passages 30, 40 of both rotary disks 13, 14 and the inflow / outflow passages 20 (the first inflow / outflow passage 21 to the eighth inflow / outflow passage 28) of the housing 2 by driving the rotary disks 13, 14 to rotate via the rotary shaft 15 with the drive unit 4, thereby selectively switching and forming a series of multiple flow paths. In other words, a "flow path switching pattern" described later is formed.

[0071] [About the control unit] The control unit 5 controls the drive unit 4 to rotate the rotary shaft 15 to rotate the first rotating disk 13 and the second rotating disk 14. The control unit 5 controls the flow path switching device 1 together with electric pumps 97, 98 in a cooling system 91 described later.

[0072] [Examples of using the flow switching device] FIG. 18 shows a circuit diagram of an example of use of the flow path switching device 1. As shown in FIG. 18, in this embodiment, the flow path switching device 1 is used in a cooling system 91 mounted on an electric vehicle 90. The cooling system 91 includes a radiator 92, a PCU 93, a battery 94, and a chiller 95 in addition to the flow path switching device 1. A first pipe 96A is connected to the radiator 92, a second pipe 96B is connected to the PCU 93, a third pipe 96C is connected to the battery 94, and a fourth pipe 96D is connected to the chiller 95. A first electric pump 97 for pumping the fluid is provided in the second pipe 96B in addition to the PCU 93. A second electric pump 98 for pumping the fluid is provided in the fourth pipe 96D in addition to the chiller 95. Both ends of the first pipe 96A are connected to the first inflow / outflow passage 21 and the fifth inflow / outflow passage 25 of the flow path switching device 1. Both ends of the second pipe 96B are connected to the third inflow / outflow passage 23 and the sixth inflow / outflow passage 26 of the flow path switching device 1. In this second pipe 96B, the inlet (suction side) of the first electric pump 97 is connected (communicated) to the third inflow / outflow passage 23, and the outlet (discharge side) of the first electric pump 97 is connected (communicated) to the sixth inflow / outflow passage 26. Both ends of the third pipe 96C are connected to the fourth inflow / outflow passage 24 and the eighth inflow / outflow passage 28 of the flow path switching device 1. Both ends of the fourth pipe 96D are connected to the second inflow / outflow passage 22 and the seventh inflow / outflow passage 27 of the flow path switching device 1. In this fourth pipe 96D, the inlet (suction side) of the second electric pump 98 is connected (communicated) to the second inflow / outflow passage 22, and the outlet (discharge side) of the second electric pump 98 is connected (communicated) to the seventh inflow / outflow passage 27.

[0073] In the cooling system 91, the flow path switching device 1 is driven to switch the flow path, thereby controlling the flow of the refrigerant as a fluid to each of the parts 92 to 95. The cooling system 91 corresponds to an example of a "cooling system" in the disclosed technology. The first pipe 96A to the fourth pipe 96D connected to the flow path switching device 1 correspond to an example of a "multiple small circuits" in the disclosed technology, the communication of which is switched by the flow path switching device 1. The first electric pump 97 and the second electric pump 98 are provided in two pipes, that is, the second pipe 96B and the fourth pipe 96D. The control unit 5 described above controls the flow path switching device 1 and the electric pumps 97 and 98, and corresponds to an example of a "control means" in the disclosed technology.

[0074] [About flow path switching patterns] Here, an example of a flow path switching pattern for the cooling system 91 described above will be described. In Figs. 19 to 23, the first to fifth switching patterns are shown as flow path switching patterns in the form of circuit diagrams. Fig. 19 shows the first switching pattern that is switched to at an extremely low temperature in winter. In this first switching pattern, the first inflow / outflow passage 21 and the second inflow / outflow passage 22 communicate with each other, and the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24 communicate with each other. In addition, the fifth inflow / outflow passage 25 and the seventh inflow / outflow passage 27 communicate with each other, and the sixth inflow / outflow passage 26 and the eighth inflow / outflow passage 28 communicate with each other. In this switching pattern, only the first electric pump 97 is turned on, and the second electric pump 98 is turned off. In this case, the second pipe 96B and the third pipe 96C form a closed circuit via the flow path switching device 1, and the refrigerant circulates between the PCU 93 and the battery 94. In addition, the first pipe 96A and the fourth pipe 96D form a closed circuit via the flow path switching device 1, but since the second electric pump 98 is turned off, the refrigerant does not circulate between the radiator 92 and the chiller 95.

[0075] FIG. 20 shows a second switching pattern that is switched to at low temperatures in winter, heating, and warm air (-7°C). In this second switching pattern, the first inflow / outflow passage 21 and the second inflow / outflow passage 22 communicate with each other, and the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24 communicate with each other, as in the first switching pattern. In addition, the fifth inflow / outflow passage 25 and the seventh inflow / outflow passage 27 communicate with each other, and the sixth inflow / outflow passage 26 and the eighth inflow / outflow passage 28 communicate with each other. In this second switching pattern, both the first and second electric pumps 97, 98 are turned on. In this case, the second pipe 96B and the third pipe 96C form a closed circuit via the flow path switching device 1, and the refrigerant circulates between the PCU 93 and the battery 94. In addition, the first pipe 96A and the fourth pipe 96D form a closed circuit via the flow path switching device 1, and the refrigerant circulates between the radiator 92 and the chiller 95.

[0076] FIG. 21 shows a third switching pattern that is switched to at low temperature in winter, heating and warm air (5°C), and at high temperature in summer, cooling and cooling (30°C). In this third switching pattern, the first inflow / outflow passage 21 and the second inflow / outflow passage 22 communicate with each other, and the fifth inflow / outflow passage 25 and the sixth inflow / outflow passage 26 communicate with each other. In addition, the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24 communicate with each other, and the seventh inflow / outflow passage 27 and the eighth inflow / outflow passage 28 communicate with each other. In this third switching pattern, both the first and second electric pumps 97, 98 are turned on. In this case, the first pipe 96A to the fourth pipe 96D form a series of closed circuits via the flow path switching device 1, and the refrigerant circulates sequentially among the radiator 92, the chiller 95, the battery 94, and the PCU 93. In this third switching pattern, the battery 94 and the PCU 93 can be cooled.

[0077] FIG. 22 shows a fourth switching pattern that is switched to during high summer temperatures, cooling, and cooling (maximum 40°C). In this fourth switching pattern, the first inflow / outflow passage 21 and the third inflow / outflow passage 23 communicate with each other, and the fifth inflow / outflow passage 25 and the sixth inflow / outflow passage 26 communicate with each other. In addition, the second inflow / outflow passage 22 and the fourth inflow / outflow passage 24 communicate with each other, and the seventh inflow / outflow passage 27 and the eighth inflow / outflow passage 28 communicate with each other. In this fourth switching pattern, both the first and second electric pumps 97, 98 are turned on. In this case, the first pipe 96A and the second pipe 96B form a closed circuit via the flow path switching device 1, and the refrigerant circulates between the radiator 92 and the PCU 93. In addition, the third pipe 96C and the fourth pipe 96D form a closed circuit via the flow path switching device 1, and the refrigerant circulates between the battery 94 and the chiller 95. In this fourth switching pattern, the battery 94 can be cooled.

[0078] FIG. 23 shows a fifth switching pattern that is switched to when the spring / autumn air conditioning is off (25°C). In this fifth switching pattern, the second inflow / outflow passage 22 and the sixth inflow / outflow passage 26 communicate with each other, and the third inflow / outflow passage 23 and the fourth inflow / outflow passage 24 communicate with each other. Also, the seventh inflow / outflow passage 27 and the eighth inflow / outflow passage 28 communicate with each other. In this fifth switching pattern, both the first and second electric pumps 97, 98 are turned on. In this case, the second pipe 96B to the fourth pipe 96D, excluding the first pipe 96A, form a series of closed circuits via the flow path switching device 1, and the refrigerant circulates sequentially between the chiller 95, the battery 94, and the PCU 93. Even in this fifth switching pattern, the battery 94 and the PCU 93 can be cooled.

[0079] [Cooling system configuration] In this embodiment, in the cooling system 91, the third inflow / outflow passage 23 and the second inflow / outflow passage 22 connected to the inlets (suction sides) of the electric pumps 97, 98 are at approximately atmospheric pressure. Therefore, the rotation passages 31, 32 of the first rotating disk 13 connected to the second inflow / outflow passage 22 and the third inflow / outflow passage 23 of the upper housing 11 are lowered to atmospheric pressure. Here, if one of the rotation passages 31, 32 is adjacent to the other to which the discharge pressure of the electric pumps 97, 98 is applied, the first rotating disk 13 that is in contact with the upper housing 11 via the first seal member 17 will inevitably tilt, and there is a concern that the first seal member 17 will suffer from poor sealing, settling, or uneven wear.

[0080] Therefore, in the cooling system 91, the flow paths are configured as follows. That is, in the flow path switching device 1 of this embodiment, for the multiple inflow / outflow paths 20 (the first inflow / outflow path 21 to the eighth inflow / outflow path 28) of the housing 2, predetermined first inflow / outflow path 21 to fourth inflow / outflow path 24 are arranged on the side of the upper housing 11 that accommodates the first rotating disk 13, and other fifth inflow / outflow path 25 to eighth inflow / outflow path 28 are arranged on the lower housing 12 that accommodates the second rotating disk 14. At least a part of the predetermined first inflow / outflow path 21 to fourth inflow / outflow path 24 is provided so as to be able to communicate with the inlets of the electric pumps 97, 98. In other words, in this cooling system 91, the third inflow / outflow passage 23 and the second inflow / outflow passage 22 connected to the inlet (suction side) of each electric pump 97, 98, and the first inflow / outflow passage 21 and the fourth inflow / outflow passage 24 connected to each of these inflow / outflow passages 22, 23 via each of the rotating passages 31, 32 of the first rotating disk 13 are concentrated and provided in the upper housing 11, i.e., on the side that accommodates the first rotating disk 13.

[0081] FIG. 24 is a schematic diagram showing the rotational position of the first rotating disk 13 relative to the upper housing 11 and the flow of the refrigerant in a cross section taken along line FF in FIG. 2 for the "second switching pattern." FIG. 25 is a schematic diagram showing the rotational position of the second rotating disk 14 relative to the lower housing 12 and the flow of the refrigerant in a cross section taken along line GG in FIG. 2 for the "second switching pattern." FIG. 26 is a schematic diagram similar to FIG. 24 showing the rotational position of the first rotating disk 13 relative to the upper housing 11 and the flow of the refrigerant in a cross section taken along line GG in FIG. 2 for the "third switching pattern." FIG. 27 is a schematic diagram similar to FIG. 25 showing the rotational position of the second rotating disk 14 relative to the lower housing 12 and the flow of the refrigerant in a cross section taken along line FF in FIG. 2 for the "third switching pattern." FIG. 28 is a schematic diagram similar to FIG. 24 showing the rotational position of the first rotating disk 13 relative to the upper housing 11 and the flow of the refrigerant in a cross section taken along line GG in FIG. FIG. 29 is a schematic diagram equivalent to FIG. 25 showing the rotational position of the second rotating disc 14 relative to the lower housing 12 and the flow of the refrigerant in the "fourth switching pattern."

[0082] [Flow path switching control] In the above-described cooling system 91, the flow path switching device 1 and the electric pumps 97, 98 are controlled by the above-described control unit 5. In this embodiment, the control unit 5 performs the flow path switching control as follows, for example. Figure 30 shows the flow path switching control performed by the control unit 5 in the form of a flowchart.

[0083] When the process moves to this routine, the control unit 5 determines whether or not there is a request to switch the flow path in step 100. If the result of this determination is positive, the control unit 5 moves the process to step 110, and if the result of this determination is negative, the control unit 5 moves the process to step 160.

[0084] In step 160, the control unit 5 holds the current switching position, and returns the process to step 100.

[0085] On the other hand, in step 110, the control unit 5 reads the requested switching pattern.

[0086] Next, in step 120, the control unit 5 judges whether or not the current state is the first switching pattern. If the judgment result is positive, the control unit 5 shifts the process to step 130, and if the judgment result is negative, the control unit 5 shifts the process to step 170.

[0087] In step 130, the control unit 5 turns on the second electric pump 98.

[0088] Next, in step 140, the control unit 5 judges whether the request is for the second switching pattern. If the result of this judgment is positive, the control unit 5 shifts the process to step 150, and if the result of this judgment is negative, the control unit 5 shifts the process to step 230.

[0089] In step 150, the control unit 5 completes the switching and returns the process to step 100.

[0090] On the other hand, in step 170, moving from step 120, the control unit 5 judges whether or not the request is the first switching pattern. If the result of this judgment is positive, the control unit 5 shifts the process to step 180, and if the result of this judgment is negative, the control unit 5 shifts the process to step 200.

[0091] In step 180, the control unit 5 judges whether or not the current state is the second switching pattern. If the judgment result is positive, the control unit 5 shifts the process to step 190, and if the judgment result is negative, the control unit 5 shifts the process to step 200.

[0092] In step 190 , the control unit 5 turns off the second electric pump 98 , and proceeds to step 150 .

[0093] On the other hand, in step 200 moving from step 170 or step 180, the control unit 5 drives the drive unit 4 to operate the flow path switching device 1.

[0094] Next, in step 210, the control unit 5 judges whether or not the request switching pattern has been switched to another request switching pattern. If the result of this judgment is positive, the control unit 5 shifts the process to step 220, and if the result of this judgment is negative, the control unit 5 returns the process to step 200.

[0095] In step 220 , the control unit 5 stops the driving unit 4 in order to stop the flow path switching device 1 , and then the process proceeds to step 150 .

[0096] On the other hand, in step 230 moving from step 140, the control unit 5 drives the drive unit 4 to operate the flow path switching device 1.

[0097] Next, in step 240, the control unit 5 judges whether or not the request switching pattern has been switched to another request switching pattern. If the result of this judgment is positive, the control unit 5 shifts the process to step 250, and if the result of this judgment is negative, the control unit 5 returns the process to step 230.

[0098] In step 250 , the control unit 5 stops the drive unit 4 in order to stop the flow path switching device 1 , and then the process proceeds to step 150 .

[0099] In the above-mentioned flow path switching control, when the flow path switching device 1 switches the communication state of each of the pipes 96A to 96D (multiple small circuits), the control unit 5 stops driving the second electric pump 98 after the communication switching is completed.

[0100] [Issues regarding sealing materials] FIG. 31 is a schematic cross-sectional view of the housing 2 (upper housing 11 and lower housing 12) and the valve body portion 3 (first rotating disk 13 and second rotating disk 14) of the flow path switching device 1 of this embodiment. As shown in FIG. 31, a housing inner space 7 is formed between the housings 11, 12 and the rotating disks 13, 14 as a space excluding the inflow / outflow passages 21-28 and the rotating passages 30, 40. In the cooling system 91 described above, when the electric pumps 97, 98 are stopped, pressure due to the refrigerant may remain in the housing inner space 7. If the rotating disks 13, 14 are pressed toward the housings 11, 12 by this residual pressure, there is a concern that the seal members 17, 18 will be pressed against the inner walls of the housings 11, 12 and be excessively crushed.

[0101] The mechanism by which the seal members 17, 18 are crushed is as follows. That is, in the cooling system 91, when the electric pumps 97, 98 are turned on (driven), the pressure of the refrigerant acts on the rotation passages 30, 40 of the rotating disks 13, 14 from the inflow / outflow passages 21-28. At this time, when the pressure of the refrigerant in the rotation passages 30, 40 of the rotating disks 13, 14 exceeds the biasing force of the compression spring 61, a gap is generated between the seal members 17, 18 and the housings 11, 12. In addition, this gap allows the refrigerant to seep into the housing space 7 from the rotation passages 30, 40, and the housing space 7 is filled with the refrigerant, causing the pressure of the refrigerant in the housing space 7 to rise.

[0102] Here, when the biasing force of the compression spring 61 is small, the refrigerant pressure in the housing internal space 7 rises to the maximum refrigerant pressure in all the inflow / outflow passages 21-28. During the operation of each electric pump 97, 98, the refrigerant pressure in each rotary passage 30, 40 and the refrigerant pressure in the housing internal space 7 act in a direction that cancels each other. Therefore, the biasing force of the compression spring 61 may be sufficient to obtain a crushing amount that allows each seal member 17, 18 to be sealed in the canceled state. However, since the housing internal space 7 is sealed, when each electric pump 97, 98 stops, the refrigerant pressure in each rotary passage 30, 40 drops to approximately atmospheric pressure, and each rotary disk 13, 14 is pressed toward each housing 11, 12, so that each seal member 17, 18 is excessively crushed. Therefore, in the flow path switching device 1 of this embodiment, the following crushing countermeasures are taken to suppress the excessive crushing of each seal member 17, 18.

[0103] [Countermeasures against crushing] In this embodiment, as shown in FIG. 2, the lower housing 12 is provided with a pressure adjustment hole 8 communicating with the sixth inflow / outflow passage 26 for adjusting the refrigerant pressure in the housing internal space 7.

[0104] In this embodiment, the pressure adjustment hole 8 is provided in correspondence with a specific sixth inflow / outflow passage 26, among the multiple inflow / outflow passages 20 (the first inflow / outflow passage 21 to the eighth inflow / outflow passage 28), with which an outlet (discharge side) of a first electric pump 97 that is constantly driven through all of the first to fifth switching patterns in the cooling system 91 of Fig. 18 is connected. Here, the first electric pump 97 whose outlet is connected to the specific sixth inflow / outflow passage 26 is configured to be constantly driven, i.e., to be driven through all of the first to fifth switching patterns.

[0105] [Actions and effects of the flow path switching device and cooling system] According to the configuration of the embodiment described above, in the flow path switching device 1 used in the cooling system 91 mounted on the electric vehicle 90, when the refrigerant is not pressure-fed to the inflow / outflow passage 20 (the first inflow / outflow passage 21 to the eighth inflow / outflow passage 28) of the housing 2 (the upper housing 11 and the lower housing 12), the pressure in the housing internal space 7 provided between the housing 2 and the first rotating disk 13 and the second rotating disk 14 is released to the one sixth inflow / outflow passage 26 via the pressure adjustment hole 8, and the pressure in the housing internal space 7 is reduced. Therefore, the residual pressure in the housing internal space 7 does not press the rotating disks 13 and 14 toward the housing 2. Therefore, in the flow path switching device 1 used in the cooling system 91 mounted on the electric vehicle 90, it is possible to suppress the application of excessive load to the seal members 17 and 18 due to the residual pressure in the housing internal space 7.

[0106] According to the configuration of this embodiment, in a cooling system 91 including the electric pumps 97, 98, the pressure adjustment hole 8 is provided corresponding to the specific sixth inflow / outflow passage 26, which is in communication with the outlet of the first electric pump 97, among the multiple inflow / outflow passages 20 (the first inflow / outflow passage 21 to the eighth inflow / outflow passage 28). Therefore, when the first electric pump 97 is driven, the pressure in the housing internal space 7 is not released by the pressure adjustment hole 8, and when the first electric pump 97 is stopped, the pressure in the housing internal space 7 is reliably released by the pressure adjustment hole 8. Therefore, when the first electric pump 97 is stopped, it is possible to reliably prevent the application of excessive load to the seal members 17, 18 due to the residual pressure in the housing internal space 7.

[0107] According to the configuration of the cooling system 91 of this embodiment, the first electric pump 97, the outlet of which is connected to the specific sixth inflow / outflow passage 26, is constantly driven throughout all of the first to fifth switching patterns, so that the pressure from the first electric pump 97 always acts on the housing internal space 7 via the pressure adjustment hole 8. Therefore, the pressure in the housing internal space 7 can always be maintained at the pressure from the first electric pump 97.

[0108] According to the configuration of the cooling system 91 of this embodiment, in the cooling system 91 equipped with the electric pumps 97, 98, the flow path switching device 1 is provided such that only the predetermined first inflow / outflow passage 21 to fourth inflow / outflow passage 24 arranged in the upper housing 11 that accommodates the first rotating disk 13 can be communicated with the inlets (suction sides) of the electric pumps 97, 98. Therefore, in the first rotating disk 13 including the rotating passages 30 (first rotating passage 31, second rotating passage 32) that communicate with the predetermined first inflow / outflow passage 21 to fourth inflow / outflow passage 24, bias in the refrigerant pressure in the rotating passages 30 is reduced. Therefore, the inclination of the first rotating disk 13 including the rotating passages 30 that communicate with the predetermined first inflow / outflow passage 21 to fourth inflow / outflow passage 24 can be suppressed.

[0109] According to the configuration of this embodiment, in the cooling system 91, when the flow path switching device 1 switches the communication state of the first pipe 96A to the fourth pipe 96D (multiple small circuits), the control unit 5 stops driving the second electric pump 98 after the switching is completed. Therefore, when the rotating disks 13, 14 are driven to switch the communication state of the pipes 96A to 96D, the electric pumps 97, 98 are driven against the biasing force of the compression spring 61, so that the pressure of the refrigerant acts on the rotating flow paths 30, 40 of the rotating disks 13, 14. Therefore, when the rotating disks 13, 14 rotate, the surface pressure applied to the seal members 17, 18 can be reduced, the drive torque of the rotating disks 13, 14 can be reduced, and uneven wear of the seal members 17, 18 can be reduced.

[0110] <Second embodiment> The second embodiment will be described in detail with reference to Figures 32 to 35. In the following description, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof will be omitted, and differences will be mainly described.

[0111] In this embodiment, in addition to the configuration of the first embodiment, the following configuration is provided for the "countermeasures against crushing" of each of the seal members 17, 18. Fig. 32 shows the first rotating disk 13 in a plan view. Fig. 33 shows the first rotating disk 13 and a part of the upper housing 11 in an enlarged cross-sectional view taken along line HH in Fig. 32. Fig. 34 shows a part of the first rotating disk 13 in a cross-sectional view taken along line II in Fig. 33. Fig. 35 shows the first rotating disk 13 and a part of the upper housing 11 in an enlarged cross-sectional view equivalent to Fig. 33. Fig. 33 shows a state in which the first rotating disk 13 is not tilted, and Fig. 35 shows a state in which the first rotating disk 13 is tilted.

[0112] In the flow path switching pattern described in the first embodiment, in the first switching pattern, the second electric pump 98 is stopped. In this case, in the first rotating disc 13 shown in Fig. 32, the second rotation passage 32 communicates with the first electric pump 97 that is constantly driven, and the first rotation passage 31 communicates with the second electric pump 98 that is stopped. Therefore, in the first switching pattern, the first rotating disc 13 on the side of the first rotation passage 31 is likely to tilt toward the upper housing 11 (upper side in Figs. 33 to 35).

[0113] In this embodiment, an engagement protrusion 63 shown in FIGS. 33 to 35 is provided on the outer peripheral edge (outside the assembly groove 13e) of the upper surface of the first rotating disk 13 in the portion surrounded by a chain circle S1 in FIG. 32, that is, the surface on the side where the first seal member 17 protrudes toward the upper housing 11. This engagement protrusion 63 is provided so as to be able to engage with the inner surface of the upper housing 11 in order to regulate the reduction of the gap G1 between the upper housing 11 and the first rotating disk 13 in order to suppress excessive crushing of the first seal member 17. The upper surface of the engagement protrusion 63 is curved along the sliding direction (the left-right direction in FIG. 34) in order to reduce the sliding resistance with the upper housing 11. This engagement protrusion 63 corresponds to an example of a "regulation means" in this disclosed technology.

[0114] When the first rotating disc 13 tilts, this engagement protrusion 63 abuts against the inner surface of the upper housing 11 to prevent the first rotating disc 13 from tilting more than a certain amount, and regulates the gap G1 between the upper housing 11 and the first rotating disc 13 from being reduced more than necessary. As shown in Fig. 35, when the first rotating disc 13 tilts, the engagement protrusion 63 abuts against the inner wall of the upper housing 11, regulating the first rotating disc 13 from tilting any further.

[0115] Although not shown and not described, the second rotating disk 14 may also be provided with an engagement protrusion in a similar manner.

[0116] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the first embodiment, the following actions and effects can be obtained. That is, even if the first rotating disk 13 is tilted due to uneven refrigerant pressure in the rotating passage 30 of the first rotating disk 13, the engagement protrusion 63 restricts the reduction of the gap G1 between the first rotating disk 13 and the upper housing 11. Therefore, even if the first rotating disk 13 is tilted, excessive squeezing of the first seal member 17 between the first rotating disk 13 and the upper housing 11 can be suppressed, and the first seal member 17 can be suppressed from being worn down or worn unevenly. The same applies when the engagement protrusion is provided on the second rotating disk 14.

[0117] According to the configuration of this embodiment, even if each rotating disk 13 (14) were to tilt, the tilt of each rotating disk 13 (14) is restricted to less than a certain amount by contacting the inner surface of each housing 11 (12) with the "tilt suppression mechanism." Therefore, even if each part has manufacturing tolerances or deterioration, the tilt of each rotating disk 13 (14) can be sufficiently suppressed.

[0118] <Third embodiment> The third embodiment will be described in detail with reference to Figures 32 to 36. This embodiment is a modification of the second embodiment.

[0119] Fig. 36 shows a plan view of the first rotating disk 13. In the second embodiment, one engagement protrusion 63 is provided on the outer periphery of the upper surface of the first rotating disk 13 and outside the assembly groove 13e, as shown by solid lines in Fig. 33 to Fig. 35, in the portion shown by the chain circle S1 in Fig. 32. In contrast, one engagement protrusion 63 can also be provided on the upper surface of the first rotating disk 13, near the outer periphery, inside the assembly groove 13e, as shown by two-dot chain lines in Fig. 33 and Fig. 35.

[0120] In the second embodiment, as shown by a chain circle S1 in FIG. 32, one engagement protrusion 63 is provided on the outer peripheral edge of the upper surface of the first rotating disk 13, outside the assembly groove 13e. In contrast, as shown by chain circles S1 and S2 in FIG. 32, a pair of engagement protrusions 63 may be provided on the outer peripheral side of the first rotating passage 31 and the outer peripheral side of the second rotating passage 32, that is, on the same diameter of the outer peripheral edge of the first rotating disk 13. Furthermore, as shown by a chain circle S3 in FIG. 36, three engagement protrusions 63 may be provided at equal angular intervals on a part of the outer peripheral side of the first rotating passage 31, a part of the outer peripheral side of the second rotating passage 32, and at the boundary between the outer peripheral sides of the first rotating passage 31 and the second rotating passage 32, and on the outer peripheral edge of the upper surface of the first rotating disk 13. That is, a plurality of engagement protrusions 63 may be provided at two or more locations in the circumferential direction on the outer peripheral edge of the first rotating disk 13. The number of engagement protrusions 63 is preferably three or more.

[0121] Here, because the housing internal space 7 is sealed, when the electric pumps 97, 98 in the cooling system 91 stop, the pressure in the rotation passages 31, 32 drops to approximately atmospheric pressure, and the first rotating disk 13 is pressed toward the upper housing 11 by the pressure in the housing internal space 7, which may result in excessive crushing of the first seal member 17. By providing a plurality of engagement protrusions 63 on the outer periphery of the first rotating disk 13, it is possible to prevent the first seal member 17 from being crushed even when the electric pumps 97, 98 stop.

[0122] Although not shown and not described, the second rotating disk 14 may also be provided with an engagement protrusion in a similar manner.

[0123] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, it is possible to obtain the same functions and effects as those of the second embodiment.

[0124] <Fourth embodiment> The fourth embodiment will be described in detail with reference to FIG.

[0125] [Configuration of flow path switching device] In this embodiment, the flow path switching device 1 is different from the above-mentioned embodiments in terms of the configuration. FIG. 37 shows the flow path switching device 1 of this embodiment in a cross-sectional view similar to FIG. 16. As shown in FIG. 37, the first and second rotational passages 31, 32 formed in the first rotating disk 13 are formed in the shape of long holes extending in an arc along the rotation trajectory of the first rotating disk 13 with the rotation shaft 15 as the center. In this embodiment, unlike the above-mentioned embodiments (see FIG. 16), the first protrusion 15c and the second protrusion 15d are arranged toward the center of the arc of each of the rotational passages 31, 32. The direction from the rotation shaft 15 toward the center of the arc of each of the rotational passages 31, 32 is the direction in which the first rotating disk 13 is likely to tilt when a difference in internal pressure occurs between the rotational passages 31, 32.

[0126] Although not shown and not described, the second rotating disk 14 can also be configured in the same manner as the first rotating disk 13.

[0127] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the above-mentioned embodiments, the following actions and effects can be obtained. That is, in this embodiment, the rotational force of the rotating shaft 15 is transmitted to the rotating disks 13, 14 by the protrusions 15c, 15d, and the rotating disks 13, 14 rotate. The protrusions 15c, 15d of the rotating shaft 15 are arranged toward the center of the arc of the two rotating passages 30, 40 that extend in an arc shape around the rotating shaft 15 on the rotating disks 13, 14. Therefore, the rotating disks 13, 14 are engaged with and supported by the protrusions 15c, 15d toward the center of the arc of the rotating passages 30, 40. Therefore, even if the refrigerant pressure in the rotating passages 30, 40 is biased and the rotating disks 13, 14 start to tilt, the tilt of the rotating disks 13, 14 can be suppressed, and the wear and uneven wear of the seal members 17, 18 can be suppressed.

[0128] <Fifth embodiment> The fifth embodiment will be described in detail with reference to FIG.

[0129] [Configuration of flow path switching device] In this embodiment, the flow path switching device 1 is different from the fourth embodiment in terms of the configuration. FIG. 38 shows the flow path switching device 1 of this embodiment in a cross-sectional view similar to FIG. 7. In this embodiment, the first rotating disk 13 includes a rotating passage 30 (first rotating passage 31, second rotating passage 32) that forms a higher pressure flow path, and the second rotating disk 14 includes a rotating passage 40 (third rotating passage 43, fourth rotating passage 44) that forms a lower pressure flow path than the rotating passage 30 in FIG. Also, in this embodiment, in the cooling system 91, in the first switching pattern (see FIG. 21), a difference in refrigerant pressure occurs between the first rotating passage 31 and the second rotating passage 32, so that the inclination of the first rotating disk 13 tends to be large. Therefore, in this embodiment, the hole length LH of the first axial hole 13a of the first rotating disk 13 on the high pressure side is set longer than the hole length LL of the second axial hole 14a of the second rotating disk 14 on the low pressure side.

[0130] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the second and third embodiments, the following actions and effects can be obtained. That is, in this embodiment, of the first rotating disk 13 and the second rotating disk 14, the first rotating disk 13 including the rotating passage 30 forming a higher pressure flow path is more likely to tilt than the second rotating disk 14. According to the configuration of this embodiment, the hole length LH of the first shaft hole 13a of the first rotating disk 13 is longer than the hole length LL of the second shaft hole 14a of the second rotating disk 14, so that the angle at which the first shaft hole 13a is allowed to tilt with respect to the rotating shaft 15 is smaller than that of the second shaft hole 14a. Therefore, the tilt of the first rotating disk 13, which is easily tilted, can be suppressed, and the wear and uneven wear of the first seal member 17 can be suppressed.

[0131] According to the configuration of this embodiment, the hole length LH of the first shaft hole 13a of the first rotating disk 13 on the high pressure side is made longer than the hole length LL of the second shaft hole 14a of the second rotating disk 14 on the low pressure side, so that the inclination of the rotating shaft 15 is suppressed by the grounding of the rotating shaft 15 and each shaft hole 13a, 14a. In this embodiment, in FIG. 38, the closer to the bearing 51, the smaller the swing range of the inclination of the rotating shaft 15 becomes, so the first rotating disk 13 on the high pressure side is disposed on the side closer to the bearing 51. Here, in a state where the engagement protrusion 63 provided on the upper surface of the first rotating disk 13 is in contact with the upper housing 11, when the first rotating disk 13 starts to rotate, the engagement protrusion 63 slides on the inner surface of the upper housing 11. In this embodiment, the inclination of the rotating shaft 15 is suppressed by the relationship between the rotating shaft 15 and the first shaft hole 13a with the long hole length LH, so that friction is unlikely to occur when the first rotating disk 13 rotates. However, when the first rotating disc 13 moves up and down in the axial direction, sliding occurs.

[0132] Sixth embodiment The sixth embodiment will be described in detail with reference to FIG.

[0133] [Configuration of flow path switching device] In this embodiment, the configuration of the flow path switching device 1 is different from that of the fifth embodiment. FIG. 39 shows the flow path switching device 1 of this embodiment in a cross-sectional view similar to FIG. 7. In the fifth embodiment, in order to suppress the tilt of the first rotating disk 13, the hole length LH of the first axial hole 13a of the first rotating disk 13 on the high pressure side is set longer than the hole length LL of the second axial hole 14a of the second rotating disk 14 on the low pressure side. In contrast, in this embodiment, in order to suppress the tilt of the first rotating disk 13, unlike the fifth embodiment, the radial clearance between the first axial hole 13a of the first rotating disk 13 and the rotating shaft 15 is set smaller than the radial clearance between the second axial hole 14a of the second rotating disk 14 and the rotating shaft 15. Specifically, in this embodiment, the hole length of the first shaft hole 13a and the hole length of the second shaft hole 14a are set to be the same, and then a metal sleeve 65 is insert molded into the inner circumference of the first shaft hole 13a, thereby making the radial clearance between the inner circumference of the first shaft hole 13a and the outer circumference of the rotating shaft 15 smaller.

[0134] [About 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, in addition to the actions and effects of the second and third embodiments, the following actions and effects can be obtained. That is, in this embodiment, of the first rotating disk 13 and the second rotating disk 14, the first rotating disk 13 including the rotating passage 30 forming the higher pressure flow path is more likely to tilt than the second rotating disk 14. According to the configuration of this embodiment, the radial clearance between the first shaft hole 13a of the first rotating disk 13 and the rotating shaft 15 is smaller than the radial clearance between the second shaft hole 14a of the second rotating disk 14 and the rotating shaft 15, so that the angle at which the first shaft hole 13a is allowed to tilt with respect to the rotating shaft 15 is smaller than that of the second shaft hole 14a. Therefore, the tilt of the first rotating disk 13, which is easily tilted, can be suppressed, and the wear and uneven wear of the first seal member 17 can be suppressed.

[0135] According to the configuration of this embodiment, the first shaft hole 13a is formed of a metal sleeve 65, thereby reducing the radial clearance between the rotating shaft 15 and the first shaft hole 13a due to the reduced product tolerance and temperature difference, and thus suppressing the inclination of the rotating shaft 15. In this embodiment, it is possible to form the second shaft hole 14a with a metal sleeve as well, but this can be omitted since it would increase costs. Also, the configuration of this embodiment can be combined with the configuration of the fifth embodiment. That is, the first shaft hole 13a, which has a long hole length LH, can be formed with a metal sleeve 65.

[0136] Seventh embodiment The seventh embodiment will be described in detail with reference to FIGS.

[0137] This embodiment differs from the first to fourth embodiments in the configuration of each seal member 17, 18. In the first to fourth embodiments, in the cooling system 91, the first inflow / outflow passage 21 to the fourth inflow / outflow passage 24 on the low pressure side connected to the inlets (suction sides) of the electric pumps 97, 98 are provided in the upper housing 11, that is, on the side of the first rotating disk 13, and are concentrated therein. Also, the fifth inflow / outflow passage 25 to the eighth inflow / outflow passage 28 on the high pressure side connected to the outlets (discharge sides) of the electric pumps 97, 98 are provided in the lower housing 12, that is, on the side of the second rotating disk 14, and are concentrated therein. Therefore, in the upper housing 11 on the low pressure side, the pressing load of the upper seal member 17 due to the internal pressure of the housing internal space 7 becomes large.

[0138] [About the composition of the sealing material] Therefore, in this embodiment, the seal members 17, 18 are configured as follows: That is, in the flow path switching device 1 of this embodiment, the material of each of the seal members 17, 18 is set so that the first seal member 17 provided in the upper housing 11 in which the predetermined first inflow / outflow passage 21 to fourth inflow / outflow passage 24 are arranged has a higher hardness or spring constant than the second seal member 18 provided in the lower housing 12 in which the other fifth inflow / outflow passage 25 to eighth inflow / outflow passage 28 are arranged.

[0139] For example, the softer the rubber seal member is, the larger the displacement amount is with respect to the load. Therefore, a seal member with low hardness is more likely to wear out than a seal member with high hardness even under the same load. As the load increases, the displacement amount increases and the wear progresses. FIG. 40 is a graph showing the relationship between the hardness of the seal member and the load required to achieve zero leakage. As shown in FIG. 40, as the hardness of the seal member increases, the zero leakage load also increases. In this embodiment, the pressing load of the first seal member 17 due to the internal pressure of the housing space 7 is increased by the amount of the load. For example, if low pressure and high pressure are mixed between the rotation passages 31 and 32 of the first rotating disk 13, it becomes difficult to distinguish the hardness of the first seal member 17. In this embodiment, the high pressure side and the low pressure side are completely separated between the upper housing 11 and the lower housing 12, so that it is easy to change the hardness between the seal members 17 and 18.

[0140] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the first embodiment, the following actions and effects can be obtained. That is, in this flow path switching device 1, the housing internal space 7 of the upper housing 11 in which the predetermined third inflow / outflow passage 23 that can be communicated with the inlet (suction side) of the first electric pump 97 and the predetermined second inflow / outflow passage 22 that can be communicated with the inlet (suction side) of the second electric pump 98 are arranged is at a low pressure close to atmospheric pressure. Therefore, the pressing load of the first seal member 17 on the upper housing 11 due to the pressure of this low-pressure housing internal space 7 is large. According to the configuration of this embodiment, the first seal member 17 corresponding to the upper housing 11 in which the housing internal space 7 is at a low pressure has a higher hardness or spring constant than the second seal member 18 corresponding to the lower housing 12 in which the other fifth inflow / outflow passage 25 to eighth inflow / outflow passage 28 are arranged, so that the first seal member 17 corresponding to the upper housing 11 is less likely to be displaced by the load. This makes it possible to suppress wear and uneven wear of the first seal member 17 corresponding to the upper housing 11 in which the predetermined first through fourth inlet / outlet passages 21 to 24 that can communicate with the inlets of the electric pumps 97, 98 are arranged.

[0141] In this embodiment, the materials of the seal members 17, 18 are set so that the first seal member 17 has a higher hardness or spring constant than the second seal member 18. In contrast, the shapes and dimensions of the seal members 17, 18 may be changed so that the first seal member 17 has a higher spring constant than the second seal member 18. For example, the second seal member 18 on the high pressure side may be formed to have an M-shaped cross section as shown in FIG. 41, and the first seal member 17 on the low pressure side may be formed of an O-ring having a circular cross section as shown in FIG. 42. FIGS. 41 and 42 show the seal members 17, 18, etc., in cross sections similar to FIG. 17.

[0142] Eighth embodiment The eighth embodiment will be described in detail with reference to FIG.

[0143] In the seventh embodiment, in the low-pressure side upper housing 11, the configuration of only the seal members 17, 18 was changed to address the problem of increased pressing load on the upper seal member 17 due to the internal pressure of the housing internal space 7. In this embodiment, to address the same problem, the configuration of the flow path switching device 1 is changed as follows.

[0144] [Changes to the configuration of the flow switching device] Fig. 43 shows a flow path switching device 9 of this embodiment in a cross-sectional view equivalent to Fig. 7. Unlike the flow path switching device 1, this flow path switching device 9 includes a partition plate 66 fixed on a rotating shaft 15 and disposed between the first rotating disk 13 and the second rotating disk 14, a first compression spring 61A (first elastic member) that urges the partition plate 66 and the first rotating disk 13 in a direction separating them from each other, and a second compression spring 61B (second elastic member) that urges the partition plate 66 and the second rotating disk 14 in a direction separating them from each other.

[0145] In this embodiment, the first compression spring 61A provided corresponding to the low-pressure side upper housing 11 in which the predetermined first inflow / outflow passage 21 to fourth inflow / outflow passage 24 are arranged has a smaller spring constant than the second compression spring 61B provided corresponding to the high-pressure side lower housing 12 in which the other fifth inflow / outflow passage 25 to eighth inflow / outflow passage 28 are arranged. Although one each of the compression springs 61A, 61B is illustrated in Fig. 43, a plurality of each of the compression springs 61A, 61B is provided.

[0146] As described above, in this embodiment, the spring constant of the first compression spring 61A that presses the first rotating disk 13 against the upper housing 11 is set smaller than the spring constant of the second compression spring 61B that presses the second rotating disk 14 against the lower housing 12, thereby reducing the surface pressure difference between the first seal member 17 and the second seal member 18. For this purpose, a partition plate 66 that rotates together with the rotating disks 13 and 14 is provided between the two rotating disks 13 and 14, so that the compression forces of the compression springs 61A and 61B act separately on the first rotating disk 13 and the second rotating disk 14, respectively. The spring constant of the first compression spring 61A corresponding to the first rotating disk 13 of the upper housing 11 on the low pressure side is set smaller than the spring constant of the second compression spring 61B for the second rotating disk 14 of the lower housing 12 on the high pressure side.

[0147] [About 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, in addition to the actions and effects of the first embodiment, the following actions and effects can be obtained. That is, in this flow path switching device 1, a first compression spring 61A is arranged on the rotating shaft 15 between the first rotating disk 13 and the partition plate 66 to urge both the first rotating disk 13 and the partition plate 66 in the direction separating them, and a second compression spring 61B is arranged between the second rotating disk 14 and the partition plate 66 to urge both the first rotating disk 13 and the partition plate 66 in the direction separating them. Here, the pressing load of the first compression spring 61A on the first seal member 17 for the upper housing 11 in which the housing space 7 is at low pressure becomes large. According to the configuration of this embodiment, the spring constant of the first compression spring 61A corresponding to the upper housing 11 in which the housing space 7 is at low pressure is smaller than that of the second compression spring 61B corresponding to the lower housing 12, so that the first seal member 17 provided for the upper housing 11 is less likely to be displaced by the load of the first compression spring 61A. This makes it possible to suppress wear and uneven wear of the first seal member 17 corresponding to the low-pressure side upper housing 11 in which the specified second and third inlet / outlet passages 22, 23 that can communicate with the inlets of each electric pump 97, 98 are arranged.

[0148] Unlike this embodiment, when the upper housing 11 is the high pressure side and the lower housing 12 is the low pressure side, the spring constant of the second compression spring 61B provided in the lower housing 12 on the low pressure side can be set to be smaller than the spring constant of the first compression spring 61A provided in the upper housing 11 on the high pressure side.

[0149] <Ninth embodiment> The ninth embodiment will be described in detail with reference to Figures 43 and 44. This embodiment is a modified example in which a part of the eighth embodiment is changed.

[0150] In the flow path switching device 9 of the eighth embodiment, the rotating shaft 15 and the partition plate 66 move up and down integrally, so if the biasing force of the first compression spring 61A is greater than the biasing force of the second compression spring 61B, a downward stress acts on the rotating shaft 15, and a downward stress is applied to the bearing 51 press-fitted and fixed to the upper part of the rotating shaft 15, which may cause uneven wear and locking of the bearing 51. Therefore, in this embodiment, the configuration of the flow path switching device 9 is changed as follows.

[0151] [Changes to the configuration of the flow switching device] FIG. 44 shows a cross-sectional view of a bearing structure provided at the lower end of the rotating shaft 15. This bearing structure is provided between the lower end of the rotating shaft 15 and the shaft hole 12a of the lower housing 12 in order to restrict the downward movement of the rotating shaft 15 in the portion surrounded by a two-dot chain line rectangle S4 in FIG. 43. This bearing structure includes a thrust bearing 69 provided between the lower end of the rotating shaft 15 and the shaft hole 12a of the lower housing 12, and a spring 70 provided between the thrust bearing 69 and the bottom surface of the shaft hole 12a. The thrust bearing 69 is plate-shaped and is disposed in the shaft hole 12a so as to contact the lower end of the rotating shaft 15. The thrust bearing 69 urges the rotating shaft 15 upward by the spring 70.

[0152] [About 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, in addition to the actions and effects of the eighth embodiment, the following actions and effects can be obtained: That is, according to the configuration of the flow path switching device 9 of this embodiment, even if a downward stress acts on the rotating shaft 15, the stress is absorbed by the thrust bearing 69, so that the downward stress acting on the bearing 51 provided on the upper part of the rotating shaft 15 can be alleviated, and uneven wear and locking of the bearing 51 can be suppressed.

[0153] Here, since the first rotating disk 13 is pressed against the upper housing 11 by the first compression spring 61A, a stress acts on the rotating shaft 15 in the upward direction. For this reason, it is necessary to provide a function for suppressing the movement of the rotating shaft 15 on the side of the upper housing 11. However, in this case, the structure for suppressing the movement of the rotating shaft 15 must be provided at the upper end of the rotating shaft 15, i.e., on the side of the drive unit 4, and it is desirable to provide it in the lower housing 12 in terms of space. In this embodiment, the thrust bearing 69 is provided in the lower housing 12, which is advantageous in terms of space. Furthermore, since the thrust bearing 69 is disposed in the refrigerant in the lower housing 12, the refrigerant can also be used as a lubricant for the thrust bearing 69.

[0154] The thrust bearing 69 may be changed to a thrust ball bearing that is rotatable via a plurality of metal balls.

[0155] Tenth embodiment The tenth embodiment will be described in detail with reference to Fig. 45. This embodiment is a modification of the fourth embodiment.

[0156] [Regarding the shape of the sealing material] This embodiment differs from the above-described embodiments mainly in the shapes of the rotation passages and the seal members provided in the respective rotating disks 13 and 14. Fig. 45 shows the first rotating disk 13 according to this embodiment in a plan view similar to Fig. 32. As shown in Fig. 45, two assembly grooves 13e are formed on the upper surface of the first rotating disk 13 so as to surround the periphery of the openings of the two rotation passages 30 (the first rotation passage 31 and the second rotation passage 32), and a first seal member 57 is fitted and fixed in the assembly grooves 13e.

[0157] In each of the above-described embodiments, as shown in Fig. 10 and Fig. 13, each of the seal members 17 and 18 has an annular shape and includes an inner circular portion 17a or 18a, an outer circular portion 17b or 18b, and partition portions 17c, 17d, 18c, and 18d. Each of the seal members 17 and 18 has two semicircular seal regions surrounded by the partition portions 17c, 17d, 18c, and 18d, the inner circular portions 17a and 18a, and the outer circular portions 17b and 18b, and the two seal regions are arranged symmetrically with respect to the partition portions 17c, 17d, 18c, and 18d as an axis of symmetry.

[0158] 45, in this embodiment, two first seal members 57 are provided for the first rotating disk 13, and have a track shape (hereinafter referred to as "cocoon shape") curved in the circumferential direction of the disk 13. The cocoon shape of the first seal members 57 matches the opening shapes of the two rotation passages 30 formed in the first rotating disk 13 in this embodiment, and the two assembly grooves 13e formed along the peripheries of the two rotation passages 30 also have a "cocoon shape."

[0159] In this embodiment, as shown in FIG. 45, the two rotation passages 30 formed in the first rotating disk 13 are formed as long holes extending in an arc shape along the rotation trajectory of the first rotating disk 13 with the rotation shaft 15 as the center. As in the fourth embodiment (see FIG. 37), the first protrusion 15c and the second protrusion 15d are disposed toward the center of the arc of each rotation passage 30. In this embodiment, the outer edge length of the first protrusion 15c is set longer than that of the second protrusion 15d. In this embodiment, two shaft hole recesses 13ja, 13jb that can be engaged with the protrusions 15c, 15d are formed on the inner circumference of the first shaft hole 13a of the first rotating disk 13. The outer edges of the protrusions 15c, 15d are formed in an arc shape, but may also be formed in a straight line.

[0160] Although not shown and not described, the rotation passage, assembly groove, each protrusion, second seal member, etc. provided on the second rotating disk 14 are also the same as those of the first rotating disk 13.

[0161] [About 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, the same action and effect as those of the fourth embodiment can be obtained. That is, in this embodiment, the rotational force of the rotating shaft 15 is transmitted to the rotating disks 13, 14 by the protrusions 15c, 15d, and the rotating disks 13, 14 rotate. The protrusions 15c, 15d of the rotating shaft 15 are arranged toward the center of the arc of the two rotating passages 30, 40 that extend in an arc shape around the rotating shaft 15 on the rotating disks 13, 14. Therefore, the rotating disks 13, 14 are engaged with and supported by the protrusions 15c, 15d toward the center of the arc of the rotating passages 30, 40. Therefore, even if the refrigerant pressure in the rotating passages 30, 40 is biased and the rotating disks 13, 14 start to tilt, the tilt of the rotating disks 13, 14 can be suppressed, and the wear and uneven wear of the seal members 17, 18 can be suppressed.

[0162] <Eleventh embodiment> The eleventh embodiment will be described in detail with reference to Fig. 46. This embodiment is a modification of the tenth embodiment.

[0163] [About the configuration of the rotating disk] This embodiment differs from the tenth embodiment mainly in the number of rotational passages and seal members provided in each of the rotating disks 13 and 14. Fig. 46 shows a plan view of the first rotating disk 13. In this embodiment, the first rotating disk 13 is provided with three rotational passages 30 (the first rotational passage 31, the second rotational passage 32, and the third rotational passage 33) and three first seal members 57, etc., which differs from the tenth embodiment in that two rotational passages 30 and two first seal members 57 are provided.

[0164] In this embodiment, as shown in FIG. 46, the three rotation passages 30 provided in the first rotating disk 13 are elongated (cocoon-shaped) holes extending in an arc shape around the rotating shaft 15. A first protrusion 15c, a second protrusion 15d, and a third protrusion 15e are provided around the rotating shaft 15, and these protrusions 15c to 15e are arranged toward the center of the arc of each of the three rotation passages 30. In this embodiment, the outer edge lengths of the protrusions 15c to 15e are the same. In this embodiment, three shaft hole recesses 13ja, 13jb, and 13jc that can be engaged with the protrusions 15c to 15e are formed on the inner circumference of the first shaft hole 13a. The number of the rotation passages 30 and the first seal members 57 may be three or more.

[0165] Although not shown and not described, the rotation passage, assembly groove, each protrusion, second seal member, etc. provided on the second rotating disk 14 are also the same as those of the first rotating disk 13.

[0166] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, although the number of rotating passages 30, 40 and the number of sealing members 57 provided in each rotating disk 13, 14 are different, the same effect and advantages as those of the tenth embodiment can be obtained in terms of the function of suppressing the tilt of each rotating disk 13, 14.

[0167] <Twelfth embodiment> The twelfth embodiment will be described in detail with reference to Figures 47 and 48. This embodiment is a modification of the tenth and eleventh embodiments.

[0168] [Configuration of flow path switching device] Fig. 47 shows a plan view of the first rotating disc 13 provided with two rotation passages 30, etc. Fig. 48 shows a plan view of the first rotating disc 13 provided with three rotation passages 30, etc. This embodiment differs from the tenth and eleventh embodiments in that the arrangement of multiple compression springs 61 provided between the first rotating disc 13 and the second rotating disc 14 and the orientation of each of the protrusions 15c-15e of the rotating shaft 15 are adjusted so as to suppress tilt of the first rotating disc 13 in accordance with the internal pressure difference between the multiple rotation passages 30 (first rotation passage 31 to third rotation passage 33) of the first rotating disc 13.

[0169] For example, as shown in Fig. 47, in a type in which the first rotating disk 13 has two rotating passages 31 and 32, when the first rotating passage 31 is at high pressure and the second rotating passage 32 is at a medium pressure slightly lower than the high pressure, in addition to the configuration of the tenth embodiment, the rubber hardness of the first seal member 17 corresponding to the second rotating passage 32 at medium pressure is set to be greater than the rubber hardness of the first seal member 17 corresponding to the first rotating passage 31 at high pressure. Also, when the internal pressure difference between the first rotating passage 31 and the second rotating passage 32 becomes large, a compression spring 61 is disposed corresponding to the center of the arc of each rotating passage 31 and 32. In addition, the biasing force of the compression spring 61 corresponding to the second rotating passage 32 at medium pressure is set to be greater than the biasing force of the compression spring 61 corresponding to the first rotating passage 31 at high pressure.

[0170] 48, in the case where the first rotating disk 13 has three rotation passages 31-33 and the third rotation passage 33 is at high pressure, the second rotation passage 32 is at medium pressure, and the first rotation passage 31 is at low pressure, in addition to the configuration of the eleventh embodiment, the rubber hardness of the first seal member 17 corresponding to the first rotation passage 31 at low pressure is set to be greater than the rubber hardness of the first seal member 17 corresponding to the second rotation passage 32 at medium pressure, and the rubber hardness of the first seal member 17 corresponding to the second rotation passage 32 at medium pressure is set to be greater than the rubber hardness of the first seal member 17 corresponding to the third rotation passage 33 at high pressure. In addition, when the internal pressure difference between the rotation passages 31-33 becomes larger, a compression spring 61 is arranged corresponding to the center of the arc of each of the rotation passages 31-33. In addition, the biasing force of the compression spring 61 corresponding to the first rotation passage 31, which is a low pressure, is set to be greater than the biasing force of the compression spring 61 corresponding to the second rotation passage 32, which is a medium pressure, and the rubber hardness of the first seal member 17 corresponding to the second rotation passage 32, which is a medium pressure, is set to be greater than the rubber hardness of the first seal member 17 corresponding to the third rotation passage 33, which is a high pressure.

[0171] Although not shown and not described, the rubber hardness of the second seal member 18 provided on the second rotating disk 14 and the biasing force of the compression spring 61 are also the same as those of the first rotating disk 13.

[0172] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, it is possible to obtain the same functions and effects as those of the tenth and eleventh embodiments.

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

[0174] [About the configuration of the shaft hole of the rotating disk] This embodiment differs from the tenth to twelfth embodiments in the configuration of each of the shaft holes 13a, 14a of the rotating disks 13, 14. Fig. 49 shows a plan view of the first rotating disk 13 when stopped in a counterclockwise direction. Fig. 50 shows an enlarged plan view of a portion including the first shaft hole 13a in Fig. 49. Fig. 51 shows a plan view of the first rotating disk 13 when stopped in a clockwise direction. Fig. 52 shows an enlarged plan view of a portion including the first shaft hole 13a in Fig. 51.

[0175] In this embodiment, as shown in Figs. 49 to 52, the first rotating disk 13 has two rotation passages 30 (first rotation passage 31, second rotation passage 32) arranged symmetrically with respect to a virtual axis of symmetry A1 passing through the center of the rotating disk 13. The first rotating disk 13 has contact surfaces 13ka, 13kb, 13kc, and 13kd in the first shaft hole 13a, which can contact the respective protrusions 15c and 15d. Here, among the contact surfaces 13ka, 13kb, 13kc, and 13kd, the contact surfaces 13kb and 13kc are parallel to the axis of symmetry A1 and can contact the respective protrusions 15c and 15d. In this embodiment, as shown in Figs. 50 and 52, two inner surfaces extending in the radial direction of one shaft hole recess 13ja are the contact surfaces 13ka and 13kb. Also, two radially extending inner surfaces of the other shaft hole recess 13jb are contact surfaces 13kc, 13kd. In this embodiment, the contact surfaces 13ka to 13kd correspond to an example of the "contact portion" of the disclosed technology. In this embodiment, the first protrusion 15c of the rotating shaft 15 has contact surfaces 15fa, 15fb extending in the radial direction, and the second protrusion 15d has contact surfaces 15fc, 15fd extending in the radial direction.

[0176] In this embodiment, in order to transmit the counterclockwise rotation of the rotating shaft 15 to the first rotating disk 13, the abutment surfaces 13ka to 13kd of each shaft hole recess 13ja, 13jb are arranged so that, in Figures 49 and 50, the abutment surfaces 13kb, 13kc parallel to the axis of symmetry A1 abut against one of the abutment surfaces 15fb, 15fc extending radially of each protrusion 15c, 15d.

[0177] 51 and 52, in this embodiment, the contact surfaces 13ka to 13kd are configured to contact one contact surface 15fa, 15fd extending in the radial direction of each of the protrusions 15c, 15d in order to transmit the clockwise rotation of the rotating shaft 15 to the first rotating disk 13. In this embodiment, the contact surfaces 13ka to 13kd correspond to an example of the "contact portion" of this disclosed technology.

[0178] Although not shown and not described, the second axial hole 14 a of the second rotating disk 14 has a configuration similar to that of the first rotating disk 13 .

[0179] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, in addition to the actions and effects of the third embodiment, the following actions and effects are obtained. That is, according to the configuration of this embodiment, the rotation passage 30 of the first rotating disk 13 is arranged line-symmetrically with respect to the symmetry axis A1, and the rotating disk 13 has contact surfaces 13kb, kc that are parallel to the symmetry axis A1 and can contact the respective protrusions 15c, 15d. Therefore, when the rotating shaft 15 stops rotating counterclockwise, the respective protrusions 15c, 15d of the rotating shaft 15 contact the contact surfaces 13Kb, 13kc of the first rotating disk 13, and the contact acts as a resistance against the inclination of the first rotating disk 13 in a direction perpendicular to the symmetry axis A1 of the rotating passage 30. Therefore, the inclination of the first rotating disk 13 in a direction perpendicular to the symmetry axis A1 of the rotating passage 30 can be suppressed, and the wear and uneven wear of the first seal member 17 can be suppressed.

[0180] Here, as shown in Figures 49 and 50, when the first rotating disk 13 stops in the counterclockwise direction, one of the contact surfaces 15fb, 15fc of each of the protrusions 15c, 15d contacts the contacted surfaces 13kb, 13kc of each of the shaft hole recesses 13ja, 13jb. As a result, the contact surfaces 15fb, 15fc and the contacted surfaces 13kb, 13kc push against each other in a direction that suppresses the tilt of the first rotating disk 13 toward the orthogonal axis B1 that intersects the symmetrical axis A1 at a right angle in Figure 49 and passes through the center of the first rotating disk 13. The same applies to the second rotating disk 14.

[0181] On the other hand, as shown in Figures 51 and 52, when the first rotating disk 13 stops in the clockwise direction, a circumferential gap 16 is generated between the other abutment surfaces 15fb, 15fc of the protrusions 15c, 15d and the abutted surfaces 13kb, 13kc of the shaft hole recesses 13ja, 13jb. Therefore, in Figure 51, the effect of suppressing the tilt of the first rotating disk 13 in the direction of the orthogonal axis B1 is reduced due to the presence of the gap 16. However, since the other abutment surfaces 15fa, 15fd are in contact with the abutted surfaces 13ka, 13kd, the tilt of the first rotating disk 13 can be suppressed.

[0182] When the first rotating disk 13 is stopped in the clockwise direction, the gap 16 reduces the effect of suppressing the inclination of the first rotating disk 13, but when the first rotating disk 13 is stopped in the clockwise direction, the rotating shaft 15 is rotated counterclockwise by the angle of the gap 16 and then stopped. This allows the contact surfaces 15fb, 15fc to contact the contacted surfaces 13kb, 13kc even after the clockwise rotation, and provides the effect of suppressing the inclination of the first rotating disk 13 in the direction of the orthogonal axis B1.

[0183] Although illustration and description are omitted, the second rotating disk 14 can also provide the same functions and effects as the first rotating disk 13.

[0184] <Fourteenth embodiment> The fourteenth embodiment will be described in detail with reference to Figures 53 and 54. This embodiment is a modification of the thirteenth embodiment.

[0185] [Configuration of the rotating disk shaft hole and rotating shaft] This embodiment differs from the thirteenth embodiment in the configuration of the shaft holes 13a, 14a of the rotating disks 13, 14 and the rotating shaft 15. Fig. 53 shows an enlarged plan view equivalent to Fig. 50 of a portion including the first shaft hole 13a of the first rotating disk 13 when stopped in the counterclockwise direction. Fig. 54 shows an enlarged plan view equivalent to Fig. 52 of a portion including the first shaft hole 13a of the first rotating disk 13 when stopped in the clockwise direction.

[0186] In this embodiment, as shown in Figures 53 and 54, the first rotating disk 13 has contact surfaces 13ka, 13kb, 13kc, and 13kd in the first shaft hole 13a, which are parallel to the symmetry axis A1 and can contact the protrusions 15c and 15d. In this embodiment, of the two shaft hole recesses 13ja and 13jb, in Figures 53 and 54, the two inner surfaces extending in the radial direction of the left shaft hole recess 13ja are the contact surfaces 13ka and 13kb, and the two inner surfaces extending in the radial direction of the right shaft hole recess 13jb are the contact surfaces 13kc and 13kd.

[0187] 53, when the counterclockwise rotation of the rotating shaft 15 is transmitted to the first rotating disk 13, the lower abutment surface 15fb of the two abutment surfaces 15fa, 15fb extending radially of the first protrusion 15c abuts against the lower abutted surface 13kb, and the upper abutment surface 15fc of the two abutment surfaces 15fc, 15fd extending radially of the second protrusion 15d abuts against the upper abutted surface 13kc. A gap 16 is formed in the circumferential direction between the upper abutment surface 15fa of the two abutment surfaces 15fa, 15fb of the first protrusion 15c and the upper abutted surface 13ka, and a gap 16 is also formed in the circumferential direction between the lower abutment surface 15fd of the second protrusion 15d and the lower abutted surface 13kd.

[0188] 54, when the clockwise rotation of the rotating shaft 15 is transmitted to the first rotating disk 13, the upper contact surface 15fa of the first protrusion 15c contacts the upper contacted surface 13ka, and the lower contact surface 15fd of the second protrusion 15d contacts the lower contacted surface 13kd. Of the two contact surfaces 15fa, 15fb of the first protrusion 15c, a gap 16 is formed in the circumferential direction between the lower contact surface 15fb and the lower contacted surface 13kb, and a gap 16 is also formed in the circumferential direction between the upper contact surface 15fc of the second protrusion 15d and the upper contacted surface 13kc.

[0189] Although not shown and not described, the second axial hole 14 a of the second rotating disk 14 has a configuration similar to that of the first rotating disk 13 .

[0190] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, for the first rotating disk 13 and the second rotating disk 14, the abutment surfaces 13ka to 13kd parallel to the symmetry axis A1 of each shaft hole recess 13ja, 13jb abut against the abutment surfaces 15fa to 15fd of each protrusion 15c, 15d, so that the inclination of each rotating disk 13, 14 can be suppressed by the abutment at two points both when each rotating disk 13, 14 is stopped in the counterclockwise direction and when each rotating disk 13, 14 is stopped in the clockwise direction.

[0191] <Fifteenth embodiment> The fifteenth embodiment will be described in detail with reference to Figures 55 to 57. This embodiment is a modification of the fourteenth embodiment.

[0192] [Configuration of the rotating disk shaft hole and rotating shaft] This embodiment differs from the 14th embodiment in the configuration of the shaft holes 13a, 14a of the rotating disks 13, 14 and the rotating shaft 15. Fig. 55 shows an enlarged plan view equivalent to Fig. 53 of a portion including the first shaft hole 13a of the first rotating disk 13 when stopped in a counterclockwise direction according to this embodiment. Fig. 56 shows an enlarged plan view of a portion of the first shaft hole 13a in Fig. 55. Fig. 57 shows an enlarged plan view equivalent to Fig. 54 of a portion including the first shaft hole 13a of the first rotating disk 13 when stopped in a clockwise direction according to this embodiment.

[0193] In the fourteenth embodiment, the first rotating disk 13 has contact surfaces 13ka to 13kd that can contact the protrusions 15c and 15d, which are provided in the first shaft hole 13a and are parallel to the symmetrical axis A1 (the same applies to the second rotating disk 14). As a result, the contact surfaces (ground surfaces) of the rotating disks 13 and 14 and the rotating shaft 15 are parallel to each other, so that the contact stress does not press the rotating disks 13 and 14 toward the rotating shaft 15. Therefore, when the rotating disks 13 and 14 are stopped from rotating, if the power transmission stress of the rotating shaft 15 to the rotating disks 13 and 14 is released, there is a concern that the rotating disks 13 and 14 may be easily separated from the contact surfaces 15fa to 15fd of the protrusions 15c and 15d of the rotating shaft 15.

[0194] Therefore, in this embodiment, as shown in Figures 55 and 56, the contact surfaces 13ka-13kd that can contact the protrusions 15c, 15d are provided in the first shaft hole 13a of the first rotating disk 13 so that they are not parallel to the symmetry axis A1, but the extended imaginary planes of the contact surfaces 13ka-13kd intersect with the symmetry axis A1 outside the rotating shaft 15. Accordingly, the angle θ of the corners at both ends where the contact surfaces 15fa-15fd of the protrusions 15c, 15d are formed is more acute in the rotation direction of the rotating shaft 15 than that of the fourteenth embodiment. (The same applies to the second rotating disk 14).

[0195] [About the action and effect of the flow switching device] According to the configuration of the flow path switching device 1 of this embodiment described above, the angle of each corner of both ends of each protrusion 15c, 15d of the rotating shaft 15 is formed at a more acute angle with respect to the rotation direction, and the contact surfaces 15fa to 15fd are brought into contact with the corresponding contacted surfaces 13ka to 13kd to rotate each rotating disk 13, 14. Therefore, each rotating disk 13, 14 rotates and stops in a state where a pressing stress is applied in the rotation direction of the rotating shaft 15. Therefore, even if a tilting stress acts on each rotating disk 13, 14, the contact state between the contact surface 15fb and the contacted surface 13kb, and between the contact surface 15fc and the contacted surface 13kc can be firmly maintained when the rotating disks 13, 14 are stopped in the counterclockwise direction as shown in FIG. On the other hand, when the rotating disks 13 and 14 are stopped in the clockwise direction as shown in Fig. 57, the contact state between the contact surface 15fa and the contacted surface 13ka, and between the contact surface 15fd and the contacted surface 13kd can be firmly maintained. As a result, the tilt of each of the rotating disks 13 and 14 can be more effectively suppressed.

[0196] <16th embodiment> The sixteenth embodiment will be described in detail with reference to Figures 58 to 60. This embodiment is a modified example of the fourteenth embodiment.

[0197] [Configuration of the rotating disk shaft hole and rotating shaft] This embodiment differs from the 14th embodiment in the configuration of each of the shaft holes 13a, 14a of the rotating disks 13, 14 and the rotating shaft 15. In the 14th embodiment, as shown in Fig. 53 and Fig. 54, for the first rotating disk 13, abutment surfaces 15fa-15fd formed on both ends of each of the protrusions 15c, 15d are formed in a surface parallel to the axis of the rotating shaft 15 and are configured to be able to abut against corresponding abutted surfaces 13ka-13kd formed on both ends of each of the shaft hole recesses 13ja, 13jb of the first shaft hole 13a. However, in the fourteenth embodiment, as shown in Fig. 53, the width (contact surface interval W1) between the adjacent contact surfaces 15fa and 15fc, and the contact surface interval W1 between the adjacent contact surfaces 15fb and 15fd are narrower than the outer diameter of the rotating shaft 15, and the effect of suppressing the tilt of the first rotating disk 13 due to the contact between the contact surfaces 15fa to 15fd and the contacted surfaces 13ka to 13kd is small. The same was true for the second rotating disk 14.

[0198] Therefore, in this embodiment, the contact surface interval W1 is configured to be larger than the outer diameter of the rotating shaft 15. Figs. 58 to 60 are enlarged plan views showing a portion including the first shaft hole 13a of the first rotating disc 13 and the rotating shaft 15 therein. Fig. 58 shows an idle state in which the contact surfaces 15fa to 15fd of the rotating shaft 15 do not come into contact with the contacted surfaces 13ka to 13kd of the first shaft hole 13a, Fig. 59 shows the first rotating disc 13 at a stop in the counterclockwise direction, and Fig. 60 shows the first rotating disc 13 at a stop in the clockwise direction.

[0199] 58 to 60, each of the protrusions 15c, 15d of the rotating shaft 15 extends along the orthogonal axis B1 with a length greater than the radius of the rotating shaft 15, and the tip of each of the protrusions 15c, 15d is arc-shaped in a plan view. Both halves of the tip arc surface of the first protrusion 15c serve as contact surfaces 15fa, 15fb, respectively, and both halves of the tip arc surface of the second protrusion 15d serve as contact surfaces 15fc, 15fd, respectively. Also, as shown in Figures 58 to 60, the first axial hole 13a has a horizontally elongated polygonal shape in a planar view, and at both ends of its longitudinal direction, abutment surfaces 13ka, 13kb that can abut against abutment surfaces 15fa, 15fb of the first protrusion 15c and abutment surfaces 13kc, 13kd that can abut against abutment surfaces 15fc, 15fd of the second protrusion 15d are formed adjacent to each other and form a convex curve.

[0200] Although not shown and not described, the second axial hole 14 a of the second rotating disk 14 has a configuration similar to that of the first rotating disk 13 .

[0201] [About 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, when the first rotating disk 13 stops in the counterclockwise direction, the contact surface 15fb of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13kb of the first shaft hole 13a, and the contact surface 15fc of the second protrusion 15d contacts the contact surface 13kc, as shown in Fig. 59. When the first rotating disk 13 stops in the clockwise direction, the contact surface 15fa of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13ka of the first shaft hole 13a, and the contact surface 15fd of the second protrusion 15d contacts the contact surface 13kd, as shown in Fig. 60. In this embodiment, the contact surface interval W1 of the rotating shaft 15 is larger than the outer diameter of the rotating shaft 15, so that when the contact surfaces 15fa-15fd come into contact with the corresponding contacted surfaces 13ka-13kd, the effect of suppressing tilt of the first rotating disc 13 can be improved more than that of the fourteenth embodiment. The same applies to the second rotating disc 14.

[0202] <Seventeenth embodiment> The seventeenth embodiment will be described in detail with reference to Figures 61 to 63. This embodiment is a modification of the sixteenth embodiment.

[0203] [Configuration of the rotating disk shaft hole and rotating shaft] This embodiment differs from the sixteenth embodiment in the configuration of the shaft holes 13a, 14a of the rotating discs 13, 14 and the rotating shaft 15. Figures 61 to 63 are enlarged plan views showing a portion including the first shaft hole 13a of the first rotating disc 13 and the rotating shaft 15 therein. The states of Figures 61 to 63 are equivalent to the plan views of Figures 58 to 60, respectively.

[0204] In this embodiment, as shown in Fig. 61 to Fig. 63, each of the protrusions 15c, 15d of the rotating shaft 15 extends along the orthogonal axis B1 with a length greater than the radius of the rotating shaft 15, and the tip of each of the protrusions 15c, 15d is formed with an enlarged head 15ca, 15da having a semicircular shape in a plan view. The two inner faces of the head 15ca of the first protrusion 15c are contact faces 15fa, 15fb, respectively, and the two inner faces of the head 15da of the second protrusion 15d are contact faces 15fc, 15fd, respectively. Also, as shown in Fig. 61 to Fig. 63, the first shaft hole 13a has a horizontally elongated shape in a plan view, and enlarged portions 13aa, 13ab having a semicircular shape in a plan view are formed at both ends in the longitudinal direction. The two inner flat surfaces of the enlarged portion 13aa on one side are contacted surfaces 13ka and 13kb that can contact the contact surfaces 15fa and 15fb of the first protrusion 15c, respectively. The two inner flat surfaces of the enlarged portion 13ab on the other side are contacted surfaces 13kc and 13kd that can contact the contact surfaces 15fc and 15fd of the second protrusion 15d, respectively.

[0205] Although not shown and not described, the second axial hole 14 a of the second rotating disk 14 has a configuration similar to that of the first rotating disk 13 .

[0206] [About 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, when the first rotating disk 13 stops in the counterclockwise direction, the contact surface 15fb of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13kb of the first shaft hole 13a, and the contact surface 15fc of the second protrusion 15d contacts the contact surface 13kc, as shown in Fig. 62. When the first rotating disk 13 stops in the clockwise direction, the contact surface 15fa of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13ka of the first shaft hole 13a, and the contact surface 15fd of the second protrusion 15d contacts the contact surface 13kd, as shown in Fig. 63. In this embodiment, the contact surface interval W1 of the rotating shaft 15 is larger than the outer diameter of the rotating shaft 15, so that when the contact surfaces 15fa to 15fd contact the corresponding contacted surfaces 13ka to 13kd, the tilt suppression effect of the first rotating disk 13 can be improved more than that of the 14th embodiment. In addition, in this embodiment, the acute outer edge portions of the heads 15ca and 15da of the protrusions 15c and 15d engage with the acute outer edge portions of the enlarged portions 13aa and 13ab of the first shaft hole 13a, so that the protrusions 15c and 15d can be firmly connected to the first shaft hole 13a. The same applies to the second rotating disk 14.

[0207] <Eighteenth embodiment> The eighteenth embodiment will be described in detail with reference to Figures 64 to 66. This embodiment is a modified example of the sixteenth embodiment.

[0208] [Configuration of the rotating disk shaft hole and rotating shaft] This embodiment differs from the 16th and 17th embodiments in the configuration of the shaft holes 13a, 14a of the rotating discs 13, 14 and the rotating shaft 15. Figures 64 to 66 are enlarged plan views showing a portion including the first shaft hole 13a of the first rotating disc 13 and the rotating shaft 15 therein. The states of Figures 64 to 66 are equivalent to the plan views of Figures 58 to 60, respectively.

[0209] In this embodiment, as shown in Figures 64 to 66, each of the protrusions 15c and 15d of the rotating shaft 15 extends along the axis of symmetry A1 and the orthogonal axis B1 with a length greater than the radius of the rotating shaft 15, and forms a square flange in plan view with the rotating shaft 15 included in the center as a whole. The left side of the axis of symmetry A1 is the first protrusion 15c, and the right side is the second protrusion 15d. The upper and lower halves of the tip edge of the first protrusion 15c are contact surfaces 15fa and 15fb, respectively, and the upper and lower halves of the tip edge of the second protrusion 15d are contact surfaces 15fc and 15fd, respectively. 64 to 66, the first shaft hole 13a is substantially square in plan view, and the upper and lower parts of the left side in the direction of the orthogonal axis B1 are abutted surfaces 13ka and 13kb that can abut against the abutment surfaces 15fa and 15fb of the first protrusion 15c, respectively. Also, the upper and lower parts of the right side in the direction of the orthogonal axis B1 are abutted surfaces 13kc and 13kd that can abut against the abutment surfaces 15fc and 15fd of the second protrusion 15d, respectively.

[0210] Although not shown and not described, the second axial hole 14 a of the second rotating disk 14 has a configuration similar to that of the first rotating disk 13 .

[0211] [About 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, when the first rotating disk 13 stops in the counterclockwise direction, the contact surface 15fa of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13ka of the first shaft hole 13a, and the contact surface 15fd of the second protrusion 15d contacts the contact surface 13kd, as shown in Fig. 65. When the first rotating disk 13 stops in the clockwise direction, the contact surface 15fb of the first protrusion 15c of the rotating shaft 15 contacts the contact surface 13kb of the first shaft hole 13a, and the contact surface 15fc of the second protrusion 15d contacts the contact surface 13kc, as shown in Fig. 66. In this embodiment, the contact surface interval W1 of the rotating shaft 15 is larger than the outer diameter of the rotating shaft 15, so that when the contact surfaces 15fa-15fd come into contact with the corresponding contacted surfaces 13ka-13kd, the effect of suppressing tilt of the first rotating disc 13 can be improved more than that of the fourteenth embodiment. The same applies to the second rotating disc 14.

[0212] <Nineteenth embodiment> The nineteenth embodiment will be described in detail with reference to FIGS.

[0213] [About the contact structure between the rotating disk and the rotating shaft] This embodiment differs from the 16th to 18th embodiments in the contact structure between the rotating disks 13, 14 and the rotating shaft 15. FIG. 67 shows the second rotating disk 14 and the rotating shaft 15 in a plan view. FIG. 68 shows the second rotating disk 14 etc. in a cross-sectional view taken along line JJ in FIG. 67, and also shows a schematic diagram of the relationship between the second rotating disk 14 and the first rotating disk 13 etc. As shown in FIGS. 67 and 68, in this embodiment, the protrusions 15c, 15d provided on the rotating shaft 15 are disposed between the first rotating disk 13 and the second rotating disk 14. Also, the protrusions 15c, 15d extend beyond the outer diameter of the rotation passages 30, 40 of the rotating disks 13, 14.

[0214] That is, in this embodiment, as shown in Fig. 67 and Fig. 68, each of the protrusions 15c, 15d is formed in a long plate shape, and extends along the orthogonal axis B1 around the rotating shaft 15, which is larger than the radius of the rotating shaft 15, and is larger than the outer diameter of each of the rotating passages 30, 40. In addition, both corners of the tip of the first protrusion 15c are contact parts 15ga, 15gb, and both corners of the tip of the second protrusion 15d are contact parts 15gc, 15gd. In addition, as shown in Fig. 67 and Fig. 68, on the upper surface of the second rotating disk 14, engagement frames 14ka, 14kb having a channel shape in a plan view are formed surrounding the tip parts of each of the protrusions 15c, 15d. The inner surfaces of both sides of the first engagement frame 14ka corresponding to the first protrusion 15c are contact parts 14ma, 14mb that can contact the contact parts 15ga, 15gb of the first protrusion 15c. The inner surfaces of both sides of the second engagement frame 14kb corresponding to the second projection 15d serve as contact portions 14mc and 14md that can come into contact with the contact portions 15gc and 15gd of the second projection 15d.

[0215] In addition, in this embodiment of the flow path switching device 1, four compression springs 61 are provided between each of the rotating disks 13, 14, and four sets of receiving holes 14f and cylindrical portions 14g are arranged on the upper surface of the second rotating disk 14 to receive the compression springs 61 so as not to interfere with each of the engagement frames 14ka, 14kb.

[0216] [About the action and effect of the flow path switching device] The configuration of the flow path switching device 1 of this embodiment described above has the following actions and effects in addition to the actions and effects of the third embodiment. That is, according to the configuration of this embodiment, the protrusions 15c, 15d extend outward beyond the outer diameter of the rotation passages 30, 40 of the rotating disks 13, 14, so that the outer diameter of each of the protrusions 15c, 15d is larger than the outer diameter of the rotation passages 30, 40. This improves the effect of each of the protrusions 15c, 15d in suppressing the tilt of each of the rotating disks 13, 14, and suppresses variations in the rotation angles of each of the rotating disks 13, 14 due to component tolerances.

[0217] According to the configuration of this embodiment, when the second rotating disk 14 stops in the counterclockwise direction, in Fig. 67, the abutment portion 15gb of the first protrusion 15c of the rotating shaft 15 abuts against the abutment portion 14mb of the first engagement frame 14ka, and the abutment portion 15gc of the second protrusion 15d abuts against the abutment portion 14mc. Also, when the second rotating disk 14 stops in the clockwise direction, in Fig. 67, the abutment portion 15ga of the first protrusion 15c of the rotating shaft 15 abuts against the abutment portion 14ma of the first engagement frame 14ka, and the abutment portion 15gd of the second protrusion 15d abuts against the abutment portion 14md. In this embodiment, each of the protrusions 15c, 15d has a long plate shape, and extends around the rotating shaft 15 to a position larger than the radius of the rotating shaft 15 and to a position outside the outer diameter of each of the rotation passages 30, 40. Therefore, when the contact portions 15ga-15gd contact the corresponding contact portions 14ma-14md, the resistance of the contact portions against the tilt of the second rotating disk 14 becomes larger. Therefore, the effect of suppressing the tilt of the second rotating disk 14 can be improved more than that of the 16th to 18th embodiments. In addition, in this embodiment, the tip portions of the protrusions 15c, 15d are surrounded by the inside of the engagement frames 14ka, 14kb, so that the protrusions 15c, 15d and the engagement frames 14ka, 14kb can be firmly connected to each other.

[0218] In addition, in this embodiment, since the protrusions 15c, 15d extend beyond the outer diameter of the rotation passages 30, 40, the variation in the rotation angle of the second rotating disk 14 due to component tolerances can also be suppressed.

[0219] <Twentieth embodiment> The twentieth embodiment will be described in detail with reference to Fig. 69. This embodiment is a modification of the nineteenth embodiment.

[0220] [About the contact structure between the rotating disk and the rotating shaft] This embodiment differs from the 19th embodiment in the abutment structure between the second rotating disk 14 and the rotating shaft 15, particularly the shape of the tip of each protrusion 15c, 15d and each engagement frame 14ka, 14kb. Figure 69 shows the second rotating disk 14 and the rotating shaft 15 in a plan view similar to Figure 67. As shown in Figure 69, this embodiment has the same configuration as each protrusion 15c, 15d and each enlarged portion 13aa, 13ab (see Figure 61) of the 17th embodiment. That is, as shown in Figure 69, the tip of each protrusion 15c, 15d is formed with enlarged heads 15ca, 15da that are semicircular in plan view. Two inner surfaces of the head 15ca of the first protrusion 15c are abutment surfaces 15fa, 15fb, respectively, and two inner surfaces of the head 15da of the second protrusion 15d are abutment surfaces 15fc, 15fd, respectively. The inner surfaces 14kaa, 14kba of the engagement frames 14ka, 14kb are formed in a substantially semicircular shape in a plan view. The two flat inner surfaces of the inner surface 14kaa of the first engagement frame 14ka are contact surfaces 14na, 14nb that can contact the contact surfaces 15fa, 15fb of the first protrusion 15c, respectively. The two flat inner surfaces of the inner surface 14kba of the second engagement frame 14kb are contact surfaces 14nc, 14nd that can contact the contact surfaces 15fc, 15fd of the second protrusion 15d, respectively.

[0221] [About 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, it is possible to obtain the same actions and effects as those of the 19th embodiment. In addition, in this embodiment, since the tip portions of the protrusions 15c, 15d and the inner surfaces of the engagement frames 14ka, 14kb have the same shapes as those of the 17th embodiment, it is possible to firmly connect the protrusions 15c, 15d and the engagement frames 14ka, 14kb.

[0222] <Another embodiment> The disclosed technology is not limited to the above-described embodiments, and may be implemented by modifying part of the configuration as appropriate without departing from the spirit of the disclosed technology.

[0223] (1) In each of the above embodiments, the flow path switching device 1 is configured as an 8-way valve, but is not limited to this, and may be configured as other multi-way valves such as a 3-way valve, a 4-way valve, or a 6-way valve.

[0224] (2) The arrangement of the pressure adjustment holes 8 in each of the above embodiments is merely an example, and is not limited to the arrangement shown in FIG.

[0225] (3) In each of the above embodiments, the first seal member 17, 57 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.

[0226] (4) In the first embodiment, the first to fourth inlet / outlet passages 21-24 are provided as predetermined communication passages in the low-pressure side upper housing 11, and the fifth to eighth inlet / outlet passages 25-28 are provided as other communication passages in the high-pressure side lower housing 12. However, it is also possible to provide other communication passages in the high-pressure side upper housing and provide a predetermined communication passage in the low-pressure side lower housing.

[0227] (5) In the seventh embodiment, the first seal member 17 provided in the low-pressure side upper housing 11 is set to have a higher hardness or spring constant than the second seal member 18 provided in the high-pressure side lower housing 12. In contrast to this, the second seal member provided in the low-pressure side lower housing can also be set to have a higher hardness or spring constant than the first seal member provided in the high-pressure side upper housing.

[0228] (6) In the eighth embodiment, the first compression spring 61A provided corresponding to the low-pressure side upper housing 11 is set to have a smaller spring constant than the second compression spring 61B provided corresponding to the high-pressure side lower housing 12. In contrast to this, the second compression spring provided corresponding to the low-pressure side lower housing can also be set to have a smaller spring constant than the first compression spring provided corresponding to the high-pressure side upper housing. [Industrial Applicability]

[0229] The disclosed technology can be utilized to switch the flow path of a fluid in a fluid circuit through which a fluid flows. [Explanation of symbols]

[0230] 1 Flow path switching device 2. Housing 3 Valve body 5 Control section (control means) 7. Housing space 8 Pressure adjustment hole 9. Flow path switching device 11 Upper housing 12 Lower housing 13 First rotating disk (first driving member) 13a First shaft hole 13ka Abutted surface (Abutted part) 13kb Abutted surface (Abutted part) 13kc Abutted surface (Abutted part) 13kd Abutted surface (Abutted part) 14 Second rotating disk (second driving member) 14a Second shaft hole 15 Rotational Axis 15c 1st protrusion (expanded diameter part) 15d 2nd protrusion (expanded diameter part) 15e 3rd protrusion (expanded diameter part) 17 First seal member 18 Second seal member 20 Inflow / outflow passage (communicating passage) 21 First inlet / outlet passage (predetermined communication passage) 22 Second inlet / outlet passage (predetermined communication passage) 23 Third inlet / outlet passage (specified communication passage) 24 Fourth inlet / outlet passage (specified connecting passage) 25 5th inlet / outlet passage (other connecting passage) 26 6th Inlet / Outlet Passage (Specific connecting passage, other connecting passage) 27 7th Inlet / Outlet Passage (other connecting passage) 28 8th Inlet / Outlet Passage (Other connecting passage) 30 Rotating passage (connecting passage) 40 Rotating passage (connecting passage) 57 First seal member 61 Compression spring (elastic member) 61A First compression spring (first elastic member) 61B Second compression spring (second elastic member) 63 Engagement protrusion (regulating means) 66 Partition 90 Electric vehicle 91 Cooling system 96A First pipe (small circuit) 96B 2nd piping (small circuit) 96C 3rd piping (small circuit) 96D 4th piping (small circuit) 97 First electric pump 98 No. 2 electric pump A1 Symmetry axis LH hole length LL hole length G1 Gap X-axis direction Y Rotation Direction

Claims

1. Housing and a valve body portion disposed inside the housing; Equipped with The valve body portion includes a first drive member and a second drive member disposed adjacent to each other, the housing and at least one of the first drive member and the second drive member each include a plurality of communication passages; a seal member for suppressing leakage of fluid is provided between a periphery of the communication passage in at least one of the first drive member and the second drive member and the housing; an elastic member is provided between the first drive member and the second drive member to bias the first drive member and the second drive member in a direction to move the first drive member and the second drive member away from each other and toward the housing in order to adjust a contact surface pressure of the seal member with respect to the housing or the first drive member and the second drive member; A flow path switching device configured to selectively switch and form a plurality of flow paths by driving the first drive member and the second drive member to combine and connect the communication path in at least one of the first drive member and the second drive member and the communication path in the housing, a housing internal space excluding the communication passage is provided between the housing and the first driving member and between the housing and the second driving member; The housing is provided with a pressure adjustment hole communicating with at least one of the communication passages in order to adjust the pressure in the space within the housing. A flow path switching device.

2. The flow path switching device according to claim 1 , At least one of the first and second driving members or the housing is provided with a restricting means for restricting reduction of a gap between the housing and at least one of the first and second driving members. A flow path switching device.

3. The flow path switching device according to claim 1 , A rotating shaft for rotating each of the driving members is further provided, The rotating shaft is inserted into each of the driving members so as to be movable in a rotational direction and an axial direction relative to the driving members, and the rotating shaft is provided with an expanded diameter portion for transmitting a driving force to each of the driving members, Each of the drive members is formed with a plurality of rotation passages in the form of elongated holes extending in an arc shape along a rotation trajectory of each of the drive members around the rotation shaft, as the communication passages; The enlarged diameter portion is disposed toward the center of the circular arc of the rotation passage. A flow path switching device.

4. The flow path switching device according to claim 3, The rotation passages of the driving members are arranged symmetrically with respect to an axis of symmetry, Each of the driving members has a contact portion that is parallel to the axis of symmetry and can contact the enlarged diameter portion. A flow path switching device.

5. The flow path switching device according to claim 3, The enlarged diameter portion is disposed between the driving members and extends beyond the outer diameter of the rotation passage of each of the driving members. A flow path switching device.

6. The flow path switching device according to claim 3, the first driving member and the second driving member each have a shaft hole through which the rotation shaft is inserted, The length of the shaft hole of one of the first and second drive members, which includes the rotation passage forming a higher pressure flow passage, is longer than the length of the shaft hole of the other drive member. A flow path switching device.

7. The flow path switching device according to claim 3, the first driving member and the second driving member each have a shaft hole through which the rotation shaft is inserted, Of the first drive member and the second drive member, one of the drive members including the rotation passage that forms a higher pressure flow passage has a radial clearance between the shaft hole and the rotary shaft that is smaller than a radial clearance between the shaft hole and the rotary shaft of the other drive member. A flow path switching device.

8. A fluid circuit system including the flow path switching device according to any one of claims 1 to 7, A pump for pumping a fluid is provided, The pressure adjustment hole is provided corresponding to a specific communication passage, among the plurality of communication passages, to which an outlet of the pump is connected. A fluid circuit system comprising:

9. The fluid circuit system according to claim 8, The pump, the outlet of which is in communication with the specific communication passage, is configured to be constantly driven. A fluid circuit system comprising:

10. A fluid circuit system including the flow path switching device according to any one of claims 1 to 7, A pump for pumping a fluid is provided, The flow path switching device includes, as the housing, an upper housing that accommodates the first driving member and a lower housing that accommodates the second driving member, a predetermined communication passage among the plurality of communication passages is disposed in one of the upper housing and the lower housing, and another communication passage is disposed in the other of the upper housing and the lower housing; At least a part of the predetermined communication passage is provided so as to be capable of communicating with the inlet of the pump. A fluid circuit system comprising:

11. The fluid circuit system according to claim 10, the flow path switching device includes a first seal member disposed between the upper housing and the first drive member, and a second seal member disposed between the lower housing and the second drive member, The first seal member or the second seal member provided in the upper housing or the lower housing in which at least a part of the predetermined communication passage is arranged has a hardness or a spring constant higher than that of the second seal member or the first seal member provided in the lower housing or the upper housing in which the other communication passage is arranged. A fluid circuit system comprising:

12. The fluid circuit system according to claim 10, the flow path switching device includes a partition plate fixed on the rotation shaft and disposed between the first drive member and the second drive member, a first elastic member that biases the partition plate and the first drive member in a direction separating them from each other, and a second elastic member that biases the partition plate and the second drive member in a direction separating them from each other, The first elastic member or the second elastic member provided corresponding to the upper housing or the lower housing in which at least a part of the predetermined communication passage is arranged has a spring constant smaller than that of the second elastic member or the first elastic member provided corresponding to the lower housing or the upper housing in which the other communication passage is arranged. A fluid circuit system comprising:

13. A fluid circuit system including the flow path switching device according to any one of claims 1 to 7, A plurality of small circuits whose communication is switched by the flow path switching device; a pump provided in each of at least two of the plurality of subcircuits; a control means for controlling the operation of the flow path switching device and the pump; Equipped with The control means stops driving the pump after the communication state of the plurality of small circuits is switched by the flow path switching device. A fluid circuit system comprising:

14. The flow path switching device according to any one of claims 1 to 7, The flow path switching device is used in the cooling system of an electric vehicle. A flow path switching device.

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