Valve device

Abstract

A rotor (16) is disposed on one side of a prescribed shaft center (Cv) in the axial direction (Da) with respect to a flow path hole forming part having a flow path hole formed in a housing, and rotates about the shaft center. A differential pressure device (24) has a pressure chamber (24a), and is disposed on one side in the axial direction with respect to the rotor. In the housing, a one-side space (11a) provided to the one side in the axial direction with respect to the rotor and other-side spaces (11b, 11c, 11d, 11e) that are provided to the side opposite to the one side in the axial direction with respect to the flow path hole forming part and that are in communication with the flow path hole are formed. When pressure in at least the other-side spaces is higher than pressure (P2) in the one-side space, the differential pressure device generates a pressing force for pressing the rotor to the flow path hole forming part by means of differential pressure between pressure (P1) in the pressure chamber and the pressure in the one-side space. As the pressure in the pressure chamber is increased with respect to the pressure in the one-side space, the pressing force is increased.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2021-198457, filed on December 7, 2021, the contents of which are incorporated herein by reference. [Technical field]

[0002] FIELD OF THE DISCLOSURE The present disclosure relates to a valve device through which fluid may flow. [Background technology]

[0003] As an example of this type of valve device, the valve device described in Patent Document 1 is known. The valve device described in Patent Document 1 includes a drive disk and a fixed disk that are stacked on top of each other and are disposed in a flow path inside a housing. The drive disk rotates about a predetermined axis while sliding against the fixed disk. In the valve device of Patent Document 1, the opening port is switched according to the rotational position of the drive disk, and the flow path inside the housing is switched. In the valve device of Patent Document 1, the drive disk is pressed against the fixed disk by a pressing spring. This seals the gap between the drive disk and the fixed disk. In other words, a constant surface pressure is applied to the contact surfaces between the drive disk and the fixed disk, which prevents leakage of fluid from between the drive disk and the fixed disk. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] European Patent No. 2917619 Summary of the Invention

[0005] In recent years, the demand for more sophisticated functions in valve devices has created the following needs that did not exist before: In a valve device, when the flow of fluid from the driving disk side to the fixed disk side is considered to be a forward flow, it has become necessary to also consider a reverse flow of fluid, that is, a flow of fluid from the fixed disk side to the driving disk side, depending on the mode of the system to which the valve device belongs.

[0006] In the reverse flow, the fluid pressure on the fixed disk side in the flow passage inside the housing becomes higher than the fluid pressure on the driving disk side, generating a back pressure that causes the driving disk to lift off the fixed disk. This back pressure becomes large, for example, when the flow rate is high or when the driving disk is fully closed and blocks the flow passage.

[0007] If the force causing the drive disk to float due to the counter pressure exceeds the load of the pressing spring, the drive disk will float away from the fixed disk, creating a gap between the drive disk and the fixed disk, which will result in fluid leakage between the drive disk and the fixed disk, impairing the function of the valve device.

[0008] To prevent such a situation, it is possible to increase the load of the pressing spring by taking back pressure into account, but since the load of the pressing spring is a constant load, it becomes larger than necessary, for example, when no back pressure is generated. If the load of the pressing spring is large, the friction torque caused by the friction between the drive disk and the fixed disk increases. Therefore, the method of increasing the load of the pressing spring by taking back pressure into account requires increasing the driving force of the actuator that rotates the drive disk, which leads to a significant increase in costs. The inventors have found the above as a result of detailed investigation.

[0009] In consideration of the above points, the present disclosure aims to provide a valve device that can prevent the drive disk from lifting up from the fixed disk while suppressing excessively large friction torque between the drive disk and the fixed disk.

[0010] In order to achieve the above object, according to one aspect of the present disclosure, a valve device includes: A housing through which a fluid flows; a flow passage hole forming portion that is disposed within the housing and is provided so as to be unable to rotate relatively to the housing, and in which a flow passage hole through which a fluid passes is formed; a rotor that is disposed on one side of the flow passage hole forming portion in the axial direction of the predetermined axis within the housing and rotates about the predetermined axis while sliding relative to the flow passage hole forming portion; a differential pressure device provided on one side of the rotor in the axial direction and having a pressure chamber into which a fluid is introduced; Within the housing, a one-side space is provided on one side of the rotor in the axial direction, and a other-side space is provided on the other side of the flow passage hole forming portion opposite to the one side in the axial direction and communicates with the flow passage hole, The rotor increases and decreases the opening of the flow passage hole with respect to the one side space as the rotor rotates, the differential pressure device generates a pressing force for pressing the rotor against the flow path hole formation portion by a pressure difference between the pressure in the pressure chamber and the pressure in the one-side space when the pressure in at least the other-side space is higher than the pressure in the one-side space, The greater the pressure in the pressure chamber relative to the pressure in the one side space, the greater the pressing force.

[0011] In this way, when the pressure in the other-side space is higher than the pressure in the one-side space, a back pressure, which is a fluid pressure that lifts the rotor off the flow path hole forming portion, is generated, but the differential pressure device presses the rotor against the flow path hole forming portion against the back pressure. The greater the pressure in the pressure chamber relative to the pressure in the one-side space, the greater the pressing force of the differential pressure device, so the pressing force of the differential pressure device is adjusted according to the magnitude of the back pressure. Therefore, it is possible to prevent the rotor from lifting off the flow path hole forming portion while suppressing excessive increase in friction torque between the rotor and the flow path hole forming portion.

[0012] Here, the rotor corresponds to the drive disk, and the flow passage hole forming portion corresponds to the fixed disk. Furthermore, the term "at least" in the case where the differential pressure device generates a pressing force means that the differential pressure device may generate the pressing force in cases other than when the pressure in the other space is higher than the pressure in the one space, and the term "at least" does not limit the configuration of the valve device to one in which the differential pressure device always generates the pressing force when the pressure in the other space is higher than the pressure in the one space.

[0013] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and specific components described in the embodiments described below. [Brief description of the drawings]

[0014] [Figure 1] FIG. 1 is a diagram showing a valve device according to a first embodiment, and is a vertical sectional view showing a section including a valve axis of the valve device. [Diagram 2] 2 is a cross-sectional view showing a cross section taken along line II-II of FIG. 1 in the first embodiment. [Diagram 3] 3 is a view showing a stator provided in the valve device according to the first embodiment by itself, as viewed in the direction of arrow III in FIG. 1. FIG. [Figure 4] 3 is a diagram showing a rotor and a lever of the valve device in the first embodiment, as viewed in the direction of arrow III in FIG. 1. FIG. [Diagram 5] FIG. 2 is a diagram showing a shaft, a shaft body, and a lever of the valve device in the first embodiment, as viewed in the direction of arrow V in FIG. [Figure 6] 6 is a view taken in the direction of an arrow VI in FIG. 5. [Figure 7] 7 is a cross-sectional view showing a cross section VII-VII of FIG. 4 in the first embodiment. [Figure 8] FIG. 2 is a partially enlarged view showing a portion VIII in FIG. 1 in the first embodiment. [Figure 9]FIG. 2 is a diagram of the differential pressure device and its surroundings extracted from the longitudinal cross-sectional view of FIG. 1, in which (a) shows the state of the differential pressure device when the pressure in the pressure chamber becomes lower than the pressure in the one-side space, and (b) shows the state of the differential pressure device when the pressure in the pressure chamber becomes higher than the pressure in the one-side space. [Figure 10] FIG. 11 is a vertical cross-sectional view illustrating a valve device according to a second embodiment, the view corresponding to FIG. [Figure 11] 11 is a partially enlarged view showing a portion XI in FIG. 10 in the second embodiment. FIG. [Figure 12] 12 is a cross-sectional view showing a cross section taken along line XII-XII of FIGS. 10 and 11 in the second embodiment, and corresponds to FIG. 2. FIG. [Figure 13] FIG. 11 is a perspective view showing a check valve element provided in a valve device according to a second embodiment, in a separate manner. [Figure 14] FIG. 11 is a vertical sectional view showing a valve device according to a third embodiment, the view corresponding to FIG. [Figure 15A] 14 is a cross-sectional view showing the XVA-XVA section of FIG. 13 in the third embodiment, illustrating a state in which the first flow passage hole of the stator is fully closed by the rotor. FIG. [Figure 15B] 15B is a cross-sectional view showing the XVB-XVB cross section of FIG. 13 in the third embodiment, showing a state in which the rotor is in the same rotational position as in FIG. 15A. FIG. [Figure 16] FIG. 11 is a perspective view showing a rotor alone in the third embodiment. [Figure 17A] 15B is a cross-sectional view corresponding to FIG. 15A and showing a cross-section taken along XVA-XVA in FIG. 13 in the third embodiment, illustrating a state in which the rotor has rotated from the rotation position in FIG. 15A to one side in the valve circumferential direction, and the first and second flow passage holes of the stator have been opened by the rotor. [Figure 17B] 17A is a cross-sectional view showing a cross section taken along line XVB-XVB of FIG. 13 and corresponding to FIG. 15B in the third embodiment, and shows a state in which the rotor is in the same rotational position as in FIG. 17A. [Figure 18A]17A is a cross-sectional view corresponding to FIG. 15A and showing a cross-section taken along XVA-XVA in FIG. 13 in the third embodiment, and shows a state in which the rotor has rotated from the rotation position in FIG. 17A to one side in the valve circumferential direction, and the second flow path hole of the stator has been fully closed by the rotor. [Figure 18B] 18A is a cross-sectional view showing a cross section taken along line XVB-XVB of FIG. 13 and corresponding to FIG. 15B in the third embodiment, and shows a state in which the rotor is in the same rotational position as in FIG. 18A. [Figure 19] FIG. 11 is a vertical sectional view showing a valve device according to a fourth embodiment, the view corresponding to FIG. [Figure 20] FIG. 11 is a circuit diagram showing a schematic configuration of a heat medium circuit including a valve device in a fourth embodiment. [Figure 21] FIG. 13 is a vertical sectional view showing a valve device according to a fifth embodiment, the view corresponding to FIG. [Figure 22] FIG. 13 is a vertical sectional view showing a valve device according to a sixth embodiment, the view corresponding to FIG. [Figure 23] FIG. 13 is a vertical sectional view showing a valve device according to a seventh embodiment, the view corresponding to FIG. [Figure 24] FIG. 13 is a vertical sectional view showing a valve device according to an eighth embodiment, the view corresponding to FIG. [Diagram 25] FIG. 14 is a perspective view showing a check valve element provided in a valve device alone in a first modified example that is a modified example of the second embodiment, and corresponds to FIG. 13. [Figure 26] FIG. 14 is a perspective view showing a check valve element provided in a valve device alone in a second modified example that is a modified example of the second embodiment, and corresponds to FIG. 13. [Figure 27] FIG. 14 is a perspective view showing a check valve element provided in a valve device alone in a third modified example that is a modified example of the second embodiment, and corresponds to FIG. 13. [Figure 28] FIG. 14 is a perspective view showing a check valve element provided in a valve device alone in a fourth modified example that is a modified example of the second embodiment, and corresponds to FIG. 13. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, each embodiment will be described with reference to the drawings. In the following embodiments, the same reference numerals are given to parts that are the same or equivalent to each other.

[0016] (First embodiment) The valve device 10 of this embodiment is a heat medium control valve for a vehicle mounted on, for example, a hybrid vehicle. The valve device 10 shown in Figures 1 and 2 constitutes a part of a heat medium circuit that circulates a heat medium by a pump to a driving power source, a radiator, a heat exchanger for cooling a battery, a heater core which is a heat exchanger for air conditioning, etc. Therefore, the heat medium circulating in the heat medium circuit flows through the valve device 10.

[0017] The valve device 10 can increase or decrease the flow rate of the heat medium in the flow path through the valve device 10 in the heat medium circuit, and can also switch or block the flow path. The heat medium flowing through the valve device 10 is a liquid fluid, and as the heat medium, for example, cooling water containing ethylene glycol is used.

[0018] 1 and 2, the valve device 10 is a disk valve in which a substantially disk-shaped rotor 16 rotates around a valve axis Cv as a predetermined axis to open and close the valve. The valve device 10 of this embodiment is a multi-way valve having five ports 110, 111, 112, 113, and 114.

[0019] In the description of this embodiment, the axial direction of the valve axis Cv is also referred to as the valve axial direction Da, the radial direction of the valve axis Cv is also referred to as the valve radial direction Dr, and the circumferential direction centered on the valve axis Cv is also referred to as the valve circumferential direction Dc.

[0020] The valve device 10 includes a housing 11, a stator 12, an actuator 14, a rotor 16, a shaft 17, a shaft body 18, a lever 20, a pressing spring 22, a differential pressure device 24, a fixed part 28, and a gasket 30.

[0021] The housing 11 constitutes the outer shell of the valve device 10, and a heat transfer medium flows inside the housing 11. The housing 11 is a non-rotating member that does not rotate, and is made of, for example, resin. The housing 11 accommodates a stator 12, a rotor 16, a shaft 17, a shaft body 18, a lever 20, a pressing spring 22, and a differential pressure device 24 inside the housing 11.

[0022] The housing 11 has a one-side port portion 110 in which a one-side port passage 110a is formed, a first other-side port portion 111 in which a first other-side port passage 111a is formed, and a second other-side port portion 112 in which a second other-side port passage 112a is formed. The housing 11 also has a third other-side port portion 113 in which a third other-side port passage 113a is formed, and a fourth other-side port portion 114 in which a fourth other-side port passage 114a is formed.

[0023] Each of the five ports 110, 111, 112, 113, and 114 is formed in a cylindrical shape. The one-side port passage 110a is disposed on one side of the first to fourth other-side port passages 111a, 112a, 113a, and 114a in the valve axial direction Da. For example, the one-side port portion 110 and the first to third other-side port portions 111, 112, and 113 each have a shape that protrudes outward in the valve radial direction Dr, and the fourth other-side port portion 114 has a shape that protrudes to the other side opposite to the one side in the valve axial direction Da. In the description of this embodiment, the first to fourth other-side port passages 111a, 112a, 113a, and 114a may be referred to as the first to fourth other-side port passages 111a to 114a.

[0024] In addition to the above-mentioned multiple port passages 110a, 111a, 112a, 113a, and 114a, multiple spaces 11a, 11b, 11c, 11d, and 11e are also formed inside the housing 11, which are separated from each other and through which the heat medium flows. Specifically, the one-side space 11a, the first other-side space 11b, the second other-side space 11c, the third other-side space 11d, and the fourth other-side space 11e are each formed inside the housing 11. In addition, the stator 12 and the rotor 16 separate the one-side space 11a from each of the first to fourth other-side spaces 11b, 11c, 11d, and 11e. The one-side space 11a is disposed on one side of the first to fourth other-side spaces 11b, 11c, 11d, and 11e in the valve axial direction Da, with the stator 12 and the rotor 16 sandwiched therebetween. In the description of this embodiment, the first to fourth other-side spaces 11b, 11c, 11d, and 11e may be referred to as the first to fourth other-side spaces 11b to 11e.

[0025] The one-side space 11a communicates with the one-side port passage 110a, the first other-side space 11b communicates with the first other-side port passage 111a, and the second other-side space 11c communicates with the second other-side port passage 112a. The third other-side space 11d communicates with the third other-side port passage 113a, and the fourth other-side space 11e communicates with the fourth other-side port passage 114a. In this embodiment, the third other-side space 11d corresponds to the other-side space of the present disclosure.

[0026] The first to fourth other-side spaces 11b to 11e are separated by partition walls provided in the housing 11 and are arranged side by side in the valve circumferential direction Dc. That is, the second other-side space 11c is arranged adjacent to one side of the first other-side space 11b in the valve circumferential direction Dc, and the third other-side space 11d is arranged adjacent to one side of the second other-side space 11c in the valve circumferential direction Dc. The fourth other-side space 11e is arranged adjacent to one side of the third other-side space 11d in the valve circumferential direction Dc, and the first other-side space 11b is arranged adjacent to one side of the fourth other-side space 11e in the valve circumferential direction Dc.

[0027] Further, the housing 11 is formed with a shaft insertion hole 11f into which the shaft 17 is inserted. This shaft insertion hole 11f is a blind hole whose bottom is on the other side in the valve axial direction Da, and extends in the valve axial direction Da with the valve axis Cv as its center line. The shaft insertion hole 11f extends further toward the other side in the valve axial direction Da from the portion of the shaft insertion hole 11f occupied by the shaft 17. That is, the shaft insertion hole 11f includes an other-side portion 11g located on the other side in the valve axial direction Da of the shaft 17 inserted into the shaft insertion hole 11f.

[0028] The shaft insertion hole 11f is disposed on the other side of the stator 12 in the valve axial direction Da, and is disposed inside the first to fourth other-side spaces 11b to 11e in the valve radial direction Dr. The housing 11 rotatably supports the shaft 17 by inserting the shaft 17 into the shaft insertion hole 11f.

[0029] 1 to 3, the stator 12 is formed, for example, in a substantially disk shape with the valve axis Cv as its center line, and is made of ceramic to obtain high sliding performance. The stator 12 is disposed within the housing 11 and is made unable to rotate relative to the housing 11, for example, by engagement between a recessed portion and a protruding portion (not shown). The stator 12 is also referred to as a fixed disk.

[0030] The stator 12 is provided as a flow passage hole forming portion in which first to fourth flow passage holes 121, 122, 123, and 124 through which the heat medium passes are formed in the housing 11. The first to fourth flow passage holes 121, 122, 123, and 124 are each formed as a through hole penetrating the stator 12 in the valve axis direction Da. In the description of this embodiment, the first to fourth flow passage holes 121, 122, 123, and 124 may be referred to as the first to fourth flow passage holes 121 to 124.

[0031] Here, the first to fourth other-side spaces 11b to 11e of the housing 11 are provided on the other side in the valve axis direction Da with respect to the stator 12. The first to fourth flow passage holes 121 to 124 of the stator 12 correspond one-to-one to the first to fourth other-side spaces 11b to 11e, respectively.

[0032] Therefore, the first other-side space 11b is connected to the first passage hole 121 of the stator 12 at one end of the first other-side space 11b in the valve axis direction Da, and communicates with the first passage hole 121. The second other-side space 11c is connected to the second passage hole 122 of the stator 12 at one end of the second other-side space 11c in the valve axis direction Da, and communicates with the second passage hole 122. The third other-side space 11d is connected to the third passage hole 123 of the stator 12 at one end of the third other-side space 11d in the valve axis direction Da, and communicates with the third passage hole 123. The fourth other-side space 11e is connected to the fourth passage hole 124 of the stator 12 at one end of the fourth other-side space 11e in the valve axis direction Da, and communicates with the fourth passage hole 124.

[0033] The first to fourth flow passage holes 121 to 124 of the stator 12 are arranged side by side in the valve circumferential direction Dc, similar to the first to fourth other-side spaces 11b to 11e. That is, the second flow passage hole 122 is arranged adjacent to one side of the first flow passage hole 121 in the valve circumferential direction Dc, and the third flow passage hole 123 is arranged adjacent to one side of the second flow passage hole 122 in the valve circumferential direction Dc. The fourth flow passage hole 124 is arranged adjacent to one side of the third flow passage hole 123 in the valve circumferential direction Dc, and the first flow passage hole 121 is arranged adjacent to one side of the fourth flow passage hole 124 in the valve circumferential direction Dc.

[0034] Further, the stator 12 is formed with an insertion hole 12a through which the shaft 17 is inserted. This insertion hole 12a penetrates the stator 12 in the valve axial direction Da, is formed with the valve axis Cv as its center line, and is disposed on the inside of the first to fourth flow passage holes 121-124 in the valve radial direction Dr.

[0035] 1 and 4, the rotor 16 is formed, for example, in a substantially disk shape with the valve axis Cv as the center line, and is made of ceramics to obtain high sliding performance. The rotor 16 is provided so as to be rotatable about the valve axis Cv. That is, the rotor 16 is rotatable about the valve axis Cv relative to the housing 11 and the stator 12. The rotor 16 is also called a drive disk.

[0036] The rotor 16 is disposed inside the housing 11 on one side of the stator 12 in the valve axial direction Da. More specifically, the rotor 16 is stacked on one side of the stator 12 in the valve axial direction Da and is in contact with the stator 12. Therefore, when the rotor 16 rotates, it rotates around the valve axis Cv while sliding against the stator 12.

[0037] The one-side space 11a of the housing 11 is provided on one side of the rotor 16 in the valve axial direction Da.

[0038] The rotor 16 is a rotary valve element that rotates around the valve axis Cv. The rotor 16 is formed with an aperture adjustment hole 161 as a through passage penetrating the rotor 16, and an interconnecting groove 162 as a return passage. The aperture adjustment hole 161 is a through hole that penetrates the rotor 16 in the valve axis direction Da.

[0039] The mutual communicating groove 162 has a groove bottom on one side in the valve axial direction Da and opens to the other side in the valve axial direction Da. The mutual communicating groove 162 is disposed away from the aperture adjustment hole 161 in the valve circumferential direction Dc, and extends in an arc shape centered on the valve axis Cv.

[0040] The rotor 16 increases and decreases the opening degree of each of the first to fourth passage holes 121 to 124 relative to the one-side space 11a as the rotor 16 rotates. For example, the rotor 16 overlaps the opening degree adjustment hole 161 on one side of the first passage hole 121 in the valve axis direction Da, and increases the overlap amount of the opening degree adjustment hole 161 with the first passage hole 121, thereby increasing the opening degree of the first passage hole 121 relative to the one-side space 11a. The opening degree of the second to fourth passage holes 122, 123, and 124 relative to the one-side space 11a is similar to this. That is, the rotor 16 selectively communicates the first to fourth passage holes 121 to 124 with the one-side space 11a via the opening degree adjustment hole 161 depending on the rotation position of the rotor 16.

[0041] The opening degree of the first passage hole 121 with respect to the one-side space 11a is the degree to which the first passage hole 121 is opened with respect to the one-side space 11a, and is expressed as 100% when the first passage hole 121 is fully opened and 0% when it is fully closed. The fully opening of the first passage hole 121 means that the opening degree of the first passage hole 121 with respect to the one-side space 11a is maximized. On the other hand, the fully closing of the first passage hole 121 means that the entire first passage hole 121 is blocked by the rotor 16 on one side of the valve axis direction Da with respect to the first passage hole 121. In this fully closed state, the flow of the heat medium between the one-side space 11a and the first other-side space 11b is blocked. The same applies to the opening degrees of the second to fourth passage holes 122, 123, and 124 with respect to the one-side space 11a. Just to confirm, among the first to fourth flow passage holes 121 to 124, a pair of flow passage holes that communicate with each other via the mutual communication groove 162 is separated from the one-side space 11a but is not completely closed.

[0042] The rotor 16 blocks one of the first to fourth passage holes 121 to 124 from the one-side space 11a while communicating the communication passage hole with a passage hole adjacent to the communication passage hole through the mutual communication groove 162, and switches the communication passage hole with the rotation of the rotor 16. In an example in which the first passage hole 121 corresponds to the communication passage hole, the rotor 16 overlaps the mutual communication groove 162 on one side of the first passage hole 121 and the second passage hole 122 in the valve axis direction Da, thereby communicating the first passage hole 121 and the second passage hole 122 through the mutual communication groove 162. Alternatively, the rotor 16 overlaps the mutual communication groove 162 on one side of the first passage hole 121 and the fourth passage hole 124 in the valve axis direction Da, thereby communicating the first passage hole 121 and the fourth passage hole 124 through the mutual communication groove 162. The same applies to the case where the second to fourth flow passage holes 122 to 124 correspond to the communicating flow passage holes.

[0043] Further, the rotor 16 is formed with an insertion hole 16a through which the shaft 17 is inserted. This insertion hole 16a is formed with the valve axis Cv as its center line, and penetrates the rotor 16 in the valve axial direction Da. The insertion hole 16a is disposed on the inside of the aperture adjustment hole 161 and the interconnecting groove 162 in the valve radial direction Dr.

[0044] The actuator 14 is a drive source that rotates the rotor 16, and includes a motor and a reducer (not shown). The motor is, for example, a stepping motor controlled by an external electronic control device, and the rotation of the motor is reduced in speed by the reducer before being transmitted to the rotor 16.

[0045] 1 and 5, the shaft body 18 is a power transmission shaft for transmitting the driving force output from the actuator 14 to the rotor 16. The shaft body 18 has a shaft portion 181 and a tubular portion 182 arranged on the other side of the shaft portion 181 in the valve axis direction Da. The shaft portion 181 and the tubular portion 182 are integrally configured.

[0046] The shaft portion 181 of the shaft body 18 extends in the valve axial direction Da with the valve axis Cv as its center line, and is rotatably supported in the housing 11 via a bearing 19. The tubular portion 182 of the shaft body 18 has a larger diameter than the shaft portion 181, and is cylindrical with a bottom on one side in the valve axial direction Da and an opening on the other side in the valve axial direction Da. Most of the tubular portion 182 of the shaft body 18 is disposed within the one-side space 11a of the housing 11.

[0047] Further, a shaft fitting hole 181a into which the shaft 17 is fitted and fixed is formed in the shaft portion 181 of the shaft body 18. This shaft fitting hole 181a is a blind hole whose bottom is on one side in the valve axial direction Da and opens at the bottom of the cylindrical portion 182, and extends in the valve axial direction Da with the valve axis Cv as its center line. Note that the bottom of the cylindrical portion 182 in this embodiment has a two-step structure with a step in the valve axial direction Da.

[0048] The shaft 17 is a mandrel with the valve axis Cv as its center line, and is for supporting the rotor 16 and the shaft body 18 rotatably around the valve axis Cv. The shaft 17 extends along the valve axis Cv from one side to the other side in the valve axis direction Da relative to the stator 12 and the rotor 16. In detail, the shaft 17 passes through the insertion hole 16a of the rotor 16 and the insertion hole 12a of the stator 12, penetrating the rotor 16 and the stator 12 in the valve axis direction Da. A small radial gap is formed between the hole wall surfaces of the insertion holes 12a, 16a and the shaft 17.

[0049] The shaft 17 has a shaft one part 171 and a shaft other part 172. The shaft one part 171 includes one end of the shaft 17 in the valve axis direction Da, and is located on one side of the valve axis direction Da with respect to a cylindrical part 182 of the shaft body 18. The shaft one part 171 is fixed to the shaft body 18 in a state where it is fitted into a shaft fitting hole 181a. This allows the shaft 17 to rotate integrally with the shaft body 18.

[0050] On the other hand, the other shaft part 172 includes the other end of the shaft 17 in the valve axial direction Da, and is located on the other side in the valve axial direction Da of the stator 12. The other shaft part 172 is inserted into the shaft insertion hole 11f of the housing 11, and is thereby supported so as to be rotatable relative to the housing 11.

[0051] Therefore, the shaft 17 and the shaft body 18 are rotatably supported by the bearing 19 on one side in the valve axial direction Da, and are rotatably supported by the hole wall surface of the shaft insertion hole 11f on the other side in the valve axial direction Da.

[0052] In addition, an O-ring 26 is provided in the insertion hole 12a of the stator 12 between the stator 12 and the shaft 17. This O-ring 26 prevents the flow of the heat transfer medium between the one-side space 11a and the shaft insertion hole 11f.

[0053] 1 and 4 to 6, the lever 20 transmits the rotation of the shaft body 18 to the rotor 16, and prevents the end 222 on the other side in the valve axis direction Da of the pressing spring 22 from being misaligned in the valve radial direction Dr. The lever 20 is accommodated in one side space 11a of the housing 11, and is disposed on one side of the rotor 16 in the valve axis direction Da.

[0054] Specifically, the lever 20 has a lever central portion 201 formed with the valve axis Cv as its center line, and a pair of arm portions 202 extending outward in the valve radial direction Dr from the lever central portion 201. The lever central portion 201 and the pair of arm portions 202 abut against the rotor 16 from one side in the valve axial direction Da.

[0055] An insertion hole 201a is formed in the lever central portion 201, which passes through the lever central portion 201 in the valve axial direction Da with the valve axis Cv as the center line. The shaft 17 is inserted through this insertion hole 201a. That is, the shaft 17 passes through the lever central portion 201 in the valve axial direction Da through the insertion hole 201a of the lever central portion 201. A small radial gap is formed between the hole wall surface of the insertion hole 201a of the lever central portion 201 and the shaft 17.

[0056] The lever central portion 201 is also formed with a spring support groove 201b provided on the outer side of the insertion hole 201a in the valve radial direction Dr. This spring support groove 201b extends in an annular shape centered on the valve axis Cv, has the other side in the valve axial direction Da as its groove bottom, and opens to one side in the valve axial direction Da. An end portion 222 of the pressing spring 22 on the other side in the valve axial direction Da is inserted into this spring support groove 201b.

[0057] As shown in Figures 4 to 7, each of the pair of arm portions 202 has an arm tip portion 202a arranged on the outside in the valve radial direction Dr, and a tip projection portion 202b protruding from the arm tip portion 202a to the other side in the valve axial direction Da.

[0058] A pair of fitting grooves 182a are formed in the cylindrical portion 182 of the shaft body 18 on the other end edge of the cylindrical portion 182 in the valve axial direction Da. The pair of fitting grooves 182a are symmetrically disposed in the valve radial direction Dr about the valve axis Cv. The arm tip portions 202a are fitted into the pair of fitting grooves 182a, respectively. This prevents the shaft body 18 and the lever 20 from rotating relative to each other.

[0059] In addition, since the depth of the fitting groove 182a in the valve axial direction Da is made larger than the width of the portion of the arm tip 202a that is fitted into the fitting groove 182a, a small axial gap 182b is formed between the bottom surface of the fitting groove 182a and the arm tip 202a. This axial gap 182b makes it possible to absorb dimensional errors in the valve axial direction Da of each component related to the relative positional relationship between the rotor 16 and the shaft body 18. In addition, since the lever 20 and the rotor 16 are constantly biased toward the other side in the valve axial direction Da by the pressing spring 22, rattling of the lever 20 and the rotor 16 in the valve axial direction Da caused by the above-mentioned axial gap 182b is prevented.

[0060] The rotor 16 has a rotor one surface 163 provided on one side of the valve axis direction Da and facing that side of the valve axis direction Da, and a pair of fitting recesses 163a (see Figs. 4, 7, and 16) recessed toward the other side of the valve axis direction Da are formed on the rotor one surface 163. The pair of fitting recesses 163a are symmetrically disposed in the valve radial direction Dr with the valve axis Cv as the center. The tip protrusions 202b of the lever 20 are fitted into the pair of fitting recesses 163a, respectively.

[0061] This prevents relative rotation between the rotor 16 and the lever 20. In other words, the lever 20, the shaft body 18, and the shaft 17 fixed to the shaft body 18 rotate together with the rotor 16 around the valve axis Cv.

[0062] 1 and 8, the pressing spring 22 and the differential pressure device 24 are pressing devices that press the rotor 16 against the stator 12, and are provided on one side of the rotor 16 in the valve axial direction Da. In this embodiment, the pressing spring 22 and the differential pressure device 24 are connected in series in a transmission path of a pressing force that presses the rotor 16 against the stator 12, and the differential pressure device 24 presses the rotor 16 in the valve axial direction Da via the pressing spring 22.

[0063] The stator 12 has a stator other surface 125 that is provided on the other side in the valve axial direction Da and faces the other side in the valve axial direction Da. A gasket 30 is provided between the stator other surface 125 and a portion of the housing 11 that faces the stator other surface 125. The gasket 30 is made of an elastic material.

[0064] The gasket 30 is disposed so as to surround the openings of the first to fourth flow passage holes 121 to 124 on the other surface 125 of the stator and separate the openings of the first to fourth flow passage holes 121 to 124 from one another. The stator 12 is pressed against the housing 11 in the valve axial direction Da by the pressing spring 22 or the differential pressure device 24, whereby the gasket 30 comes into close contact with the housing 11 and the stator 12, thereby sealing the gap between the housing 11 and the stator 12.

[0065] The pressing spring 22 is a compression coil spring that is disposed in the one-side space 11a of the housing 11 in a state in which it is compressed and deformed in the valve axial direction Da. In other words, the pressing spring 22 is an elastic body that can be elastically deformed. Since the pressing spring 22 is in a state in which it is compressed and deformed in the valve axial direction Da, it constantly generates a repulsive force against the compressive deformation. The pressing spring 22 is in the form of a coil that extends in the valve axial direction Da with the valve axis Cv as its center line.

[0066] The pressing spring 22 has one end 221 which is an end 221 on one side in the valve axial direction Da, and the other end 222 which is an end 222 on the other side in the valve axial direction Da. The pressing spring 22 is disposed between a pressing portion 242 of the differential pressure device 24 and a lever central portion 201, and the one end 221 of the pressing spring 22 abuts against the pressing portion 242 of the differential pressure device 24, while the other end 222 of the pressing spring 22 abuts against the lever central portion 201. With this arrangement, the pressing spring 22 presses the rotor 16 to the other side in the valve axial direction Da (in other words, toward the stator 12) via the lever 20 by the repulsive force against the compressive deformation of the pressing spring 22. The shaft 17 is inserted inside the pressing spring 22.

[0067] The differential pressure device 24 has a pressure chamber 24a into which the heat medium is introduced. The differential pressure device 24 generates a pressing force that presses the rotor 16 against the stator 12 by the pressure difference (in other words, the pressure difference) between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a.

[0068] Specifically, the differential pressure device 24 has a diaphragm 241 and a pressing portion 242 disposed inside the cylindrical portion 182 of the shaft body 18. Also, the pressure chamber 24a of the differential pressure device 24 is formed inside the cylindrical portion 182. In detail, the pressure chamber 24a is formed so as to be surrounded by the diaphragm 241, the pressing portion 242, and a part of the cylindrical portion 182 of the shaft body 18. This pressure chamber 24a is also referred to as a back pressure chamber.

[0069] The diaphragm 241 is a flexible film-like object, and is made of, for example, a thin metal sheet, resin, or rubber. The diaphragm 241 is formed in a substantially disk shape that spreads in the valve radial direction Dr around the valve axis Cv, and a through hole that penetrates in the valve axis direction Da is formed in the center of the diaphragm 241. The shaft 17 passes through the through hole of the diaphragm 241 and extends through the diaphragm 241.

[0070] The diaphragm 241 has an outer peripheral end 241a provided on the outside in the valve radial direction Dr, and an inner peripheral end 241b provided on the inside in the valve radial direction Dr. The outer peripheral end 241a is fixed to the cylindrical portion 182 of the shaft body 18 by a fixing part 28 fitted inside the cylindrical portion 182. In other words, the differential pressure device 24 is supported rotatably about the valve axis Cv with respect to the housing 11 via the shaft 17 fixed to the shaft body 18, and rotates integrally with the rotor 16 about the valve axis Cv. The space between the outer peripheral end 241a of the diaphragm 241 and the cylindrical portion 182 is airtight.

[0071] Moreover, an inner peripheral end 241b of the diaphragm 241 is fixed to a pressing portion 242 of the differential pressure device 24. The space between the inner peripheral end 241b of the diaphragm 241 and the pressing portion 242 is airtight.

[0072] The pressing portion 242 of the differential pressure device 24 is a bush into which the shaft 17 is inserted, and constitutes a portion of the differential pressure device 24 that presses the rotor 16 to the other side in the valve axial direction Da. In detail, since the pressing spring 22 and the lever central portion 201 are interposed between the pressing portion 242 and the rotor 16, the pressing portion 242 presses the rotor 16 via the pressing spring 22 and the lever central portion 201.

[0073] A pressing portion through-hole 242a penetrating in the valve axis direction Da is formed inside the pressing portion 242, and the shaft 17 is inserted into the pressing portion through-hole 242a. The pressing portion 242 is movable in the valve axis direction Da relative to the shaft 17. In other words, the inner peripheral end 241b of the diaphragm 241 connected to the pressing portion 242 is a movable end provided to be movable in the valve axis direction Da.

[0074] The space between the pressing portion 242 and the shaft 17 is airtight or substantially airtight to the extent that leakage of the heat medium does not affect the pressure P1 in the pressure chamber 24a. The pressing portion 242 stops at one end of its movement in the valve axial direction Da by hitting a stopper (not shown) provided on the shaft body 18, for example.

[0075] The diaphragm 241 and the pressing portion 242 are provided on the other side of the pressure chamber 24a of the differential pressure device 24 in the valve axis direction Da, and separate the pressure chamber 24a from the one-side space 11a. That is, the diaphragm 241 and the pressing portion 242 face the pressure chamber 24a, and face the one-side space 11a on the opposite side to the pressure chamber 24a side. Therefore, the pressure P1 in the pressure chamber 24a acts to press the pressing portion 242 toward the other side in the valve axis direction Da, and conversely, the pressure P2 in the one-side space 11a acts to press the pressing portion 242 toward one side in the valve axis direction Da.

[0076] In this embodiment, the pressure receiving area of ​​the diaphragm 241 and the pressing portion 242 on the pressure chamber 24a side is the same as the pressure receiving area of ​​the diaphragm 241 and the pressing portion 242 on the one-side space 11a side. Therefore, when the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1>P2", the differential pressure device 24 generates a pressing force that presses the rotor 16 against the stator 12 by the differential pressure between those pressures P1 and P2. On the other hand, when the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1≦P2", the differential pressure device 24 does not generate a pressing force that presses the rotor 16 against the stator 12 by the differential pressure between those pressures P1 and P2.

[0077] The pressure-receiving area on the pressure chamber 24a side is an area obtained by projecting the areas of the diaphragm 241 and the pressing portion 242 facing the pressure chamber 24a onto a virtual plane perpendicular to the valve axis direction Da along the valve axis direction Da. The pressure-receiving area on the one-side space 11a side is an area obtained by projecting the areas of the diaphragm 241 and the pressing portion 242 facing the one-side space 11a onto a virtual plane perpendicular to the valve axis direction Da along the valve axis direction Da.

[0078] As described above, the diaphragm 241 and the pressing portion 242 face the pressure chamber 24a, and a portion of the cylindrical portion 182 of the shaft body 18 also faces the pressure chamber 24a. Therefore, the portion of the cylindrical portion 182 facing the pressure chamber 24a constitutes a portion of the shaft body 18 and also constitutes a portion of the differential pressure device 24.

[0079] 1 and 8, the shaft 17 penetrates the pressure chamber 24a in the valve axial direction Da between the pressing portion 242 of the differential pressure device 24 and one shaft portion 171. Therefore, the shaft 17 has a pressure chamber exposed portion 173 exposed to the pressure chamber 24a.

[0080] A communication passage 17a that communicates the third other-side space 11d and the pressure chamber 24a is formed inside the shaft 17. This communication passage 17a extends in the valve axis direction Da. The communication passage 17a has one end 17b located on one side of the valve axis direction Da and the other end 17c located on the other side of the valve axis direction Da. The communication passage 17a extends inside the shaft 17 from one side to the other side in the valve axis direction Da relative to the stator 12 and the rotor 16.

[0081] The communication passage 17a is bent in the valve radial direction Dr at one end 17b and opens facing outward in the valve radial direction Dr at a pressure chamber exposed portion 173 of the shaft 17. As a result, the communication passage 17a communicates with the pressure chamber 24a at one end 17b.

[0082] The other end 17c of the communication passage 17a is an end of the shaft 17 on the other side of the valve axis direction Da and opens toward the other side of the valve axis direction Da. As a result, the communication passage 17a communicates with the shaft insertion hole 11f at the other end 17c. The housing 11 is formed with a connection hole 11j that penetrates between the shaft insertion hole 11f and the third other-side space 11d, and this connection hole 11j connects the other side portion 11g of the shaft insertion hole 11f and the third other-side space 11d to communicate with each other. Therefore, the other end 17c of the communication passage 17a communicates with the third other-side space 11d via the other side portion 11g of the shaft insertion hole 11f and the connection hole 11j.

[0083] In this way, the pressure chamber 24a communicates with the third other-side space 11d through the communication passage 17a of the shaft 17, the other-side portion 11g of the shaft insertion hole 11f, and the connection hole 11j in sequence. That is, since the communication passage 17a of the shaft 17 allows the third other-side space 11d and the pressure chamber 24a to communicate with each other, the pressure P1 in the pressure chamber 24a becomes the same as the pressure in the third other-side space 11d. Therefore, when the pressure in the third other-side space 11d is higher than the pressure P2 in the one-side space 11a, the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1 > P2". In this case, the differential pressure device 24 generates a pressing force that presses the rotor 16 against the stator 12 by the differential pressure between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a. And that pressing force increases as the pressure P1 in the pressure chamber 24a becomes larger relative to the pressure P2 in the one-side space 11a.

[0084] On the other hand, when the pressure in the third other-side space 11d is lower than the pressure P2 in the one-side space 11a, the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1 < P2". And when the pressure in the third other-side space 11d is the same as the pressure P2 in the one-side space 11a, the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1 = P2". In these cases, the differential pressure between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a does not bias the pressing portion 242 of the differential pressure device 24 to the other side in the valve shaft direction Da. In other words, the differential pressure device 24 does not generate a pressing force that presses the rotor 16 against the stator 12 by that differential pressure.

[0085] For example, when the discharge side of the pump in the heat medium circuit is connected to the one-side port passage 110a and the third flow path hole 123 of the stator 12 is fully closed, the pressure in the third other-side space 11d becomes lower than the pressure P2 in the one-side space 11a. Also, when the discharge side of the pump in the heat medium circuit is connected to the one-side port passage 110a and the heat medium flows from the one-side space 11a to the third other-side space 11d, the pressure in the third other-side space 11d also becomes lower than the pressure P2 in the one-side space 11a. In these cases, the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a become "P1 < P2". Therefore, the differential pressure between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a does not urge the pressing portion 242 of the differential pressure device 24 to the other side in the valve shaft direction Da. As a result, the pressing portion 242 moves to the moving end on the one side in the valve shaft direction Da as shown in Fig. 9(a) by the elastic force of the pressing spring 22.

[0086] On the other hand, for example, when the discharge side of the pump in the heat medium circuit is connected to the third other-side port passage 113a and the third flow path hole 123 of the stator 12 is fully closed, the pressure in the third other-side space 11d becomes higher than the pressure P2 in the one-side space 11a. Also, when the discharge side of the pump in the heat medium circuit is connected to the third other-side port passage 113a and the heat medium flows from the third other-side space 11d to the one-side space 11a, the pressure in the third other-side space 11d also becomes higher than the pressure P2 in the one-side space 11a. In these cases, the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a become "P1 > P2".

[0087] As a result, the pressing portion 242 of the differential pressure device 24 is pushed to the other side in the valve shaft direction Da by the differential pressure between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a, and moves from the moving end on the one side in the valve shaft direction Da to the other side in the valve shaft direction Da as shown in Fig. 9(b). Thereby, the differential pressure device 24 generates a pressing force for pressing the rotor 16 against the stator 12.

[0088] 1, in the valve device 10 configured as above, the driving force of the actuator 14 is first transmitted to the shaft body 18, and then from the shaft body 18 to the lever 20 and the rotor 16. The driving force of the actuator 14 causes the shaft body 18, rotor 16, shaft 17, lever 20, pressing spring 22, differential pressure device 24 and fixed component 28 to rotate together about the valve axis Cv.

[0089] For example, when the rotor 16 rotates, the other-side space that communicates with the one-side space 11a via the aperture adjustment hole 161 of the rotor 16 is switched among the first to fourth other-side spaces 11b to 11e in accordance with the rotation of the rotor 16. Also, as the rotor 16 rotates, a pair of other-side spaces that communicate with each other via the mutual communication groove 162 of the rotor 16 is switched among the first to fourth other-side spaces 11b to 11e.

[0090] In this embodiment, a forward flow of the heat medium and a reverse flow of the heat medium can occur. The forward flow of the heat medium is a flow of the heat medium from the one-side port passage 110a to any one of the multiple other-side port passages 111a, 112a, 113a, and 114a. The reverse flow of the heat medium is a flow of the heat medium from any one of the multiple other-side port passages 111a, 112a, 113a, and 114a to the one-side port passage 110a.

[0091] For example, in the case where the heat medium flows between the one-side port passage 110a and the third other-side port passage 113a, both a forward flow and a reverse flow of the heat medium can occur. In either case of the forward flow or the reverse flow of the heat medium, the opening degree of the third flow passage hole 123 of the stator 12 with respect to the one-side space 11a is increased or decreased depending on the rotational position of the rotor 16, and the third flow passage hole 123 can be fully closed or fully open. This is also true for the case where the heat medium flows between the one-side port passage 110a and each of the first, second, and fourth other-side port passages 111a, 112a, and 114a.

[0092] As described above, according to this embodiment, as shown in Figs. 1 and 8, when the pressure in the third other-side space 11d is higher than the pressure P2 in the one-side space 11a, the differential pressure device 24 operates as follows. That is, in this case, the differential pressure device 24 generates a pressing force for pressing the rotor 16 against the stator 12 by the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a. The pressing force increases as the pressure P1 in the pressure chamber 24a increases relative to the pressure P2 in the one-side space 11a. In other words, the pressing force increases as the pressure P1 in the pressure chamber 24a is equal to or higher than the pressure P2 in the one-side space 11a and the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a increases.

[0093] Here, when the pressure in the third other-side space 11d is higher than the pressure P2 in the one-side space 11a, a back pressure, which is a fluid pressure that lifts the rotor 16 from the stator 12, is generated, and the force that lifts the rotor 16 is proportional to the back pressure. In contrast, in this embodiment, the differential pressure device 24 presses the rotor 16 against the stator 12 via the pressing spring 22 and the lever 20 against the back pressure. The pressing force of the differential pressure device 24 increases as the pressure P1 in the pressure chamber 24a increases relative to the pressure P2 in the one-side space 11a, so that the pressing force of the differential pressure device 24 is adjusted according to the magnitude of the back pressure. For example, if no back pressure is generated, the pressing force of the differential pressure device 24 is minimized.

[0094] Therefore, in the forward flow and the reverse flow of the heat medium between the one-side space 11a and the third other-side space 11d, it is possible to prevent the friction torque between the rotor 16 and the stator 12 from becoming excessively large. And, while preventing the friction torque from becoming excessively large, it is possible to prevent the rotor 16 from lifting up from the stator 12.

[0095] For example, the pressure-receiving areas of the one-side space 11a side and the pressure chamber 24a side of the diaphragm 241 and the pressing portion 242 may be designed so that the lifting load that tries to lift the rotor 16 from the stator 12 when a back pressure occurs is balanced with the pressing force of the differential pressure device 24. In this way, the pressing force of the differential pressure device 24 for suppressing the lifting of the rotor 16 is neither too much nor too little in proportion to the magnitude of the back pressure. Therefore, whether the heat medium is flowing in the forward direction or the reverse direction, the pressing force pressing the rotor 16 against the stator 12 does not change significantly, and the driving torque for rotating the rotor 16 does not change significantly either.

[0096] (1) According to this embodiment, the communication passage 17a is provided to communicate the third other-side space 11d with the pressure chamber 24a. Therefore, when a back pressure that lifts the rotor 16 from the stator 12 due to the pressure in the third other-side space 11d is acting, the differential pressure device 24 can press the rotor 16 against the stator 12. This can suppress the rotor 16 from lifting up due to the back pressure. Furthermore, when no back pressure is occurring, for example, in the case of a forward flow of the heat medium, the pressing force of the differential pressure device 24 is minimized, so that it is possible to reduce the drive torque that rotates the rotor 16.

[0097] (2) Furthermore, according to this embodiment, the communication passage 17a that communicates the third other-side space 11d and the pressure chamber 24a is formed inside the shaft 17. Therefore, for example, compared to a case in which the communication passage 17a is provided in an external pipe installed outside the housing 11, it is possible to configure the valve device 10 more compactly.

[0098] (3) Furthermore, according to this embodiment, the differential pressure device 24 is rotatably supported around the valve axis Cv relative to the housing 11 via the shaft 17, and rotates together with the rotor 16 around the valve axis Cv. Therefore, it is possible for the pressing portion 242 of the differential pressure device 24 to press the rotor 16 against the stator 12 without causing sliding in the valve circumferential direction Dc between the pressing portion 242 of the differential pressure device 24 and the rotor 16. Furthermore, because there is no sliding in the valve circumferential direction Dc between the pressing portion 242 and the rotor 16, there is no increase in torque due to friction caused by the sliding.

[0099] (4) Furthermore, according to this embodiment, the diaphragm 241 of the differential pressure device 24 is provided on the other side in the valve axis direction Da with respect to the pressure chamber 24a of the differential pressure device 24, and separates the pressure chamber 24a from the one-side space 11a. The diaphragm 241 has an inner peripheral end portion 241b as a movable end portion that is provided movably in the valve axis direction Da and connected to the pressing portion 242 of the differential pressure device 24. The pressure P1 in the pressure chamber 24a acts to press the pressing portion 242 toward the other side in the valve axis direction Da, and the pressing portion 242 presses the rotor 16 toward the other side in the valve axis direction Da.

[0100] Therefore, by using the diaphragm 241, it is possible to reduce the volume occupied by the configuration in which the rotor 16 is pressed against the stator 12 by the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a.

[0101] (5) Furthermore, according to this embodiment, the pressing spring 22, which is an elastic body, is installed in a state in which it is compressed and deformed in the valve axial direction Da, and the repulsive force against the compressive deformation presses the rotor 16 to the other side in the valve axial direction Da. Therefore, regardless of the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a, it is possible to constantly generate a pressing force that presses the rotor 16 against the stator 12.

[0102] Second embodiment Next, a second embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described. Also, parts that are the same as or equivalent to the above-mentioned embodiment will be omitted or simplified. This also applies to the following embodiments.

[0103] As shown in Figs. 10 to 13, the valve device 10 of this embodiment includes a check valve 32. The check valve 32 is accommodated in the other side portion 11g of the shaft insertion hole 11f. The check valve 32 is made of, for example, metal or resin. The check valve 32 is made of a thin elastic plate material, and is formed into a cylindrical shape by bending the plate material around the valve axis Cv. The check valve 32 is in close contact with the peripheral wall surface of the other side portion 11g of the shaft insertion hole 11f over its entire circumference due to the elasticity of the check valve 32 tending to expand in diameter. That is, the check valve 32 has a simple rolled plate shape in which a thin plate material is rolled around the peripheral wall surface of the other side portion 11g.

[0104] In addition, in the housing 11 of this embodiment, a first connecting hole 115a, a second connecting hole 115b, a third connecting hole 115c, and a fourth connecting hole 115d are formed instead of the connecting hole 11j (see FIG. 1) of the first embodiment. The first connecting hole 115a penetrates between the other side portion 11g of the shaft insertion hole 11f and the first other side space 11b in the valve radial direction Dr, and communicates between the other side portion 11g and the first other side space 11b via the check valve body 32. The second connecting hole 115b penetrates between the other side portion 11g of the shaft insertion hole 11f and the second other side space 11c in the valve radial direction Dr, and communicates between the other side portion 11g and the second other side space 11c via the check valve body 32.

[0105] The third connecting hole 115c penetrates between the other side portion 11g of the shaft insertion hole 11f and the third other-side space 11d in the valve radial direction Dr, and communicates between the other side portion 11g and the third other-side space 11d via the check valve body 32. The fourth connecting hole 115d penetrates between the other side portion 11g of the shaft insertion hole 11f and the fourth other-side space 11e in the valve radial direction Dr, and communicates between the other side portion 11g and the fourth other-side space 11e via the check valve body 32. The third connecting hole 115c is the same as the connecting hole 11j in the first embodiment.

[0106] Since the first to fourth connecting holes 115a, 115b, 115c, and 115d are provided in this manner, the communication passage 17a of the shaft 17 is connected to the first to fourth other-side spaces 11b to 11e, respectively, via the check valve body 32. In the description of this embodiment, the first to fourth connecting holes 115a, 115b, 115c, and 115d may be referred to as the first to fourth connecting holes 115a to 115d.

[0107] Among the first to fourth connecting holes 115a to 115d, connecting holes adjacent to each other in the valve circumferential direction Dc are arranged so as to be staggered in the valve axial direction Da. For example, the first connecting hole 115a and the third connecting hole 115c are arranged shifted to the other side in the valve axial direction Da with respect to the second connecting hole 115b and the fourth connecting hole 115d. The position of the first connecting hole 115a in the valve axial direction Da is the same as the position of the third connecting hole 115c, and the position of the second connecting hole 115b in the valve axial direction Da is the same as the position of the fourth connecting hole 115d.

[0108] The check valve element 32 has a portion covering the opening of the first connecting hole 115a as a first check valve portion 321, and a portion covering the opening of the second connecting hole 115b as a second check valve portion 322. The check valve element 32 has a portion covering the opening of the third connecting hole 115c as a third check valve portion 323, and a portion covering the opening of the fourth connecting hole 115d as a fourth check valve portion 324.

[0109] For example, the operation of the first check valve portion 321 will be described. When the heat medium flows from the first other-side space 11b to the communicating passage 17a, the first check valve portion 321 deforms and rises from the peripheral wall surface of the shaft insertion hole 11f, creating a gap between the first check valve portion 321 and the peripheral wall surface of the shaft insertion hole 11f. As a result, the heat medium can flow through the gap, and the first check valve portion 321 allows the heat medium to flow from the first other-side space 11b to the communicating passage 17a.

[0110] On the other hand, with respect to the flow of the heat medium from the communication passage 17a to the first other-side space 11b, the first check valve portion 321 is pressed against the peripheral wall surface of the shaft insertion hole 11f by the pressure in the shaft insertion hole 11f and is in close contact with the peripheral wall surface, so that the first check valve portion 321 blocks the flow of the heat medium from the communication passage 17a to the first other-side space 11b.

[0111] The second to fourth check valves 322, 323, and 324 operate in the same manner as the first check valve 321. The second check valve 322 allows the heat medium to flow from the second other-side space 11c to the communication passage 17a, while blocking the heat medium from the communication passage 17a to the second other-side space 11c. The third check valve 323 allows the heat medium to flow from the third other-side space 11d to the communication passage 17a, while blocking the heat medium from the communication passage 17a to the third other-side space 11d. The fourth check valve 324 allows the heat medium to flow from the fourth other-side space 11e to the communication passage 17a, while blocking the heat medium from the communication passage 17a to the fourth other-side space 11e.

[0112] Here, for example, it is assumed that the first other-side space 11b among the first to fourth other-side spaces 11b to 11e is the highest pressure, and the above-mentioned back pressure occurs. In this case, the first check valve portion 321 operates to allow the heat medium to flow from the first other-side space 11b to the communication passage 17a, so that the pressure in the shaft insertion hole 11f and the pressure P1 in the pressure chamber 24a become the same as the pressure in the first other-side space 11b. On the other hand, the pressures in the second to fourth other-side spaces 11c, 11d, and 11e are all lower than the pressure in the shaft insertion hole 11f, so that the second to fourth check valve portions 322, 323, and 324 are in close contact with the peripheral wall surface of the shaft insertion hole 11f, respectively, and block the second to fourth connecting holes 115b, 115c, and 115d. Therefore, the heat medium that has flowed from the first other-side space 11b into the shaft insertion hole 11f is prevented from flowing into any of the second to fourth other-side spaces 11c, 11d, and 11e.

[0113] This also applies to the case where any one of the second to fourth other-side spaces 11c, 11d, and 11e among the first to fourth other-side spaces 11b to 11e becomes the highest pressure, causing the above-mentioned back pressure.

[0114] 10, a pressure reduction hole 182c extending from the pressure chamber 24a to the one-side space 11a of the housing 11 is formed in the cylindrical portion 182 of the shaft body 18. This pressure reduction hole 182c is provided as a leakage passage that allows leakage of the heat medium from the pressure chamber 24a to the one-side space 11a when the pressure P1 in the pressure chamber 24a is higher than the pressure P2 in the one-side space 11a.

[0115] The flow passage cross section of this decompression hole 182c is very small. Specifically, the decompression hole 182c is formed to increase the flow passage resistance for all of the heat medium flow passages connecting each of the first to fourth other-side spaces 11b to 11e and the pressure chamber 24a. Therefore, when the above-mentioned back pressure occurs, the decompression hole 182c does not prevent the pressure of the heat medium causing the back pressure, among the pressures of the heat medium in the first to fourth other-side spaces 11b to 11e, from being introduced into the pressure chamber 24a, causing the pressure P1 in the pressure chamber 24a to rise.

[0116] (1) As described above, according to this embodiment, the valve device 10 includes the first to fourth check valve portions 321, 322, 323, and 324. The first check valve portion 321 allows the heat medium to flow from the first other-side space 11b to the communicating passage 17a, while blocking the heat medium from flowing from the communicating passage 17a to the first other-side space 11b. The second to fourth check valve portions 322, 323, and 324 operate in the same manner as the first check valve portion 321 for the second to fourth other-side spaces 11c, 11d, and 11e.

[0117] Therefore, the pressure of the heat medium can be guided from any of the first to fourth other-side spaces 11b to 11e to the pressure chamber 24a of the differential pressure device 24. That is, even if the above-mentioned back pressure occurs due to any of the pressures in the first to fourth other-side spaces 11b to 11e, the differential pressure device 24 can generate a pressing force that presses the rotor 16 against the stator 12. And, it is possible to prevent the first to fourth other-side spaces 11b to 11e from communicating with each other via the shaft insertion hole 11f.

[0118] (2) Furthermore, according to this embodiment, the pressure reduction hole 182c of the shaft body 18 is provided as a leakage passage that allows leakage of the heat medium from the pressure chamber 24a to the one-side space 11a when the pressure P1 in the pressure chamber 24a is higher than the pressure P2 in the one-side space 11a.

[0119] Here, since the check valve 32 is provided, the pressure P1 in the pressure chamber 24a does not escape to any of the first to fourth other-side spaces 11b to 11e through the communication passage 17a. Therefore, if the decompression hole 182c is not provided, the pressure P1 in the pressure chamber 24a, which has increased due to the introduction of the heat medium from any of the first to fourth other-side spaces 11b to 11e, would be maintained at that increased pressure. The decompression hole 182c is provided to prevent this.

[0120] That is, when the counter pressure acts once on the rotor 16 and then ceases to act thereon, and a pressure higher than the pressure P2 in the one-side space 11a is no longer introduced into the pressure chamber 24a, the heat medium can be discharged from the pressure chamber 24a to the one-side space 11a through the pressure reduction hole 182c. In short, when the counter pressure ceases to act on the rotor 16, the pressure chamber 24a can be quickly reduced in pressure, and the pressing force with which the differential pressure device 24 presses the rotor 16 against the stator 12 can be weakened.

[0121] Furthermore, according to this embodiment, the first to fourth check valve portions 321, 322, 323, and 324 are included in the check valve element 32 made of a single roll plate. Therefore, it is not necessary to provide check valve portions made of separate parts for the first to fourth connecting holes 115a to 115d, respectively.

[0122] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0123] Third embodiment Next, a third embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described.

[0124] As shown in Figs. 14 to 15B, the housing 11 of this embodiment is formed with a first connecting hole 116a, a second connecting hole 116b, a third connecting hole 116c, and a fourth connecting hole 116d instead of the connecting hole 11j (see Fig. 1) of the first embodiment. The first connecting hole 116a penetrates between the shaft insertion hole 11f and the first other-side space 11b in the valve radial direction Dr, and communicates the shaft insertion hole 11f with the first other-side space 11b. The second connecting hole 116b penetrates between the shaft insertion hole 11f and the second other-side space 11c in the valve radial direction Dr, and communicates the shaft insertion hole 11f with the second other-side space 11c. In this embodiment, the shaft insertion hole 11f corresponds to the insertion hole of the present disclosure.

[0125] The third connecting hole 116c penetrates between the shaft insertion hole 11f and the third other-side space 11d in the valve radial direction Dr, and communicates the shaft insertion hole 11f with the third other-side space 11d. The fourth connecting hole 116d penetrates between the shaft insertion hole 11f and the fourth other-side space 11e in the valve radial direction Dr, and communicates the shaft insertion hole 11f with the fourth other-side space 11e. The first to fourth connecting holes 116a, 116b, 116c, and 116d are arranged so that their positions in the valve axial direction Da are the same. In the description of this embodiment, the first to fourth connecting holes 116a, 116b, 116c, and 116d may be referred to as the first to fourth connecting holes 116a to 116d.

[0126] In this embodiment, the shaft 17 is inserted over substantially the entire length of the shaft insertion hole 11f, so that the other side portion 11g (see FIG. 1) of the shaft insertion hole 11f is extremely small. The first to fourth connecting holes 116a to 116d in this embodiment open within the range of the shaft insertion hole 11f in the valve axis direction Da that the shaft 17 occupies. In other words, the first to fourth connecting holes 116a to 116d are arranged so as to overlap the outside of the shaft other part 172 in the valve radial direction Dr.

[0127] In this embodiment, similarly to the first embodiment, the other shaft part 172 is rotatable relative to the housing 11. However, in this embodiment, the gap between the other shaft part 172 and the peripheral wall surface of the shaft insertion hole 11f is airtight or approximately airtight to the extent that leakage of the heat medium can be ignored.

[0128] In this embodiment, as shown in Fig. 15A and Fig. 16, the rotor 16 has a fully closed angle range Ac which is an angle range centered on the valve axis Cv and in which the aperture adjustment hole 161 and the mutual communication groove 162 are not provided. The first passage hole 121 is fully closed when a portion of the rotor 16 in this fully closed angle range Ac covers, for example, the entire opening of the first passage hole 121 of the stator 12. The same applies to the fully closed second to fourth passage holes 122, 123, 124. The fully closed angle range Ac is the same as in the first embodiment described above.

[0129] 14 to 15B, unlike the first embodiment, the other shaft part 172 of the present embodiment is formed with a side hole 172b that opens on the outer circumferential surface 172a of the other shaft part 172. This side hole 172b is included in the communication passage 17a and forms an end portion of the communication passage 17a that is located on the other side in the valve axial direction Da.

[0130] Specifically, on the outer circumferential surface 172a of the other shaft part 172, the side hole 172b of the other shaft part 172 opens at a predetermined position within the fully closed angular range Ac of the rotor 16. The predetermined position is determined so that the first connecting hole 116a and the side hole 172b communicate with each other when the first flow passage hole 121 of the stator 12 is fully closed, and the second connecting hole 116b and the side hole 172b communicate with each other when the second flow passage hole 122 is fully closed. Since the shaft 17 and the rotor 16 rotate integrally, the relative positional relationship between the side hole 172b of the other shaft part 172 and the fully closed angular range Ac of the rotor 16 does not change even when the shaft 17 rotates.

[0131] Therefore, as shown in, for example, Fig. 15A and Fig. 15B, when the entire opening of the first passage hole 121 on the rotor 16 side enters within the fully closed angle range Ac of the rotor 16, the first passage hole 121 is fully closed by the rotor 16. At this time, the opening of the first connecting hole 116a and the opening of the side hole 172b of the shaft other part 172 face each other, and the side hole 172b selectively communicates only with the first connecting hole 116a among the first to fourth connecting holes 116a to 116d. As a result, the pressure in the first other-side space 11b is introduced into the pressure chamber 24a in a state in which the first to fourth other-side spaces 11b to 11e are disconnected from each other. Note that Fig. 15B shows the orientation of the side hole 172b (in other words, the orientation of the shaft 17) when the rotor 16 is in the rotation position shown in Fig. 15A.

[0132] When the rotor 16 rotates slightly to one side in the valve circumferential direction Dc from the state shown in Figures 15A and 15B, the rotor 16 and the shaft 17 reach the state shown in Figures 17A and 17B. Note that Figure 17B shows the orientation of the side hole 172b when the rotor 16 is in the rotational position shown in Figure 17A.

[0133] 17A and 17B, none of the first and second flow passage holes 121, 122 of the stator 12 are fully closed. The side hole 172b of the other shaft part 172 is located between the first connecting hole 116a and the second connecting hole 116b in the valve circumferential direction Dc, and does not communicate with any of the first to fourth connecting holes 116a to 116d.

[0134] Furthermore, when the rotor 16 rotates slightly from the state shown in Fig. 17A and Fig. 17B to one side in the valve circumferential direction Dc, the rotor 16 and the shaft 17 reach the state shown in Fig. 18A and Fig. 18B. In this state shown in Fig. 18A and Fig. 18B, the entire opening of the second passage hole 122 on the rotor 16 side is within the full-closing angle range Ac of the rotor 16, so the second passage hole 122 is fully closed by the rotor 16. At this time, the opening of the second connection hole 116b and the opening of the side hole 172b of the shaft other part 172 face each other, and the side hole 172b selectively communicates only with the second connection hole 116b among the first to fourth connection holes 116a to 116d. As a result, the pressure in the second other-side space 11c is introduced into the pressure chamber 24a in a state in which the communication between the first to fourth other-side spaces 11b to 11e is blocked. It should be noted that FIG. 18B shows the orientation of the side hole 172b when the rotor 16 is in the rotational position shown in FIG. 18A.

[0135] Here, it is assumed that the suction side of a pump that circulates the heat medium in a heat medium circuit including the valve device 10 of this embodiment is connected to the one-side port passage 110a. It is also assumed that the discharge side of the pump is connected to all of the other-side port passages except for one of the pair of other-side port passages that are communicated via the mutual communication groove 162 of the rotor 16 among the first to fourth other-side port passages 111a to 114a.

[0136] In this case, in the state shown in FIG. 15A and FIG. 15B, the flow of the heat medium occurs in the second to fourth other-side spaces 11c, 11d, and 11e among the first to fourth other-side spaces 11b to 11e, but the reverse flow of the heat medium is blocked by the rotor 16 in the first other-side space 11b. In the flow path in which the fluid flows, pressure loss occurs when the fluid passes through the heat exchanger and piping included in the heat medium circuit, so the pressure of the fluid drops when the fluid reaches the valve device 10. However, since no fluid flows in the blocked flow path, the pressure of the fluid does not drop, and the discharge pressure of the pump acts on the valve device 10 as it is. Therefore, the first other-side space 11b is the highest pressure space among the first to fourth other-side spaces 11b to 11e. That is, the first other-side space 11b becomes the highest pressure space by fully closing the first flow path hole 121 of the stator 12. As shown in FIG. 15B, the communication passage 17a of the shaft 17 communicates with the first other-side space 11b when the first other-side space 11b is the highest pressure space.

[0137] 18A and 18B, the flow of the heat medium occurs in the first, third and fourth other-side spaces 11b, 11d and 11e among the first to fourth other-side spaces 11b to 11e, but the reverse flow of the heat medium is blocked by the rotor 16 in the second other-side space 11c. Therefore, the second other-side space 11c is the maximum pressure space. That is, the second other-side space 11c becomes the maximum pressure space by fully closing the second flow passage hole 122 of the stator 12. Then, as shown in FIG. 18B, the communication passage 17a of the shaft 17 communicates with the second other-side space 11c when the second other-side space 11c becomes the maximum pressure space.

[0138] In this way, the maximum pressure space switches from the first other-side space 11b to the second other-side space 11c as the rotor 16 rotates to one side in the valve circumferential direction Dc. Conversely, the maximum pressure space switches from the second other-side space 11c to the first other-side space 11b as the rotor 16 rotates to the other side in the valve circumferential direction Dc.

[0139] 15A and 15B, the pressures in the first to fourth other-side spaces 11b to 11e all act on the rotor 16 as the above-mentioned back pressures, with the pressure in the first other-side space 11b, which is the highest pressure space, being the largest back pressure. Also, in the state shown in Figures 18A and 18B, the pressures in the first to fourth other-side spaces 11b to 11e all act on the rotor 16 as the above-mentioned back pressures, with the pressure in the second other-side space 11c, which is the highest pressure space, being the largest back pressure.

[0140] In this embodiment, the third flow passage hole 123 of the stator 12 may be entirely covered by a portion of the fully closed angle range Ac of the rotor 16 and be entirely closed. In this case, the side hole 172b of the other shaft part 172 communicates only with the third connecting hole 116c among the first to fourth connecting holes 116a to 116d. Similarly, the fourth flow passage hole 124 may be entirely covered by a portion of the fully closed angle range Ac of the rotor 16 and be entirely closed. In this case, the side hole 172b of the other shaft part 172 communicates only with the fourth connecting hole 116d among the first to fourth connecting holes 116a to 116d.

[0141] (1) As shown in Figures 15A, 15B, 18A and 18B, according to this embodiment, when the counter pressure acts on the rotor 16, the highest pressure space among the first to fourth other-side spaces 11b to 11e switches, for example, as follows. That is, the highest pressure space switches from the first other-side space 11b to the second other-side space 11c as the rotor 16 rotates to one side in the valve circumferential direction Dc. The communication passage 17a of the shaft 17 communicates with the first other-side space 11b when the first other-side space 11b is the highest pressure space, and communicates with the second other-side space 11c when the second other-side space 11c is the highest pressure space.

[0142] Therefore, the pressure of the heat medium can be guided from either the first or second other-side space 11b, 11c to the pressure chamber 24a of the differential pressure device 24. Moreover, whichever of the first or second other-side space 11b, 11c becomes the highest pressure space, the pressure in that highest pressure space can be guided to the pressure chamber 24a of the differential pressure device 24. That is, it is possible to generate a pressing force that presses the rotor 16 against the stator 12 by the pressure P1 in the pressure chamber 24a, with a magnitude corresponding to the largest of the above-mentioned back pressures.

[0143] Furthermore, according to this embodiment, when the first other-side space 11b is the highest pressure space depending on the rotational position of the rotor 16, the first connecting hole 116a of the housing 11 and the side hole 172b of the shaft other part 172 communicate with each other. When the second other-side space 11c is the highest pressure space, the second connecting hole 116b of the housing 11 and the side hole 172b of the shaft other part 172 communicate with each other.

[0144] Therefore, it is possible to communicate the communication passage 17a of the shaft 17 with the highest pressure space among the first to fourth other-side spaces 11b to 11e while preventing the first to fourth other-side spaces 11b to 11e from communicating with each other through the shaft insertion hole 11f. And, it is possible to guide the counter pressure to the pressure chamber 24a while preventing the first to fourth other-side spaces 11b to 11e from communicating with each other without adding a part such as the check valve body 32 of the second embodiment (see FIG. 11).

[0145] Furthermore, according to this embodiment, the first other-side space 11b becomes the highest pressure space when the first flow passage hole 121 of the first to fourth flow passage holes 121 to 124 of the stator 12 is fully closed. The second other-side space 11c becomes the highest pressure space when the second flow passage hole 122 of the stator 12 is fully closed.

[0146] Here, which of the first and second flow passage holes 121, 122 of the stator 12 is fully closed is determined according to the rotational position of the rotor 16 and the opening shape of the rotor 16 (for example, the arrangement of the aperture adjustment hole 161 and the mutual communication groove 162). Since the rotor 16 and the shaft 17 rotate together about the valve axis Cv, the side hole 172b of the other shaft part 172 also rotates together with the rotor 16.

[0147] Therefore, the opening direction of the communicating passage 17a (specifically, the direction of the side hole 172b) can be easily determined in accordance with the above-mentioned opening shape of the rotor 16 so that the connecting passage 17a of the shaft 17 connects to the highest pressure space.

[0148] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0149] (Fourth embodiment) Next, a fourth embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described.

[0150] 19 and 20, in the present embodiment, as in the first embodiment, the valve device 10 constitutes a part of a heat medium circuit 70 in which a heat medium circulates. The heat medium circuit 70 corresponds to the fluid circuit of the present disclosure. The heat medium circuit 70 includes a pump 71, which is disposed outside the valve device 10, i.e., outside the housing 11 of the valve device 10.

[0151] In the heat medium circuit 70 , the heat medium is discharged from a discharge port 711 of the pump 71 , and the discharged heat medium circulates through the heat medium circuit 70 before being sucked into a suction port 712 of the pump 71 .

[0152] In the heat medium circuit 70 of this embodiment, the discharge side of the pump 71 can be connected to each of the first to fourth other-side port passages 111a to 114a of the valve device 10 via an intermediate circuit 701 that constitutes a part of the heat medium circuit 70. The intermediate circuit 701 is composed of, for example, a plurality of heat exchangers and pipes. The discharge side of the pump 71 may be connected to any of the first to fourth other-side port passages 111a to 114a or to all of the first to fourth other-side port passages 111a to 114a depending on the circuit configuration of the intermediate circuit 701. In this embodiment, the one-side port passage 110a of the valve device 10 is connected to the suction side of the pump 71.

[0153] Further, an external communication hole 11k is formed in the housing 11 of the valve device 10, penetrating from the other side portion 11g of the shaft insertion hole 11f to the outside of the housing 11. A discharge port 711 of the pump 71 is connected to this external communication hole 11k via a pipe of the heat medium circuit 70. Inside the housing 11, the external communication hole 11k is communicated with the pressure chamber 24a of the differential pressure device 24 via the other side portion 11g of the shaft insertion hole 11f and the communication passage 17a of the shaft 17 in this order. Therefore, the communication passage 17a of the shaft 17 in this embodiment communicates the discharge side of the pump 71 with the pressure chamber 24a of the differential pressure device 24.

[0154] In this embodiment, the connecting hole 11j (see FIG. 1) of the first embodiment is not formed in the housing 11. Therefore, the shaft insertion hole 11f does not communicate with any of the first to fourth other-side spaces 11b to 11e.

[0155] (1) Here, when the back pressure acts on the rotor 16 from any of the first to fourth other-side spaces 11b to 11e, the source of the back pressure is the pump 71 of the heat medium circuit 70. As described above, according to this embodiment, the communication passage 17a of the shaft 17 communicates the discharge side of the pump 71 arranged outside the housing 11 with the pressure chamber 24a of the differential pressure device 24.

[0156] Therefore, no matter which other-side space among the first to fourth other-side spaces 11b to 11e from which the back pressure occurs, the discharge side of the pump 71, which is the source of the back pressure, is connected to the pressure chamber 24a, so that it is possible to press the rotor 16 against the stator 12 with a pressing force corresponding to the back pressure.

[0157] Therefore, in this embodiment, there is no need to use a check valve body 32 (see FIG. 11) as in the second embodiment described above, or to switch the connection destination of the communicating passage 17a using the side hole 172b (see FIG. 15B) of the other shaft part 172 as in the third embodiment.

[0158] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0159] Fifth embodiment Next, a fifth embodiment will be described. In this embodiment, differences from the fourth embodiment will be mainly described.

[0160] 21, the pump 71 of the heat medium circuit 70 is integral with the valve device 10. Therefore, piping for connecting the discharge port 711 of the pump 71 to the external communication hole 11k of the valve device 10 is not required.

[0161] Except for the points described above, this embodiment is similar to the fourth embodiment. In this embodiment, the same effects as those of the fourth embodiment can be obtained from the configuration common to the fourth embodiment.

[0162] Sixth embodiment Next, a sixth embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described.

[0163] 22, in this embodiment, the connecting hole 11j (see FIG. 1) of the first embodiment is not formed in the housing 11. Instead, the valve device 10 of this embodiment includes an external pipe 34 provided outside the housing 11. In this embodiment, since there is no connecting hole 11j (see FIG. 1), the shaft insertion hole 11f does not communicate with any of the first to fourth other-side spaces 11b to 11e.

[0164] In this embodiment, the communication passage 17a of the shaft 17 communicates with the pressure chamber 24a, but extends from the pressure chamber 24a to one side in the valve axial direction Da, not to the other side. The communication passage 17a communicates with the pressure chamber 24a at an end on the other side in the valve axial direction Da, and opens at an end face of the shaft 17 on one side in the valve axial direction Da.

[0165] Therefore, the communication passage 17a in this embodiment does not communicate with the shaft insertion hole 11f, and does not communicate with the third other-side space 11d. On the other hand, the communication passage 17a communicates with the first other-side port passage 111a via the external passage 34a formed in the external piping 34. Therefore, in this embodiment, the first other-side space 11b, not the third other-side space 11d, corresponds to the other-side space of the present disclosure. When the pressure in the first other-side space 11b is higher than the pressure P2 in the one-side space 11a, the differential pressure device 24 generates a pressing force that presses the rotor 16 against the stator 12 by the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a.

[0166] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0167] Seventh embodiment Next, a seventh embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described.

[0168] As shown in Fig. 23, the valve device 10 of this embodiment is not provided with the pressing portion 242 shown in Fig. 8. Instead, the differential pressure device 24 constituting a part of the valve device 10 has a lever central portion 201 as a pressing portion that presses the rotor 16 to the other side in the valve axial direction Da. Therefore, the lever central portion 201 is a part of the lever 20 and also a part of the differential pressure device 24.

[0169] In addition, since the pressing portion 242 of the first embodiment is not provided in this embodiment, for example, one end 221 (see FIG. 8) of the pressing spring 22 abuts against the shaft body 18, and the position of the one end 221 is maintained.

[0170] Specifically, the lever 20 of this embodiment has a lever central portion 201 and a pair of arm portions 202, similar to the first embodiment. Therefore, in this embodiment, similar to the first embodiment, the driving force of the actuator 14 is first transmitted to the shaft body 18, and then transmitted from the shaft body 18 to the lever 20 and the rotor 16, in that order.

[0171] However, in the lever 20 of this embodiment, the lever central portion 201 has a central cylindrical portion 201c that extends cylindrically from a portion on the outer side of the spring support groove 201b (see FIG. 4) in the valve radial direction Dr to one side in the valve axial direction Da. This central cylindrical portion 201c is disposed on the outer side of the pressing spring 22 in the valve radial direction Dr. The central cylindrical portion 201c has one end portion 201d provided on one side in the valve axial direction Da.

[0172] Also, an inner peripheral end 241b (see FIG. 8) of the diaphragm 241 is fixed to one end 201d of the central cylindrical portion 201c. An airtight structure is formed between the inner peripheral end 241b of the diaphragm 241 and one end 201d of the central cylindrical portion 201c. Since the central cylindrical portion 201c is connected to the diaphragm 241 in this manner, it forms a part of the pressure chamber 24a of the differential pressure device 24.

[0173] The pressing spring 22 of this embodiment is disposed in a pressure chamber 24a of the differential pressure device 24. The pressing spring 22 presses the rotor 16 via the lever central portion 201 toward the other side in the valve axial direction Da.

[0174] In the present embodiment, the lever central portion 201 and the shaft 17 are capable of relative movement in the valve axial direction Da. However, unlike the first embodiment, in this embodiment, the peripheral wall surface of the insertion hole 201a of the lever central portion 201 is in contact with the shaft 17, and the gap between the peripheral wall surface of the insertion hole 201a and the shaft 17 is airtight or substantially airtight to the extent that leakage of the heat medium can be ignored.

[0175] (1) As described above, according to this embodiment, the pressing spring 22 is disposed in the pressure chamber 24a of the differential pressure device 24, and presses the rotor 16 toward the other side in the valve axial direction Da via the lever central portion 201. Therefore, after providing the pressing spring 22 that presses the rotor 16 against the stator 12, when the differential pressure device 24 presses the rotor 16 toward the other side in the valve axial direction Da, it can press the rotor 16 without going through the pressing spring 22.

[0176] As a result, even if the differential pressure device 24 operates to push the rotor 16 to the other side in the valve axial direction Da, the lever center portion 201 as the pressing portion is hardly displaced. That is, even if the pressure difference between the pressure P1 (see FIG. 8) in the pressure chamber 24a and the pressure P2 in the one-side space 11a fluctuates, the diaphragm 241 is hardly deformed. Therefore, it is possible to improve the durability of the diaphragm 241 compared to a configuration in which the differential pressure device 24 pushes the rotor 16 via the pressing spring 22.

[0177] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0178] Although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any of the second to sixth embodiments described above.

[0179] Eighth embodiment Next, an eighth embodiment will be described. In this embodiment, differences from the first embodiment will be mainly described.

[0180] 24, in the valve device 10 of this embodiment, an insertion hole 201a is formed in the lever central portion 201, but a spring support groove 201b (see FIG. 1) is not formed. Instead, the pressing portion 242 of the differential pressure device 24 of this embodiment has a spring support portion 243 in which a spring support groove 243a is formed, and a cylindrical portion 244.

[0181] In this embodiment, the lever 20 has a lever central portion 201 and a pair of arm portions 202 similarly to the first embodiment, except that the spring support groove 201b is not provided. Therefore, in this embodiment, similarly to the first embodiment, the driving force of the actuator 14 is first transmitted to the shaft body 18, and then transmitted from the shaft body 18 to the lever 20 and the rotor 16 in this order.

[0182] The spring support portion 243 in this embodiment is disposed on one side in the valve axis direction Da with respect to the lever central portion 201, and abuts against the lever central portion 201 from one side in the valve axis direction Da. Therefore, the pressing portion 242 including this spring support portion 243 presses the rotor 16 to the other side in the valve axis direction Da via the lever central portion 201 without via the pressing spring 22.

[0183] Further, a pressing portion through hole 242a similar to that of the first embodiment is formed inside the spring support portion 243, and the shaft 17 is inserted into the pressing portion through hole 242a. The spring support portion 243 is movable in the valve axis direction Da relative to the shaft 17 inserted into the pressing portion through hole 242a. The airtightness of the pressing portion through hole 242a in this embodiment is the same as that of the first embodiment, and the gap between the spring support portion 243 and the shaft 17 is airtight or nearly airtight.

[0184] The spring support groove 243a of this embodiment extends in an annular shape centered on the valve axis Cv, like the spring support groove 201b of the first embodiment, has a groove bottom on the other side in the valve axis direction Da, and opens to one side in the valve axis direction Da. The other end 222 of the pressing spring 22 is inserted into the spring support groove 243a.

[0185] The tubular portion 244 extends from a portion of the spring support portion 243 that is on the outer side of the spring support groove 243a in the valve radial direction Dr to one side in the valve axial direction Da, and is formed in a cylindrical shape centered on the valve axis Cv. The tubular portion 244 is disposed on the outer side of the pressing spring 22 in the valve radial direction Dr. The tubular portion 244 has one end portion 244a provided on one side in the valve axial direction Da.

[0186] Further, an inner peripheral end 241b (see FIG. 8) of the diaphragm 241 is fixed to one end 244a of the cylindrical portion 244. The space between the inner peripheral end 241b of the diaphragm 241 and one end 244a of the cylindrical portion 244 is configured to be airtight.

[0187] The pressing spring 22 of this embodiment is disposed in the pressure chamber 24a of the differential pressure device 24. One end 221 (see FIG. 8) of the pressing spring 22 abuts against, for example, the shaft body 18, and the position of the one end 221 is maintained. The other end 222 of the pressing spring 22 abuts against the spring support portion 243 in the spring support groove 243a. Therefore, the pressing spring 22 presses the rotor 16 toward the other side in the valve axis direction Da via the spring support portion 243 and the lever central portion 201.

[0188] The pressing portion 242 of the differential pressure device 24 in this embodiment is constantly pressed against the lever central portion 201 by the pressing spring 22. Therefore, unlike the first embodiment, this embodiment does not have a stopper (not shown) that determines the movement end of the pressing portion 242 in the movement to one side in the valve axial direction Da.

[0189] (1) As described above, according to this embodiment, the pressing spring 22 is disposed in the pressure chamber 24a of the differential pressure device 24, and presses the rotor 16 toward the other side in the valve axis direction Da via the spring support portion 243 of the pressing portion 242. Therefore, similar to the seventh embodiment, after providing the pressing spring 22 that presses the rotor 16 against the stator 12, when the differential pressure device 24 presses the rotor 16 toward the other side in the valve axis direction Da, it can press the rotor 16 without going through the pressing spring 22.

[0190] As a result, in this embodiment as well as in the seventh embodiment, even if the pressure difference between the pressure P1 (see FIG. 8) in the pressure chamber 24a and the pressure P2 in the one-side space 11a varies, the diaphragm 241 hardly deforms. Therefore, compared to a configuration in which the differential pressure device 24 presses the rotor 16 via the pressing spring 22, it is possible to improve the durability of the diaphragm 241.

[0191] Except for the points described above, this embodiment is similar to the first embodiment. In this embodiment, the same effects as those of the first embodiment can be obtained from the configuration common to the first embodiment.

[0192] Although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any of the second to sixth embodiments described above.

[0193] (Other embodiments) (1) In each of the above-described embodiments, the valve device 10 is a five-way valve having five ports 110, 111, 112, 113, and 114, as shown in Figures 1 and 2, but it may be a two-way valve or a six-way valve. For example, if the valve device 10 is a two-way valve, there will be one space corresponding to the multiple other-side spaces 11b to 11e formed in the housing 11 of the present embodiment.

[0194] (2) In the above-described first embodiment, as shown in Fig. 1 and Fig. 4, one aperture adjustment hole 161 and one interconnecting groove 162 are formed in the rotor 16, but various flow path patterns consisting of the aperture adjustment hole 161 and the interconnecting groove 162 are assumed. For example, the rotor 16 may have a V-shaped notch instead of the aperture adjustment hole 161. Alternatively, the rotor 16 may have only the aperture adjustment hole 161 without the interconnecting groove 162.

[0195] (3) In the second embodiment described above, as shown in Fig. 10, the decompression hole 182c is formed in the shaft body 18, but this is just one example. The decompression hole 182c may be provided anywhere that separates the one-side space 11a of the housing 11 from the pressure chamber 24a. In addition, if there is a slight leakage of the heat medium between the pressing portion 242 of the differential pressure device 24 and the shaft 17, the portion where the heat medium leaks between the pressing portion 242 and the shaft 17 may function as the decompression hole 182c.

[0196] (4) In the second embodiment described above, as shown in Fig. 11 and Fig. 13, the check valve body 32 has a simple rolled plate shape in which a single sheet material is rolled around one turn along the peripheral wall surface of the other side portion 11g, but this is just one example. For example, as shown in Fig. 25, the check valve body 32 may be configured such that the roll plate in Fig. 13 is divided into two in the valve axial direction Da, and is composed of a one-side roll plate 32a and a other-side roll plate 32b arranged on the other side of the one-side roll plate 32a in the valve axial direction Da. In this case, the second check valve portion 322 and the fourth check valve portion 324 are included in the one-side roll plate 32a, and the first check valve portion 321 and the third check valve portion 323 are included in the other-side roll plate 32b.

[0197] As shown in FIG. 26, the check valve body 32 may be formed of a rolled plate made by rolling a single thin plate material into a spiral shape more than one turn.

[0198] Also, the check valve element 32 may be formed such that a wound plate wound about one turn is partially cut out, and the first to fourth check valve portions 321, 322, 323, 324 each have a reed valve shape, as shown in Fig. 27. In Fig. 27, in order to clearly show the shape of the check valve element 32, the non-cutout parts of the outer circumferential surface of the check valve element 32 are hatched in dots, and the cutout parts are not hatched in dots.

[0199] Furthermore, the check valve element 32 does not have to be made of a rolled plate made of a thin metal or resin plate material, but may be made of rubber as shown in Fig. 28. In the check valve element 32 of Fig. 28 as well, the first to fourth check valve portions 321, 322, 323, 324 each have a reed valve shape.

[0200] (5) In the above-described fourth embodiment, as shown in Fig. 20, the one-side port passage 110a of the valve device 10 is always connected to the suction side of the pump 71, but this is just one example. For example, the intermediate circuit 701 may be different from that shown in Fig. 20, and the discharge side of the pump 71 may be selectively connectable to not only the first to fourth other-side port passages 111a to 114a of the valve device 10 but also the one-side port passage 110a. In that case, when the discharge side of the pump 71 is connected to the one-side port passage 110a, any one of the first to fourth other-side port passages 111a to 114a is connected to the suction side of the pump 71.

[0201] Here, even in the above-mentioned configuration in which the discharge side of the pump 71 can also be connected to the one-side port passage 110a, the discharge side of the pump 71 is always connected to the external communication hole 11k shown in Fig. 19, and the discharge pressure of the pump 71 is always led to the pressure chamber 24a, as in the above-mentioned fourth embodiment. That is, the discharge pressure of the pump 71 is led to the pressure chamber 24a regardless of whether the heat medium flows in the forward direction or the reverse direction in the valve device 10. Therefore, for example, when the discharge side of the pump 71 is connected to the one-side port passage 110a and the heat medium flows in the forward direction in the valve device 10, there is a concern that the differential pressure device 24 may unnecessarily press the rotor 16 against the stator 12.

[0202] However, when the discharge pressure of the pump 71 is applied to the one-side port passage 110a, the pressure P2 in the one-side space 11a and the pressure P1 in the pressure chamber 24a shown in Fig. 8 similarly rise to the discharge pressure of the pump 71. Therefore, since no pressure difference occurs between the one-side space 11a and the pressure chamber 24a, the pressing force pressing the rotor 16 against the stator 12 is not generated due to the pressure P1 in the pressure chamber 24a. In other words, when the forward flow of the heat medium occurs, the differential pressure device 24 does not press the rotor 16 too much.

[0203] (6) In the above-described fourth embodiment, as shown in Fig. 20, the heat medium circuit 70 includes one pump 71, but this is just one example. For example, it is also possible to assume that an independent pump having a constant discharge pressure and having a discharge side that is not connected to any of the port passages 110a, 111a, 112a, 113a, and 114a is provided in addition to the pump 71 shown in Fig. 20.

[0204] In this case, when a forward flow of the heat transfer medium occurs in the valve device 10, the discharge pressure of the independent pump may be set so that the pressure P1 in the pressure chamber 24a is slightly higher than the pressure P2 in the one-side space 11a.

[0205] This is because, in this case as well, the pressure P2 in the one-side space 11a is lower when the heat medium flows in the reverse direction than when it flows in the forward direction, and the pressing force of the differential pressure device 24 pushing the rotor 16 is greater when the heat medium flows in the reverse direction than when it flows in the forward direction. That is, as in the fourth embodiment, the pressing force of the differential pressure device 24 is adjusted according to the magnitude of the back pressure acting on the rotor 16.

[0206] Therefore, the pressing force of the differential pressure device 24 pressing the rotor 16 against the stator 12 due to the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a does not need to become zero in the case of a forward flow of the heat transfer medium. In other words, the pressing force of the differential pressure device 24 does not need to become zero even when the pressure P2 in the one-side space 11a is higher than any of the pressures in the first to fourth other-side spaces 11b to 11e.

[0207] In short, it is sufficient that the pressing force of the differential pressure device 24 is generated when at least any of the pressures in the first to fourth other-side spaces 11b to 11e is higher than the pressure P2 in the one-side space 11a. The word "at least" means that the pressing force of the differential pressure device 24 may be generated in cases other than when any of the pressures in the first to fourth other-side spaces 11b to 11e is higher than the pressure P2 in the one-side space 11a. And the word "at least" does not limit the configuration of the differential pressure device 24 to a case where the pressing force of the differential pressure device 24 is always generated when any of the pressures in the first to fourth other-side spaces 11b to 11e is higher than the pressure P2 in the one-side space 11a.

[0208] (7) In each of the above-described embodiments, the fluid passing through the valve device 10 is a heat transfer medium, but the fluid may be a fluid other than a heat transfer medium. In addition, the fluid passing through the valve device 10 may be a gas rather than a liquid.

[0209] (8) In each of the above-described embodiments, the valve device 10 is mounted on, for example, a hybrid vehicle, but the use of the valve device 10 is not limited to vehicles.

[0210] (9) In each of the above-described embodiments, the valve device 10 includes the actuator 14 for driving the rotor 16 to rotate, as shown in Fig. 1, but this is merely an example. For example, the valve device 10 may not include the actuator 14, and the rotor 16 may be rotated by an external drive source provided outside the valve device 10.

[0211] (10) In each of the above-described embodiments, rotor 16 and stator 12 shown in FIG. 1 are both made of ceramic. However, for example, one or both of rotor 16 and stator 12 may be made of a resin with high sliding performance.

[0212] (11) In each of the above-described embodiments, the housing 11 and the stator 12 are configured as separate parts as shown in Fig. 1, but this is just one example. For example, the housing 11 and the stator 12 may be configured as a single molded part that includes both of them.

[0213] (12) In each of the above-described embodiments, as shown in Fig. 8, the differential pressure device 24 has a diaphragm 241 in order to adjust the pressing force pressing the rotor 16 against the stator 12 to a magnitude corresponding to the pressure difference between the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a. However, this is only one example. For example, it is also conceivable that the differential pressure device 24 includes a piston mechanism instead of the diaphragm 241, and the piston mechanism is used to adjust the pressing force pressing the rotor 16 against the stator 12 to a magnitude corresponding to the pressure difference.

[0214] (13) In the first embodiment described above, as shown in Fig. 1, the communication passage 17a that communicates between the third other-side space 11d and the pressure chamber 24a is formed inside the shaft 17. However, this is just one example. For example, the communication passage 17a may be connected to the pressure chamber 24a without passing through the shaft 17.

[0215] (14) In the above-described first embodiment, as shown in Fig. 8, when the pressure P1 in the pressure chamber 24a and the pressure P2 in the one-side space 11a have a relationship of "P1>P2", the differential pressure device 24 generates a pressing force that presses the rotor 16 against the stator 12 by the differential pressure between these pressures P1 and P2. However, this is just one example. For example, a predetermined value Px greater than zero may be specified, and the differential pressure device 24 may generate the pressing force on the condition that the pressures P1 and P2 have a relationship of "P1>P2+Px".

[0216] (15) In each of the above-described embodiments, for example as shown in Fig. 1, the pressing spring 22 and the differential pressure device 24 are provided as a pressing device for pressing the rotor 16 against the stator 12, but this is only one example. For example, it is also possible that the differential pressure device 24 is provided but the pressing spring 22 is not provided.

[0217] (16) The present disclosure is not limited to the above-described embodiment, and can be implemented in various modified forms. Furthermore, the above-described embodiments are not unrelated to each other, and can be appropriately combined, except in cases where the combination is clearly impossible.

[0218] In each of the above embodiments, the elements constituting the embodiment are not necessarily essential, unless otherwise specified as essential or considered to be obviously essential in principle. In each of the above embodiments, when the numbers, values, amounts, ranges, etc. of the components of the embodiment are mentioned, they are not limited to the specific numbers, except when specified as essential or when they are obviously limited to a specific number in principle. In each of the above embodiments, when the materials, shapes, positional relationships, etc. of the components are mentioned, they are not limited to the materials, shapes, positional relationships, etc., except when specified as essential or when they are obviously limited to a specific material, shape, positional relationship, etc. in principle.

[0219] Features of the Disclosure [First viewpoint] 1. A valve device comprising: A housing (11) through which a fluid flows; a flow passage hole forming portion (12) disposed within the housing and unable to rotate relative to the housing, the flow passage hole forming portion (12) having flow passage holes (121, 122, 123, 124) through which a fluid passes; a rotor (16) disposed on one side of the flow passage hole forming portion in an axial direction of a predetermined axis (Cv) relative to the flow passage hole forming portion within the housing and rotating around the predetermined axis while sliding relative to the flow passage hole forming portion; a differential pressure device (24) provided on the one side of the rotor in the axial direction and having a pressure chamber (24a) into which a fluid is introduced, Within the housing, a one-side space (11a) is provided on the one side in the axial direction with respect to the rotor, and a other-side space (11b, 11c, 11d, 11e) is provided on the other side opposite to the one side in the axial direction with respect to the flow passage hole forming portion and communicates with the flow passage hole, the rotor increases and decreases an opening degree of the flow passage hole with respect to the one-side space as the rotor rotates, the differential pressure device generates a pressing force for pressing the rotor against the flow path hole formation portion by a pressure difference between the pressure (P1) in the pressure chamber and the pressure in the one-side space when at least the pressure in the other-side space is higher than the pressure (P2) in the one-side space, The valve device, wherein the pressing force increases as the pressure in the pressure chamber increases relative to the pressure in the one-side space. [Second viewpoint] The valve device according to a first aspect, further comprising a communication passage (17a) that communicates the other side space with the pressure chamber. [Third Perspective] a shaft (17) disposed within the housing, extending along the predetermined axis from the one side to the other side in the axial direction relative to the flow passage hole forming portion and the rotor, and having a pressure chamber exposed portion (173) exposed into the pressure chamber, A communication passage (17a) is formed inside the shaft to communicate the other side space with the pressure chamber, The valve device according to a first aspect, wherein the communicating passage extends inside the shaft from the one side to the other side in the axial direction relative to the flow passage hole forming portion and the rotor, and opens to the pressure chamber at the pressure chamber exposed portion. [Fourth viewpoint] The valve device according to a third aspect, wherein the differential pressure device is rotatably supported about the predetermined axis relative to the housing via the shaft, and rotates together with the rotor about the predetermined axis. [Fifth viewpoint] a first check valve portion (321) and a second check valve portion (322), A plurality of the other-side spaces are formed in the housing, The plurality of other-side spaces include a first other-side space (11b) and a second other-side space (11c), a plurality of the flow passage holes are formed in the flow passage hole forming portion so as to correspond to the plurality of the other-side spaces, the communication passage is connected to each of the first other-side space and the second other-side space, the first check valve portion allows fluid to flow from the first other-side space to the communication passage while preventing fluid from flowing from the communication passage to the first other-side space, The valve device according to any one of the second to fourth aspects, wherein the second check valve portion allows fluid to flow from the second other-side space to the communicating passage while preventing fluid from flowing from the communicating passage to the second other-side space. [Sixth viewpoint] The valve device according to a fifth aspect, further comprising a leakage passage (182c) that allows leakage of fluid from the pressure chamber to the one-side space when the pressure in the pressure chamber is higher than the pressure in the one-side space. [Seventh viewpoint] A plurality of the other-side spaces are formed in the housing, the plurality of other-side spaces include a first other-side space (11b) and a second other-side space (11c) disposed on one side of the first other-side space in the circumferential direction (Dc) of the predetermined axis, a plurality of the flow passage holes are formed in the flow passage hole forming portion so as to correspond to the plurality of the other-side spaces, the shaft rotates integrally with the rotor about the predetermined axis, When a space having the highest pressure among the plurality of other-side spaces is defined as a maximum pressure space, the maximum pressure space is switched from the first other-side space to the second other-side space as the rotor rotates toward the one side in the circumferential direction, The valve device according to a third or fourth aspect, wherein the communication passage communicates with the first other-side space when the first other-side space becomes the highest pressure space, and communicates with the second other-side space when the second other-side space becomes the highest pressure space. [Eighth viewpoint] the shaft has a shaft other portion (172) located on the other side in the axial direction relative to the flow passage hole forming portion, The housing is provided with an insertion hole (11f) that is disposed inside the plurality of other-side spaces in a radial direction (Dr) of the specified axis and into which the other portion of the shaft is inserted, a first connecting hole (116a) that connects the first other-side space and the insertion hole, and a second connecting hole (116b) that connects the second other-side space and the insertion hole, the communication passage includes a side hole (172b) formed in the other shaft portion and opening at an outer circumferential surface (172a) of the other shaft portion, When the first other-side space is the highest pressure space, the first connecting hole and the side hole communicate with each other, The valve device according to a seventh aspect, wherein the second connecting hole and the side hole communicate with each other when the second other-side space becomes the highest pressure space. [Ninth viewpoint] The first other-side space becomes the highest pressure space when a first flow passage hole (121) that is in communication with the first other-side space among the plurality of flow passage holes is fully closed, The valve device according to the seventh or eighth aspect, wherein the second other-side space becomes the highest pressure space when a second flow path hole (122) communicating with the second other-side space among the plurality of flow path holes is fully closed. [10th viewpoint] The valve device according to a first aspect, further comprising a communication passage (17a) for communicating between a discharge side of a pump (71) arranged outside the housing and the pressure chamber. [Eleventh viewpoint] A valve device constituting a part of a fluid circuit (70) in which a fluid is circulated by a pump (71), In the fluid circuit, a discharge side of the pump is connectable to the other side space, The valve device according to a first aspect, further comprising a communication passage (17a) for communicating between the discharge side of the pump and the pressure chamber. [12th viewpoint] the differential pressure device includes a diaphragm (241) that is provided on the other side of the pressure chamber in the axial direction and separates the pressure chamber from the one-side space, and a pressing portion (242, 201) that presses the rotor toward the other side in the axial direction, the shaft extends through the diaphragm; The diaphragm has a movable end portion (241b) that is movable in the axial direction and connected to the pressing portion, The valve device according to a third or fourth aspect, wherein the pressure in the pressure chamber acts to press the pressing portion towards the other side in the axial direction. [13th viewpoint] an elastic body (22) that is disposed in a state where it is compressed and deformed in the axial direction and that pushes the rotor toward the other side in the axial direction by a repulsive force against the compressive deformation; The valve device according to a twelfth aspect, wherein the elastic body is disposed within the pressure chamber and presses the rotor via the pressing portion. [14th viewpoint] The valve device according to any one of the first to twelfth aspects, further comprising an elastic body (22) that is installed in a state where it is compressed and deformed in the axial direction and that pushes the rotor toward the other side in the axial direction by a repulsive force against the compressive deformation.

Claims

1. 1. A valve device comprising: A housing (11) through which a fluid flows; a flow passage hole forming portion (12) disposed within the housing and provided so as to be unable to rotate relative to the housing, the flow passage hole (121, 122, 123, 124) through which a fluid passes being formed; a rotor (16) disposed on one side of the flow passage hole forming portion in an axial direction (Da) of a predetermined axis (Cv) in the housing and rotating around the predetermined axis while sliding against the flow passage hole forming portion; a differential pressure device (24) provided on the one side of the rotor in the axial direction and having a pressure chamber (24a) into which a fluid is introduced; Within the housing, a one-side space (11a) is provided on one side of the rotor in the axial direction, and a other-side space (11b, 11c, 11d, 11e) is provided on the other side of the flow passage hole forming portion opposite to the one side in the axial direction and communicates with the flow passage hole, the rotor increases and decreases an opening degree of the flow passage hole with respect to the one-side space as the rotor rotates, the differential pressure device generates a pressing force for pressing the rotor against the flow path hole formation portion by a pressure difference between the pressure (P1) in the pressure chamber and the pressure in the one-side space when at least the pressure in the other-side space is higher than the pressure (P2) in the one-side space, The valve device, wherein the pressing force increases as the pressure in the pressure chamber increases relative to the pressure in the one-side space.

2. The valve device according to claim 1, further comprising a communication passage (17a) for communicating the other space with the pressure chamber.

3. a shaft (17) disposed within the housing, extending from the one side to the other side in the axial direction relative to the flow passage hole forming portion and the rotor along the predetermined axis, and having a pressure chamber exposed portion (173) exposed within the pressure chamber, A communication passage (17a) is formed inside the shaft to communicate the other side space with the pressure chamber, 2. The valve device according to claim 1, wherein the communication passage extends inside the shaft from the one side to the other side in the axial direction relative to the flow passage hole forming portion and the rotor, and opens to the pressure chamber at the pressure chamber exposed portion.

4. 4. The valve device according to claim 3, wherein the differential pressure device is rotatably supported about the predetermined axis relative to the housing via the shaft, and rotates together with the rotor about the predetermined axis.

5. A first check valve portion (321) and a second check valve portion (322), A plurality of the other-side spaces are formed in the housing, The plurality of other-side spaces include a first other-side space (11b) and a second other-side space (11c), a plurality of the flow passage holes are formed in the flow passage hole forming portion so as to correspond to the plurality of the other-side spaces, the communication passage is connected to each of the first other-side space and the second other-side space, the first check valve portion allows fluid to flow from the first other-side space to the communication passage while preventing fluid from flowing from the communication passage to the first other-side space, 5. The valve device according to claim 2, wherein the second check valve portion allows fluid to flow from the second other-side space to the communication passage, while preventing fluid from flowing from the communication passage to the second other-side space.

6. 6. The valve device according to claim 5, further comprising a leakage passage (182c) for allowing leakage of fluid from the pressure chamber to the one-side space when the pressure in the pressure chamber is higher than the pressure in the one-side space.

7. A plurality of the other-side spaces are formed in the housing, the plurality of other-side spaces include a first other-side space (11b) and a second other-side space (11c) disposed on one side of the first other-side space in a circumferential direction (Dc) of the predetermined axis, a plurality of the flow passage holes are formed in the flow passage hole forming portion so as to correspond to the plurality of the other-side spaces, the shaft rotates integrally with the rotor about the predetermined axis, When a space having the highest pressure among the plurality of other-side spaces is defined as a maximum pressure space, the maximum pressure space is switched from the first other-side space to the second other-side space as the rotor rotates toward the one side in the circumferential direction, 5. The valve device according to claim 3, wherein the communication passage communicates with the first other-side space when the first other-side space is the highest pressure space, and communicates with the second other-side space when the second other-side space is the highest pressure space.

8. The shaft has a shaft other portion (172) located on the other side in the axial direction relative to the flow passage hole forming portion, The housing is provided with an insertion hole (11f) that is disposed inside the plurality of other-side spaces in a radial direction (Dr) of the specified axis and into which the other portion of the shaft is inserted, a first connecting hole (116a) that connects the first other-side space and the insertion hole, and a second connecting hole (116b) that connects the second other-side space and the insertion hole, the communication passage includes a side hole (172b) formed in the other shaft portion and opening at an outer circumferential surface (172a) of the other shaft portion, When the first other-side space is the highest pressure space, the first connecting hole and the side hole communicate with each other, 8. The valve device according to claim 7, wherein the second connecting hole and the side hole communicate with each other when the second other-side space is the highest pressure space.

9. The first other-side space becomes the highest pressure space when a first flow passage hole (121) communicating with the first other-side space among the plurality of flow passage holes is fully closed, The valve device according to claim 7, wherein the second other-side space becomes the highest pressure space when a second flow passage hole (122) communicating with the second other-side space among the plurality of flow passage holes is fully closed.

10. 2. The valve device according to claim 1, further comprising a communication passage (17a) for communicating a discharge side of a pump (71) disposed outside the housing with the pressure chamber.

11. A valve device constituting a part of a fluid circuit (70) in which a fluid is circulated by a pump (71), In the fluid circuit, a discharge side of the pump is connectable to the other side space, 2. The valve device according to claim 1, further comprising a communication passage (17a) for communicating between the discharge side of the pump and the pressure chamber.

12. the differential pressure device includes a diaphragm (241) that is provided on the other side of the pressure chamber in the axial direction and separates the pressure chamber from the one-side space, and a pressing portion (242, 201) that presses the rotor toward the other side in the axial direction, the shaft extends through the diaphragm; The diaphragm has a movable end portion (241b) that is movable in the axial direction and connected to the pressing portion, 5. The valve device according to claim 3, wherein the pressure in the pressure chamber acts to press the pressing portion toward the other side in the axial direction.

13. an elastic body (22) that is disposed in a state where it is compressed and deformed in the axial direction and that pushes the rotor toward the other side in the axial direction by a repulsive force against the compressive deformation; The valve device according to claim 12 , wherein the elastic body is disposed within the pressure chamber and presses the rotor via the pressing portion.

14. 5. The valve device according to claim 1, further comprising an elastic body (22) that is disposed in a compressively deformed state in the axial direction and that pushes the rotor toward the other side in the axial direction by a repulsive force against the compressive deformation.

Images