JP6913283B2 - valve - Google Patents

Description

The present invention includes a case for accommodating a working fluid and a housing for reciprocating the inside of the case along the axis of the case while partitioning the inside of the case into a first fluid chamber and a second fluid chamber. The present invention relates to a valve that controls the operation of the provided valve body to adjust the operating characteristics of the housing.

Conventionally, as such a valve, for example, there is one described in Patent Document 1 below.

This technology is a vibration damper provided in a vehicle suspension or the like, and uses an actuator to change the operating characteristics of a valve body to control the flow characteristics of a working fluid. This adjusts the cushioning effect of the vibration damper.

In the device of Patent Document 1, a working fluid is filled inside the cylinder 9 and a piston 6 is provided, and the cylinder 9 is divided into a lower working chamber 7 and an upper working chamber 8 by the piston 6. ing. Inside the piston 6, a valve body 10 that can move relative to the piston is provided. When the piston 6 moves inside the cylinder 9 and a predetermined pressure acts on the valve body 10 from the working fluid, the valve body 10 operates to open the flow path, and the working fluids move between the working chambers 7 and 8 of both. It circulates between. As a result, the operating speed of the piston 6 is controlled.

Inside the piston 6, a drive element 2 or the like that comes into contact with the valve body 10 and adjusts the operating characteristics of the valve body 10 is provided. By appropriately adjusting the positions of the drive element 2 and the like, the pressure of the working fluid required for the valve body 10 to shift from the closed state to the open state of the flow path is set. As a result, a vibration damper capable of controlling the operating characteristics of the piston 6 is configured.

Japanese Unexamined Patent Publication No. 11-721133

In a vibration damper provided with a valve body capable of controlling the flow rate of the working fluid, including the vibration damper as shown in Patent Document 1, it is necessary to enhance the operation responsiveness of the valve body in order to improve the damping function. be. However, in many valve bodies provided in a normal damping mechanism such as the valve body disclosed in Patent Document 1, the outer peripheral surface of the valve body slides with the inner surface of the casing holding the valve body. Therefore, a constant frictional force is generated between the two, and particularly when the static frictional force is large, the initial movement of the valve body tends to be delayed and the operation of the shock absorber becomes slow.

In order to eliminate such inconvenience, it is conceivable to expand the gap between the outer peripheral surface of the valve body and the inner surface of the casing. However, in order to prevent leakage of the working fluid, there is a certain limit in expanding the gap size. Therefore, in order to improve the operational responsiveness of the valve body, the cost of the product is increased by improving the processing accuracy of the parts and using a material that does not easily expand or deform even if the operating temperature changes. I will be there.

In view of these problems, there has been a demand for a valve having a pressure damping function having excellent operation responsiveness and being configured at low cost.

(Characteristic composition)
The characteristic configuration of the valve according to the present invention is
A case that houses the working fluid and
A bottomed tubular housing that divides the inside of the case into a first fluid chamber and a second fluid chamber and has a cylindrical space inside that communicates with the second fluid chamber.
It has a valve portion that is arranged in the cylindrical space and abuts on a valve seat provided in a part of the housing, and the bottom of the housing is from the closed position with the closing position where the valve portion abuts on the valve seat as an end point. A valve body that reciprocates along the inner surface of the cylindrical space on the side,
The housing is provided with an urging portion for urging the valve body toward the closed position.
The wall portion of the housing is provided with an opening for communicating the contact position between the valve portion and the valve seat and the first fluid chamber, and also provides an opening for communicating with the first fluid chamber.
At least one of the valve portion and the valve seat is formed with a communication portion that communicates the first fluid chamber and the cylindrical space with the valve body in the closed position.
A point is that a rotation drive unit for rotating the valve body by a working fluid flowing through the communication portion is provided on the outer surface of the valve body.

(effect)
In the valve of this configuration, when the working fluid flows inside the housing provided in the case, the flow rate of the working fluid across the first fluid chamber and the second fluid chamber is caused by the operation of the valve body provided inside the housing. It controls.

The valve body can be moved over a predetermined distance inside the housing and is always in a closed position where the urging portion narrows the opening. In this state, for example, when the pressure in the second fluid chamber increases, the valve body is pushed by the working fluid to open the valve body, and the working fluid flows from the second fluid chamber to the first fluid chamber through the opening. do. At this time, the flow rate of the working fluid is regulated according to the opening area of the gap between the valve portion and the valve seat, and the damping function of the valve is exhibited.

In the valve of this configuration, the valve body rotates due to the flow of the working fluid. This makes it possible to reduce the friction between the inner surface of the cylindrical space of the housing and the valve body. Therefore, in particular, the start and reversal movement of the valve body becomes agile, and the damping response to the pressure fluctuation of the working fluid becomes extremely good.

In addition, the posture of the valve body is stabilized by the rotation of the valve body. Therefore, when the valve body reciprocates on the inner surface of the cylindrical space, the corners of the valve body do not bite into the inner surface of the cylindrical space, and the reciprocating movement of the valve body becomes smooth.

(Characteristic composition)
In the valve according to the present invention, it is convenient that the rotary drive portion includes a first blade portion provided on the inner peripheral side of the valve portion.

(effect)
When the first blade portion is provided on the inner peripheral side of the valve portion, the first blade portion is in contact with the working fluid of the second fluid chamber. When the pressure in the second fluid chamber increases and the working fluid in the second fluid chamber flows out to the first fluid chamber through the communication portion, the working fluid always passes through the inner peripheral side of the valve portion. Therefore, the first blade portion receives the kinetic energy of the working fluid to rotate the valve body. With this configuration, the valve body can start operating quickly, especially when the pressure in the second fluid chamber increases.

(Characteristic composition)
In the valve according to the present invention, the rotation drive portion may include a second blade portion provided on the outer peripheral side of the valve portion.

(effect)
When the second blade portion is provided on the outer peripheral side of the valve portion, the second blade portion is in contact with the working fluid of the first fluid chamber. When the pressure in the first fluid chamber increases and the working fluid in the first fluid chamber flows out to the second fluid chamber through the communication portion, the working fluid always passes through the outer peripheral side of the valve portion. Therefore, the second blade portion receives the kinetic energy of the working fluid to rotate the valve body. With this configuration, the valve body can start operating quickly, especially when the pressure in the first fluid chamber increases.

(Characteristic composition)
In the valve according to the present invention, it is convenient that a pressure receiving surface that is in contact with the working fluid and has a normal line in the direction opposite to the urging direction by the urging portion is provided on the outer peripheral side of the valve portion. be.

(effect)
When the working fluid of the second fluid chamber described above presses the end face of the valve body, the valve body is easy to open and operate because the direction in which the working fluid exerts pressure and the direction in which the valve body moves coincide with each other. However, in order to open and operate the valve body even when the internal pressure of the first fluid chamber increases, the working fluid in the valve body applies pressure so that the valve body moves from the second fluid chamber to the first fluid chamber. It is necessary to devise the shape of the affected part. Therefore, in this configuration, a pressure receiving surface that is in contact with the working fluid and has a component in the direction opposite to the urging direction by the urging portion is provided on the outer peripheral side of the valve portion. As a result, the valve body opens easily due to the pressure of the working fluid in the first fluid chamber, and a good damping function can be exhibited.

(Characteristic composition)
In the valve according to the present invention, a plurality of the communication portions are provided along the circumferential direction of the valve body with respect to the rotation shaft core, and each of the communication portions is one side in the circumferential direction so as to be separated from the rotation shaft core. It is convenient if it extends to a state of deviation to.

(effect)
The communication part is located at the boundary between the first fluid chamber and the second fluid chamber, and especially when the valve body is in the closed position, the working fluid always flows through the communication part according to the pressure difference between the two fluid chambers. do. In this configuration, the extension direction of the communication portion is deviated to one side in the circumferential direction so as to be separated from the rotation axis so that the rotation of the valve body is promoted by the working fluid flowing through the communication portion.

If the communication portion is provided in the valve portion of the valve body, the valve body rotates due to the reaction force of the working fluid flowing through the communication portion. On the other hand, even when the valve seat is provided with the communication portion, the working fluid flowing through the communication portion can act on the first blade portion or the second blade portion provided on the valve body to rotate the valve body. ..

(Characteristic composition)
In the valve according to the present invention, the communication portion can be configured by a slit provided in the valve portion.

(effect)
By providing the communication portion in the valve portion of the valve body, the working fluid flowing through the communication portion acts directly on the valve body, so that the rotation of the valve body is further promoted. Further, if the communicating portion is a slit, for example, a notch may be formed in the end face of the valve portion, and such processing is extremely easy. Further, the groove width can be freely set, and a valve body having good rotation efficiency can be rationally constructed.

(Characteristic composition)
In the valve according to the present invention, a plurality of the openings are provided along the circumferential direction of the valve body with respect to the rotation shaft core, and the more the respective openings are separated from the rotation shaft core, the more the opening is biased to one side in the circumferential direction. It is convenient to extend to the state of being ranked.

(effect)
The opening is formed near the contact position between the valve portion and the valve seat in order to communicate the first fluid chamber and the cylindrical space and form a smooth flow of the working fluid. Since the working fluid flowing through the opening maintains an appropriate flow velocity, it is convenient if the kinetic energy of the working fluid can be efficiently used for the rotation of the valve body. Therefore, as in this configuration, the extended state of the opening is deviated to one side in the circumferential direction so as to be separated from the rotation axis of the valve body.

As a result, for example, the working fluid that collides with the valve body from the first fluid chamber through the opening collides with the valve body while maintaining the velocity component in the circumferential direction. Therefore, the valve body starts to rotate quickly, the opening and closing operation of the valve portion becomes smooth, and a valve having good damping response can be obtained.

(Characteristic composition)
In the valve according to the present invention, it is convenient that the urging portion is a coil-shaped spring, and a ring member that can rotate relative to the coiled spring is provided between the valve body and the coil-shaped spring. ..

(effect)
While the valve body is configured to rotate, the coiled spring that urges the valve body to the valve seat side is not necessarily rotatably attached to the housing, but rather fixed to the housing. It is convenient to be done. However, in this case, friction occurs between the coiled spring and the valve body, and the rotation of the valve body is impaired. Therefore, by providing the ring member as in this configuration, the frictional force between the coiled spring and the valve body is reduced, and the rotational resistance of the valve body is reduced. This makes the operation of the valve body even more agile.

Explanatory drawing which shows the structure of the valve which concerns on 1st Embodiment Explanatory drawing which shows the structure of the valve which concerns on 1st Embodiment Perspective view which shows the structure of the valve body which concerns on 1st Embodiment Explanatory drawing which shows operation mode of valve body which concerns on 1st Embodiment Explanatory drawing which shows the structure of the valve which concerns on 2nd Embodiment Explanatory drawing which shows the structure of the valve which concerns on other embodiment

[First Embodiment]
(overview)
The valve GV according to the present embodiment is used for a shock absorber or the like of an automobile. For example, the housing H slides with respect to the inner surface C1 of the case C to change the flow rate of the working fluid flowing inside the housing H. By doing so, the moving speed of the housing H is adjusted.

The flow rate of the working fluid flowing inside the housing H is controlled by the valve body V that reciprocates inside the housing H, and the damping response of the valve GV is greatly affected by the operating characteristics of the valve body V. The present invention is configured so that the valve body V can rotate inside the housing H in order to improve the operating characteristics of the valve body V. Hereinafter, the first embodiment of the valve GV according to the present embodiment will be described with reference to FIGS. 1 to 4.

The valve GV of the present embodiment includes a case C for accommodating a working fluid and a housing H for partitioning the inside of the case C into a first fluid chamber 1 and a second fluid chamber 2. The housing H has a bottomed tubular shape and has a cylindrical space inside which communicates with the second fluid chamber 2. The first valve body V1 is arranged inside the housing H. The first valve body V1 has a first valve portion V11 that abuts on the first valve seat H11 provided in a part of the housing H, and a closed position where the first valve portion V11 abuts on the first valve seat H11. As an end point, it reciprocates from the closed position to the bottom side of the housing H along the inner surface of the housing H. Further, in the space on the back side of the first valve body V1 in the inside of the housing H, a first spring S1 is provided as an urging portion S for urging the first valve body V1 toward the closed position.

The wall portion H12 of the housing H is provided with a first port P1 which is an opening P for communicating the contact positions of the first valve portion V11 and the first valve seat H11 with the first fluid chamber 1. The first valve portion V11 and the first valve seat H11 are provided at positions close to the first port P1, and when the first valve body V1 is opened and operated, the first fluid chamber 1 and the second fluid chamber 2 are formed. It is configured so that the working fluid flows smoothly between them. A communication portion between at least one of the first valve portion V11 and the first valve seat H11 so as to communicate the first fluid chamber 1 and the inside of the housing H with the first valve body V1 in the closed position. 7 is formed. Further, on the outer surface of the first valve body V1, a rotary drive unit 8 for rotating the first valve body V1 by a working fluid flowing through the communication portion 7 is provided. Hereinafter, each configuration will be described in more detail.

(Case / housing)
As shown in FIG. 1, the case C has, for example, a cylindrical shape. Inside the case C, a housing H that can reciprocate in the direction of the axis X of the case C while being in contact with the inner surface C1 of the case C is provided. The housing H is attached to the tip of the rod 6, for example, the other end of the rod 6 is connected to the frame of the vehicle and the end of the case C is connected to the suspension of the wheel. The housing H partitions the internal space of the case C into a first fluid chamber 1 and a second fluid chamber 2.

The housing H includes a first housing H1 and a second housing H2 that are adjacent to each other along the direction of the axis X of the case C. The first housing H1 is provided with a member such as the first valve body V1 that comes into direct contact with the working fluid. On the other hand, the second housing H2 is provided with an actuator 4 or the like that controls the operating range of the first valve body V1. The first housing H1 and the second housing H2 are connected to each other by screwing or fitting.

(1st housing)
The first housing H1 is provided with a first port P1 as an opening P for communicating the first fluid chamber 1 and the second fluid chamber 2. In addition, inside the first housing H1, a control mechanism 5 for controlling the operating speed of the housing H by adjusting the flow rate of the working fluid flowing through the first fluid chamber 1 and the second fluid chamber 2 is provided. Has been done.

Inside the first housing H1, a substantially tubular retainer R is provided so as to have a double structure with respect to the first housing H1. A second valve body V2, which will be described later, is housed in this retainer R as one of the valve bodies V. Further, the first valve body V1 described later is housed in the space between the first housing H1 and the retainer R. A first pilot chamber PR1 is formed in the space between the first housing H1 and the retainer R, and communicates with the first fluid chamber 1 via the first orifice OR1. The first orifice OR1 is set to a predetermined opening area, and the flow rate of the working fluid passing through the first orifice OR1 is limited to a predetermined amount. As shown in FIG. 1, for example, the first orifice OR1 opens in the radial direction to the cylindrical wall portion H12 of the first housing H1.

As shown in FIGS. 1 and 4, the first port P1 has a rotating shaft core X of the second valve body V2 (since it is a coaxial core with the shaft core X of the case C, the “rotating shaft core X” is prioritized thereafter. A plurality of them are provided along the circumferential direction with respect to (used). The first port P1 communicates the first fluid chamber 1 with the inside of the first housing H1 and abuts the first valve portion V11 and the first valve seat H11 in order to form a smooth flow of the working fluid. Formed near the location. Each of the first ports P1 extends to a state in which the first port P1 is displaced to one side in the circumferential direction so as to be separated from the rotation axis X.

As a result, for example, the working fluid that collides with the first valve body V1 from the first fluid chamber 1 via the first port P1 collides with the first valve body V1 while maintaining the velocity component in the circumferential direction. Since the working fluid maintains an appropriate flow velocity, the kinetic energy of the working fluid is transmitted to the first valve body V1 so that the first valve body V1 can be rotated.

As shown in FIG. 1, the first valve seat H11 is provided at a position inside the first housing H1 and radially inside the first port P1. Therefore, a tubular valve seat member H13 is provided on the inner surface of the first housing H1 by screwing or the like. The position of the first valve seat H11 with respect to the first port P1 can be set by adjusting the screwing position of the valve seat member H13 with respect to the first housing H1. An annular first valve seat H11 is formed at the tip of the valve seat member H13.

The first valve seat H11 repeatedly contacts and separates from the first valve portion V11 of the first valve body V1, and the first valve portion V11 rotates relative to each other. Therefore, the first valve seat H11 is preferably made of a material having excellent wear resistance or a material having a small friction coefficient. For example, in addition to hard general steel materials and stainless steel materials, hard resin materials can also be used. A member having a low coefficient of friction, such as polytetrafluoroethylene (PTFE), can be mounted on these materials.

(Retainer)
Inside the retainer R, a tubular second valve body V2 that divides the internal space of the retainer R into two is arranged. The second valve body V2 includes a substantially cylindrical main body portion V21 and an annular flange portion V22 protruding outward from the main body portion V21. The second valve body V2 can reciprocate by a predetermined distance along the direction of the rotating shaft core X while sliding the flange portion V22 on the inner surface of the retainer R.

The side wall of the retainer R is provided with the second port P2 and the third port P3 separated from each other along the direction of the rotation axis X from the side closer to the second housing H2. A guide hole R1 that serves as a guide for the plunger 3a is formed on both ends of the retainer R on the side of the solenoid 4a, which will be described later, in the direction of the rotation shaft core X, through which the plunger 3a, which will be described later, is inserted. On the other hand, a bottom hole R2 penetrating in the direction of the rotating shaft core X is formed at the end on the opposite side. An annular second valve seat R3 is formed in the bottom hole R2 so that the end portion of the main body portion V21 of the second valve body V2 comes into contact with the bottom hole R2.

A first pilot chamber PR1 is formed in the space between the retainer R and the first housing H1. The first pilot chamber PR1 communicates with the first fluid chamber 1 via the first orifice OR1. On the other hand, the second port P2 and the third port P3 provided on the peripheral wall of the retainer R communicate with the third pilot chamber PR3 and the first pilot chamber PR1 inside the retainer R. Further, the bottom hole R2 provided at the bottom of the retainer R communicates with the second pilot chamber PR2 provided outside the retainer R.

(Actuator)
Of the retainer R, for example, a coiled second spring S2 is provided around the second valve seat R3, and the flange portion V22 of the second valve body V2 is always urged toward the plunger 3a. The plunger 3a is driven by, for example, a solenoid 4a as an actuator 4 provided in the second housing H2, and changes the position of the second valve body V2 in the direction along the rotation axis X to adjust the flow rate of the working fluid. It constitutes the adjustment mechanism 3. As a result, the second valve body V2 is always urged to the side away from the second valve seat R3. The other end of the second valve body V2 along the direction of the rotating shaft core X is in contact with the tip of the plunger 3a. The second valve body V2 urged by the second spring S2 is always in contact with the end portion of the plunger 3a, and the second valve body V2 of the second valve body V2 responds to a change in the position of the plunger 3a along the direction of the rotation axis X. The position also moves.

As the plunger 3a retreats to the side of the solenoid 4a, the distance between the second valve body V2 and the second valve seat R3 becomes wider, and the second pilot communicating with the first pilot chamber PR1 via the bottom hole R2 of the retainer R. The flow rate of the working fluid flowing through the chamber PR2 increases. On the other hand, when the plunger 3a is pushed out into the third pilot chamber PR3, the other end of the second valve body V2 comes into contact with the second valve seat R3. However, a second slit V25 extending in the radial direction is formed in at least one of the second valve body V2 and the plunger 3a so that a certain amount of working fluid can flow. In the present embodiment, the second slit V25 is formed in the second valve body V2. When the second valve body V2 is in this position, the flow amount of the working fluid is minimized, and the effect of attenuating the sliding of the housing H is maximized.

In this embodiment, the plunger 3a includes a rod-shaped member 3b. Such a rod-shaped member 3b can easily transmit the driving effect of the solenoid 4a to the second valve body V2 located at a position separated from the solenoid 4a by a predetermined distance. When the rod-shaped member 3b mainly transmits the driving force along the direction of the rotating shaft core X, the outer diameter dimension of the rod-shaped member 3b should be smaller than the outer diameter dimension of the solenoid 4a and the second valve body V2. Can be done. That is, although the circumference of the rod-shaped member 3b inside the second housing H2 is used as a guide portion of the rod-shaped member 3b, the rod-shaped member 3b is relatively thin, so that it is easy to secure another space. Therefore, with this configuration, it becomes easy to secure an installation space for the check valve V3, which will be described later, and it becomes easy to obtain a more compact valve GV.

(2nd valve body)
As shown in FIGS. 1 and 2, a conical portion V23 is formed at one end of the main body portion V21 of the second valve body V2. When the plunger 3a protrudes toward the third pilot chamber PR3 by a predetermined length, the second valve body V2 is pressed against the plunger 3a by the second spring S2, and the second valve body V2 and the second valve seat R3 Gap at regular intervals is formed between them.

By forming the conical portion V23, when the housing H is pushed toward the second fluid chamber 2 and the internal pressure of the second pilot chamber PR2 becomes higher than the internal pressure of the third pilot chamber PR3, the conical portion V23 The pressure of the working fluid acts on the inner surface of the second valve body V2 and is pressed against the plunger 3a. On the other hand, when the housing H is pulled toward the first fluid chamber 1 and the internal pressure of the third pilot chamber PR3 becomes higher than the internal pressure of the second pilot chamber PR2, the pressure of the working fluid acts on the outer surface of the conical portion V23. Then, the second valve body V2 is pressed against the second valve seat R3. In this way, by configuring the inner surface and the outer surface of the conical portion V23 as a predetermined shape and pressing the second valve body V2 to either side, the housing H is individually pushed and pulled. The pressure receiving area can be set and the optimum damping characteristics can be obtained.

(Check valve)
A check valve V3 is provided at the bottom of the first housing H1. At the bottom of the first housing H1 facing the first pilot chamber PR1, the fourth port P4 penetrating in the direction of the rotating shaft core X is dispersedly arranged around the rotating shaft core X in the circumferential direction. .. The fourth port P4 communicates with an annular space V31 formed between the first housing H1 and the second housing H2 facing in the direction of the rotation axis X. The annular space V31 further communicates with the first fluid chamber 1 from here via a fifth port P5 penetrating the wall portion H22 of the second housing H2 in the radial direction. The fifth port P5 is also distributed in the circumferential direction with respect to the wall portion H22 of the second housing H2.

Inside the annular space V31, at a position where the fourth port P4 opens, for example, a thin plate-shaped check valve V3 is provided so as to close the fourth port P4. The check valve V3 is made of, for example, an annular material having elasticity by itself, and is fixed between the first housing H1 and the second housing H2 via an annular fixing member V32.

(1st valve body)
The first valve body V1 of the present embodiment is rotated by the flow of the working fluid. As a result, the friction between the inner surface of the first housing H1 and the first valve body V1 is reduced, and in particular, the start and reversal movement of the first valve body V1 are made agile, and the valve GV against the pressure fluctuation of the working fluid is made. It is intended to enhance the damping response of the.

Further, the posture of the first valve body V1 is stabilized by the rotation of the first valve body V1. Therefore, when the first valve body V1 reciprocates on the inner surface of the first housing H1, the corner portion of the first valve body V1 does not bite into the inner surface of the first housing H1 and the first valve body V1 reciprocates. Will be smooth.

Specifically, as shown in FIGS. 1 and 2, the first valve body V1 is provided between the wall portion H12 of the first housing H1 and the retainer R. The first valve body V1 has a substantially cup shape, and the cylindrical outer peripheral surface is guided by the inner surface of the wall portion H12 to rotate. Therefore, no special shaft portion or the like is provided at the center position of the first valve body V1. The first valve body V1 reciprocates in a predetermined range along the rotation axis X, particularly inside the fixed first housing H1. As a result, the gap between the first valve seat H11 and the first valve seat H11 is increased or decreased, and the flow rate of the working fluid over the first fluid chamber 1 and the second fluid chamber 2 is changed to adjust the damping effect. As will be described later, the first valve body V1 moves when the moving speed of the housing H with respect to the case C is high and the internal pressure difference between the first pilot chamber PR1 and the second pilot chamber PR2 becomes larger than a predetermined value, and the first valve body V1 moves. The flow rate of the working fluid through the 1 fluid chamber 1 and the 2nd fluid chamber 2 is increased.

A coiled first spring S1 as an urging portion S is provided between the bottom surface of the first housing H1 (upper in FIG. 1) and the end surface V15 of the first valve body V1. Is always urged to the side of the first valve seat H11. A ring member 9 for reducing friction between the first spring S1 and the end surface V15 of the first valve body V1 is provided.

While the first valve body V1 is configured to rotate, the first spring S1 that urges the first valve body V1 toward the first valve seat H11 is not necessarily provided so as to be rotatable relative to the first housing H1. It's not a thing. Rather, it is convenient to fix it to the first housing H1. However, in this case, friction occurs between the first spring S1 and the first valve body V1, and the rotation of the first valve body V1 is impaired. Therefore, by providing the ring member 9 as in this configuration, the frictional force between the first spring S1 and the first valve body V1 is reduced, and the rotational resistance of the first valve body V1 is reduced. As a result, the operation of the first valve body V1 becomes more agile.

As the ring member 9, it is preferable to use a metal material having normal wear resistance, a washer formed of PTFE or the like having a small coefficient of friction, or the like.

An annular vertical wall portion is provided as the first valve portion V11 on the outer edge portion of the bottom portion of the first valve body V1 that faces the second fluid chamber 2. In the first valve portion V11, the first slit V14 as the communication portion 7 is dispersedly arranged along the circumferential direction of the first valve portion V11. As a result, as shown in FIG. 1, the working fluid slightly flows through the first fluid chamber 1 and the second fluid chamber 2 even when the first valve portion V11 is in contact with the first valve seat H11. Can be done. As will be described later, the flow rate of the working fluid flowing through the first fluid chamber 1 and the second fluid chamber 2 is changed according to the distance between the first valve seat H11 and the first valve portion V11 to have a damping effect. Is adjusted.

As shown in FIGS. 1 and 4, the first slit V14 is located at the boundary position between the first fluid chamber 1 and the second fluid chamber 2, and a plurality of the first slits V1 are provided along the circumferential direction with respect to the rotation axis X of the first valve body V1. It is provided. When the first valve body V1 is in the closed position, the working fluid always flows through the first slit V14 according to the pressure difference between the first fluid chamber 1 and the second fluid chamber 2. In this configuration, the extension direction of the first slit V14 is set to one side in the circumferential direction so as to be separated from the rotation axis X so that the working fluid flowing through the first slit V14 promotes the rotation of the first valve body V1. It is displaced and formed in a substantially spiral shape.

When the first slit V14 is provided in the first valve portion V11 in this way, the first valve body V1 can easily rotate due to the reaction force of the working fluid flowing through the first slit V14. However, the first slit V14 may be provided in the first valve seat H11 as long as the working fluid flowing through the first slit V14 can act on the first valve body V1 to rotate the first valve body V1.

Further, in order to form the communication portion 7 with such a first slit V14, for example, as shown in FIGS. 3 and 4, a notch may be formed in the end surface of the first valve portion V11, and such processing may be performed. Is extremely easy. Further, the width of the first slit V14 can be freely set, and the first valve body V1 having good rotation efficiency can be rationally configured.

(1st blade of 1st valve body)
As shown in FIG. 3, the first valve body V1 is provided with a first blade portion 81 as a rotation drive portion 8. The first blade portion 81 is provided on the inner peripheral side of the first valve portion V11, and when viewed from the side of the second fluid chamber 2 along the rotation shaft core X, the normal direction F is the rotation shaft core X. On the other hand, it is provided with a plurality of inclined surfaces having a circumferential component centered on the rotation axis X while being inclined. For example, as shown in FIG. 3, it can be configured in the shape of a screw such as a ship or a turbine blade of a turbocharger.

When the first blade portion 81 is formed on the inner peripheral side of the first valve portion V11 on the outer surface of the first valve body V1, the working fluid collides with the first valve body V1 along the rotation axis X. It is advantageous in some cases. That is, mainly when the pressure in the second fluid chamber 2 increases, the first valve body V1 is rotated while changing the flow of the working fluid from the direction along the rotation axis X in the radial direction.

As shown in FIGS. 1 to 3, the surface of the first blade portion 81 is recessed, and the outer surface V16 of the bottom portion of the first valve body V1 is also recessed. As a result, the working fluid that collides with the first blade portion 81 in the direction of the rotating shaft core X can be smoothly guided in the radial direction.

By rotating the first valve body V1, the friction between the inner surface of the wall portion H12 of the first housing H1 and the outer peripheral surface of the first valve body V1 is reduced. That is, the dynamic friction force when moving relative to each other is smaller than the static friction force acting when they are not moving relative to each other. Therefore, in particular, the operating characteristics when the first valve body V1 opens and starts moving or when the operating direction is reversed becomes agile, and the damping response of the valve GV to the pressure fluctuation of the working fluid becomes extremely good. ..

Further, the posture of the first valve body V1 is stabilized by the rotation of the first valve body V1. Therefore, when the first valve body V1 reciprocates on the inner surface of the first housing H1, the corner portion of the first valve body V1 does not bite into the inner surface, and the reciprocating movement of the first valve body V1 is smooth. It becomes.

In addition, when the first valve body V1 rotates, the working fluid easily forms a liquid film between the inner surface of the wall portion H12 of the first housing H1 and the outer peripheral surface of the first valve body V1 to operate. It is also expected that the lubricating action of the fluid will be improved.

In order to reduce the rotational friction of the first valve body V1, at least one of the inner surface of the first housing H1 and the outer peripheral surface of the first valve body V1 is provided with a material having a friction reducing effect such as PTFE. It may be provided.

(2nd blade of 1st valve body)
As shown in FIGS. 1 to 4, a second blade portion 82 as a rotation drive portion 8 is provided on the outer peripheral side of the first valve portion V11 of the first valve body V1. The second blade portion 82 is a working fluid when the working fluid of the first fluid chamber 1 flows into the second fluid chamber 2 through the first slit V14, particularly when the first valve body V1 is in the closed position. It catches the flow.

A cylindrical outer surface V11a and a pressure receiving surface V11b substantially perpendicular to the outer surface V11a are formed on the outer peripheral side of the first valve portion V11. Since the pressure receiving surface V11b opens and operates the first valve body V1 by receiving the pressure of the working fluid of the first fluid chamber 1, it is not necessarily perpendicular to the outer surface V11a as shown in FIGS. 1 and 3. The normal line may be formed of a surface having a component in the urging direction of the first spring S1.

As shown in FIGS. 3 and 4, the second blade portions 82 project from the outer surface V11a in the outer diameter direction, and a plurality of the second blade portions 82 are formed along the circumferential direction. For example, when viewed along the rotation axis X, it can be formed by a substantially triangular convex portion. That is, a first surface 82a projecting from the outer surface V11a in the outer diameter direction is formed, and a second surface 82b is provided so as to asymptotically approach the outer surface V11a from the outermost edge portion of the first surface 82a. In this case, the first surface 82a is the surface that receives the working fluid. Therefore, the rotation direction is limited by the shape of the second blade portion 82. As shown in FIG. 4, the rotation direction and the direction of the first surface 82a are preferably set so that the working fluid flowing in from the first port P1 collides with the first surface 82a at an angle close to a right angle. It is preferable that the first surface 82a is slightly inclined from a right angle so that the working fluid is guided to the first slit V14 formed at the base end portion of the first surface 82a.

When the rotation direction is not limited, the second blade portion 82 may be a plate-shaped portion or the like protruding in the outer diameter direction from the outer surface V11a, and a plurality of the second blade portions 82 may be provided along the circumferential direction.

As shown in FIGS. 3 and 4, in the case of the second blade portion 82, it is convenient to configure the first slit V14 so as to open to the base portion of the first surface 82a. That is, since the working fluid concentrates on the corners of the first surface 82a and the outer surface V11a in the vicinity thereof while applying pressure to the second blade portion 82, the working fluid can be provided here by providing the first slit V14. It becomes easy to guide to the first slit V14.

In this case, as shown in FIGS. 4A and 4B, if the direction of the first slit V14 and the opening direction of the first port P1 are aligned in the same direction, the flow of the working fluid becomes smooth and the working fluid operates. The kinetic energy of the fluid can be easily transmitted to the first valve body V1.

FIG. 4A shows a state in which the working fluid flows out from the first blade portion 81 to the second blade portion 82. It is convenient to configure the first slit V14 and the first port P1 so that the angles match in this way, especially when the working fluid is discharged into the second fluid chamber 2.

On the other hand, FIG. 4B shows a state in which the working fluid flows from the second blade portion 82 to the side of the first blade portion 81. In this case, the working fluid that has flowed from the first port P1 to the surface of the outer surface V11a of the first valve body V1 flows into the inside of the wall portion H12 of the first housing H1 and reliably presses the first surface 82a. 1 Rotate the valve body V1.

A second orifice OR2 penetrating in the direction of the rotation shaft core X is provided at the center of the first valve body V1. The second orifice OR2 communicates with the second pilot chamber PR2 and the second fluid chamber 2. The second orifice OR2 and the first orifice OR1 are set to a preset opening area so that a predetermined amount of working fluid can flow.

The first valve body V1 can be configured by using various materials. However, in order to make the rotation characteristics and the movement along the direction of the rotation axis X agile, it is preferable to use a light material. For example, in addition to various resin materials, it can be composed of an aluminum material, a magnesium alloy, titanium, or the like.

(Operation mode / Pushing operation)
FIG. 1 shows, for example, the case where the rod 6 is pushed down. When the housing H begins to compress the second fluid chamber 2, the working fluid of the second fluid chamber 2 flows from the second orifice OR2 into the second pilot chamber PR2 as shown by the broken line in FIG. 1, and the plunger 3a The third pilot chamber PR3 is reached through the second slit V25 between the second valve body V2 and the second valve body V2 or the gap between the second valve body V2 and the second valve seat R3, and further, the second port P2 and the third port P3. It is discharged to the first fluid chamber 1 through the first pilot chamber PR1 and the first orifice OR1.

At this time, as shown by a thin broken line in FIG. 1, the working fluid also flows out to the first fluid chamber 1 through the first slit V14 and the first port P1 provided in the first valve body V1. Even when the first valve body V1 is in the closed position, the working fluid flows out from the second fluid chamber 2 to the first fluid chamber 1 through the first slit V14. The flow of the working fluid causes the first blade portion 81 to receive a rotational force, and the first valve body V1 starts rotating. As a result, the frictional force between the first valve body V1 and the wall portion H12 of the first housing H1 is reduced.

When the housing H descends, the internal pressure of the second pilot chamber PR2 increases due to the working fluid flowing in through the second orifice OR2. However, since the flow rate of the working fluid passing through the second orifice OR2 is limited to a certain amount, the rising speed of the internal pressure of the second pilot chamber PR2 is suppressed to a predetermined speed. However, when the descending speed of the housing H is high, the pressure of the working fluid acting on the outer surface V16 at the bottom of the first valve body V1 rapidly increases, so that the pressure acting on the outer surface V16 is the pressure acting on the outer surface V16 of the second pilot chamber PR2. It becomes larger than the pressure acting on the inner surface V17 at the bottom of the first valve body V1 inside. Therefore, the first valve body V1 is separated from the first valve seat H11 against the urging force of the first spring S1, and the working fluid flows toward the first fluid chamber 1 through the gap generated here. As a result, the housing H can be lowered relatively quickly when a large downward force acts on the housing H.

When the pressure in the second fluid chamber 2 is further increased, the first valve body V1 itself is pushed toward the bottom side of the first housing H1 to start the opening operation. As a result, a gap is formed between the first valve body V1 and the first valve seat H11, and the flow velocity of the working fluid increases. Due to this increase in the flow velocity, the rotation speed of the first valve body V1 is further increased, and the rotational state becomes stable.

The pressure required to open and operate the first valve body V1 is determined by the position of the plunger 3a. The more the plunger 3a protrudes toward the third pilot chamber PR3, the smaller the gap between the second valve body V2 and the second valve seat R3. Therefore, the working fluid flowing out from the second pilot chamber PR2 to the third pilot chamber PR3 is throttled, and the second pilot chamber PR2 when the working fluid flows into the second pilot chamber PR2 via the second orifice OR2. The internal pressure of the body rises faster. In this case, the difference from the pressure acting on the outer surface V16 at the bottom of the first valve body V1 is small, and the first valve body V1 becomes difficult to open and operate. As a result, the flow rate of the working fluid discharged from the second fluid chamber 2 to the first fluid chamber 1 is limited, and the damping effect accompanying the operation of the housing H is enhanced.

(Operation mode / pulling operation)
On the other hand, FIG. 2 shows a case where the rod 6 is pulled upward in FIG. When the housing H begins to compress the first fluid chamber 1, the working fluid of the first fluid chamber 1 flows in the direction of the broken line in FIG. 2 and flows from the first orifice OR1 into the first pilot chamber PR1. The third pilot chamber PR3 is reached via the 1st port P1 and the 2nd port P2, and further, the second slit V25 or the second valve body V2 and the second valve seat R3 between the plunger 3a and the second valve body V2 It is discharged to the second fluid chamber 2 through the second pilot chamber PR2 and the second orifice OR2 through the gap between the two.

At this time, even when the first valve body V1 is in the closed position, the working fluid flows into the second fluid chamber 2 through the first slit V14 provided in the first port P1 and the first valve body V1. Note that FIG. 2 shows a state in which the first valve body V1 is open. The flow of the working fluid causes the second blade portion 82 to receive a rotational force, and the first valve body V1 starts rotating. As a result, the frictional force between the first valve body V1 and the wall portion H12 of the first housing H1 is reduced.

When the housing H rises in FIG. 1, the internal pressure of the first pilot chamber PR1 rises due to the working fluid flowing in through the first orifice OR1. However, since the flow rate of the working fluid passing through the first orifice OR1 is limited to a certain amount, the rising speed of the internal pressure of the first pilot chamber PR1 is suppressed to a predetermined speed. However, when the ascending speed of the housing H is high, the pressure of the working fluid acting on the first port P1 increases sharply, so that the pressure acting on the pressure receiving surface V11b of the first valve body V1 is the pressure acting on the pressure receiving surface V11b of the first pilot chamber PR1. It becomes larger than the pressure acting on the end face V15 of the first valve body V1 inside. Therefore, the first valve body V1 is separated from the first valve seat H11 against the urging force of the first spring S1, and as shown by the broken line in FIG. 2, the working fluid is the first through the gap generated here. 2 Flows into the fluid chamber 2. At this time, the flow velocity of the working fluid increases, the force acting on the second blade portion 82 also increases, the rotational speed of the first valve body V1 further increases, and the rotational state becomes stable.

The timing at which the first valve body V1 opens and starts the operation is determined by the position of the plunger 3a. As the plunger 3a protrudes toward the third pilot chamber PR3, the gap between the second valve body V2 and the second valve seat R3 becomes smaller, and the working fluid flowing out from the third pilot chamber PR3 to the second pilot chamber PR2. Is squeezed. As a result, when the working fluid flows into the first pilot chamber PR1 through the first orifice OR1, the internal pressure of the first pilot chamber PR1 increases rapidly. In this case, the difference between the pressure acting on the outer surface V16 at the bottom of the first valve body V1 and the pressure acting on the end surface V15 of the first valve body V1 is small, and the first valve body V1 becomes difficult to open. As a result, the flow rate of the working fluid discharged from the first fluid chamber 1 to the second fluid chamber 2 is limited, and the damping effect of the valve GV is enhanced.

When the solenoid 4a fails, the control mechanism 5 operates as follows.
The plunger 3a is pushed by the second valve body V2 by the urging force of the second spring S2 and retreats to the side of the second housing H2. As a result, the second valve body V2 moves to a position where it comes into contact with the bottom portion of the first housing H1, and the second port P2 is shielded by the flange portion V22 of the second valve body V2. As a result, the first pilot room PR1 and the third pilot room PR3 communicate with each other only through the third port P3. The opening area of the third port P3 is set and formed so as to have a predetermined size, and is set smaller than the opening area of the first orifice OR1 or the area of the gap between the second valve body V2 and the second valve seat R3. ing. Therefore, when the solenoid 4a fails, the flow of the working fluid is controlled by the third port P3.

[Second Embodiment]
The valve GV of the present invention can also be configured as shown in FIG. It should be noted that the configurations included in the present embodiment, which are common to the above-mentioned first embodiment, are assumed to have the same configurations and functions as those of the first embodiment. Further, as the reference reference numerals of the components, the same numbers are used for the same reference numerals as those in the above embodiment.

In the present embodiment, the second valve body V2, the first pilot chamber PR1, and the like are eliminated, and only the housing H, the valve body V, and the urging portion S have a simple configuration. Here, too, the housing H has a bottomed tubular shape and has a cylindrical space inside. A valve body V is arranged inside the housing H. The valve body V has a valve portion V11 that abuts on the valve seat H11 provided in a part of the housing H, and the closing position where the valve portion V11 abuts on the valve seat H11 is set as an end point, and the housing H is moved from the closed position. Move back and forth to the bottom side. Further, in the space H14 on the back side of the valve body V in the inside of the housing H, a spring mechanism as an urging portion S for urging the valve body V toward the closed position is provided.

(housing)
Similar to the first embodiment, the housing H is provided with a plurality of first ports P1 as openings P along the circumferential direction. The first port P1 also extends so as to be separated from the rotation axis X so that it deviates to one side in the circumferential direction. As a result, for example, the working fluid that collides with the valve body V from the first fluid chamber 1 through the first port P1 collides with the valve body V while maintaining the velocity component in the circumferential direction. The kinetic energy of this working fluid is transmitted to the valve body V, and the valve body V rotates.

The housing H is provided with a valve seat H11 that comes into contact with the valve body V. The valve seat H11 is located near the first port P1 at a position radially inside with respect to the first port P1, and when the valve body V opens and operates, the first fluid chamber 1 and the second fluid chamber 2 meet. It is provided at a position where the working fluid flows smoothly between them. The valve seat H11 is provided at the tip of a valve seat member H13 provided on the inner surface of the housing H, for example, by screwing, and the position of the valve seat H11 with respect to the first port P1 can be adjusted by the screwed portion.

(Valve body)
As shown in FIG. 5, the valve body V also has a substantially cup shape, and the cylindrical outer peripheral surface is guided by the inner surface of the wall portion H12 of the housing H to rotate. An annular valve portion V11 is formed so as to project from the outer surface V16 of the bottom portion, a first blade portion 81 is formed on the inner peripheral side of the valve portion V11, and a second blade portion 82 is formed on the outer peripheral side. .. Further, the valve portion V11 is formed with a spiral slit V14 as a communication portion 7 as in the first embodiment. The slit V14 may be provided on the side of the valve seat H11.

(Burning department)
In the present embodiment, the urging portion S is provided in the space H14 inside the housing H and on the back side of the valve body V. Specifically, the urging portion S includes a core member S31 that presses the valve body V from the back side, and a spring member S32 that presses the core member S31 against the back surface of the valve body V.

The core member S31 is provided with a tapered tip portion for pushing the back surface of the rotating valve body V, and abuts on the back surface of the valve body V at a position that is the center of rotation. As a result, the frictional resistance generated between the valve body V and the core member S31 is reduced.

A guide cylinder S33 for slidably storing the core member S31 is provided on the bottom surface of the housing H. Inside the guide cylinder S33, for example, a coil-shaped spring member S32 is installed so as to abut the end surface of the core member S31 and the bottom surface of the housing H and urge them to separate from each other. The spring member S32 sets the spring constant according to the hydraulic pressure of the working fluid when the valve body V is opened and moved. The greater the urging force of the spring member S32, the later the opening timing of the valve body V. In order to prevent wear of the member, a hard material may be arranged on the back surface of the valve body V or the tip of the core member S31.

(Check valve)
Due to the relationship between the urging force of the urging portion S and the hydraulic pressure of the working fluid acting on the outer surface V16 of the valve body V, the valve body V needs to be pushed into the housing H, so that the housing H operates. A check valve V3 for discharging the fluid to the first fluid chamber 1 is provided, and a breathing hole V18 is provided on the bottom surface of the valve body V.

When the valve body V operates, the working fluid flows into the space H14 on the back side of the valve body V through the gap between the wall portion H12 of the housing H and the outer peripheral surface of the valve body V. Therefore, normally, the space H14 on the back side of the valve body V is filled with the working fluid. Therefore, it is necessary to appropriately discharge the working fluid so that the pushing operation of the valve body V is not hindered. Therefore, for example, a check valve V3 is provided on the back surface of the housing H.

The check valve V3 is provided with at least one discharge hole that communicates the space H14 on the back side of the valve body V with the first fluid chamber 1. In FIG. 5, a plurality of fourth ports P4 are dispersedly arranged around the rotation shaft core X, and the working fluid is discharged from the plurality of fifth ports P5 via the annular space V31. A check valve V3 made of an annular elastic member is fixed to the annular space V31 by using an annular fixing member V32.

Since the position of the valve body V should be controlled by the urging force of the urging portion S, the opening of the fourth port P4 so that the operation of the valve body V is not affected by the pressure of the working fluid in the space H14. Set the area large enough.

The breathing hole V18 provided in the valve body V is located on the back side of the valve body V from the second fluid chamber 2 when the valve body V pushed by the working fluid of the second fluid chamber 2 is pushed back to the closed position with respect to the valve seat H11. The working fluid is allowed to flow into the space H14. Therefore, the opening area of the breathing hole V18 is set to a predetermined value. That is, when the valve body V is pushed in, it is necessary to limit the flow of the working fluid so that the pressure in the space H14 on the back side of the valve body V is maintained lower than the pressure in the second fluid chamber 2.

On the other hand, when the valve body V is pushed back by the spring member S32, the outer surface V16 at the bottom of the valve body V is in a state where no particular pressure is applied from the second fluid chamber 2, so that the valve body V is the spring member S32. The speed of being pushed back by is not limited. Therefore, the size of the breathing hole V18 may be determined by the relationship between the degree of pressure increase in the space H14 when the valve body V is pushed in and the return speed of the valve body V.

The valve body V is also pushed in when the housing H is pulled toward the first fluid chamber 1 and the pressure in the first fluid chamber 1 increases. At this time, the pressure of the working fluid acts on the pressure receiving surface V11b provided on the outer periphery of the valve body V, and the pressure acting on the pressure receiving surface V11b is compared with the pressure in the space H14, so that the breathing hole V18 does not particularly work. However, when the pressurization from the first fluid chamber 1 is lost and the valve body V is pushed back, the breathing hole V18 functions in the same manner as described above.

In the valve GV having this configuration, the valve body V closes when the housing H moves in any direction of the case C and the working fluid flows between the first fluid chamber 1 and the second fluid chamber 2. Even in the position, the valve body V starts to rotate due to the working fluid flowing through the slit V14. As a result, the frictional force between the valve body V and the wall portion H12 of the housing H is reduced. Therefore, the operation of the valve body V becomes agile when the valve body V continues to open and operate. Thereby, a valve GV having a good damping response can be obtained.

[Other Embodiments]
In addition to the above-described embodiments, the urging portion S may be, for example, one in which the coiled spring member S32 in FIG. 5 is replaced with a leaf spring and the leaf spring is fixed to the bottom of the housing H. If it is a leaf spring, its own installation space is small, and a compact valve GV can be obtained.

Further, a magnetic force may be used as the urging portion S. For example, as shown in FIG. 6, a magnet 10 is provided in the vicinity of the first port P1 in the wall portion H12 of the housing H, and the valve body V is composed of a metal member or the like attracted by the magnet 10. .. Incidentally, the wall portion H12 of the housing H is preferably made of a non-magnetic metal material or resin material in order to prevent the magnetic field lines of the magnet 10 from wrapping around. As a result, the valve body V can always be attracted to the valve seat H11 side. In this case, there is no component of the urging portion S that comes into contact with the valve body V, and the valve body V having low rotational resistance can be obtained.

Further, as another configuration of the urging portion S, although not shown, the space H14 on the back side of the valve body V is filled with air of a predetermined pressure, and the valve body utilizes the expansion / contraction characteristics of the air. It may be the one that urges V. With this configuration, since no member of the urging portion S comes into contact with the rotating valve body V, the rotational resistance of the valve body V can be kept to a minimum, and a valve GV with extremely good responsiveness can be obtained. can.

In the above embodiment, the housing H is reciprocated with respect to the case C, but the housing H may be fixed inside the case C. For example, the valve GV is provided so as to partition the inside of the case C into the first fluid chamber 1 and the second fluid chamber 2, and the working fluid is first generated by another piston or the like provided inside the case C. It is also possible to configure the structure so that the fluid chamber 1 and the second fluid chamber 2 are moved back and forth.

The valve according to the present invention is widely applied, for example, as a valve for partitioning the inside of a case into a first fluid chamber and a second fluid chamber and adjusting the flow rate of a working fluid across the first fluid chamber and the second fluid chamber. be able to.

1 1st fluid chamber 2 2nd fluid chamber 7 Communication part 8 Rotational drive part 81 1st blade part 82 2nd blade part 9 Ring member C Case GV valve H Housing H11 Valve seat H12 Wall part P Opening S Bias part S1 Coil Spring V Valve body V11 Valve part V11b Pressure receiving surface V14 Slit X Rotating shaft core

Claims (8)

A case that houses the working fluid and
A bottomed tubular housing that divides the inside of the case into a first fluid chamber and a second fluid chamber and has a cylindrical space inside that communicates with the second fluid chamber.
It has a valve portion that is arranged in the cylindrical space and abuts on a valve seat provided in a part of the housing, and the bottom of the housing is from the closed position with the closing position where the valve portion abuts on the valve seat as an end point. A valve body that reciprocates along the inner surface of the cylindrical space on the side,
The housing is provided with an urging portion for urging the valve body toward the closed position.
The wall portion of the housing is provided with an opening for communicating the contact position between the valve portion and the valve seat and the first fluid chamber, and also provides an opening for communicating with the first fluid chamber.
At least one of the valve portion and the valve seat is formed with a communication portion that communicates the first fluid chamber and the cylindrical space with the valve body in the closed position.
A valve provided with a rotary drive unit on the outer surface of the valve body to rotate the valve body by a working fluid flowing through the communication portion. The valve according to claim 1, wherein the rotation drive portion includes a first blade portion provided on the inner peripheral side of the valve portion. The valve according to claim 1 or 2, wherein the rotation drive portion includes a second blade portion provided on the outer peripheral side of the valve portion. 3. Described valve. A plurality of the communication portions are provided along the circumferential direction of the valve body with respect to the rotation shaft core, and each of the communication portions extends so as to be separated from the rotation shaft core so as to be displaced to one side in the circumferential direction. The valve according to any one of claims 1 to 4. The valve according to claim 5, wherein the communication portion is a slit provided in the valve portion. A plurality of the openings are provided along the circumferential direction of the valve body with respect to the rotation shaft core, and each of the openings extends to one side in the circumferential direction so as to be separated from the rotation shaft core. The valve according to any one of claims 1 to 6. The method according to any one of claims 1 to 7, wherein the urging portion is a coil-shaped spring, and a ring member that can rotate relative to the valve body is provided between the valve body and the coil-shaped spring. Valve.

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