JP2019027563A - valve - Google Patents

Abstract

To provide a valve which comprises a pressure attenuation function improved in operation responsiveness and reduces cost.SOLUTION: The present invention relates to a valve GV comprising: a case C; a bottomed cylindrical housing H which divides the inside of the case C into a first fluid chamber 1 and a second fluid chamber 2 and includes a cylindrical space communicating to the second fluid chamber 2 insides; a valve body V disposed in the cylindrical space, including a valve part which is abutted to a valve seat H11 provided in the housing H, and reciprocally movable to the bottom side of the housing H with a closing position where the valve part is abutted to the valve seat H11 defined as an end point; and an energizing part S which is provided in the housing H and energizes the valve body H to the closing position. An opening P communicating an abutment position of the valve part and the valve seat H11 with the first fluid chamber 1 is provided on a wall part H12 of the housing H. A communication part 7 communicating the first fluid chamber 1 with the inside of the housing H in a state where the valve body V is located at the closing position is formed in at least any one of the valve part V11 and the valve seat H11. A rotary drive part 8 based on a working fluid flowing through the communication part 7 is provided on an outer surface V16 of the valve body V.SELECTED DRAWING: Figure 1

Description

  The present invention includes a case that contains a working fluid, and a housing that reciprocates 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 characteristics of a housing by controlling the operation of a provided valve body.

  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. Thereby, the buffering effect of the vibration damper is adjusted.

  In the apparatus of Patent Document 1, a working fluid is filled in a cylinder 9 and a piston 6 is provided. The piston 6 partitions the cylinder 9 into a lower working chamber 7 and an upper working chamber 8. ing. A valve body 10 is provided inside the piston 6 and is movable relative to the piston. When the piston 6 moves inside the cylinder 9 and a predetermined pressure is applied to the valve body 10 from the working fluid, the valve body 10 is actuated to open the flow path, and the working fluid flows between the working chambers 7 and 8. Circulate between. Thereby, the operation speed of the piston 6 is controlled.

  Inside the piston 6, there is provided a drive element 2 that contacts the valve body 10 and adjusts the operating characteristics of the valve body 10. By appropriately adjusting the position of the drive element 2 and the like, the pressure of the working fluid necessary for the valve body 10 to shift from the closed state to the open state is set. Thereby, the vibration damper which can control the operation characteristic of piston 6 is constituted.

JP-A-11-72133

  In a vibration damper having a valve body capable of controlling the flow rate of the working fluid, including the vibration damper shown in Patent Document 1, it is necessary to improve the operation responsiveness of the valve body in order to improve the damping function. is there. However, in the valve body provided in the normal damping mechanism including the valve body disclosed in Patent Document 1, the outer peripheral surface of the valve body often 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 an 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 enlarging the gap size. Therefore, in order to improve the operation responsiveness of the valve body, the cost of the product is increased, for example, by increasing the machining accuracy of the parts or using a material that does not easily cause thermal expansion or deformation even when the operating temperature changes. I will.

  In view of such a problem, there has been a demand for a valve that has a pressure damping function with excellent operation response and is configured at low cost.

(Feature configuration)
The characteristic configuration of the valve according to the present invention is:
A case for containing a working fluid;
A bottomed cylindrical housing that divides the inside of the case into a first fluid chamber and a second fluid chamber, and has a cylindrical space communicating with the second fluid chamber;
A valve portion disposed in the cylindrical space and in contact with a valve seat provided in a part of the housing, the closed position where the valve portion is in contact with the valve seat as an end point from the closed position to the bottom of the housing; A valve body reciprocating along the inner surface of the cylindrical space on the side;
A biasing portion provided in the housing and biasing the valve body toward the closed position;
The wall of the housing is provided with an opening that communicates the contact position of the valve portion and the valve seat 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 rotation driving unit is provided on the outer surface of the valve body to rotate the valve body with a working fluid flowing through the communication portion.

(effect)
When the working fluid flows through the inside of the housing provided in the case, the valve of this configuration has a flow rate of the working fluid over the first fluid chamber and the second fluid chamber by the operation of the valve body provided in the housing. Is to control.

  The valve body is movable over a predetermined distance inside the housing, and is normally in a closed position where the opening is narrowed by the urging portion. 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. To 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 is rotated by the flow of the working fluid. Thereby, the friction between the inner surface of the cylindrical space of the housing and the valve body can be reduced. For this reason, in particular, the start and reversal of the reciprocating movement of the valve body becomes agile, and the damping response to the pressure fluctuation of the working fluid becomes extremely good.

  Moreover, the posture of the valve body is stabilized by the rotation of the valve body. Therefore, when the valve element reciprocates on the inner surface of the cylindrical space, the corner of the valve element does not bite into the inner surface of the cylindrical space, and the reciprocating movement of the valve element becomes smooth.

(Feature configuration)
In the valve according to the present invention, it is convenient that the rotation driving 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 in 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 and rotates the valve body. Thus, with this configuration, particularly when the pressure in the second fluid chamber increases, the operation of the valve element is agile.

(Feature configuration)
In the valve according to the present invention, the rotation driving unit may include a second blade portion provided on an outer peripheral side of the valve unit.

(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 in 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 and rotates the valve body. In this way, with this configuration, in particular, when the pressure in the first fluid chamber increases, the operation of the valve element is quick to start.

(Feature configuration)
In the valve according to the present invention, it is advantageous that a pressure receiving surface that is in contact with the working fluid and has a component in a direction opposite to the biasing direction by the biasing portion is provided on the outer peripheral side of the valve portion. is there.

(effect)
When the working fluid in the second fluid chamber presses the end face of the valve body, the direction in which the working fluid exerts pressure coincides with the direction in which the valve body moves, so that the valve body easily opens. However, in order to open the valve body even when the internal pressure of the first fluid chamber increases, the working fluid in the valve body increases the pressure so that the valve body moves from the second fluid chamber toward the first fluid chamber. It is necessary to devise the shape of the affected part. In view of this, in this configuration, a pressure receiving surface is provided on the outer peripheral side of the valve portion so as to be in contact with the working fluid and have a normal component in a direction opposite to the biasing direction by the biasing portion. Thereby, the valve body is easily opened by the pressure of the working fluid in the first fluid chamber, and a good damping function can be exhibited.

(Feature configuration)
As the valve according to the present invention, a plurality of the communication portions are provided along a circumferential direction of the valve body with respect to the rotation axis, and each of the communication portions is located on one side in the circumferential direction as being separated from the rotation axis. It is convenient if it is extended to a state of being deviated.

(effect)
The communication portion is at the boundary position between the first fluid chamber and the second fluid chamber. Particularly when the valve body is in the closed position, the working fluid always flows through the communication portion according to the pressure difference between the two fluid chambers. To do. In this configuration, the extending direction of the communicating portion is shifted to one side in the circumferential direction as the distance from the rotation axis is increased so as to promote the rotation of the valve body by the working fluid flowing through the communicating portion.

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

(Feature configuration)
In the valve according to the present invention, the communication part can be constituted by a slit provided in the valve part.

(effect)
By providing the communication part in the valve part of the valve body, the working fluid flowing through the communication part directly acts on the valve body, so that the rotation of the valve body is further promoted. Moreover, if a communicating part is a slit, what is necessary is just to process a notch in the end surface of a valve part, for example, and such a process is very easy. Furthermore, the groove width can be set freely, and a valve body with good rotational efficiency can be rationally configured.

(Feature configuration)
In the valve according to the present invention, a plurality of the openings are provided along the circumferential direction with respect to the rotation axis of the valve body, and the more the openings are separated from the rotation axis, the more they are biased toward one side in the circumferential direction. It is convenient to extend to the position where it stands.

(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 rate, it is advantageous if the kinetic energy of the working fluid can be efficiently used for the rotation of the valve body. Therefore, as in the present configuration, the extended state of the opening is shifted to one side in the circumferential direction as the distance from the rotational axis of the valve body increases.

  Thereby, 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, and the opening and closing operation of the valve portion becomes smooth, so that a valve with good damping response can be obtained.

(Feature configuration)
In the valve according to the present invention, it is convenient that the urging portion is a coiled spring, and a ring member that can rotate relative to the valve body and the coiled spring is provided. .

(effect)
While the valve body is configured to rotate, the coiled spring that urges the valve body toward the valve seat is not necessarily rotatably attached to the housing, but rather is fixed to the housing. It is easy to be done. However, in this case, friction is generated 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 | bulb which concerns on 1st Embodiment. Explanatory drawing which shows the structure of the valve | bulb which concerns on 1st Embodiment. The perspective view which shows the structure of the valve body which concerns on 1st Embodiment. Explanatory drawing which shows the operation | movement aspect of the valve body which concerns on 1st Embodiment. Explanatory drawing which shows the structure of the valve | bulb which concerns on 2nd Embodiment. Explanatory drawing which shows the structure of the valve | bulb 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, and the flow rate of the working fluid flowing through the housing H is changed. This adjusts the moving speed of the housing H.

  The flow rate of the working fluid flowing through the housing H is controlled by the valve body V that reciprocates within the housing H, and the damping response of the valve GV is greatly influenced 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, a first embodiment of a valve GV according to this embodiment will be described with reference to FIGS. 1 to 4.

  The valve GV of the present embodiment includes a case C that contains a working fluid, and a housing H that partitions the inside of the case C into a first fluid chamber 1 and a second fluid chamber 2. The housing H has a bottomed cylindrical shape, and includes a cylindrical space communicating with the second fluid chamber 2 inside. Inside the housing H, the first valve body V1 is disposed. The 1st valve body V1 has the 1st valve part V11 which contacts the 1st valve seat H11 provided in a part of housing H, and the 1st valve part V11 is in the closed position where it contacted the 1st valve seat H11. The end point reciprocates along the inner surface of the housing H from the closed position to the bottom side of the housing H. Further, in the interior of the housing H, a space on the back side of the first valve body V1 is provided with a first spring S1 as an urging portion S that urges the first valve body V1 toward the closed position.

  The wall H12 of the housing H is provided with a first port P1 that is an opening P that communicates the contact position 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 opens, the first fluid chamber 1 and the second fluid chamber 2 The working fluid is configured to smoothly flow between the two. At least one of the first valve portion V11 and the first valve seat H11 is connected to the first fluid chamber 1 and the interior of the housing H so that the first valve body V1 is in the closed position. 7 is formed. Furthermore, a rotation drive unit 8 is provided on the outer surface of the first valve body V1 to rotate the first valve body V1 with a working fluid that flows through the communication unit 7. Hereinafter, each configuration will be described in more detail.

(Case and housing)
As shown in FIG. 1, the case C has a cylindrical shape, for example. Inside the case C, there is provided a housing H that can reciprocate in the direction of the axis X of the case C while contacting the inner surface C1 of the case C. 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 the first fluid chamber 1 and the second fluid chamber 2.

  The housing H includes a first housing H1 and a second housing H2 that are adjacent 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 directly touches the working fluid. On the other hand, the second housing H2 is provided with an actuator 4 for controlling 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.

(First housing)
The first housing H <b> 1 is provided with a first port P <b> 1 as an opening P that communicates the first fluid chamber 1 and the second fluid chamber 2. In addition, a control mechanism 5 that controls 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 inside the first housing H1. It has been.

  A substantially cylindrical retainer R is provided in the first housing H1 so as to have a double structure with respect to the first housing H1. The retainer R houses a second valve body V2 described later as one of the valve bodies V. Further, a first valve body V1 described later is accommodated 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 therethrough is limited to a predetermined amount. As shown in FIG. 1, for example, the first orifice OR1 opens in the radial direction in the cylindrical wall portion H12 of the first housing H1.

  As shown in FIGS. 1 and 4, the first port P1 has a rotational axis X of the second valve body V2 (because it is coaxial with the axial center X of the case C, and hereinafter, “rotational axis X” has priority). Are provided along the circumferential direction. The first port P1 communicates between the first fluid chamber 1 and the inside of the first housing H1, and abuts between the first valve portion V11 and the first valve seat H11 to form a smooth flow of the working fluid. Formed near the position. Each first port P1 extends in a state of being deviated to one side in the circumferential direction as it is separated from the rotation axis X.

  Thereby, 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 a circumferential velocity component. Since the working fluid maintains an appropriate flow rate, the kinetic energy of the working fluid is transmitted to the first valve body V1, and the first valve body V1 can be rotated.

  As shown in FIG. 1, the first valve seat H11 is provided inside the first housing H1 and at a position radially inward with respect to the first port P1. For this purpose, a cylindrical 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 repeats contact and separation with the first valve portion V11 of the first valve body V1, and the first valve portion V11 rotates relatively. Therefore, the first valve seat H11 is preferably composed of a material having excellent wear resistance and a material having a small friction coefficient. For example, hard resin materials can be used in addition to hard general steel materials and stainless steel materials. A member having a low coefficient of friction such as polytetrafluoroethylene (PTFE) can be attached on these materials.

(Retainer)
Inside the retainer R, a cylindrical second valve body V2 that divides the internal space of the retainer R into two is disposed. The second valve body V2 includes a substantially cylindrical body portion V21 and an annular flange portion V22 projecting from the body portion V21 in the radially outward direction. The second valve body V2 can reciprocate a predetermined distance along the direction of the rotation axis X while sliding the flange portion V22 on the inner surface of the retainer R.

  On the side wall of the retainer R, the second port P2 and the third port P3 are provided in a state of being separated along the direction of the rotation axis X from the side close to the second housing H2. A guide hole R1 is formed on the side of a solenoid 4a, which will be described later, in the direction of the rotation axis X in both ends of the retainer R, and a plunger 3a, which will be described later, is inserted therethrough to serve as a guide for the plunger 3a. On the other hand, a bottom hole R2 penetrating in the direction of the rotation axis X is formed at the opposite end. In the bottom hole R2, an annular second valve seat R3 with which the end of the main body V21 of the second valve body V2 abuts is formed.

  A first pilot chamber PR1 is formed in a 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 the third pilot chamber PR3 and the first pilot chamber PR1 inside the retainer R. Further, the bottom hole R2 provided in the bottom portion of the retainer R communicates with the second pilot chamber PR2 provided outside the retainer R.

(Actuator)
Of the retainer R, for example, a coil-shaped second spring S2 is provided around the second valve seat R3, and always biases the flange portion V22 of the second valve body V2 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. The adjustment mechanism 3 is configured. Thus, 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 rotation axis 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 of the plunger 3a, and the second valve body V2 is changed according to the position change of the plunger 3a along the direction of the rotation axis X. The position also moves.

  As the plunger 3a is retracted toward the solenoid 4a, the distance between the second valve body V2 and the second valve seat R3 increases, and the second pilot communicates 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 fixed 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 rate of the working fluid is minimized, and the effect of attenuating the sliding of the housing H is maximized.

  In the present embodiment, the plunger 3a includes a rod-shaped member 3b. Such a rod-shaped member 3b can easily transmit the drive effect of the solenoid 4a to the second valve body V2 located at a predetermined distance from the solenoid 4a. When the rod-shaped member 3b mainly transmits the driving force along the direction of the rotation axis X, the outer diameter of the rod-shaped member 3b is configured to be smaller than the outer diameter of the solenoid 4a or the second valve body V2. Can do. That is, although the rod-shaped member 3b is used as a guide portion of the rod-shaped member 3b around the rod-shaped member 3b in the second housing H2, it is easy to secure another space because the rod-shaped member 3b is relatively thin. Therefore, with this configuration, it is easy to secure an installation space for a check valve V3, which will be described later, and it becomes easier to obtain a more compact valve GV.

(Second 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. In a state where the plunger 3a protrudes by a predetermined length toward the third pilot chamber PR3, 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 A gap with a constant interval is formed between the two.

  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 the second valve body V2 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. As described above, the inner and outer surfaces of the conical portion V23 have a predetermined shape and the second valve body V2 is pressed against either side, so that the housing H is pressed and pulled separately. The pressure receiving area can be set, and an optimum attenuation characteristic can be obtained.

(Check valve)
A check valve V3 is provided at the bottom of the first housing H1. At the position facing the first pilot chamber PR1 in the bottom of the first housing H1, the fourth ports P4 penetrating in the direction of the rotation axis X are distributed in the circumferential direction around the rotation axis X. . 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 through a fifth port P5 that penetrates the wall H22 of the second housing H2 in the radial direction. The fifth ports P5 are also distributed in the circumferential direction with respect to the wall portion H22 of the second housing H2.

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

(1st disc)
The 1st valve body V1 of this embodiment rotates with the flow of a working fluid. As a result, friction between the inner surface of the first housing H1 and the first valve body V1 is reduced, and particularly, the start and reversal movement of the first valve body V1 is made agile. It is intended to improve the attenuation response of the.

  Moreover, the attitude | position of the 1st valve body V1 is stabilized because the 1st valve body V1 rotates. Therefore, when the first valve body V1 reciprocates on the inner surface of the first housing H1, the corner 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 H12 of the first housing H1 and the retainer R. The first valve body V1 has a substantially cup shape, and a cylindrical outer peripheral surface is guided by the inner surface of the wall H12 and rotates. Therefore, a special shaft portion or the like is not 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 inside the fixed first housing H1. Thereby, the clearance gap with 1st valve-seat H11 is increased / decreased, the flow volume of the working fluid over the 1st fluid chamber 1 and the 2nd fluid chamber 2 is changed, and a damping effect is adjusted. 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 fast, and the internal pressure difference between the first pilot chamber PR1 and the second pilot chamber PR2 becomes larger than a predetermined value. The flow rate of the working fluid between the first fluid chamber 1 and the second fluid chamber 2 is increased.

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

  While the first valve body V1 is configured to rotate, the first spring S1 that biases the first valve body V1 toward the first valve seat H11 is not necessarily provided so as to be relatively rotatable with respect to the first housing H1. It is not a thing. Rather, it is convenient to fix the first housing H1. However, in this case, friction is generated 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. Thereby, the operation of the first valve body V1 becomes more agile.

  As the ring member 9, a metal material having normal wear resistance, a washer formed of PTFE having a small friction coefficient, or the like may be used.

  An annular standing wall portion is provided as the first valve portion V11 on the outer edge portion of the surface facing the second fluid chamber 2 in the bottom portion of the first valve body V1. In the first valve portion V11, first slits V14 as the communication portion 7 are distributed and arranged along the circumferential direction of the first valve portion V11. Thereby, as shown in FIG. 1, the working fluid slightly circulates between 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 do. 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, thereby reducing the 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 first slits V14 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 the present configuration, the extending direction of the first slit V14 is made closer to one side in the circumferential direction so as to be separated from the rotation axis X so as to promote the rotation of the first valve body V1 by the working fluid flowing through the first slit V14. It is deviated and formed in a substantially spiral shape.

  Thus, when the 1st slit V14 is provided in the 1st valve part V11, the 1st valve body V1 becomes easy to rotate with the reaction force of the working fluid which distribute | circulates the 1st slit V14. However, 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, the first slit V14 may be provided in the first valve seat H11.

  Further, in order to configure such a first slit V14 as the communication portion 7, for example, a notch may be processed in the end face of the first valve portion V11 as shown in FIGS. 3 and 4. Is very easy. Furthermore, the width of the first slit V14 can be freely set, and the first valve body V1 with good rotational efficiency can be rationally configured.

(First blade part of the first valve body)
As shown in FIG. 3, the first valve body V <b> 1 is provided with a first blade portion 81 as the rotation driving portion 8. The first blade portion 81 is provided on the inner peripheral side of the first valve portion V11. When viewed from the second fluid chamber 2 side along the rotation axis X, the normal direction F is the rotation axis X. A plurality of inclined surfaces having a circumferential component around the rotation axis X while being inclined are provided. 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 in the outer surface of the first valve body V1, the working fluid collides with the first valve body V1 along the rotation axis X. Is advantageous in some cases. That is, mainly when the pressure in the second fluid chamber 2 is increased, the first valve body V1 is rotated while changing the flow of the working fluid from the direction along the rotation axis X to the radial direction.

  As shown in FIGS. 1 to 3, the surface of the first blade portion 81 is recessed, and a recess is also formed in the outer surface V16 of the bottom portion of the first valve body V1. Thereby, the working fluid that has collided with the first blade portion 81 in the direction of the rotation axis X can be smoothly guided in the radial direction.

  By rotating the first valve body V1, 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 not moving relative to each other. As a result, the operating characteristics when the first valve body V1 starts to open and move and when the operating direction is reversed are agile, and the damping response of the valve GV with respect to pressure fluctuations of the working fluid is extremely good. .

  Moreover, the attitude | position of the 1st valve body V1 is stabilized because the 1st valve body V1 rotates. Therefore, when the first valve body V1 reciprocates along the inner surface of the first housing H1, the corners of the first valve body V1 do not bite into the inner surface, and the first valve body V1 reciprocates smoothly. It becomes.

  In addition, since the first valve body V1 rotates, the working fluid can easily form 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. The improvement of the lubrication effect by the fluid can also be expected.

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

(Second blade part of the first valve body)
As shown in FIGS. 1 to 4, a second blade 82 serving as the rotation drive unit 8 is provided on the outer peripheral side of the first valve unit V11 in the first valve body V1. The second blade portion 82 is configured so that the working fluid in the first fluid chamber 1 flows into the second fluid chamber 2 through the first slit V14 when the first valve body V1 is in the closed position. It will catch 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. The pressure receiving surface V11b receives the pressure of the working fluid in the first fluid chamber 1 to open and operate the first valve body V1, and therefore is not necessarily perpendicular to the outer surface V11a as shown in FIGS. It suffices that the normal line has a surface having a component in the urging direction of the first spring S1.

  As shown in FIGS. 3 and 4, the second blade portion 82 protrudes radially outward from the outer surface V <b> 11 a, and a plurality of second blade portions 82 are formed along the circumferential direction. For example, when viewed along the rotation axis X, it can be formed with a substantially triangular convex portion. That is, a first surface 82a that protrudes radially outward from the outer surface V11a is formed, and a second surface 82b that is inclined so as to gradually approach the outer surface V11a from the outermost edge portion of the first surface 82a is provided. In this case, the first surface 82a is a surface that receives the working fluid. Therefore, the direction of rotation is limited by the shape of the second blade portion 82. 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 as shown in FIG. The first surface 82a is preferably inclined slightly from the 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.

  If the rotation direction is not limited, the second blade portion 82 may be a plate-like portion or the like that protrudes radially outward 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 V <b> 14 to open to the base portion of the first surface 82 a. That is, 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, so that the working fluid can be obtained by providing the first slit V14 here. 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 operation It becomes easy to transmit the kinetic energy of the fluid 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. If the first slit V14 and the first port P1 are configured to have the same angle in this way, it is particularly convenient when the working fluid is discharged to 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 first blade portion 81 side. In this case, the working fluid that has flowed into the surface of the outer surface V11a of the first valve body V1 from the first port P1 flows into the inner side of the wall portion H12 of the first housing H1, and presses the first surface 82a with certainty. 1 The valve body V1 is rotated.

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

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

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

  At this time, the working fluid also flows out into the first fluid chamber 1 via the first slit V14 and the first port P1 provided in the first valve body V1, as indicated by a thin broken line in FIG. 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 via the first slit V14. Due to the flow of the working fluid, the first blade 81 receives a rotational force and the first valve body V1 starts to rotate. 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 rises 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 constant amount, the rising speed of the internal pressure in the second pilot chamber PR2 is suppressed to a predetermined speed. However, when the lowering speed of the housing H is high, the pressure of the working fluid acting on the outer surface V16 of the bottom portion of the first valve body V1 increases rapidly, so that the pressure acting on the outer surface V16 is increased in the second pilot chamber PR2. It becomes larger than the pressure which acts on the inner surface V17 of the bottom part of the 1st valve body V1 inside. Therefore, the first valve body V1 moves away 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. Thereby, when a large downward force acts on the housing H, the housing H can be lowered relatively quickly.

  When the pressure in the second fluid chamber 2 further increases, the first valve body V1 itself is pushed to the bottom side of the first housing H1, and an opening operation is started. As a result, a gap is generated between the first valve body V1 and the first valve seat H11, and the flow rate of the working fluid is increased. Due to the increase in the flow velocity, the rotation speed of the first valve body V1 is further increased, and the rotation state is stabilized.

  The pressure required to open 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 through the second orifice OR2. The increase in internal pressure is accelerated. In this case, the difference with the pressure which acts on the outer surface V16 of the bottom part of the 1st valve body V1 is small, and the 1st valve body V1 becomes difficult to open. 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 associated with the operation of the housing H is enhanced.

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

  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 via the first port P1 and the first slit V14 provided in the first valve body V1. FIG. 2 shows a state in which the first valve body V1 is opened. Due to the flow of the working fluid, the second blade portion 82 receives a rotational force, and the first valve body V1 starts to rotate. 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 fixed amount, the rising speed of the internal pressure in 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 abruptly. Therefore, the pressure acting on the pressure receiving surface V11b of the first valve body V1 is increased in the first pilot chamber PR1. The pressure is larger than the pressure acting on the end face V15 of the first valve body V1 inside. Therefore, the first valve body V1 moves away from the first valve seat H11 against the urging force of the first spring S1, and the working fluid passes through the gap generated here as shown by the broken line in FIG. 2 flows into the fluid chamber 2. At this time, the flow rate of the working fluid is increased, the force acting on the second blade portion 82 is also increased, the rotational speed of the first valve body V1 is further increased, and the rotational state is stabilized.

  The timing at which the first valve body V1 starts to open 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 flows out from the third pilot chamber PR3 to the second pilot chamber PR2. Is squeezed. As a result, the increase in the internal pressure of the first pilot chamber PR1 when the working fluid flows into the first pilot chamber PR1 via the first orifice OR1 is accelerated. 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.

If 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 retracts toward the second housing H2. As a result, the second valve body V2 moves to a position where it abuts against the bottom of the first housing H1, and the second port P2 is shielded by the flange portion V22 of the second valve body V2. Thereby, the first pilot chamber PR1 and the third pilot chamber PR3 communicate with each other only through the third port P3. The opening area of the third port P3 is set to be 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. Note that the configuration included in the present embodiment and the configuration common to the first embodiment are assumed to have the same configuration and function as the first embodiment. Moreover, the same reference numerals are used for the same reference numerals as 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 a housing H, a valve body V, and an urging portion S are used. Again, the housing H has a bottomed cylindrical shape and has a cylindrical space inside. A valve body V is disposed inside the housing H. The valve body V has a valve portion V11 that comes into contact with a valve seat H11 provided in a part of the housing H. The closed position where the valve portion V11 comes into contact with the valve seat H11 is used as an end point from the closed position of the housing H. Move back and forth to the bottom. Furthermore, a spring mechanism as a biasing portion S that biases the valve body V toward the closed position is provided in a space H14 on the back side of the valve body V in the housing H.

(housing)
As in the first embodiment, the housing H is provided with a plurality of first ports P1 serving as the openings P along the circumferential direction. This 1st port P1 is also extended to the state which shifted to the one side in the circumferential direction, so that it separated from the rotating shaft X. Thereby, for example, the working fluid that collides with the valve body V from the first fluid chamber 1 via the first port P1 collides with the valve body V while maintaining a circumferential velocity component. 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 contacts the valve body V. The valve seat H11 is near the first port P1 at a position radially inward with respect to the first port P1, and when the valve body V is opened, the valve seat H11 is formed between the first fluid chamber 1 and the second fluid chamber 2. It is provided at a position where the working fluid smoothly flows 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 by, for example, screwing, and the position of the valve seat H11 with respect to the first port P1 can be adjusted by this screwing part.

(Valve)
As shown in FIG. 5, the valve body V is also substantially cup-shaped, and a cylindrical outer peripheral surface is guided by the inner surface of the wall portion H <b> 12 of the housing H and rotates. An annular valve portion V11 protrudes from the outer surface V16 of the bottom portion, a first blade portion 81 is formed on the inner peripheral side across the valve portion V11, and a second blade portion 82 is formed on the outer peripheral side. . Further, a spiral slit V14 is formed in the valve portion V11 as the communication portion 7 as in the first embodiment. The slit V14 may be provided on the valve seat H11 side.

(Energizing Department)
In the present embodiment, an urging portion S is provided in a 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 has a tapered tip for pushing the back surface of the rotating valve body V, and abuts on a position that is the center of rotation on the back surface of the valve body V. Thereby, the frictional resistance generated between the valve body V and the core member S31 is reduced.

  On the bottom surface of the housing H, there is provided a guide cylinder S33 for slidably storing the core member S31. Inside the guide tube S33, for example, a coiled spring member S32 is installed so as to abut against the end surface of the core member S31 and the bottom surface of the housing H and urge them away from each other. The spring member S32 sets a spring constant according to the hydraulic pressure of the working fluid when the valve body V is opened and moved. The opening timing of the valve body V is delayed as the biasing force of the spring member S32 is increased. In order to prevent wear of the member, a hard material may be disposed on the back surface of the valve body V or the tip of the core member S31.

(Check valve)
The valve body V needs to be pushed into the housing H because of 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. 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, the space H14 on the back side of the valve body V is normally 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. For this purpose, for example, a check valve V3 is provided on the back surface of the housing H.

  As the check valve V3, at least one discharge hole for communicating the space H14 on the back side of the valve body V and the first fluid chamber 1 is provided. In FIG. 5, a plurality of fourth ports P4 are arranged in a distributed manner around the rotation axis 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 using an annular fixing member V32.

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

  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 in the second fluid chamber 2 is pushed back to the closed position with respect to the valve seat H11. The working fluid is caused 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 restrict 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 there is no special pressurization from the second fluid chamber 2, and therefore the valve body V is the spring member S32. The speed pushed back by may be moderate. 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 since the pressure acting on the pressure receiving surface V11b is compared with the pressure in the space H14, the breathing hole V18 does not particularly work. However, when no pressure is applied from the first fluid chamber 1 and the valve body V is pushed back, the breathing hole V18 functions as described above.

  In the case of the valve GV having this configuration, 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, the valve body V is closed. Even in the position, the valve body V starts to rotate by the working fluid flowing through the slit V14. As a result, the frictional force between the valve body V and the wall H12 of the housing H is reduced. Therefore, the operation of the valve body V when the valve body V continues to open is agile. Thereby, it is possible to obtain the valve GV having a good damping response.

[Other Embodiments]
The urging portion S may be, for example, a member that replaces the coiled spring member S32 in FIG. 5 with a leaf spring and fixes the leaf spring to the bottom of the housing H in addition to those in the above embodiments. If it is a leaf | plate spring, its own installation space may be small and the compact valve | bulb GV can be obtained.

  Further, the urging unit S may use a magnetic force. For example, as shown in FIG. 6, a magnet 10 is provided in the vicinity of the first port P <b> 1 in the wall portion H <b> 12 of the housing H, and the valve body V is configured with a metal member attracted by the magnet 10. . Incidentally, the wall H12 of the housing H is preferably made of a nonmagnetic metal material or resin material in order to prevent the magnetic lines of force of the magnet 10 from turning around. Thereby, it is possible to always attract the valve body V toward the valve seat H11. In this case, there is no component part of the urging portion S that contacts the valve body V, and the valve body V with low rotational resistance can be obtained.

  Further, as another configuration of the urging portion S, although not shown in the drawing, the space H14 on the back side of the valve body V is filled with air of a predetermined pressure, and the valve body is utilized using the expansion / contraction characteristics of air. V may be energized. 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 highly responsive valve GV can be obtained. it can.

  In the above-described embodiment, the configuration in which the housing H reciprocates with respect to the case C is shown. However, the housing H may be fixed inside the case C. For example, the valve GV is provided in a state in which the inside of the case C is partitioned into a first fluid chamber 1 and a second fluid chamber 2, and the working fluid is first filtered by another piston or the like provided inside the case C. It can also be set as the structure which goes back and forth between the fluid chamber 1 and the 2nd fluid chamber 2. FIG.

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

DESCRIPTION OF SYMBOLS 1 1st fluid chamber 2 2nd fluid chamber 7 Communication part 8 Rotation drive part 81 1st blade | wing part 82 2nd blade | wing part 9 Ring member C Case GV Valve H Housing H11 Valve seat H12 Wall part P Opening S Energizing part S1 Coil Shaped spring V Valve body V11 Valve portion V11b Pressure receiving surface V14 Slit X Rotating shaft core

Claims (8)

A case for containing a working fluid;
A bottomed cylindrical housing that divides the inside of the case into a first fluid chamber and a second fluid chamber, and has a cylindrical space communicating with the second fluid chamber;
A valve portion disposed in the cylindrical space and in contact with a valve seat provided in a part of the housing, the closed position where the valve portion is in contact with the valve seat as an end point from the closed position to the bottom of the housing; A valve body reciprocating along the inner surface of the cylindrical space on the side;
A biasing portion provided in the housing and biasing the valve body toward the closed position;
The wall of the housing is provided with an opening that communicates the contact position of the valve portion and the valve seat 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 in which an outer surface of the valve body is provided with a rotation drive unit that rotates the valve body by a working fluid that flows through the communication portion.   The valve according to claim 1, wherein the rotation drive unit includes a first blade portion provided on an inner peripheral side of the valve unit.   The valve according to claim 1 or 2, wherein the rotation driving unit includes a second blade portion provided on an outer peripheral side of the valve portion.   4. The pressure receiving surface according to claim 1, wherein a pressure receiving surface that is in contact with the working fluid and has a component in a direction opposite to a biasing direction by the biasing portion is provided on an outer peripheral side of the valve portion. The described valve.   A plurality of the communication portions are provided along the circumferential direction of the valve body with respect to the rotation axis, and each of the communication portions extends to a state of being displaced to one side in the circumferential direction as the distance from the rotation axis is increased. The valve according to any one of claims 1 to 4.   The valve according to claim 5, wherein the communication part is a slit provided in the valve part.   A plurality of the openings are provided along a circumferential direction with respect to the rotation axis of the valve body, and each of the openings extends in a state of being deviated to one side in the circumferential direction as the opening is separated from the rotation axis. The valve according to any one of claims 1 to 6.   The said urging | biasing part is a coil-shaped spring, The ring member which can rotate relatively with these between the said valve body and the said coil-shaped spring is provided. Valve.

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