JP4997082B2 - Damping valve - Google Patents

Description

  The present invention relates to a damping valve, and more particularly, to an improvement of a damping valve suitable for implementation in a hydraulic shock absorber such as a front fork mounted on the front wheel side of a motorcycle or a rear cushion mounted on the rear wheel side of the motorcycle. .

  There have been various proposals so far for damping valves suitable for implementation in hydraulic shock absorbers such as a front fork mounted on the front wheel side of a motorcycle and a rear cushion mounted on the rear wheel side of the motorcycle.

  Among them, the proposal disclosed in Patent Document 1 has a compression side damping valve in a housing part formed on a bottom member that forms an axle bracket while forming a bottom part while a front fork forms a bottom part. .

  In appearance, the compression side damping valve is disposed laterally on the axle bracket, that is, at the bottom portion of the front fork so that the axial direction is the front-rear direction.

  The pressure-side damping valve functionally has a high speed adjuster that is removably mounted in the housing portion that becomes the valve housing, and the high speed adjuster is advanced and retracted by a rotation operation from the outside. The spring force of the biasing spring that biases the leaf valve from the rear side is changed, and the cracking pressure in the leaf valve is changed.

  Therefore, in the proposal disclosed in Patent Document 1, not only the desired damping force control is possible, but also the compression side damping valve is not arranged in the front fork and is arranged in the axle bracket portion. Therefore, the configuration in the front fork can be simplified, and it is advantageous in terms of operability with respect to the compression side damping valve, and is advantageous in terms of maintenance such as replacement of a leaf valve.

Incidentally, the simplification, advantageous operability, and maintainability of this configuration are the same even if the compression side damping valve is embodied in a rear cushion that is a hydraulic shock absorber mounted on the rear wheel side of the two-wheeled vehicle.
JP 2007-255476 A (see abstract, paragraphs 0014 and 0020 in the specification, FIG. 1 and FIG. 2)

  However, in the above proposal, it is fundamental in that the configuration of the hydraulic shock absorber is simplified while enabling the desired damping force control, the operability to the compression side damping valve is advantageous, and the maintainability is advantageous. Although there is no problem, there is a possibility that it is pointed out that there is a slight defect in the intention of reducing the weight of the hydraulic shock absorber.

  That is, in the above proposal, the high-speed adjuster constituting the compression side damping valve changes the length of the urging spring that urges the leaf valve by its advance and retreat, and changes the cracking pressure in the leaf valve.

  Therefore, in the above proposal, the base end of the urging spring interposed in the high speed adjuster is opposed to the leaf valve, that is, supported under the spring support, while the tip of the urging spring is placed on the high speed adjuster side. In this state, the tip position of the biasing spring is moved in synchronism with the advancement and retraction of the high speed adjuster to change the length of the biasing spring.

  Therefore, the high-speed adjuster not only supports the base end with the biasing spring interposed, but also locks the tip, so that the shaft length is sufficient to interpose the biasing spring. That is, it is formed to have a length larger than the length of the biasing spring.

  This means that the housing portion, which is the valve housing to which the high-speed adjuster is mounted, is made bulky by projecting the bottom portion of the hydraulic shock absorber in the radial direction, and thus the hydraulic shock absorber having the bottom portion. Inhibits weight reduction.

  The present invention was devised in view of such a current situation, and an object of the present invention is to reduce the weight of the hydraulic shock absorber as well as to enable a desired damping force control. Contributing and providing a damping valve that is optimal for expecting improved versatility of the hydraulic shock absorber.

In order to achieve the above object, the means of the present invention defines a valve housing, a high speed adjuster mounted in the valve housing, and an upstream oil chamber and a downstream oil chamber in the valve housing. In addition, a valve seat member having a port communicating with the upstream oil chamber and the downstream oil chamber, a leaf valve seated on the valve seat member to open and close the port, and the leaf valve on the valve seat member side An urging spring for urging, the valve housing being opened near the opening end, and an upper flow path through which hydraulic oil flows from the outside of the valve housing into the upstream oil chamber, and is opened toward the inner bottom. And a lower flow path through which hydraulic oil flows out of the valve housing from the downstream oil chamber, and the high-speed adjuster is moved forward and backward by a rotation operation from outside to thereby apply the spring force of the biasing spring. Further, in the damping valve for changing the cracking pressure in the leaf valve, the high-speed adjuster is mounted in the valve housing from an oblique direction, and the high-speed adjuster is attached to the base end operating portion and the base end operating portion. An intermediate portion provided continuously and a tip rod portion provided continuously to the intermediate portion, and the valve seat member, the leaf valve, and the biasing spring are inserted into the outer periphery of the tip rod portion, respectively. Further, a ring nut is screwed into the valve housing, and a bottomed cylindrical spring holder is inserted into the valve housing so as to face the ring nut, and the base end operation of the high speed adjuster is inserted into the ring nut. The valve seat member is inserted into the inner periphery of the spring receiver and the tip of the biasing spring is locked to the bottom. Be Te is characterized in.

Therefore, in the present invention, an upstream channel that allows influx into the upstream side chamber of the hydraulic oil from outside the valve housing the valve housing is perforated in the open end near, it is perforated in the inner bottom toward since it made and a downstream passage to allow outflow of the working oil of the valve housing outside from the downstream side chamber to induce hydraulic oil through the upstream path from outside the valve housing to the leaf valve in the valve housing Further, it is easy to guide the hydraulic oil out of the valve housing through the downstream flow path of the hydraulic oil in the valve housing that has passed through the leaf valve .

In the present invention, the high-speed adjuster is composed of a base end operating part, an intermediate part connected to the base end operating part, and a tip rod part connected to the intermediate part, A valve seat member, a leaf valve, and an urging spring are inserted into the outer periphery of the tip rod portion, respectively, and a bottomed cylindrical spring receiver is inserted into the valve housing, and the valve seat is inserted into the inner periphery of the spring receiver. As the member is inserted and the tip of the urging spring is locked to the bottom to prevent movement of the urging spring, even if the base end of the urging spring is locked to the high speed adjuster, It is not necessary to lock the tip of the spring spring on the high speed adjuster side, the axial length of the high speed adjuster can be shortened, and when embodied in a hydraulic shock absorber, the radial dimension of the hydraulic shock absorber can be reduced.
Further, since the adjuster for high speed is mounted in the valve housing so as to be able to protrude and retract from an oblique direction, as in the proposal disclosed in Patent Document 1, the damping valve is arranged in the front-rear direction so as to cross the axial direction of the front fork. The operability is improved as compared with the case where it is performed.
As a result, the front fork embodying the damping valve according to the present invention enables generation of a desired damping force and control over a wide area while simplifying the configuration, and also reduces the weight on the front wheel side of the motorcycle. Since it can be reduced, it is optimal for preventing an unreasonable increase in the overall cost and expecting improved versatility.

In the following, the present invention will be described based on the illustrated embodiment. In the illustrated embodiment, the damping valve V according to the present invention is mounted on the front wheel side of the two-wheeled vehicle, and the front wheel of the two-wheeled vehicle is suspended while the front wheel is suspended. 1 is embodied in a front fork that is a hydraulic shock absorber that absorbs road surface vibrations input to the front fork, and as shown in FIG. 1, is disposed on a bottom member B that forms an axle bracket for a front wheel in the front fork.
As shown in FIG. 4, the damping valve V includes a housing portion H that is a valve housing, a high-speed adjuster 11 mounted in the housing portion H, an upstream oil chamber and a downstream oil in the housing portion H. A valve seat member 16 having a port 16a that defines the chamber and communicates the upstream oil chamber and the downstream oil chamber, and a leaf valve 13 that sits on the valve seat member 16 and opens and closes the port 16a. And an urging spring 14 for urging the leaf valve 13 toward the valve seat member 16 side.
Further, the housing part H is opened near the opening end and the upper flow path B1 for flowing the hydraulic oil from the outside of the housing part H to the upstream oil chamber, and the downstream oil chamber is opened near the inner bottom. And a lower flow path B2 through which hydraulic oil flows out of the housing portion H, and the spring adjuster 11 is moved forward and backward by changing the spring force of the biasing spring 14 by changing the spring force. The cracking pressure in the leaf valve 13 is changed.
The high-speed adjuster 11 is mounted in the housing portion H from an oblique direction, and the high-speed adjuster 11 is connected to the proximal end operating portion 111 and the intermediate portion 112 connected to the proximal end operating portion 111. The valve rod member 16, the leaf valve 13, and the biasing spring 14 are inserted into the outer periphery of the tip rod portion 113, respectively.
Further, a ring nut 10 is screwed into the housing part H, and a bottomed cylindrical spring receiver 15 is inserted into the housing part H so as to face the ring nut 10, and the high speed is inserted into the ring nut 10. The base end operating portion 111 of the adjuster 11 is screwed so as to be retractable, the valve seat member 16 is inserted into the inner periphery of the spring receiver 15, and the tip of the biasing spring 14. is locked to the bottom. .
This will be described in more detail below.

  The front fork is inserted into the cylinder body 1 erected on the shaft core portion of the wheel side tube T1 so that the lower end side of the rod body 2 suspended from the shaft core portion of the vehicle body side tube T2 can be inserted and retracted. The upper end opening is sealed with a bearing 3 that allows the rod body 2 to pass through the shaft core, and the reservoir R is located above the cylinder body 1.

  This front fork has a suspension spring S made up of a coil spring which is housed in the reservoir R and whose lower end is carried by the bearing 3 and whose upper end is locked to the upper end of the rod body 2. The urging force of the suspension spring S is urged in the direction in which the wheel side tube T1 protrudes from within the vehicle body side tube T2, that is, in the extension side direction in which the rod body 2 protrudes from within the cylinder body 1.

Further, in the front fork, the lower end opening of the wheel side tube T1 and the lower end opening of the cylinder body 1 are closed by the bottom member B. In the present invention, the bottom member B serves as the axle bracket. While forming, a housing portion H which is a valve housing is formed, and a main portion of the damping valve V is accommodated in the housing portion H.

  Incidentally, in the illustrated front fork, the rod body 2 is a vehicle body side member, whereas the cylinder body 1 is a wheel side member, and the wheel side tube T1 is an outer cylinder.

  By the way, in this front fork, since the bottom member B has the damping valve V, a passage L is formed between the wheel side tube T1 and the cylinder body 1, and the passage L is in the housing portion H. Is set to communicate with the inside of the cylinder body 1.

  Therefore, in the present invention, the housing portion H is opened near the opening end and the upper flow passage B1 communicating the flow passage L with the housing portion H, and the housing portion H is opened near the inner bottom. And a lower flow path B2 for communicating the portion H with the cylinder body 1.

  On the other hand, in the present invention, the damping valve V causes the hydraulic oil flowing out from the cylinder body 1 to the flow path L to flow when the front fork is extended in the cylinder body 1 and the rod body 2 is raised. It flows into the cylinder body 1 from the path L and generates a predetermined extension side damping force.

  In the front fork, as described above, the upper portion of the cylinder body 1 is a reservoir R that is blocked from the flow path L, and the reservoir R is an oil level O that appears on the outer periphery of the rod body 2. It has an air chamber A that borders.

  Further, in this front fork, the rod body 2 is composed of a pipe body, and therefore, one is advantageous in reducing the weight of the rod body 2, and two in the front fork. This is advantageous in realizing a configuration in which the passage 2a is provided inside the rod body 2. Incidentally, the passage 2a communicates with the above-described reservoir R through a through-hole 2b opened in the rod body 2.

  In the front fork, a piston portion is formed at the lower end portion of the rod body 2 present in the cylinder body 1, and this piston portion is an extension side oil chamber R <b> 1 that is an upper oil chamber in the cylinder body 2. And a pressure side oil chamber R2 as a lower oil chamber.

  As shown in the drawing, the above-described piston portion is formed in a bottomed cylindrical shape, and the piston 22 is fixed by a nut 21 that is screwed to the lower end portion of the rod body 2, and the nut 21 is opened to the shaft core portion. 21a and communicates a passage 2a in the rod body 2 with a pressure side oil chamber R2 to be described later in the cylinder body 1.

  Then, the piston 22 causes the outer periphery to slide in contact with the inner periphery of the cylinder body 1 to define the above-described expansion side oil chamber R1 and the compression side oil chamber R2 in the cylinder body 1, and the expansion side oil chamber of the compression side oil chamber R2 Although the communication to R1 is permitted, it has an extension check valve 23 that prevents the opposite extension side oil chamber R1 from communicating with the pressure side oil chamber R2.

  In the front fork, in the vicinity of the upper end of the cylinder body 1, a through hole 1 b for communicating the inside and outside of the cylinder body 1 at a position where the front fork is not closed by the piston 22 when the front fork is fully extended is provided. Have.

  In addition, in the front fork, the bearing 3 that seals the upper end opening of the cylinder body 1 is, in principle, slidably contacted with the inner periphery of the wheel side tube T1. A check ring 31 is interposed on the outer periphery of the check ring 31, and the outer periphery of the check ring 31 is in sliding contact with the inner periphery of the wheel side tube T1.

  As shown in FIG. 2, the check ring 31 has a rectangular cross section and is loosely fitted in an annular groove 3a formed on the outer peripheral portion of the bearing 3, and has a notch passage 31a on the lower end side portion. When rising, it functions as a pressure side check valve to prevent the above-mentioned flow path L from communicating with the above-mentioned reservoir R, and when communicating down, allows communication of the reservoir R to the flow path L.

  Therefore, the front fork having the check ring 31 can facilitate the oiling operation when the front fork is assembled, that is, the operation of injecting the hydraulic oil into the flow path L, and the flow path L during the contraction operation. Alternatively, negative pressure in the extension side oil chamber R1 can be avoided by the inflow of hydraulic oil from the reservoir R.

  Therefore, in this front fork, when the rod body 2 is reversed to the extension operation so as to come out of the cylinder body 1 from the most contracted state (not shown), the piston 22 has the extension side check valve 23. The hydraulic fluid in the expansion side oil chamber R1 that becomes the outflow flows into the compression side oil chamber R2 in the cylinder body 1 through the through hole 1a, the flow path L, and the damping valve V, and the damping valve V generates a predetermined stretching side damping force. To do.

  An amount of hydraulic oil corresponding to the withdrawal rod volume that is insufficient in the pressure side oil chamber R2 during this extension operation is replenished from the reservoir R to the pressure side oil chamber R2 through the through hole 2b and the passage 2a of the rod body 2.

  Incidentally, when the front fork reverses from the most extended state shown in the drawing and contracts, the rod body 2 descends in the cylinder body 1, and therefore an amount corresponding to the excess rod body integral that becomes redundant in the cylinder body 1. The hydraulic fluid flows out to the reservoir R through the passage 2a and the through hole 2b of the rod body 2, and the compression side damping force is generated when the flow speed when the hydraulic oil passes through the through hole 2b is fast.

  Note that the position of the oil level O in the reservoir R is a height position that does not expose the through hole 2b functioning as the orifice to the air chamber A even when the front fork is extended to the maximum.

  Further, regarding the opening position of the through hole 2b in the rod body 2, even when the front fork is in the most contracted state, it is set to a position where it does not interfere with the lower bearing 3 and is not blocked.

  In the front fork formed as described above, as shown in FIG. 3, the damping valve V has a so-called assembled body portion formed on the bottom member B with respect to the housing portion H formed from the outside. The front fork can be attached and detached without disassembling with a simple operation.

  Therefore, in this damping valve V, as shown in FIG. 4, the damping valve V has a ring nut 10 that is screwed to the housing portion H, and the ring nut 10 is rotated and separated from the housing portion H. The so-called main body can be extracted from the housing H (see FIG. 3).

  The damping valve V is screwed to the housing portion H so as to be able to protrude and retract through the ring nut 10 and to the shaft core portion of the high speed adjuster 11 so as to protrude and retract. And a low-speed adjuster 12.

  The high speed adjuster 11 controls the operation of the valve mechanism when the retraction speed of the rod body 2 from the cylinder body 1 is in a high speed region, and the leaf valve 13 is attached from the rear side by a rotation operation from the outside. The cracking pressure in the leaf valve 13 is changed by changing the spring force of the biasing spring 14 to be applied.

  The low speed adjuster 12 controls the operation of the throttle mechanism when the retraction speed of the rod body 2 from the cylinder body 1 is in the low speed region, and bypasses the leaf valve 13 by a rotation operation from the outside. The needle valve body 12a is made to project and retract with respect to the flow path 11a formed in the high-speed adjuster 11 so as to form a bypass path, thereby widening and narrowing the annular throttle formed between the needle valve body 12a and the flow path 11a.

  On the other hand, the high-speed adjuster 11 includes a base end operating portion 111 that enables an external turning operation, and a base end operating portion 111 that is connected to the base end operating portion 111 so that the inside of the housing portion H is upstream and downstream. It has an intermediate portion 112 having a stepped portion 112a for locking the defining valve seat member 16 under the arrangement of the check valve 14a, and a tip rod portion 113 provided continuously to the intermediate portion 112.

  The check valve 14a is disposed in such a manner that the check valve 14a is seated on the valve seat member 16 and closes a port 16a described later so as to be openable. Although not shown, it may be disposed between the valve seat member 16 and the cylinder body 1, that is, for example, in the upper flow path B1 or in the flow path L.

  The distal end rod portion 113 includes the valve seat member 16 on the outer periphery, the leaf valve 13 seated on the valve seat member 16, and the biasing spring 14 that biases the leaf valve 13 from the rear side. And intervening.

  The valve seat member 16 is formed in an annular shape, and has a port 16a that opens an upstream end outside the intermediate portion 112. The downstream end of the port 16a is closed so as to be opened by a leaf valve 13 formed in an annular shape. Has been.

  The leaf valve 13 is formed by laminating a plurality of sheets having different diameters, is seated on the valve seat member 16 with the inner peripheral end fixed and the outer peripheral end is free, and allows the passage of hydraulic oil when the outer peripheral end bends. Generates a damping force.

  The urging spring 14 has a base end opposed to the leaf valve 13, that is, as shown in the figure, is supported on the back surface of the leaf valve 13 under the presence of the spring receiver 14 b, and a distal end is shown on the valve housing side, that is, illustrated. By the way, it is locked to the inner bottom side of the valve housing via the spring receiver 15.

  The spring receiver 15 is formed in a bottomed cylindrical shape. When the ring nut 10 is screwed to the housing part H, the spring receiver 15 is introduced into the housing part H and fixed in advance, and then the ring nut 10 is detached from the housing part H. When removed, it remains in the housing part H.

  The spring receiver 15 is formed in a split form consisting of two parts, a cylindrical part 15a and a bottom part 15b formed in a ring shape, so as to facilitate so-called part manufacture.

  Therefore, in consideration of its function, the spring receiver 15 is formed in a divided manner as shown in the figure, but it is not shown in the figure, but a so-called bottomed cylinder in which the cylinder part 15a and the bottom part 15b are integrated. It may be formed in a shape.

  And the front-end | tip of the urging | biasing spring 14 is latched by the bottom part 15b in the spring receiver 15 made into the valve housing side, Therefore, the urging | biasing spring in the above-mentioned prior art example is latched to the high-speed adjuster side. In comparison, the axial length of the high speed adjuster 11 can be reduced.

  As a result, in the damping valve V of the present invention, the axial length of the high speed adjuster 11 can be shortened. Therefore, when this is embodied in the bottom portion of the hydraulic shock absorber, the radial dimension of the bottom portion is set. Therefore, the bottom portion of the hydraulic shock absorber does not protrude greatly in the radial direction and is not bulky, and the weight reduction of the hydraulic shock absorber is not hindered.

  In the damping valve V of the present invention formed as described above, when the proximal end operation portion 111 in the high speed adjuster 11 is rotated, the leaf valve 13 that is protruded and retracted with respect to the ring nut 10 and constitutes the valve mechanism is provided. The biasing spring 14 to be biased is expanded and contracted to adjust the cracking pressure in the leaf valve 13.

  Then, as shown in the figure, when the high-speed adjuster 11 is rotated and extracted from the ring nut 10, the biasing spring 14 extends to leave its tip, and the cracking pressure in the leaf valve 13 decreases.

  On the other hand, the low speed adjuster 12 is a needle valve body 12a that protrudes and protrudes with respect to the flow path 11a formed in the shaft core portion of the tip rod portion 113 of the high speed adjuster 11 so as to constitute a bypass path that bypasses the leaf valve 13. And an annular throttle (not shown) that is formed between the needle valve body 12a and the flow passage 11a and constitutes the throttle mechanism in the present invention when the high-speed adjuster 11 moves in and out is adjusted in width.

  As shown in the figure, the low speed adjuster 12 is interposed in the shaft core portion of the high speed adjuster 11 in the presence of the detent mechanism D.

  Therefore, in the front fork having the damping valve V, a desired extension side damping force is generated depending on the speed at which the rod body 2 moves up in the cylinder body 1.

  That is, when the retraction speed of the rod body 2 from the cylinder body 1 is in a speed region where the speed is lower than that in the high speed region, a desired extension side damping force is adjusted by the annular throttle constituting the throttle mechanism. 12 is adjusted.

  When the retraction speed of the rod body 2 from the cylinder body 1 is in a speed area that is higher than that in the low speed area, a desired extension side damping force is mainly applied to the high speed by the leaf valve 13 constituting the valve mechanism. Adjustment is performed by the adjuster 11.

  From the above, the proposal of disposing a damping valve on the bottom member that forms the axle bracket in the front fork is also disclosed in Patent Document 1 described above.

  However, what is disclosed in Patent Document 1 is a proposal in which a compression-side damping valve is disposed on a bottom member that forms an axle bracket, and a damping valve that functions as an extension-side damping valve as in the present invention is provided. It is not a proposal to be disposed on the bottom member that forms the axle bracket.

  That is, in many front forks proposed in the past, the extension side damping force is generated by the extension side damping valve disposed in the piston part in the cylinder of the damper built in the front fork.

  At this time, in order to make it possible to adjust the extension side damping force generated in the piston part in the cylinder, for example, a bypass path that bypasses the extension side damping valve is provided, and a flow control valve is disposed in the bypass path. Then, the flow rate control valve is moved back and forth to adjust the amount of flow in the bypass passage, and the damping force generated by the extension side damping valve is adjusted to be high or low.

  On the other hand, in the present invention, basically, a damper is not built in the front fork, and therefore a damping valve is not disposed in the piston portion in the cylinder body constituting the damper, so the configuration in the front fork body is simplified. In the illustrated case, the desired damping force can be controlled over a wide area.

  Further, in the conventional front fork, when changing the setting of the damping valve disposed in the piston part in the cylinder, the front fork needs to be disassembled. In the present invention, the front fork needs to be disassembled. Therefore, it is possible to change the setting at the damping valve V portion.

  As is apparent from the drawings, in the damping valve V according to the present invention, the axial direction of the damping valve V is inclined with respect to the axial direction of the front fork, and the so-called rear end of the main body portion is formed. It is directed diagonally upward.

Therefore, the operability with respect to the damping valve V is improved as compared with the case where the damping valve is set in the front-rear direction so as to cross the axial direction of the front fork as in the proposal disclosed in Patent Document 1 described above.

  As a result, in the front fork embodying the damping valve V according to the present invention, it is possible to generate a desired damping force and control it over a wide area while simplifying the configuration, and to reduce the weight on the front wheel side of the motorcycle. This makes it possible to prevent an unreasonable increase in the overall cost and to expect an improvement in its versatility.

  As described above, the damping valve V is set to extend the biasing spring 14 to lower the cracking pressure in the leaf valve 13 when the high speed adjuster 11 is pulled out of the ring nut 10 from the state shown in the drawing. In short, the cracking pressure of the leaf valve 13 only needs to be changed when the high speed adjuster 11 is rotated. Therefore, although not shown, the cracking pressure increases when the high speed adjuster 11 is pushed into the ring nut 10. Alternatively, the cracking pressure may be changed by turning at a fixed position.

  In the above description, the damping valve V is disposed on the bottom member B that forms the axle bracket in the front fork that is a hydraulic shock absorber. It is good also as arrange | positioning at the rear cushion which is a hydraulic shock absorber.

It is a fragmentary longitudinal cross-sectional view which shows a front fork in which a damping valve according to the present invention is disposed on a bottom member and is partially broken. It is an enlarged half vertical longitudinal cross-sectional view which shows a front fork partially. It is a partial half vertical longitudinal cross-sectional view which shows the state by which the damping valve was extracted from the front fork. It is a longitudinal cross-sectional view which expands and shows a damping valve.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder body 2 Rod body 10 Ring nut 11 High speed adjuster 11a Flow path which comprises a throttle mechanism 12 Low speed adjuster 12a Needle valve body which comprises a throttle mechanism 13 Leaf valve which comprises a valve mechanism 14 Energizing spring 14a Check valve 15 Spring bearing 15b Bottom portion 16 Valve seat member 111 Base end operation portion 112 Intermediate portion 112a Step portion 113 End rod portion B Bottom member B1 Upper flow path B2 Lower flow path H Housing portion constituting the valve housing L Flow path T1 Wheel side tube T2 Car body side Tube V damping valve

Claims (4)

The valve housing , a high speed adjuster mounted in the valve housing, the valve housing is defined as an upstream oil chamber and a downstream oil chamber, and the upstream oil chamber and the downstream oil chamber are communicated with each other. A valve seat member having a port; a leaf valve that is seated on the valve seat member to open and close the port; and a biasing spring that biases the leaf valve toward the valve seat member. Is opened near the opening end to flow the hydraulic oil from the outside of the valve housing to the upstream oil chamber, and is opened near the inner bottom to draw the hydraulic oil from the downstream oil chamber to the outside of the valve housing. And the high-speed adjuster is advanced and retracted by a rotation operation from the outside to change the spring force of the urging spring, thereby the clutch in the leaf valve is In the damping valve for changing the knocking pressure, the high-speed adjuster is mounted in the valve housing from an oblique direction, and the high-speed adjuster is connected to the base end operation part, and the intermediate part connected to the base end operation part, A distal end rod portion connected to the intermediate portion, and the valve seat member, the leaf valve, and the biasing spring are inserted into the outer periphery of the distal end rod portion, respectively, and a ring nut is inserted into the valve housing. Similarly, a bottomed cylindrical spring support is inserted into the valve housing so as to face the ring nut, and the base end operating portion of the high speed adjuster is screwed into the ring nut so as to be retractable. A damping valve formed by inserting the valve seat member into the inner periphery of the spring receiver and engaging the tip of the biasing spring at the bottom . The high-speed adjuster has a bypass path that bypasses the leaf valve, and a low-speed adjuster is removably mounted on the shaft core, and the low-speed adjuster is advanced and retracted by a rotation operation from the outside to operate in the bypass path. The damping valve according to claim 1, wherein the flow rate of oil is changed . While the valve housing is a housing part formed in the bottom member constituting the hydraulic shock absorber, the hydraulic shock absorber is inserted into the cylinder body serving as the wheel side member so that the lower end side of the rod body serving as the vehicle body side member can protrude and retract. At the same time, the lower end piston portion of the rod body is slidably accommodated in the cylinder body, thereby defining an extension side oil chamber in the cylinder body, and this extension side oil chamber is arranged outside the cylinder body and the cylinder body. The fluid is communicated with a flow path defined between the outer cylinder and the flow passage, which communicates with the upper flow path of the valve housing. The hydraulic oil from the chamber is allowed to flow into the valve housing through the flow path and the upper flow path, and the hydraulic oil that has flowed into the valve housing is downstream of the opening of the valve housing. Damping valve according to claim 1 or 2 comprising allowing the outflow to the cylinder body via the. A check valve is disposed between the valve seat member and the cylinder body, and the check valve allows the hydraulic oil from the extension side oil chamber to flow into the upstream oil chamber in the valve housing. 4. The damping valve according to claim 3, wherein the reverse flow is prevented.

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