JP5346324B2 - Damping valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damping valve that can generate a stable damping force at a damper by suppressing the oscillation of a valve body. <P>SOLUTION: The damping valve 1 includes: a valve hole 3 having an annular valve seat 4; the valve body 5 axially and movably inserted into the valve hole 3; a spring seat 10 fixed into the valve hole 3; and a coil spring 6 interposed between the valve body 5 and the spring seat 10. The damping valve also includes a cylindrical collar 7 which is located in the valve hole 3 and rises toward the annular valve seat side from the external peripheral side of the spring seat 10, and into which the coil spring 6 is inserted, and the end position of the annular valve seat side of the collar 7 is in a range of an inverted-annular valve seat side which is the annular valve seat side apart from an opening with respect to the valve hole 3 of a port 11, and inverted rather than the end of the inverted-annular valve seat side of a valve body which is seated on the annular valve seat 4. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

  The present invention relates to an improved damping valve.

  The damping valve is a device that gives resistance to the flow of the working fluid that accompanies expansion and contraction of the shock absorber and exerts a damping force on the shock absorber. For example, a reservoir is formed between the cylinders in a double-tube shock absorber. Used to be incorporated into a rod guide that supports a piston rod that is fitted to both ends of the outer cylinder and is slidably inserted into the cylinder, and to be supported by the piston rod. .

  For example, in a damping valve incorporated in a rod guide of a double cylinder type shock absorber, a valve hole provided in the rod guide and communicated with an upstream cylinder and a downstream reservoir, and a valve hole A valve seat provided on the inner periphery of the valve body, a valve body inserted into the valve hole so as to be movable in the axial direction, and a coil spring for biasing the valve body toward the valve seat side (for example, a patent) Reference 1).

  Further, the multi-cylinder shock absorber divides the rod side chamber and the piston side chamber filled with the working fluid in the cylinder, and only the flow of the working fluid from the piston side chamber toward the rod side chamber, and the piston connected to the piston rod. A check valve that is allowed and a suction valve that allows only a flow of working fluid from the reservoir to the piston side chamber are provided, and the valve hole communicates the rod side chamber in the cylinder and the reservoir.

  This double-cylinder shock absorber discharges the working fluid from the cylinder to the reservoir through the valve hole regardless of whether it is extended or contracted. A damping force is exerted by applying resistance to the flow of the working fluid. Note that the working fluid that is insufficient in the cylinder at the time of extension is supplied into the cylinder via the suction valve.

JP 2002-349629 A

  In this conventional damping valve, the valve body is urged by a coil spring, the valve opening pressure is adjusted by the initial load of the coil spring, and the spring constant of the coil spring is used in the double cylinder type shock absorber. The attenuation characteristic can be adjusted.

  However, in such a damping valve that biases the valve body with a coil spring, if the double-tube shock absorber exhibits high speed operation, that is, if the double-tube shock absorber repeatedly expands and contracts at high speed, There is a problem that the axial vibration of the valve body is excited and oscillates due to the pressure fluctuation, and the damping force generated by the double-cylinder shock absorber becomes unstable and vibrates.

  Therefore, the present invention was devised in order to improve the above-mentioned problems, and the object of the present invention is to provide a damping that can suppress the oscillation of the valve body and generate a stable damping force in the shock absorber. It is to provide a valve.

  In order to achieve the above-described object, the problem solving means of the present invention is configured such that one chamber of the two chambers formed in the shock absorber is in the upstream and the other chamber is in the downstream and communicated with the one chamber. A housing having a valve hole having an annular valve seat, a valve body having a disc-like valve body that is inserted in the valve hole so as to be movable in the axial direction and is seated on and off the annular valve seat, and a side of the valve hole A port that opens to the other chamber and communicates with the other chamber, a spring seat that is disposed in the valve hole and on the side opposite to the annular seat, and is interposed between the valve body and the spring seat. A tubular collar in which a rising coil spring is inserted into the valve hole from the outer peripheral side of the spring seat toward the annular valve seat side in a damping valve having a coil spring biased toward the annular valve seat side The annular valve seat side end position of the collar in the axial direction from the opening to the valve hole of the port. Than anti annular valve seat side end of the valve body of the seating state to a valve seat side annular valve seat, characterized in that in the range of anti-annular valve seat side.

  According to the damping valve of the present invention, even if the shock absorber operates at high speed and the flow rate of the fluid passing through the damping valve increases, the lateral vibration of the coil spring is suppressed and the axial vibration of the valve body is suppressed. A stable damping force can be exhibited without exciting the.

It is sectional drawing of the double cylinder type shock absorber with which the damping valve in one Embodiment was mounted. It is an expanded side sectional view of the damping valve in one embodiment. It is an expanded side sectional view of one modification of the spring seat and collar of the damping valve of one embodiment. It is an expanded side sectional view of another modification of the spring seat and collar of the damping valve of one embodiment. It is an expanded side sectional view of a damping valve in one modification of an embodiment. It is the figure which showed the damping characteristic of the damping valve in one deformation | transformation of one Embodiment. It is an expanded side sectional view of the damping valve in other modifications of an embodiment. It is the figure which showed the damping characteristic of the damping valve in one modification of one Embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIGS. 1 and 2, the damping valve 1 in one embodiment is provided on a rod guide 2 that is fitted to both ends of a cylinder 20 and an outer cylinder 21 in a double-tube shock absorber D. The rod guide 2 is used as a housing, and is connected to a rod side chamber R1 as one chamber. A valve hole 3 having an annular valve seat 4 is provided in the middle of the rod guide 2, and the rod provided with the valve hole 3 1, a valve body 5 having a disc-like valve body 5a that is inserted in the valve hole 3 so as to be movable in the left-right direction in FIGS. A port 11 that opens from the side of the hole 3 and communicates with the reservoir R as the other chamber, a spring seat 10 that is disposed in the valve hole 3 on the side opposite to the annular valve seat from the port 11, and the valve body 5 Between the spring seat 10 and the valve body 5 toward the annular valve seat side A coil spring 6 for energizing the rising coil spring 6 toward the annular valve seat side is configured with a cylindrical collar 7 which is inserted a within valve bore 3 from the outer peripheral side of the spring seat 10.

  On the other hand, a double-cylinder shock absorber D to which the damping valve 1 is applied includes a cylinder 20, an outer cylinder 21 that forms a reservoir R between the cylinder 20, and a cylinder 20 that is slidably inserted into the cylinder 20. A piston 22 that is divided into a rod-side chamber R1 and a piston-side chamber R2 filled with working oil as working fluid, a piston rod 23 that is movably inserted into the cylinder 20 and connected to the piston 22, and a cylinder The rod guide 2 fitted to both ends of the cylinder 20 and the outer cylinder 21 and pivotally supporting the piston rod 23, the partition member 24 fitted to the lower end of the cylinder 20 in FIG. A lid 25 for closing the middle and lower ends, a piston passage 26 communicating with the piston side chamber R2 and the rod side chamber R1 provided in the piston 22, and a piston passage 26 provided in the piston passage 26 from the piston side chamber R2. A check valve 27 that allows only the flow of hydraulic oil toward the cylinder side chamber R1, a suction passage 28 that is provided in the partition member 24 and communicates the reservoir R and the piston side chamber R2, and a reservoir R that is provided in the suction passage 28. And a suction valve 29 that allows only the flow of hydraulic oil toward the piston side chamber R2. In addition to the working oil, it is possible to employ a working fluid that can be applied to a shock absorber such as gas, water, aqueous solution, electrorheological fluid, and magnetorheological fluid.

  When the double-cylinder shock absorber D is extended and the piston 22 moves upward in FIG. 1, the damping valve 1 is opened and connected to the valve hole 3 and the port 11 from the rod side chamber R1 to be compressed. The hydraulic oil flows into the reservoir R through the pipe 9, and resistance is applied to the flow of the hydraulic oil by the damping valve 1, so that the rod side chamber R1 is pressurized, and the double-cylinder shock absorber D exhibits a damping force that suppresses the extension operation. To do. In this extension operation, the piston 22 rises in FIG. 1 to increase the volume of the piston-side chamber R2, but the suction valve 29 provided in the suction passage 28 opens and the hydraulic oil corresponding to the increase is stored in the reservoir R. To the piston side chamber R2.

  Further, when the double cylinder type shock absorber D is contracted and the piston 22 moves downward in FIG. 1, the check valve 27 provided in the piston passage 26 is opened and compressed from the piston side chamber R2 to the rod side chamber R1. As the hydraulic fluid moves to the cylinder 20, the hydraulic fluid corresponding to the volume of the piston rod 23 entering the cylinder 20 becomes excessive in the cylinder 20, so that the damping valve 1 is opened and this excess hydraulic oil is opened. The hydraulic oil flows to the reservoir R through the hole 3 and the pipe 9, and resistance is applied to the flow of the hydraulic oil by the damping valve 1, whereby the overall pressure in the cylinder 20 rises and the double cylinder type shock absorber D is contracted. Demonstrates damping force.

  In other words, the double cylinder type shock absorber D is configured such that the hydraulic oil flows from the rod side chamber R1 through the damping valve 1 to the reservoir R and repeats the expansion and contraction operation during the expansion operation and the contraction operation. The uniflow type shock absorber in which hydraulic oil circulates in the order of the rod side chamber R1, the reservoir R, the piston side chamber R2, and the rod side chamber R1 is set. That is, in this case, one chamber upstream of the damping valve 1 formed in the double-tube shock absorber D is the rod-side chamber R1, and the other chamber downstream is the reservoir R.

  Hereinafter, the damping valve 1 will be described in detail. The rod guide 2 has a cylindrical shape, and the outer periphery is fitted to the inner periphery of the outer cylinder 21 at the upper end in FIG. 1 and the inner periphery is fitted to the outer periphery of the upper end of the cylinder 20 in FIG.

  Further, the inner peripheral diameter of the lower end in FIG. 1 of the rod guide 2 is set to a diameter that can be fitted to the outer periphery of the cylinder 20, and the upper inner periphery in FIG. A recess 2a is formed in which a seal member 30 for sealing is mounted, and a cylindrical bearing 31 slidably in contact with the outer periphery of the piston rod 23 is mounted on the inner periphery and below the recess 2a. In addition, the inner diameter of the intermediate portion 2 b that is the inner circumference of the rod guide 2 and below the mounting portion of the bearing 31 and above the fitting portion of the cylinder 20 is set larger than the outer diameter of the piston rod 23. A gap is formed between the piston rod 23 and the piston rod 23.

  Subsequently, the valve hole 3 provided in the rod guide 2 opens from the outer periphery of the rod guide 2 and passes through the intermediate portion 2 b, and opens from the end of the rod guide 2 facing the reservoir R to reach the middle of the valve hole 3. The port 11 communicates with the reservoir R.

  The valve hole 3 has an inner diameter of the intermediate portion 2b of the rod guide 2 and a small diameter portion 3a communicating with the rod side chamber R1, and a large diameter portion having an inner diameter continuous with the small diameter portion 3a larger than the small diameter portion 3a. 3b, an annular valve seat 4 provided on the inner peripheral edge of the step portion 3c between the small diameter portion 3a and the large diameter portion 3b, and a screw portion 3d provided on the inner periphery on the right end in FIG. 2 of the large diameter portion 3b. A collar 7 to be described later is screwed to the screw portion 3d.

  A port 11 that opens from the middle of the large-diameter portion 3b of the valve hole 3 to the end facing the reservoir R of the rod guide 2 is provided. The port 11 is also provided with a screw portion 11a. Then, the pipe 9 is fixed to the rod guide 2 by screwing the screw 9a provided on the outer periphery of the upper end in FIG. The pipe 9 is protruded and accommodated in the reservoir R, and its lower end opening end in FIG. Therefore, the rod side chamber R1 of the cylinder 20 and the reservoir R are communicated with each other through the valve hole 3, the port 11, and the pipe 9. The pipe 9 may be fixed to the port 11 by press-fitting or welding other than screw connection.

  The valve body 5 is accommodated in the valve hole 3 so as to be movable in the axial direction. The valve body 5 has a notch 5f on the outer periphery and is attached to and detached from the annular valve seat 4, and the annular valve seat of the valve body 5a. A columnar shaft portion 5b extending from the left end in FIG. 2 serving as a side end, a spring fitting portion 5c protruding to the right in FIG. 2 serving as an anti-annular valve seat side of the valve body 5a, and a shaft portion 5b are provided. A groove 5d and an orifice passage 5e communicating from the groove 5d to the end of the spring fitting portion 5c are configured.

  The shaft portion 5 b is slidably inserted into a small diameter portion 3 a that is the inner periphery of the annular valve seat 4 in the valve hole 3, and the valve body 5 is swung with respect to the valve hole 3 using the shaft portion 5 b as a guide. It can move in the axial direction without any problems.

  When the left end of the valve body 5a in FIG. 2 is brought into contact with the right end surface of the annular valve seat 4 in FIG. 2, the damping valve 1 is closed and the flow of hydraulic oil into the valve hole 3 is blocked. Can be done. Further, the shaft portion 5b is provided with a U-shaped groove 5d from the distal end to the proximal end, and the annular valve seat side end which is the left end in FIG. 2 of the valve body 5a is the right end surface in FIG. 2, the groove 5d enters the inside of the valve hole 3 from the small diameter portion 3a and the damping valve 1 is opened according to the retracted amount. The hydraulic oil can flow into the valve hole 3 through the groove 5d. The valve opening area of the damping valve 1 increases as the groove 5d enters the valve hole 3 in accordance with the retraction amount of the valve body 5a in the valve body 5. The shape of the shaft portion 5b is not limited to the above, and in particular, a guide shaft and a bearing that supports the guide shaft are provided at the tip and the spring seat of the spring fitting portion 5c of the valve body 5. In this case, it is not necessary to obtain a guide function for the shaft portion 5b.

  A cylindrical collar 7 is accommodated in the large diameter portion 3 b of the valve hole 3. The collar 7 includes a reduced diameter portion 7a that forms an annular gap with the large diameter portion 3b of the valve hole 3, and a screw portion 3d that is formed in the large diameter portion 3b of the valve hole 3 and that continues to the reduced diameter portion 7a. The diameter-reduced portion 7b to be screwed is provided, and the position of the annular valve seat side end which is the left end in FIG. It is on the annular valve seat side from the opening with respect to the hole 3 and within the range on the anti-annular valve seat side from the anti-annular valve seat side end of the valve body 5a seated on the annular valve seat 4. That is, as shown in FIG. 2, the position A of the collar 7 on the side of the annular valve seat side when viewed from the direction orthogonal to the axial direction is the annular valve seat of the opening of the port 11 with respect to the valve hole 3. The position is set to be within the range of the position Y of the side end of the valve body 5a seated on the annular valve seat 4 from the position X of the side end. By setting in this way, the reduced diameter portion 7a of the collar 7 is completely opposed to the port 11, and the port 11 faces an annular gap formed between the collar 7 and the valve hole 3. Yes.

  Further, a spring seat 10 is screwed to the end portion on the outer peripheral side of the rod guide in the enlarged diameter portion 7b of the collar 7 thus configured. Specifically, the spring seat 10 is screwed to a cylindrical spring fitting portion 10 a and a screw portion 7 c provided on the outer periphery of the spring fitting portion 10 a and provided on the inner periphery of the enlarged diameter portion 7 b of the collar 7. And a flange-shaped spring receiving portion 10b. That is, the spring seat 10 is integrated with the collar 7 by screwing.

  A coil spring 6 is interposed between the spring seat 10 and the valve body 5. The coil spring 6 is interposed between the spring seat 10 and the valve body 5 in a compressed state and is given an initial load. The valve body 5 is energized by the initial load of the compressed coil spring 6. Is pressed toward the annular valve seat 4 even in a state of being seated on the annular valve seat 4.

  A spring fitting portion 10a of the spring seat 10 is fitted to the inner circumference of the right end in FIG. 2 that is one end of the coil spring 6, and the inner circumference of the left end in FIG. The spring fitting portion 5c of the valve body 5 is fitted, and the coil spring 6 is positioned in the radial direction. The collar 7 rises from the outer peripheral side of the spring seat 10 toward the annular valve seat side, and the position of the annular valve seat side end is set as described above. Inserted into. Since the coil spring 6 is positioned in the radial direction, the coil spring 6 inserted into the collar 7 is prevented from interfering with the collar 7.

  Further, in the case of this embodiment, since the collar 7 is screwed into the valve hole 3 and the spring seat 10 is screwed into the collar 7, the position A of the collar 7 on the annular valve seat side end is adopted. Can be freely set within the range from the position X of the opening of the port 11 on the side of the annular valve seat side to the valve hole 3 of the port 11 to the position Y of the end of the valve main body 5a seated on the annular valve seat 4. In addition, since the axial position of the spring seat 10 can be freely set, there is an advantage that the initial load applied to the coil spring 6 can be arbitrarily adjusted with respect to the setting of the position A of the annular valve seat side end of the collar 7. is there.

  Since the collar 7 only needs to have a structure extending from the outer peripheral side of the spring seat to the annular valve seat side, the adjustment of the position of the annular valve seat side end of the collar 7 and the adjustment of the initial load of the coil spring 6 are performed independently. If not necessary, as shown in FIG. 3, it is also possible to adopt a structure in which the collar 7 has a bottomed cylindrical shape, a spring fitting portion 34 is provided on the bottom 33, and the collar 7 is integrated with the outer periphery of the spring seat. Is possible. As shown in FIG. 4, the collar 7 can be formed into a bottomed cylindrical shape, and a spring seat 37 provided with a spring fitting portion 36 can be accommodated inside the collar 7 and placed on the bottom 35 of the collar 7. In this case, since the collar 7 and the spring seat 37 are separate members, the processing is facilitated as compared with the structure in which the collar and the spring seat are integrally molded, and the collar 7 and the bottom portion 35 of the collar 7 are interposed. By interposing a disc-shaped or single or plural annular shims, it is possible to adjust the initial load of the coil spring 6 in addition to the adjustment of the position of the collar 7 on the annular valve seat side end. The spring seat 37 shown in FIG. 4 is pressed by the coil spring 6 so that it is positioned in the axial direction within the collar 7, thereby being fixed to the valve hole 3.

  In the damping valve 1 configured as described above, the pressure in the rod side chamber R1 acts on the shaft portion 5a of the valve body 5, and the force pushing the valve body 5 biases the valve body 5 of the coil spring 6. When the force is exceeded, the valve opens, and the fluid that has pushed the valve body 5 away and passed through the groove 5d flows into the valve hole 3 and escapes to the port 11 through the annular gap between the collar 7 and the valve hole 3. Then, it passes through the pipe 9 and moves to the reservoir R.

  As the pressure acting on the distal end side of the valve body 5 increases, the amount of retreat inward of the valve hole 3 that is away from the annular valve seat 4 and becomes the anti-annular valve seat side increases. The valve opening area limited by the valve body 5 and the annular valve seat 4 increases with the increase, and the flow rate of the fluid passing through the damping valve 1 also increases. However, as described above, the collar 7 is annular from the outer peripheral side of the spring seat 10. The rising coil spring 6 is inserted into the valve seat side, and the position A of the annular valve seat side end of the collar 7 is changed from the position X of the annular valve seat side end of the opening to the valve hole 3 of the port 11. Since the collar 7 faces the port 11 because the valve body 5a is seated on the annular valve seat 4 in the position Y at the end on the side opposite to the annular valve seat, the fluid that has passed through the valve body 5 and the annular valve seat 4 Passes through the annular gap between the collar 7 and the valve hole 3 and is led to the port 11. Flow across the coil spring 6 of the fluid is reduced.

  Therefore, even if the flow rate of the fluid passing through the damping valve 1 increases due to the high-speed operation of the double-tube shock absorber, the lateral vibration of the coil spring 6 can be suppressed from being excited, and the double-tube shock absorber can be operated at high speed. Even if the pressure fluctuation in the cylinder becomes intense due to repeated expansion and contraction, a stable damping force can be exhibited without exciting the axial vibration of the valve body 5. That is, even when the shock absorber operates at a high speed that expands and contracts at high speed, the vibration in the axial direction of the valve body is suppressed and oscillation is prevented, and the damping force generated by the shock absorber becomes stable and vibrational. The problem is solved.

  Further, when the position A of the collar 7 on the annular valve seat side end in the axial direction is separated from the annular valve seat 4 by a predetermined amount in the axial direction, the position A is within the range on the annular valve seat side from the anti-annular valve seat end of the valve body 5a. In other words, as shown in FIG. 5, the position A of the annular valve seat side end of the collar 7 is the position of the anti-annular valve seat side end of the valve body 5 a in a state where the valve body 5 a is seated on the annular valve seat 4. When the position Y and the valve body 5a are set so as to be between the position Y1 of the anti-annular valve seat end of the valve body 5a when the valve body 5a is retracted to the maximum extent and lifted, the valve body 5 is When the seat is lifted away from the annular valve seat 4, the collar 7 and the valve body 5 a eventually overlap each other in the axial direction, narrowing the annular gap between the collar 7 and the valve body 5 a, and forming an annular throttle with the annular gap. Then, the pressure in the collar 7 increases, the inside of the collar 7 functions as a back pressure chamber, and the valve body 5 is the pressure in the collar 7. Since the pressed, excitation of the vibration of the valve body 5 is prevented. That is, when the valve body 5 is separated from the annular valve seat 4 by a predetermined amount in the axial direction at the position A of the collar 7 on the annular valve seat side end, the position within the range on the annular valve seat side from the anti-annular valve seat end of the valve body 5a As a result, not only the lateral vibration of the coil spring 6 can be suppressed, but also the inside of the collar 7 can function as a back pressure chamber to reliably prevent the vibration of the valve body 5. The damping force can be exhibited with the damping characteristics as shown in FIG. In FIG. 6, at a piston speed α or higher at which the collar 7 and the valve body 5a overlap in the axial direction, the valve body 5 is pressed toward the annular valve seat 4 by the back pressure, so that the damping coefficient becomes high.

  Further, the position of the end of the collar 7 on the side of the annular valve seat is a range on the side of the anti-annular valve seat from the position of the end of the valve body 5a in the axial direction when the valve body 5 is farthest from the annular valve seat 4 in the axial direction. In other words, as shown in FIG. 7, even if the valve body 5a is fully retracted from the annular valve seat 4 and lifted, the position A at the annular valve seat side end of the collar 7 is the anti-annular valve of the valve body 5a. In addition to being able to suppress the vibration of the valve body 5 by preventing the excitation of the vibration in the lateral direction of the coil spring 6 when setting so as to be positioned on the side opposite to the annular valve seat from the position Y of the seat end. Since an annular throttle is not formed in the annular gap between the valve body 5a and the collar 7 and a large back pressure does not act on the valve body 5, as shown in FIG. 8, the damping coefficient does not increase midway. There is an advantage that a linear attenuation characteristic can be obtained.

  Note that the expansion and contraction speed of the double-tube shock absorber D is low, the force pressing the valve body 5 due to the pressure of the rod side chamber R1 acting on the valve body 5 is small, and overcomes the initial load of the coil spring 6 so that the valve body 5 Cannot be separated from the valve seat 4, the hydraulic oil passes through the orifice passage 5 e that connects the groove 5 d in the valve body 5 and the end of the spring fitting portion 5 c to the reservoir R. The double-cylinder shock absorber D exhibits a damping force with a higher damping coefficient until after the valve body 5 is separated from the annular valve seat 4 until the valve body 5 is separated from the annular valve seat 4. Yes. In this case, the piston speed of the double cylinder type shock absorber D is low and the problem that the valve body 5 vibrates does not occur. Depending on the required attenuation characteristics, the orifice passage 5e may not be provided.

  Further, since only the collar 7 is installed, it is not necessary to newly process the housing provided with the valve hole 3, in this case, to the rod guide 2, so that the existing damping valve can be easily and costly. Can be incorporated without

  In the above description, the case where the damping valve 1 of the present invention is incorporated in the double cylinder type shock absorber D has been described as an example. However, the present invention can also be applied to a shock absorber other than the double cylinder type shock absorber. Can be demonstrated. For example, regardless of whether the cylinder is a single cylinder type or a multiple cylinder type, a shock absorber piston can be used as a housing and a damping valve can be incorporated therein. In this case, one chamber is one of a rod side chamber and a piston side chamber, and the other is The damping valve can generate a damping force in the shock absorber when the shock absorber is extended or contracted, with the other chamber being the other of the rod side chamber and the piston side chamber. In addition, when the shock absorber is a double-tube shock absorber and is set to biflow, the piston side chamber is set as one upstream chamber, the reservoir is set as the other downstream chamber, and a damping valve is incorporated in the base valve portion to You may make it exhibit a damping force to a buffer at the time of contraction.

  This is the end of the description of the embodiment of the present invention, but the scope of the present invention is of course not limited to the details shown or described.

  The damping valve of the present invention can be used for a shock absorber.

DESCRIPTION OF SYMBOLS 1 Damping valve 2 Rod guide 2a Recessed part 2b Middle part 3 Valve hole 3a Small diameter part 3b in valve hole Large diameter part 3c in valve hole 3d in valve hole Screw part in valve hole 4 Annular valve seat 5 Valve body 5a In valve body Valve body 5b Shaft portion 5c in the valve body Spring fitting portion 5d in the valve body Groove 5e in the valve body Orifice passage 5f in the valve body Notch 6 in the valve body 7 Coil spring 7 Collar diameter 7a Diameter reduction part 7b Collar diameter expansion part 7c Screw portion 9 in collar Collar 9a Screw portion 10 Spring seat 10a Spring fitting portion 10b Spring receiving portion 11 Port 11a Screw portion 20 in port Cylinder 21 Outer cylinder 22 Piston 23 Piston rod 24 Partition member 25 Lid 26 Piston passage 27 Check valve 28 Suction passage 29 Suction valve 30 Sealing member 31 Bearing 33 Collar bottom 34 Spring fitting Joint portion 35 Collar bottom portion 36 Spring fitting portion 37 Spring seat D Double cylinder type shock absorber R Reservoir R1 Rod side chamber R2 Piston side chamber

Claims (6)

A housing provided with a valve hole having an annular valve seat in the middle of the two chambers formed in the shock absorber and having one chamber upstream and the other chamber downstream. A valve body having a disc-shaped valve body that is inserted in the axial direction so as to be movable in and out of the annular valve seat, a port that opens from the side of the valve hole and communicates with the other chamber, And a spring seat disposed on the side opposite to the annular valve seat from the port, and a coil spring interposed between the valve body and the spring seat to urge the valve body toward the annular valve seat side. The damping valve includes a cylindrical collar into which a rising coil spring is inserted from the outer periphery side of the spring seat toward the annular valve seat side in the valve hole, and the end position of the collar on the annular valve seat side is the axial direction. The anti-annular valve of the valve body seated on the annular valve seat on the annular valve seat side from the port opening Damping valve, characterized in that of the side edge is in the range of anti-annular valve seat side. The annular valve seat side end position of the collar is in a range on the anti-annular valve seat side from the anti-annular valve seat end of the valve body when the valve body is farthest from the annular valve seat in the axial direction. Item 4. The damping valve according to Item 1. The annular valve seat side end position of the collar is within the range on the annular valve seat side from the anti-annular valve seat end of the valve body when the valve body is separated from the annular valve seat by a predetermined amount in the axial direction. The damping valve according to claim 1, wherein an annular throttle is formed by the annular gap. 4. The collar according to claim 1, wherein the collar is screwed into the valve hole, and the spring seat is screwed into the inner periphery of the collar and fixed to the valve hole via the collar. Damping valve. 4. The collar according to claim 1, wherein the collar has a bottomed cylindrical shape and is screwed into the valve hole, and a spring seat is fitted in the collar and placed on the bottom. Damping valve. A disc-shaped valve body on which the valve body is attached to and detached from the annular valve seat, and a shaft portion that extends from the valve body and slides in contact with the inner periphery of the annular valve seat to guide movement in the perspective direction to the annular valve seat of the valve body. The damping valve according to any one of claims 1 to 5, wherein:

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