JP2007205444A - Shock absorber valve structure and shock absorber - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shock absorber valve structure for satisfying both vehicle ride comfort and a stroke length, and to provide a shock absorber. <P>SOLUTION: The shock absorber valve structure comprises a valve disc having a port, a shaft member rising up from the axial center of the valve disc, an annular relief valve through the inner periphery side of which the shaft member is inserted and which is stacked on the valve disc for closing the port, and an energizing means for energizing the relief valve in the direction of closing the port. The energizing means has an annular valve retaining member through the inner periphery side of which the shaft member is inserted and which is stacked on the relief valve, and one or more annular plate supported at its inner periphery side by the shaft member and having elasticity. The valve retaining member has a cylinder portion for abutting on the annular plate. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an improved shock absorber valve structure and shock absorber.

  Conventionally, this kind of shock absorber valve structure is embodied in, for example, a piston portion of a shock absorber for a vehicle, and an annular leaf valve is laminated on the outlet end of a port provided in the piston portion. A valve that opens and closes a port is known.

  In particular, in the valve structure of the above-described shock absorber that opens and closes the port with the leaf valve by fixing and supporting the inner peripheral side of the leaf valve and bending the outer peripheral side, the damping force in the medium and high speed region becomes too large. In order to solve this problem, the inner periphery of the leaf valve L is not fixedly supported on the piston rod R, and the inner periphery of the leaf valve L is not fixedly supported as shown in FIG. A valve structure of a shock absorber is proposed in which the rear surface of the leaf valve L is urged by a coil spring S through a valve restraining member M by being brought into sliding contact with the outer periphery of a cylindrical piston nut N or the like that is attached and fixes the piston P. As shown in the figure, the extension side damping valve of the shock absorber is embodied (see, for example, Patent Document 1).

In the shock absorber to which this valve structure is applied, as shown in the figure, when the piston speed when the piston P moves upward is in the low speed region, the valve holding member M in which the outer peripheral side of the leaf valve L is stacked on the leaf valve L is shown. Therefore, when the piston speed reaches the middle-high speed region, the hydraulic fluid that passes through the port Po will be able to exhibit the same damping characteristics as the valve structure in which the inner periphery is fixedly supported. The pressure acts on the leaf valve L, and the leaf valve L lifts in the axial direction from the piston P together with the valve restraining member M against the biasing force of the coil spring S, so that the inner periphery is fixedly supported. Compared to the valve structure of the shock absorber, the flow path area is increased and the damping force is suppressed from being excessive, thereby improving the riding comfort in the vehicle.
Japanese Patent Laid-Open No. 9-291196 (FIG. 1)

  However, the proposed valve structure as described above and the shock absorber to which the valve structure is applied are useful techniques in that the ride comfort in the vehicle can be improved. is there.

  This is because in the proposed valve structure, the leaf valve L is urged by the coil spring S so that the damping force is not excessive when the piston speed is in the medium to high speed region. Compared to the conventional valve structure with a leaf valve that is not provided with a spring S and whose inner periphery is fixedly supported, the length of the entire piston portion including the valve is necessarily equal to the length of the coil spring S. Becomes longer, and the stroke length, which is the extendable range of the shock absorber, is shortened by the length.

  And if it is going to secure the said stroke length to the same extent as the said conventional valve structure, the length of the whole buffer will become long and the mounting property to a vehicle will deteriorate.

  In the proposed valve structure, it is necessary to secure the lift amount of the leaf valve L so that the damping force does not become excessive when the piston speed is in the medium to high speed range. Therefore, it is difficult to cut down the length of the coil spring S itself.

  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 shock absorber valve structure capable of satisfying both the ride comfort and the stroke length in a vehicle, and Is to provide a shock absorber.

  In order to solve the above-described object, the problem-solving means in the present invention includes a valve disk in which a port is formed, a shaft member that rises from the axial center of the valve disk, and the shaft member that is inserted into the inner peripheral side. And a valve structure of a shock absorber comprising an annular leaf valve stacked on the valve disk and closing the port, and an urging means for urging the leaf valve in the direction of closing the port. The above-mentioned shaft member is inserted on the side, and an annular valve restraining member stacked on the leaf valve, and one or a plurality of annular plates having elasticity whose inner peripheral side is supported by the shaft member are provided. The member includes a cylindrical portion that abuts the annular plate.

  Another problem-solving means of the present invention is a cylinder, a piston that is slidably inserted into the cylinder and separates two pressure chambers in the cylinder, and a tip projecting from the axial center of the piston. A piston rod connected to the piston and movably inserted into the cylinder, a port communicating with the two pressure chambers provided in the piston, the piston rod being inserted into the inner peripheral side, and the piston In a shock absorber provided with an annular leaf valve that is stacked and closes a port, and a biasing means that biases the leaf valve in the direction of closing the port, There is one annular valve restraining member that is inserted and stacked on the leaf valve, and one that has the elasticity that the inner peripheral side is supported on the tip side from the valve restraining member of the piston rod Includes a plurality of annular plate, the valve restraining member is provided with a cylindrical portion in contact with the annular plate.

  According to the valve structure of the shock absorber and the shock absorber of the present invention, it is possible to improve the riding comfort in the vehicle so that the damping force when the piston speed is in the medium to high speed region does not become excessive, and to expand and contract the shock absorber. The stroke length which is a possible range can also be ensured, that is, it is possible to satisfy both the riding comfort and the stroke length in the vehicle.

  The valve structure of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view of a part of a piston portion of a shock absorber in which a valve structure according to an embodiment is embodied. FIG. 2 is a longitudinal sectional view of a part of a piston portion of a shock absorber in which the valve structure of the shock absorber according to a modification of the embodiment is embodied.

  As shown in FIG. 1, the valve structure of the shock absorber in one embodiment is embodied as an extension side damping valve of the piston portion of the shock absorber, and includes a piston 1 as a valve disk in which a port 2 is formed, and a piston A piston rod 4 that is a shaft member that rises from the axial center of 1, an annular leaf valve 10 that is stacked on the piston 1 and closes the port 2 when the piston rod 4 is inserted on the inner peripheral side, and on the inner peripheral side An annular valve restraining member 11 that is inserted into the piston valve 4 and stacked on the leaf valve 10, and an annular plate 15 that biases the leaf valve 10 through the valve restraining member 11 in the direction of closing the port 2. It is prepared for.

  On the other hand, a shock absorber in which this valve structure is embodied is well known and will not be described in detail, but specifically, for example, a cylinder 40 and a head member (not shown) that seals the upper end of the cylinder 40. ), A piston rod 4 slidably penetrating a head member (not shown), the piston 1 provided at the tip 4a of the piston rod 4, and two cylinders 40 separated by the piston 1 An upper chamber 41 and a lower chamber 42 that are pressure chambers, a sealing member (not shown) that seals the lower end of the cylinder 40, and an illustration that compensates for a change in the cylinder volume corresponding to the volume of the piston rod 4 that protrudes and retracts from the cylinder 40. The cylinder 40 is filled with a fluid, specifically, hydraulic oil. In the present embodiment, the tip 4 a of the piston rod 4 is connected to the piston 1 so that the tip 4 a of the piston rod 4 protrudes from the shaft center of the piston 1. It is a shaft member that rises from the top.

  In the valve structure, when the piston 1 moves upward in FIG. 1 with respect to the cylinder 40, the pressure in the upper chamber 41 rises, and the port 2 passes from the upper chamber 41 to the lower chamber 42. When the hydraulic oil moves, the leaf valve 10 provides resistance to the movement of the hydraulic oil to cause a predetermined pressure loss, thereby functioning as a damping force generating element that generates a predetermined damping force in the shock absorber.

  Hereinafter, the valve structure will be described in detail. The piston 1 serving as a valve disk is formed in a bottomed cylindrical shape, and an insertion hole 1b through which the piston rod 4 of the shock absorber is inserted into the axial center portion of the bottom 1a; A port 2 arranged on the same circumference, an annular window 3 communicating with the port 2, an annular valve seat 1c formed on the outer peripheral side of the window 3 serving as an outlet end of the port 2, and a bottom 1a The outer cylinder part 1f extended in the outer periphery of this is provided and comprised. The piston 1 includes a plurality of pressure-side ports 1d that allow a flow of hydraulic oil from the lower chamber 42 to the upper chamber 41 when the shock absorber contracts, more outward than the port 2 on the extended side of the bottom portion 1a. Is provided.

  The piston rod 4 is inserted into the insertion hole 1b of the piston 1 as described above, and the tip 4a of the piston rod 4 is projected downward in FIG. The outer diameter of the tip 4a of the piston rod 4 is set to be smaller than the outer diameter on the upper side in FIG. 1 with respect to the tip 4a, and a step 4b is formed at a portion where the outer diameter is different between the upper side and the tip. Yes.

  The tip 4a of the piston rod 4 is inserted into the insertion hole 1b of the piston 1 together with the laminated leaf valve 100 constituted by laminating a plurality of pressure side leaves, the spacer 101 and the valve stopper 102. 1, a guide cylinder 6 disposed on the outer peripheral side of the tip 4a of the piston rod 4, an annular plate 15 and a spacer 9 which will be described later are inserted, and a screw portion in which the piston nut 5 is provided on the tip 4a of the piston rod 4. By being screwed to 4c, the piston 1 is clamped between the step 4b of the piston rod 4 and the upper end of the piston nut 5 and fixed to the piston rod 4.

  Further, the lower end opening portion of the insertion hole 1b provided in the bottom portion 1a of the piston 1 is enlarged in diameter to provide an enlarged diameter portion 1e to form a stepped portion, and the upper end of the guide tube 6 in FIG. Is now possible.

  In addition, by providing the enlarged diameter portion 1e, the guide cylinder 6 can be positioned in the radial direction with respect to the piston 1, and a leaf valve 10, spacers 7 and 8, and a valve restraining member 11, which will be described later, are provided in the guide cylinder 6. After the assembly, these members can be attached together with the piston 1 to the tip 4a of the piston rod 4 for convenience in manufacturing, but the enlarged diameter portion 1e may be omitted.

  Further, as described above, by forming the piston 1 in the shape of a bottomed cylinder, it is possible to house the members constituting the valve structure such as the leaf valve in the piston 1, and downsize the piston portion. can do.

  A plurality of annular spacers 7 having a smaller diameter than the leaf valve 10 slidably in contact with the outer periphery of the guide cylinder 6 are stacked on the bottom 1 a of the piston 1, and are slid onto the outer periphery of the guide cylinder 6 from below the spacer 7. A plurality of annular spacers 8 that are smaller in diameter than the leaf valve 10 and are in sliding contact with the outer periphery of the guide tube 6 are stacked from the lower side of the leaf valve 10. A valve hold-down member 11 that is also slidably contacted with the outer periphery of the guide cylinder 6 from below is laminated.

  The leaf valve 10 is configured as a laminated leaf valve by laminating a plurality of leaves formed in an annular shape, and closes the port 2 of the piston 1 by bringing the upper surface in FIG. 1 into contact with the valve seat 1c. Can be done. In this embodiment, the leaf valve 10 is configured as a laminated leaf valve, but the number of leaves is arbitrary depending on the damping characteristic (relationship of the damping force to the piston speed) realized by this valve structure. Depending on the attenuation characteristics generated in the shock absorber, a plurality of sheets or a single sheet may be used, and the outer diameter of each leaf can be set differently depending on the attenuation characteristics generated in the shock absorber.

  The axial thickness of the spacer 7 as a whole is set shorter than the axial length in the vertical direction in FIG. 1 from the bottom 1a of the piston 1 to the lower end of the valve seat 1c. When an urging force acts on the side, the leaf valve 10 can be given initial deflection.

  Further, the valve pressing member 11 stacked in the lower part in FIG. 1 includes an annular part 11a whose inner periphery is in sliding contact with the guide tube 6, a flange part 11b extending from the lower outer periphery in FIG. 1b, and a cylindrical portion 11c extending downward in FIG. 1 from the outer periphery of the portion 11b. The cylindrical portion 11b is movable up and down in FIG. 1 so that the upper end of the annular portion 11a in FIG. 8 are stacked.

  As described above, both the leaf valve 10 and the valve holding member 11 described above are formed in an annular shape, and the piston rod 4 is inserted through the guide tube 6 on the inner peripheral side thereof.

  Subsequently, as shown in FIG. 1, the three annular plates 15 stacked are sandwiched between the lower end of the guide tube 6 and the spacer 9, and the inner peripheral side is sandwiched between the screw portions 4 c of the tip 4 a of the piston rod 4. It is fixed to the piston rod 4 by a piston nut 5 screwed to the piston rod 4. That is, the annular plate 15 is supported by the piston rod 4 that is a shaft member via the guide cylinder 6 and the piston nut 5 on the inner peripheral side, that is, the inner peripheral edge and the inner peripheral portion thereof. Since the annular plate 15 is an annular plate having elasticity, the outer peripheral side of the spacer 9 is a free end on the outer peripheral edge of the spacer 9 and can be bent downward in FIG.

  The leaf constituting the leaf valve for generating the damping force described above can be adopted as the annular plate 15. When the annular plate 15 is such a leaf, the components in the valve structure are shared. Since there is no need to produce a special annular plate, the economy is improved.

  Further, of the annular plate 15, the lower end in FIG. 1 of the cylindrical portion 11 c of the valve holding member 11 is brought into contact with the outer peripheral edge of the uppermost annular plate 15 in FIG. 1. 1 in the state where the spacer 7, the leaf valve 10, the spacer 8, and the valve holding member 11 are stacked on the piston 1 without a gap, the upper end of the annular plate 15 is the piston rod 4. Thus, the annular plate 15 is always bent so that the urging force acts on the inner peripheral side of the leaf valve 10. The urging force of 15 gives the leaf valve 10 an initial deflection and presses the leaf valve 10 against the valve seat 1c.

  Specifically, the lower end in FIG. 1 of the cylindrical portion 11c from the step portion formed by the enlarged diameter portion 1e in a state where the spacer 7, the leaf valve 10, the spacer 8, and the valve holding member 11 are stacked on the piston 1 without a gap. Is set to be longer than the axial length of the guide cylinder 6 in the vertical direction in FIG. 1, so that the upper end of the annular plate 15 is supported by the piston rod 4 from the position of the cylinder portion 11 c. The position of the lower end in FIG. 1 is arranged below in FIG.

  That is, the urging force of the annular plate 15 is applied to the inner peripheral side of the leaf valve 10 via the valve restraining member 11, and the leaf valve 10 is urged in the direction of closing the port 2 with the annular plate 15. The urging means includes the annular plate 15 and the valve holding member 11.

  Therefore, the leaf valve 10 and the valve restraining member 11 resist the urging force when the piston 1 moves upward in FIG. 1 and the difference between the pressure in the upper chamber 41 and the pressure in the lower chamber 42 increases. Then, the outer peripheral side of the annular plate 15 is bent downward in FIG. 1 so that the entire leaf valve 10 moves backward from the piston 1 in the axial direction, that is, lifts downward in FIG.

  The adjustment of the urging force that the annular plate 15 gives the initial deflection to the leaf valve 10 is not limited to the elastic coefficient of the annular plate 15, the adjustment of the number of the annular plates 15, the adjustment of the diameter of the cylinder part 11 c, 1c of FIG. 1 and the position where the upper end of the annular plate 15 is supported by the piston rod 4 can be adjusted. In particular, when the urging force for urging the leaf valve 10 by the annular plate 15 is adjusted by adjusting the diameter of the cylindrical portion 11c and changing the position of contact with the annular plate 15, the above-described valve structure is realized. Since the length of the piston in the axial direction in FIG. 1 which is the vertical direction in FIG. 1 is not increased, it is advantageous for securing the stroke length.

  Then, by adjusting the amount of initial deflection of the leaf valve 10, the valve opening pressure when the leaf valve 10 leaves the valve seat 1c and opens the port 2 is adjusted to adjust the damping characteristic of the shock absorber. The amount of deflection of this initial deflection can be changed by the overall thickness of the spacer 7 and is set to be optimal for a vehicle to which a shock absorber is applied. The spacer 7 can be omitted depending on the axial length from the bottom 1a of the piston 1 to the lower end of the valve seat 1c.

  Further, the spacer 8 interposed between the leaf valve 10 and the valve holding member 11 is not necessarily provided, but the fulcrum of bending of the leaf valve 10 can be easily changed by changing the outer diameter of the spacer 8. In addition, even when the urging force of the annular plate 15 is adjusted at the lower end of the cylindrical portion 11c in FIG. 1, the thickness of the valve restraining member 11 in the vertical direction in FIG. This is convenient in that only the adjustment of the number of 8 is necessary, and also when the number of stacked layers in the leaf valve 10 is changed, it is convenient in that the urging force of the annular plate 15 can be adjusted by increasing or decreasing the number of spacers 8.

  Further, the spacer 9 is provided in order to provide a space in which the annular plate 15 bends between the piston nut 5 and the lower surface of the annular plate 15 in FIG. If the protrusion 5a is provided at the upper end of the nut 5 and a space for bending the annular plate 15 can be secured, the spacer 9 can be omitted. When the spacer 9 is omitted, the bending fulcrum of the annular plate 15 is the outer peripheral edge of the protrusion 5a. Further, the maximum amount of bending of the annular plate 15 can be limited by bending the outer peripheral end of the annular plate 15 and abutting against the upper end of the piston nut 5 other than the protrusion 5a in FIG. The maximum lift amount when the leaf valve 10 moves backward from the piston 1 can be limited by limiting the maximum deflection amount. The adjustment of the maximum lift amount is not only the adjustment of the thickness and number of the spacers 9, but also when the projection 5a is provided on the piston nut 5, the axial length that is the vertical length of the projection 5a in FIG. It can also be done by adjusting.

  Note that the maximum clearance formed between the leaf valve 10 and the valve seat 1c can be adjusted by adjusting the maximum lift amount of the leaf valve 10, so that when the piston speed is in the middle to high speed region. It is possible to adjust the attenuation characteristic generated by the shock absorber.

  Next, the operation of the valve structure and the shock absorber in the embodiment will be described. As described above, when the piston 1 moves upward in FIG. 1 with respect to the cylinder 40, the pressure in the upper chamber 41 increases, The hydraulic oil in the upper chamber 41 tries to move into the lower chamber 42 through the port 2.

  When the piston speed, which is the expansion / contraction speed of the shock absorber, is in the low speed region, the leaf valve 10 cannot be lifted back from the piston 1 against the urging force of the annular plate 15, and the leaf valve 10 is annular. Since it is urged by the plate 15 and pressed so as to close the port 2, the outer peripheral edge of the leaf valve 10 bends with the outer peripheral edge of the spacer 8 as a fulcrum, and the hydraulic oil flows through the port 2 to the leaf valve. 10 passes through a gap between the leaf valve 10 and the valve seat 1c formed by separating from the valve seat 1c.

  On the other hand, when the speed of the piston 1 reaches the middle speed region, the difference between the pressure in the upper chamber 41 and the pressure in the lower chamber 42 increases, and the force for pushing down the leaf valve 10 of the hydraulic oil downward in FIG. 1 increases. When the force overcomes the urging force of the annular plate 15, the entire leaf valve 10 is retracted from the bottom 1a of the piston 1 in the axial direction which is the vertical direction in FIG. 1, that is, moves downward in FIG. I will let you.

  At this time, the entire leaf valve 10 is separated from the bottom 1a of the piston 1, and the gap between the valve seat 1c and the leaf valve 10 is larger than when the piston speed is in the low speed region, and is proportional to the piston speed. The gap becomes larger.

  In other words, when the piston speed is in the low speed region, it exhibits damping characteristics substantially the same as a shock absorber to which an old valve structure in which the inner periphery of the leaf valve 10 is fixedly supported is applied, and the piston speed is medium to high. When reaching the region, the pressure of the hydraulic oil passing through the port 2 acts on the leaf valve 10, and the leaf valve 10 lifts from the piston 1 together with the valve holding member 11 in the axial direction against the urging force of the annular plate 15. Since it moves backward, the flow path area is larger and the damping force is controlled to be excessive compared to a shock absorber that uses the conventional valve structure with the inner circumference fixedly supported. It can be improved.

  The piston speed when the leaf valve 10 is lifted can be adjusted by the urging force that the annular plate 15 acts on the leaf valve 10.

  In this valve structure, the leaf valve 10 is not energized by the coil spring, but is energized by the annular plate 15 and the valve restraining member 11, so that it is compared with the one using the coil spring. Since the axial length of the urging means for urging the leaf valve 10 is drastically shortened, the entire piston portion including each part constituting the valve structure is also shortened, and the shock absorber can be expanded and contracted. There is no problem that the stroke length is shortened, and the mountability to the vehicle does not deteriorate.

  Therefore, in the valve structure of the shock absorber according to the present embodiment, it is possible to improve the riding comfort in the vehicle so that the damping force when the piston speed is in the middle to high speed region does not become excessive, and the shock absorber. It is also possible to ensure the stroke length that is the range of expansion and contraction of the vehicle, that is, it is possible to satisfy both the riding comfort and the stroke length in the vehicle.

  Moreover, the adjustment of the urging force of the annular plate 15 can also be performed by adjusting the diameter of the cylinder part 11c, and the stroke length of the shock absorber is not sacrificed when adjusting the urging force by the diameter of the cylinder part 11c.

  Furthermore, since the generation source of the urging force is the annular plate 15, the urging force is applied uniformly over the entire circumference of the annular contact surface with which the annular portion 11 a of the valve holding member 11 of the leaf valve 10 contacts. Therefore, it can be expected to generate a stable damping force without variation in product units.

  Further, the shape of the valve pressing member is the same as that of the valve pressing member 16 in the valve structure in the modification of the embodiment shown in FIG. 2, but the flange portion 11b is eliminated and the cylindrical portion 16b is directly connected from the outer periphery of the annular portion 16a. It does not matter if it has a standing shape. Since the other parts of the valve structure are the same as those in the embodiment, the same members as those in the embodiment are denoted by the same reference numerals in FIG. Will be omitted, and the description of the same member will be omitted.

  In particular, in the valve structure shown in FIG. 2, the outer diameter of the annular plate 17 constituting a part of the urging means is set smaller than the outer diameter of the annular plate 15 shown in FIG. Therefore, the shape of the valve holding member 16 is as described above. Therefore, the annular plate 17 in this modification is smaller in outer diameter than the annular plate 15 in one embodiment, and the fulcrum of bending is the outer peripheral edge of the spacer 9 as in the case of the actual case. When the annular plate 15 is formed of the same material as that of the annular plate 15, the annular plate 17 and the valve holding member 16, which are the urging means in this modification, give the leaf valve 10 a larger urging force than that of the embodiment. It is possible to give.

  As described above, the shape of the valve pressing member may be appropriately changed depending on the outer diameter of the annular plate, and the shape of the valve pressing member includes a cylindrical portion that comes into contact with the annular plate and does not hinder the passage of hydraulic oil. Other shapes may be used.

  Further, by applying the valve restraining member 16 shown in FIG. 2 instead of the valve restraining member 11 to the valve structure in the embodiment, the contact position of the tubular portion of the valve restraining member of the annular plate 15 is shifted inward. It is possible to adjust the urging force that urges the leaf valve 10 of the annular plate 15, and such a change corresponds to changing the diameter of the cylinder portion of the valve holding member described above.

  Further, in each of the above-described embodiments, the annular plates 15 and 16 are fixed using the guide cylinder 6 and the piston nut 5, but may be supported by the piston rod 4 by other means. Further, the piston 1 is provided with an insertion hole 1a so that the tip 4a of the piston rod 4 is inserted, and the tip 4a constitutes a shaft member. In addition to the tip 4a of the piston rod 4, a valve disk is provided. A shaft member integral with or separate from the piston 1 may be provided at the axial center of the piston 1.

  This is the end of the description of the embodiment of the valve structure, but the valve structure of the present invention can be embodied in the compression side damping valve of the piston portion of the shock absorber, or in the base valve portion. Of course, the present invention can be applied to a valve of a shock absorber that functions as a damping force generating element that generates a damping force.

  It should be noted that the scope of the present invention is not limited to the details shown or described.

It is a longitudinal cross-sectional view in a part of piston part of the shock absorber by which the valve structure of the shock absorber in one embodiment was embodied. It is a longitudinal cross-sectional view in a part of piston part of the shock absorber by which the valve structure of the shock absorber in the modification of one Embodiment was embodied. It is a longitudinal cross-sectional view of the piston part of the buffer which actualized the valve structure of the conventional buffer.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Piston 1a which is a valve disc Bottom part 1b Insertion hole 1c Valve seat 1d, 2 Port 1e Expanded part 1f Outer cylinder part 3 Window 4 Piston rod 4a Piston rod tip 4b which is a shaft member Step part 4c Screw part 5 Piston nut 5a Protrusion 6 Guide cylinder 7, 8, 9, 101 Spacer 10 Leaf valve 11, 16 Valve restraining member 11 a, 16 a Annular portion 11 b 鍔 11 c, 16 b Cylindrical portion 15, 16 Annular plate 40 Cylinder 41 Upper chamber 42 Lower chamber 100 Laminated leaf valve 102 Valve stopper

Claims (2)

A valve disk in which a port is formed, a shaft member that rises from the axial center of the valve disk, an annular leaf valve that is stacked on the valve disk and closes the port when the shaft member is inserted on the inner peripheral side; In the valve structure of the shock absorber having an urging means for urging the leaf valve in the direction of closing the port, the urging means has an annular shape in which the shaft member is inserted on the inner peripheral side and stacked on the leaf valve A valve holding member, and one or a plurality of annular plates having elasticity that are supported by a shaft member on the inner peripheral side, and the valve holding member includes a cylindrical portion that contacts the annular plate. The shock absorber valve structure. A cylinder, a piston that is slidably inserted into the cylinder and that separates two pressure chambers, and a piston that is connected to the piston so that its tip protrudes from the axial center of the piston and is movably inserted into the cylinder A piston rod, a port communicating the two pressure chambers provided in the piston, an annular leaf valve that is stacked on the piston and closes the port when the piston rod is inserted on the inner peripheral side, And a biasing means for biasing the leaf valve in the direction of closing the port, the biasing means is an annular member that is inserted into the inner peripheral side of the tip of the piston rod and stacked on the leaf valve. A valve holding member, and one or a plurality of annular plates having an elasticity whose inner peripheral side is supported on the tip side from the valve holding member of the piston rod. Buffer member is characterized by comprising comprises a cylindrical portion in contact with the annular plate.

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