JP2012092860A - Valve structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve structure achieving improved assemblability and further preventing the occurrence of assembling failure.SOLUTION: The valve structure includes a valve disk 1 in which a port 2 is formed, a shaft member 5a rising from an axis part of the valve disk 1, a guide member 11 mounted on an outer periphery of the shaft member 5a, a main valve 13 slidably mounted on an outer periphery of the guide member 11, and an annular spring member 12 for biasing the main valve 13 toward the valve disk 1. The valve structure further includes an aligning member 14 which opposes to an outer periphery of the spring member 12 and suppresses radial displacement of the spring member 12.

Description

  The present invention relates to an improved valve structure.

  Conventionally, this type of valve structure is embodied in, for example, a piston portion of a shock absorber for a vehicle, and an annular leaf valve is stacked on an outlet end of a port provided in the piston portion. Those that open and close ports are known.

  In particular, in the above valve structure in which the port is opened and closed by the leaf valve by fixing and supporting the inner periphery of the leaf valve and bending the outer periphery, the damping force in the low speed region is reduced when the leaf valve deflection rigidity is reduced. On the other hand, if the flexural rigidity is increased, the damping force in the medium / high speed region becomes too large, and it is difficult to satisfy the riding comfort in the vehicle in all speed regions.

  Therefore, in order to solve this problem, the inner peripheral side of the leaf valve is fixed by a guide member laminated on the leaf valve, and is slidably mounted on the outer periphery of the guide member by a disc spring mounted on the outer periphery of the guide member. A valve structure has been proposed in which a leaf valve is urged toward a piston through a valve holding member, and can be embodied as a damping valve on both sides of pressure expansion of a shock absorber (see, for example, Patent Document 1). .

  In the shock absorber to which this valve structure is applied, when the piston speed when the piston moves is in a low speed region, the damping structure exhibits substantially the same damping characteristics as the valve structure in which the inner periphery is fixedly supported. When the speed reaches the middle to high speed range, the hydraulic oil pressure that passes through the port acts on the leaf valve, the leaf valve bends greatly against the urging force of the disc spring, and the port can be opened greatly, and the damping force is excessive. The ride comfort in the vehicle can be improved.

JP 2003-254375 A (FIG. 1)

  When actually assembling the valve structure as described above, an assembling apparatus as disclosed in Japanese Patent Application Laid-Open No. 2006-959 is used. Specifically, the assembling apparatus includes a holding needle, and a leaf valve, a guide member, a valve holding member, and a disc spring are once assembled with the holding needle together with a piston, and the piston, leaf valve, guide member, valve holding member, and plate are assembled. The valve structure is assembled by pulling out the spring from the holding needle, moving it to the outer periphery of the piston rod, and mounting it.

  However, when using the assembly method as described above, the leaf valve, the guide member, the valve holding member, and the disc spring are independent parts, and the axes of these parts are aligned with each other by the folding angle holding needle. However, when moving to the tip of the piston rod, each part may be scattered and the assembly may not be performed easily.

  Also, after the leaf valve, guide member, valve restraining member and disc spring are transferred to the piston rod, a piston nut is screwed onto the tip of the piston rod, and the above-mentioned members are tightened with the piston nut and fixed to the piston rod. However, since the inner diameter of the disc spring is larger than the outer diameter of the holding needle and the piston rod so as to be mounted on the outer circumference of the guide member, the inner circumference of the disc spring is changed to the guide member when the holding needle is transferred to the piston rod. If the piston nut is tightened, the disc spring may be sandwiched between the piston nut and the guide member, which may cause an assembly failure. There is time and effort that must be done for each product.

  Therefore, the present invention has been developed to improve the above-mentioned problems, and its object is to provide a valve structure that can improve the assemblability, and other objects. Is to provide a valve structure capable of preventing the occurrence of defective assembly.

  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 rising from the axial center of the valve disk, and an annular shape that is mounted on the outer periphery of the shaft member. A guide member, a ring-shaped main valve that is mounted on the outer periphery of the shaft member and stacked on the valve disk to open and close the port, and a main valve that is mounted on the outer periphery of the guide member and faces the valve disk. A valve structure including an annular spring member to be biased is provided with a centering member that suppresses radial displacement of a spring member that is disposed inwardly facing the outer periphery of the spring member. To do.

  According to the valve structure of the present invention, if the spring member is properly attached to the outer periphery of the guide member, the alignment member suppresses the radial displacement of the spring member. There is no need to ride on the end portion, and the members constituting the valve can be easily assembled to the shaft member, and the assemblability of the valve structure is improved.

  Further, when the spring member rides on the end portion of the guide member, the spring member is not accommodated in the aligning member, but is protruded outward from the aligning member, so that the nut member is tightened. Assembling failure can be visually recognized before, and occurrence of assembling failure can be prevented.

It is a longitudinal cross-sectional view in the piston part of the shock absorber in which the valve structure in one embodiment was embodied. It is a perspective view of the alignment member in the valve | bulb structure in one Embodiment. It is a longitudinal cross-sectional view in the state which assembled | attached each member with which the valve structure in one Embodiment was embodied to the holding needle. It is a figure explaining the damping characteristic of the buffer with which the valve structure in one embodiment was embodied. It is a longitudinal cross-sectional view in the piston part of the shock absorber in which the valve structure in one modification of one embodiment was embodied.

  The valve structure of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the valve structure in one embodiment is embodied as an expansion-side damping valve of a piston portion of a shock absorber, and includes a piston 1 that is a valve disk in which a port 2 is formed, and a shaft of the piston 1. The tip 5a of the piston rod 5 as a shaft member rising from the center, the guide member 11 that is annular and mounted on the outer periphery of the tip 5a, and the port 2 is slidably mounted on the outer periphery of the guide member 11. A main valve 13 that opens and closes, a disc spring 12 as an annular spring member that is attached to the outer periphery of the guide member 11 and biases the main valve 13 toward the piston 1, and between the main valve 13 and the disc spring 12. And a centering member 14 interposed between them.

  On the other hand, a shock absorber in which the valve structure is embodied is well known and will not be described in detail, but specifically, for example, a cylinder 40 and a rod guide for sealing a lower end (not shown) of the cylinder 40 (FIG. A piston rod 5 that slidably passes through a rod guide (not shown), a piston 1 that is inserted into a tip 5a of a piston rod 5 that forms a shaft member and is fixed to the tip 5a, An upper side chamber 41 and a lower side other chamber 42 in FIG. 1 separated by a piston 1 in the cylinder 40, a sealing member (not shown) for sealing an upper end (not shown) of the cylinder 40, and the cylinder The cylinder 40 is provided with a reservoir or an air chamber (not shown) that compensates for the volume change in the cylinder corresponding to the volume of the piston rod 5 protruding and retracting from the cylinder 40, and the cylinder 40 is filled with fluid, specifically, hydraulic oil. To have.

  In this case, in this case, when the piston 1 moves downward in FIG. 1 with respect to the cylinder 40, the pressure in the other chamber 42 rises and the port from the other chamber 42 to the one chamber 41 is ported. As a hydraulic force generating element for generating a predetermined damping force in the shock absorber by causing the main valve 13 to resist the movement of the hydraulic oil through the main valve 13 and causing a predetermined pressure loss. It is functioning.

  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 tip 5a of the piston rod 5 of the shock absorber is inserted into the axial center of the bottom 1a; A port 2, a window 3 communicating with the port 2, an annular valve seat 1 c formed on the outer peripheral side of the window 3 serving as an outlet end of the port 2 and projecting from the bottom 1 a of the piston 1 toward the main valve 13; It is comprised including the cylinder part 1e extended in this.

  The piston 1 is provided with a pressure-side port 1d that allows the flow of hydraulic oil from the one chamber 41 to the other chamber 42 when the shock absorber contracts, on the outer peripheral side of the port 2 on the extended side of the bottom portion 1a. It has been.

  Further, as described above, by making the piston 1 in a bottomed cylindrical shape, the sliding length in the axial direction necessary for avoiding the shaft shake with respect to the cylinder 40 is secured, and the main valve 13 and the like are secured. Part or all of the members constituting the valve structure can be accommodated in the cylindrical portion 1e of the piston 1, and the length from the lower end of the piston 1 in FIG. 1 to the upper end of the piston nut 6 in FIG. There is an advantage that it can be shortened and the piston portion can be reduced in size.

  The piston rod 5 is inserted into the insertion hole 1b of the piston 1 as described above, and the tip 5a of the piston rod 5 is projected upward in FIG. The outer diameter of the tip 5a of the piston rod 5 is set to be smaller than the outer diameter on the lower side in FIG. 1 from the tip 5a, and the step portion 5b is formed at a portion where the outer diameters of the lower side of the piston rod 5 and the tip 5a are different. Is formed.

  Then, after inserting the tip 5a of the piston rod 5 into the annular valve stopper 22, the annular spacer 21, the inner periphery of the annular pressure side check valve 20 and the insertion hole 1b of the piston 1 in this order, 1 after assembling the annular orifice forming member 10, the guide member 11, the main valve 13, the aligning member 14, the annular shim 15, the disc spring 12, and the washer 16 disposed in the upper part of FIG. By screwing a piston nut 6 into a screw portion 5c provided at the tip 5a, the piston 1 and each of the above members are sandwiched between a step portion 5b of the piston rod 5 and a piston nut 6 serving as a nut member. Fixed.

  In the case of this embodiment, the suction side end, which is the upper end in FIG. 1 of the port 1d, is arranged on the outer peripheral side from the opening end of the port 2 by the main valve 13 and the orifice forming member 10 stacked on the piston 1. The suction side end which is the lower end in FIG. 1 of the port 2 is not blocked by a hole 20 a provided in the check valve 20. If the port 2 is not blocked by the check valve 20 and the port 1d is not blocked by the main valve 13 and the orifice forming member 10, the arrangement and shape of the port 2 are not limited to those illustrated. A configuration may be adopted in which 1d is arranged on the same circumference and the valve seat is a so-called petal type.

  An orifice forming member 10 is laminated on the bottom 1 a of the piston 1. The orifice forming member 10 is annular and is mounted on the outer periphery of the tip 5 a of the piston rod 5, and the inner peripheral side is formed by the piston 1 and the piston nut 6. While being clamped and fixed, the outer periphery is a free end and the outer periphery is allowed to bend.

  Further, the orifice forming member 10 has a plurality of notches 10a provided with the lower surface in FIG. 1 in contact with the valve seat 1c and provided from the outer edge toward the inner periphery. When the main valve 13 is stacked on the orifice forming member 10 configured as described above, the notch 10a is placed on the outer edge side of the orifice forming member 10 by the main valve 13 stacked above the orifice forming member 10 in FIG. The orifice is formed while the orifice forming member 10 is seated on the valve seat 1c.

  In the case of this embodiment, the orifice forming member 10 is interposed between the main valve 13 and the piston 1 as a valve disc so as to form the orifice, but the valve seat 1c is stamped. The orifice forming member 10 may be eliminated when the orifice is formed by providing the recess or when the orifice is formed by providing the recess on the side surface of the valve seat 1c of the main valve 13. However, since the orifice forming member 10 can be manufactured by punching a thin plate, an orifice having a higher dimensional accuracy than that provided with a recess in the valve seat 1c or a recess in the main valve 13 is formed. There are advantages that can be done.

  Next, as shown in FIG. 1, the guide member 11 has an outer diameter smaller than the outer diameter of the orifice forming member 10, and is fixed to the piston rod 5 by a piston nut 6 as a nut member. The inner periphery of the orifice forming member 10 is also fixed.

  A main valve 13 that is annular and is stacked on the piston 1 via an orifice forming member 10 is slidably mounted on the outer periphery of the guide member 11. Also, a disc spring 12 is provided as a spring member that is annular and is mounted on the outer periphery of the guide member 11 and positioned in the radial direction. The disc spring 12 has the outer peripheral side, which is the lower end in FIG. 1, facing the main valve 13, and the inner periphery, which is the upper end in FIG. 1, faces the piston nut 6, and is assembled to the piston rod 5 together with the guide member 11. 1 is supported by the piston nut 6 and is compressed in the axial direction that is the vertical direction in FIG. 1 to exert the urging force that pushes the main valve 13 toward the piston 1 side. is doing. That is, the disc spring 12 is interposed between the piston nut 6 and the main valve 13 in a state where initial deflection is applied, and biases the main valve 13 and the orifice forming member 10 toward the piston 1.

  Subsequently, as shown in FIGS. 1 and 2, the aligning member 14 is annular and is slidably mounted on the outer periphery of the guide member 11, and is interposed between the disc spring 12 and the main valve 13. An annular portion 14a to be mounted and a plurality of arms 14b extending from the outer periphery of the annular portion 14a and disposed on the outer periphery of the disc spring 12 are configured.

  In the case of this embodiment, six arms 14b are provided radially at equal intervals in the circumferential direction from the outer periphery of the annular portion 14a, and are arranged on the outer periphery of the disc spring 12 as a spring member. It is opposed to the outer periphery of 12 through a gap, and the displacement in the radial direction of the disc spring 12 is suppressed. Since the disc spring 12 is assembled to the tip 5a of the piston rod 5, the outer diameter changes when the deflection amount changes, and the outer diameter becomes maximum when the disc spring 12 is completely crushed and flattened. Is opposed to the outer periphery of the disc spring 12 through a gap that does not interfere with this maximum deflection.

  An annular shim 15 having an outer diameter equal to or larger than the outer diameter of the disc spring 12 is interposed between the disc spring 12 and the annular portion 14a of the aligning member 14. The shim 15 is a guide member. 11 is slidably mounted on the outer periphery of 11 and is movable together with the main valve 13 in the axial direction which is up and down in FIG. The shim 15 is interposed between the disc spring 12 and the aligning member 14 in order to adjust the initial deflection amount of the disc spring 12. The shim 15 can be replaced with a shim 15 having a different thickness or a different thickness. By doing so, the initial deflection amount of the disc spring 12 can be adjusted. That is, by increasing the thickness of the shim 15 or increasing the number of interposed members, the initial deflection amount of the disc spring 12 can be increased, and the urging force for urging the main valve 13 can be increased. The initial deflection amount of the disc spring 12 can be reduced by reducing the thickness of 15 or the number of interposed members, and the urging force for urging the main valve 13 can be reduced. Note that the alignment of the alignment member 14 and the shim 15 can be exchanged.

  The initial deflection amount of the disc spring 12 can be adjusted by the axial length of the guide member 11, the axial length of the main valve 13, and the number of intervening sheets, but the number of shims 15 having a certain thickness can be adjusted. Adjusting the initial deflection amount of the disc spring 12 unifies the dimensions of each member, which is advantageous in terms of component management and manufacturing costs. When the aligning member 14 slides in the axial direction with respect to the guide member 11 together with the main valve 13, the disc spring 12 changes the amount of bending. At that time, the outer diameter expands and contracts, and the outer periphery is disc spring. The alignment member 14 can be protected by interposing a high-hardness shim 15.

  In the inner circumference of the disc spring 12, an operation is performed so that the contact surface of the member in contact with the disc spring 12 is turned by the change in the deflection amount. An annular high hardness washer 16 is interposed between the upper end and the piston nut 6, and the washer 16 protects the piston nut 6 from turning of the inner periphery of the disc spring 12. If it is not necessary to protect the alignment member 14 and the piston nut 6 or adjust the initial deflection amount of the disc spring 12, the shim 15 and the washer 16 can be omitted. Further, if a high hardness material is used for the aligning member 14, the shim 15 can be omitted. In the present embodiment, the two disc springs 12 are stacked and used, but the number of stacked layers can be arbitrarily changed according to the characteristics of the desired damping force.

  When the valve structure as described above is actually assembled, as shown in FIG. 3, as in the prior art, the piston 1, the orifice forming member 10, the guide member 11, the main valve 13, After assembling each member constituting the valve of the aligning member 14, the annular shim 15, the disc spring 12 and the washer 16 to the holding needle W at one end, the above-mentioned members are removed from the holding needle W and the piston rod 5 Assemble to the tip 5a.

  When assembling each member constituting the valve to the holding needle W, or when removing each member from the holding needle W and transferring it to the tip 5a of the piston rod 5, it is mounted on the outer periphery of the guide member 11. When the power disc spring 12 is properly attached to the guide member 11, the disc spring 12 is accommodated inside the alignment member 14. That is, all the arms 14 b are in a state of wrapping the disc spring 12 facing the outer periphery of the disc spring 12. In this state, even if the disc spring 12 comes out of the guide member 11 and rides its inner circumference onto the upper end of the guide member 11, the outer circumference of the disc spring 12 interferes with the arm 14 b, and the guide member 11 of the disc spring 12. Thus, the displacement of the disc spring 12 disposed inside the alignment member 14 in the radial direction is suppressed. That is, each of the arms 14b does not interfere with the outer diameter expansion due to the bending of the disc spring 12, but the arm 14b does not move against a radial displacement that the disc spring 12 rides on the guide member 11. It interferes with the outer periphery of the disc spring 12 and suppresses the positional displacement in the radial direction with respect to the guide member 11. In this way, each arm 14b is intended for alignment of the disc spring 12 as a spring member, so it is sufficient that three or more arms 14b are provided if they are provided at equal intervals in the circumferential direction.

  The arm 14b may be integrated with the main valve 13. In other words, a plurality of arms 14b may be provided on the outer periphery of the upper end in FIG. In addition, a cylinder facing the outer periphery of the disc spring 12 instead of the arm 14b may be provided on the outer periphery of the annular portion 14a of the aligning member 14 so as to suppress the displacement of the disc spring 12 in the radial direction. The cylinder may be integrated with the main valve 13. Thus, integrating the aligning member 14 with the main valve 13 has an advantage that the number of parts can be reduced and the increase in cost can be suppressed low.

  Thus, in the valve structure of the present embodiment, if the disc spring 12 as the spring member is properly mounted on the outer periphery of the guide member 11, the radial position of the disc spring 12 as the spring member is adjusted by the aligning member 14. Since the displacement is suppressed, the inner circumference of the disc spring 12 does not run on the end of the guide member 11, and it is easy to assemble each member constituting the valve to the tip 5a of the piston rod 5 as a shaft member, The assembly of the valve structure is improved.

  Further, when the disc spring 12 rides on the end of the guide member 11, the disc spring 12 is not accommodated in the aligning member 14, and is protruded outward from the aligning member 14. Assembly failure can be visually recognized before the piston nut 6 is tightened.

  In the case of this embodiment, the length from the lower end of the main valve 13 to the upper end of the disc spring 12 in a state where the main valve 13, the aligning member 14, the shim 15 and the unloaded disc spring 12 are laminated, that is, The axial length on the inner peripheral side in the state in which these members are laminated is set to be about half the inner peripheral thickness of the disc spring 12 than the axial length of the guide member 11. Is fixed to the tip 5 a of the piston rod 5, the disc spring 12 is pressed against the piston nut 6 via the washer 16, and the disc spring 12 is given an initial deflection and is compressed to energize the main valve 13. Demonstrate power.

  Next, the operation of the valve structure in the embodiment will be described. As described above, when the piston 1 moves downward in FIG. 1 with respect to the cylinder 40, the pressure in the other chamber 42 increases, and the other chamber 42 increases. The hydraulic fluid inside passes through the port 2 and tries to move into the one chamber 41.

  When the piston speed, which is the expansion / contraction speed of the shock absorber, is in the low speed region, the main valve 13 cannot bend the outer periphery against the urging force of the disc spring 12 with the pressure received from the port 2, and the orifice forming member The oil 10 passes through the orifice formed by the notch 10a provided in the orifice forming member 10 seated on the valve seat 1c, while the port 2 is kept closed while being seated on the valve seat. To do.

  Therefore, the damping characteristic (relationship of the damping force to the piston speed) at this time is as shown in FIG. 4, and the damping coefficient is relatively large in this low speed region.

  On the other hand, when the speed of the piston 1 reaches the middle to high speed region, the difference between the pressure in the other chamber 42 and the pressure in the one chamber 41 becomes large, and the force for pushing down the main valve 13 of the hydraulic oil upward in FIG. Thus, the force overcomes the urging force of the disc spring 12, the main valve 13 moves backward from the piston 1, the orifice forming member 10 is bent, and the port 2 is greatly opened. Thus, when the main valve 13 is retracted from the piston 1 as a valve disk, a gap is generated between the valve seat 1c and the orifice forming member 10, and the port 2 is greatly opened. The gap is proportional to the piston speed. And get bigger. That is, the damping characteristic when the piston speed is in the medium-high speed region is as shown in FIG. 4, which is proportional to the increase in piston speed, but the damping coefficient is smaller than the low speed region, and the slope of the damping characteristic is small. Become.

  Therefore, in the valve structure according to the embodiment, the disc forming spring 10 is used instead of the coil spring to bias the orifice forming member 10, and the axial length can be shorter than that of the coil spring. Since the amount of bending of the forming member 10 can be ensured, the damping coefficient when the piston speed is in the medium to high speed region can be reduced, and there is no possibility that the riding comfort in the vehicle will be impaired.

  In the valve structure according to the present embodiment, if the disc spring 12 as the spring member is properly mounted on the outer periphery of the guide member 11, the alignment member 14 causes the disc spring 12 as the spring member in the radial direction. Since the displacement is suppressed, the inner circumference of the disc spring 12 does not run on the end of the guide member 11, and the members constituting the valve can be easily assembled to the tip 5a of the piston rod 5 as a shaft member. Assembling property of the valve structure is improved. Further, when the disc spring 12 rides on the end of the guide member 11, the disc spring 12 is not accommodated in the aligning member 14, and is protruded outward from the aligning member 14. Before tightening the piston nut 6, it is possible to visually recognize the assembly failure, and it is possible to prevent the assembly failure.

  Note that, as described above, the inner diameter of the orifice forming member 10 is set to be smaller than the outer diameter of the guide member 11, and is sandwiched between the guide member 11 and the piston 1, and the piston rod 5 whose inner periphery is a shaft member. Although the orifice forming member 10 is slidably mounted on the outer periphery of the guide member 11 when the port 2 is opened, the orifice forming member 10 together with the main valve 13 is removed from the piston 1. You may make it reverse.

  Further, as shown in FIG. 5, the axial length of the guide member 11 is set to be at least larger than the axial length from the main valve 13 mounted on the outer periphery of the guide member 11 to the disc spring 12 as a spring member. May be. That is, in this case, the axial length of the guide member 11 is not less than the axial length (vertical length in FIG. 5) to the main valve 13, the alignment member 14, the shim 15 and the unloaded disc spring 12. May be set. In the case of this embodiment, the washer 16 is also mounted on the outer periphery of the guide member 11 and stacked on the side opposite to the valve disc of the disc spring 12, so that the guide is determined from the axial length from the main valve 13 to the washer 16. The axial length of the member 11 is set to be long.

  In addition to the setting of the length of the guide member 11, the tip of the guide member 11 serving as the upper end in FIG. 5 is inserted into the lower end in FIG. A recess 6a that abuts the member 11 and a spring receiving portion 6b that presses the disc spring 12 and compresses the disc spring 12 on the outer peripheral side from the recess 6a are provided.

  By doing so, when assembling from the holding needle W to the tip 5 a of the piston rod 5, the main valve 13, the aligning member 14, and the disc spring 12 mounted on the outer periphery of the guide member 11 come off from the guide member 11. There is no worry and the assembly becomes even easier. In this embodiment, the shim 15 and the washer 16 are also guided by the guide member 11 when assembled from the holding needle W to the tip 5a of the piston rod 5 in the same manner as the main valve 13, the alignment member 14 and the disc spring 12. There is no worry of getting out of it.

  Even if the axial length of the guide member 11 is set longer than the axial length from the upper end to the lower end of each member mounted on the outer periphery of the guide member 11 as described above, the recess 6a and the spring are provided in the piston nut 6. Since the receiving portion 6b is provided, the bottom surface of the concave portion 6a is brought into contact with the opposite end of the guide member 11 on the side opposite to the valve disc, and the members constituting the valve structure by the piston nut 6 and the step portion 5b of the piston rod 5 are provided. Since the disc spring 12 can be pressed and compressed by the spring receiving portion 6b when the guide member 11 is inserted into the concave portion 6a, the valve structure is shown in FIG. Attenuation characteristics of travel can be realized.

  In the present embodiment, in order to explain the change of the damping characteristic, the piston speed is provided with the sections of low speed and medium speed, but the speed of the boundary between these sections can be set arbitrarily. it can.

  In addition to the disc spring 12, the spring member may be an elastic body such as a wave washer or rubber, and the shaft member is the tip 5a of the piston rod 5 as described above. It is good also as a structure provided in a valve disc.

  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. Thus, the effects of the present invention are not lost.

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

The present invention is applicable to a valve such as a shock absorber.

1 Valve Piston 1a Piston Bottom 1b Piston Insertion Hole 1c Piston Valve Seat 1d Piston Pressure Side Port 1e Piston Tube 2 Port 3 Window 5 Piston Rod 5a Shaft Member 5b Piston Rod Step 5c Screw part 6 in piston rod 10 Piston nut 10 Orifice forming member 10a Notch 11 Guide member 12 Belleville spring 13 as spring member Main valve 14 Alignment member 14a Annular part 14b in alignment member Arm 15 in alignment member Shim 16 Washer 20 Check Valve 20a Hole 21 in check valve Spacer 22 Valve stopper 40 Cylinder 41 One chamber 42 Other chamber

Claims (5)

A valve disk in which a port is formed, a shaft member rising from the axial center of the valve disk, an annular guide member mounted on the outer periphery of the shaft member, and slidably mounted on the outer periphery of the guide member In a valve structure including an annular main valve that opens and closes a port and an annular spring member that is attached to the outer periphery of the guide member and biases the main valve toward the valve disc, the valve structure faces the outer periphery of the spring member. A valve structure comprising a centering member that suppresses displacement of a spring member in a radial direction. The aligning member includes a plurality of arms disposed on the same circumference and facing the outer periphery of the spring member, and the arms suppress radial displacement of the spring member according to claim 1. The valve structure described. The valve structure according to claim 1 or 2, wherein the aligning member is integrated with the main valve. The axial length of the guide member is set to at least the axial length from the main valve mounted on the outer periphery of the guide member to the spring member, and the guide member is screwed into the shaft member in cooperation with the shaft member. A nut member is provided for clamping, and the nut member includes a recess in which the tip of the guide member is inserted and abutted against the guide member, and a spring receiving portion that is on the outer peripheral side from the recess and presses the spring member to compress the spring member. The valve structure according to any one of claims 1 to 3, further comprising: 6. The valve structure according to claim 1, wherein an orifice forming member having a notch for forming an orifice on an outer periphery is interposed between the main valve and the valve disk.

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