JP2015072052A - Hydraulic damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic damper which can change an elongation/contraction speed of the hydraulic damper in an elongation-side stroke according to a speed at which a piston operates.SOLUTION: A hydraulic damper comprises a cylinder mechanism Z which is composed of a piston member 80 located between a piston 40 and a partitioning member 60, and a cylinder member 70 in which the piston member 80 advances to and retreats from an opening part. The pressure of an oil pressure chamber L in the cylinder member 70 is controlled by making the piston member 80 relatively advance and retreat to/from the cylinder member 70 on the basis of the motion of the piston 40, a brake member 73 which imparts a brake force while abutting on a piston rod 15 is arranged, and the brake force is imparted to the piston 40 at elongation by making the brake member 73 deform and contact with the piston rod 15 in a direction of the piston rod on the basis of the pressure of the oil pressure chamber L.

Description

  The present invention relates to a hydraulic shock absorber, and more particularly to a hydraulic shock absorber capable of obtaining a damping force corresponding to an extension speed.

  Conventionally, in a hydraulic shock absorber such as a front fork or a rear cushion of a motorcycle, as shown in Patent Document 1, the extension speed when shifting from the compression side stroke to the extension side stroke is decelerated by the urging force of the suspension spring, and in the extension direction The urging force is received by a rebound spring.

JP 2012-92944 A

  However, since the load received by the rebound spring is constant regardless of the extension speed of the front fork during traveling, there is a problem that steering stability is deteriorated in a certain extension speed region. For example, the front fork compressed by braking before entering the corner shifts from the compression side stroke to the extension side stroke when the brake is released after entering the corner. However, since the extension speed of the front fork at this time is not constant depending on the situation at the time of traveling, it has been considered that instability in steering stability may occur.

  The present invention has been made in view of these problems, and an object of the present invention is to provide a hydraulic shock absorber capable of changing the extension speed of the hydraulic shock absorber in the extension stroke according to the speed at which the piston operates. .

  As a configuration of the hydraulic shock absorber for solving the above-described problems, a telescopic cylinder made of a slidable inner and outer cylinder, a partition member that partitions the inside of the telescopic cylinder into a spring chamber and a hydraulic oil chamber, and the hydraulic oil chamber side And a piston rod extending along the central axis of the cylinder from the cap side of the telescopic cylinder, attached to the piston rod, and sliding in the cylinder corresponding to the expansion and contraction of the telescopic cylinder A hydraulic shock absorber provided with a piston is provided with a cylinder mechanism that is located between the piston and the partition member and includes a piston member and a cylinder member in which the piston member advances and retreats from an opening. The piston member is moved forward and backward relative to the cylinder member to control the pressure of the oil pressure chamber in the cylinder member. Since a braking member that applies a braking force in contact with the rod is provided and this braking member is deformed and contacted in the direction of the piston rod based on the pressure of the oil pressure chamber, the braking force is applied to the piston when extended. Since the expansion / contraction speed of the telescopic cylinder changes according to the speed at which the piston operates, the steering stability during traveling can be improved.

  Further, as another configuration of the hydraulic shock absorber according to the present invention, the piston member is provided on the partition member side of the piston, and the cylinder member is supported by an elastic support portion attached to the partition member side. The upward movement of the cylinder member when moving toward the cylinder member can be restricted.

  As another configuration of the hydraulic shock absorber according to the present invention, the braking member is formed in a cylindrical shape surrounding the outer periphery of the piston rod, and the cylinder member is a ring-shaped base material surrounding the outer periphery of the piston rod. Formed from a cylindrical cylinder body that protrudes further, a ring-shaped recess for accommodating the braking member is formed on the inner peripheral side of the base material, and communicates with the oil pressure chamber of the cylinder member on the bottom surface side of the recess. A hydraulic chamber is provided, and the pressure from the oil pressure chamber side is guided to the hydraulic chamber by the operation of the piston, and the pressure of the hydraulic chamber is applied to the outer periphery of the brake member to bend the brake member in the piston rod direction. However, since the contact is made, a large braking force can be applied to the piston rod in a well-balanced manner.

  As another configuration of the hydraulic shock absorber according to the present invention, the axial dimension of the hydraulic chamber is set to be shorter than the axial length of the braking member, so that the axial center of the braking member may be bent. it can.

  Further, as another configuration of the hydraulic shock absorber according to the present invention, an oil passage that guides the pressure from the oil pressure chamber side to the hydraulic chamber is formed in the base material. Can be the same pressure as the pressure.

  Further, as another configuration of the hydraulic shock absorber according to the present invention, the outer periphery of the piston member in the hydraulic shock absorber is shorter than the piston member in the axial direction and is a collar that moves up and down within a certain range, and a gap is formed. When the piston member enters the cylinder member, the lower end of the collar is pressed in close contact with the piston member, and when the piston member leaves, the lower end of the collar is the piston. Since the member leaves the member in a separated state, the hydraulic oil is prevented from flowing into the hydraulic chamber between the lower end of the collar and the piston member and through the gap, and the pressure of the oil pressure chamber is suppressed to a negative pressure state. It is possible to prevent the operation from being delayed when the member smoothly slips out of the cylinder member and the telescopic cylinder shifts from the extension side stroke to the compression side stroke.

  Further, as another configuration of the hydraulic shock absorber according to the present invention, since the collar retaining means is provided at a position away from the upper end of the collar on the tip side of the piston member, the collar is fixed on the outer periphery of the piston member. It can be moved up and down within the range.

  As another configuration of the hydraulic shock absorber according to the present invention, the retaining means includes a fastener that has a length that does not contact the inner periphery of the cylinder member and protrudes from the piston member. The hydraulic oil can be distributed outside.

It is sectional drawing of the hydraulic shock absorber provided with the expansion-contraction cylinder. It is an enlarged view of a cylinder mechanism. It is an enlarged view of a damping force generator. It is an operation | movement figure of the cylinder mechanism in an extension side stroke. It is a figure which shows the other form of a hydraulic shock absorber. It is an operation | movement figure of the other form of a hydraulic shock absorber.

  FIG. 1 is a cross-sectional view showing an embodiment of a hydraulic shock absorber according to the present invention. As shown in the figure, a front fork 10 as a telescopic cylinder of a hydraulic shock absorber has an outer tube 11 having a lower opening on the vehicle body side, and is slidable by being fitted into the outer tube 11 on an axle side. And an inverted front fork. The lower and upper bearings 12A and 12B, which are spaced apart in the axial direction, are attached to the inner circumference of the large-diameter outer tube 11, and the outer circumference of the inner tube 12 is slidable by the bearings 12A and 12B. Provided. A suspension spring 14 for urging the outer tube 11 and the inner tube 12 in the direction of separating in the vertical direction is attached to the inner periphery of the inner tube 12.

  A cap 13 for sealing the upper end opening is screwed to the outer tube 11. The cap 13 includes a base nut 24 whose outer periphery is screwed in an airtight manner with the inner periphery of the outer tube 11, and an adjustment bolt 21 is interposed in an airtight state in a hole 24 </ b> A provided on the center side of the base nut 24. The The adjusting bolt 21 is rotatably attached to the base nut 24 by holding means (not shown) so as not to move up and down with respect to the base nut 24. The adjustment bolt 21 includes a small-diameter cylindrical portion 21A that extends in the central axis direction of the inner tube 12 at the lower portion. The hollow portion 21B of the small-diameter cylindrical portion 21A is provided with an air vent hole 21C that communicates with the hollow portion 21B and the inner space above the outer tube 11. A sealing screw 22 for blocking communication between the outer tube 11 and the outside is detachably attached to the upper end side of the hollow portion 21B. By removing the sealing screw 22 from the adjusting bolt 21, the internal pressure of the outer tube 11 can be set to atmospheric pressure. A screw that is screwed to the inner periphery of the upper end of the lifting nut 23 is formed on the outer periphery of the tip of the small diameter cylindrical portion 21A, and the lifting nut 23 can be moved up and down by turning the small diameter cylindrical portion 21A in the left-right direction.

  The elevating nut 23 includes a flange-shaped upper spring receiving portion 25 on the outer periphery of which the upper end of the suspension spring 14 is seated. Accordingly, the lifting nut 23 rotates the adjustment bolt 21 to move the lifting nut 23 up and down with respect to the adjustment bolt 21. The urging force of the suspension spring 14 can be adjusted by raising and lowering the upper spring receiving portion 25 in the axial direction.

The inner side of the elevating nut 23 is partitioned up and down by a partition 23A, and the inner periphery on the lower side is threaded, and the threaded portion on the outer periphery on the upper end side of the piston rod 15 is screwed therein.
The piston rod 15 is formed of a small-diameter cylindrical rod, extends along the central axis of the cylinder tube 51 in the inner tube 12, the lower end side slidably penetrates the central side of the partition member 60, and the piston 40 at the lower end. Are screwed together.

The piston 40 is slidably provided inside the cylinder tube 51. The piston rod 15 projects in the direction of the outer tube 11 from the axle holder 50 side. Reference numeral 70 denotes a cylinder member having a cylinder body 71 commonly called an oil lock collar, and the piston member 80 constitutes a cylinder mechanism Z. The above-described cylindrical piston member 80 (oil lock piece) surrounding the outer periphery of the piston rod 15 is formed on the piston 40, and the piston member 80 is formed by a ring-shaped base material 70 m constituting the cylinder member 70. The pressure in the oil pressure chamber L formed in the cylinder body 71 of the cylinder member 70 can be increased or decreased by moving forward and backward from the lower end opening of the cylindrical cylinder body 71 protruding downward.
As shown in FIG. 2, the base material 70 m has a trapezoidal outer diameter, has seal grooves 77 having seal members 76 on the upper and lower sides of the inner periphery, and a ring-shaped recess 74 between the upper and lower seal members 76. The braking member 73 positioned on the outer peripheral side of the piston rod 15 is accommodated in the recess 74. The braking member 73 is made of a resin such as fluorine resin (for example, Teflon (registered trademark)), or a flexible member such as rubber or synthetic rubber. A hydraulic chamber 75 that is narrower (shorter) than the vertical length of the braking member 73 is formed on the bottom surface side of the recess 74, and the hydraulic chamber 75 is an oil pressure chamber between the cylinder member 70 and the piston member 80. The other end of an oil passage 78 having one end communicating with L is connected to L. The cylinder member 70 has a spring receiving portion 79, and the upper end of the spring receiving portion 79 is attached to the lower end of a rebound spring 64 as an elastic support portion attached to the lower end of the partition member 60. Thereby, the cylinder member 70 receives a downward pressing force. The oil pressure chamber L is formed so as to be separated from the outer periphery of the piston rod 15 by a length that exceeds the inner circumference of the cylinder body 71 substantially by the thickness of the piston member 80.
Therefore, when the piston 40 moves upward and the piston member 80 constituting the cylinder mechanism Z enters the cylinder main body 71 of the cylinder member 70 at the time of extension, the pressure of the oil pressure chamber L rises. This is transmitted to the hydraulic chamber 75 via the oil passage 78, and the center side of the braking member 73 is bent in the outer peripheral direction of the piston rod 15, so that the upward movement of the piston 40 can be braked. The seal member 76 fitted in the upper and lower seal grooves 77 is made of a flexible material such as rubber such as an O-ring.
The hydraulic oil K flowing in the hydraulic chamber 75 on the back surface of the braking member 73 is sealed so as not to leak outside from the gap between the recess 74 and the braking member 73 by the above-described seal members 76;

  The rebound spring 64 receives a load when the front fork 10 is extended, and has a length corresponding to a predetermined stroke (rebound stroke) in the front fork 10 so as to restrict the movement of the cylinder member 70. Is set.

The piston 40 screwed and attached to the lower end of the piston rod 15 is formed of a cylindrical body whose inner peripheral side is vertically divided by a partition portion 40E, and a small diameter portion above the partition portion 40E is formed as a piston member 80. The piston member 80 has an upper rod mounting portion 40A that is threaded so that the outer periphery on the lower end side of the piston rod 15 is screwed on the inner periphery of the piston member 80, and the upper end side of the extension rod 16 on the outer periphery of the large-diameter cylindrical body. The lower rod attachment part 40B threaded so that the outer periphery may be screwed is provided.
As described above, the piston 40 is configured such that the small diameter portion on the upper side is the piston member 80 and the large diameter portion on the lower side is the piston main body 81.

  The piston member 80 on the upper side of the piston 40 is gradually inserted from the lower end opening of the oil pressure chamber L from the upper end side to apply pressure to the hydraulic oil K in the oil pressure chamber L in the extension side stroke. That is, the outer periphery 80 a of the piston member 80 is formed in a cylindrical shape so as to slide with a predetermined gap E with respect to the inner periphery 71 a of the cylinder member 70. The gap E is set to a clearance that allows a desired rate of increase of the hydraulic pressure in the oil pressure chamber L to be obtained. Examples of a method for setting the clearance E as the clearance include a method for obtaining an increase rate of the hydraulic pressure in accordance with the spring rate of the rebound spring 64.

Here, when the gap E is too narrow, it is difficult for the piston member 80 to enter the oil pressure chamber L when the piston member 80 moves up, and the rebound spring 64 functions from an early stage of the extension side stroke. After the rebound spring 64 functions, the piston member 80 enters the oil pressure chamber L, and the braking member 73 is pressed against the piston rod 15 with a large force, so that the extension force is suppressed.
Further, when the gap E is too wide, the piston member 80 easily enters the oil pressure chamber L, and the oil pressure chamber L gradually increases in hydraulic pressure, so that the above-described braking member 73 is pressed against the piston rod 15. The rebound spring 64 functions at a stage where the force rises slowly and the extension side stroke is slow.
Therefore, the above-mentioned gap E is set to such a dimension that the pressure of the oil pressure chamber L changes according to the position when the piston member 80 enters the oil pressure chamber L, and the action of the rebound spring 64 is suitably changed. Set to

A piston ring 40 </ b> C that maintains a liquid-tight state with the inner periphery of the cylinder tube 51 is provided on the outer periphery of the piston main body 81 below the piston 40.
The extension rod 16 attached to the piston 40 is inserted into a guide tube 52 provided in the inner tube 12 described later. The extension rod 16 has the same outer diameter as the piston rod 15, and is set to a length that does not come out of the guide tube 52 when the front fork 10 is fully extended, and does not strike the axle when the front fork 10 is contracted to the minimum.
The above-described piston rod 15 and extension rod 16 are not limited to two, and may be configured such that one piston rod penetrates the partition portion 40E. In this case, the piston 40 may be fixed to the outer periphery of the one piston rod by a fixing means (not shown) such as a C ring or an E ring.

  In FIG. 1, the inner tube 12 is formed of a cylindrical body having a predetermined length formed with a constant outer diameter from the upper end to the lower end, and the lower end is attached to the axle holder 50. The axle holder 50 includes a rectangular axle support portion 50A that supports the axle, and a cylindrical assembly portion 50B to which the inner tube 12 is assembled. The axle support portion 50A is provided with an axle through hole 50a penetrating in a direction orthogonal to the axis of the axle holder 50, and a split portion 50b is formed from the inner periphery of the axle through hole 50a toward the lower end surface of the axle holder 50. Extend. A screw hole 50c is formed in one of the cut portions 50b, and a through hole 50m is formed in the other cut portion 50b. By inserting a bolt (not shown) from the through hole 50m side into the screw hole 50c, the screw hole 50c is tightened. An axle (not shown) is clamped and fixed.

  A threaded portion 53a is formed on the outer periphery of the upper portion of the assembly portion 50B, and the inner periphery of the lower end side of the inner tube 12 is threaded. The axle holder 50 and the inner tube 12 are disposed below the threaded portion 53a. A sealing member 53b such as an O-ring that maintains a liquid-tight state is provided, and an annular abutting portion 53c that abuts the tip of the inner tube 12 to position the axle holder 50 is provided. By abutting the lower end of the inner tube 12 against the abutting portion 53c, the inner tube 12 is screwed in a liquid-tight state.

A cylinder tube fixing part 54a for fixing the cylinder tube 51 to the upper side of the inner periphery of the middle thick part of the assembly part 50B, and a guide tube fixing part 54b for fixing the guide tube 52 to the inner peripheral side of the lower thick part. Are provided concentrically.
The cylinder tube 51 is erected on the cylinder tube fixing portion 54a so as to form an annular gap e1 between the inner peripheral surface 53d of the assembly portion 50B and the outer periphery 51a of the cylinder tube 51. The lower end of the cylinder tube 51 is fixed by abutting against an annular abutting portion 54c formed in an annular shape between the cylinder tube fixing portion 54a and the guide tube fixing portion 54b. The annular abutting portion 54c is formed to be positioned below the abutting portion 53c of the axle holder 50 described above.

  The partition member 60 provided on the upper end side of the cylinder tube 51 and partitioned into the air chamber S and the hydraulic oil chamber A is composed of a base portion 60D and a cylinder portion 60C. The base portion 60D has a guide portion 60A on the inner periphery of the central hole through which the above-described piston rod 15 passes, and is a sealing portion that seals in close contact with the inner peripheral surface of the inner tube 12 in a liquid-tight state. 60B is provided on the outer periphery. The guide portion 60A is provided with a seal member 60a that allows sliding in a liquid-tight state with the outer periphery of the piston rod 15. The sealing portion 60B is provided with a seal member 60b that maintains liquid tightness with the inner periphery of the inner tube 12. The lower end of the suspension spring 14 is seated on the upper surface side of the base portion 60D.

  The cylinder part 60C of the partition member 60 is screwed with the outer periphery on the upper end side of the cylinder tube 51 on the inner periphery on the lower end side of the cylinder part 60C so that the base part 60D is raised a predetermined distance from the upper end of the cylinder tube 51. The cylinder portion 60 </ b> C is provided with a flow hole 61 that allows communication between the inner space of the cylinder tube 51 and the outer space and allows the hydraulic oil K to flow between each other. The flow hole 61 may be provided in the cylinder tube 51 as long as it is above the stroke range of the piston 40.

  A partition member 60 is attached, and an upper side of the partition member 60 is partitioned into an air chamber S having the suspension spring 14, and a lower side is partitioned into a hydraulic oil chamber A containing the hydraulic oil K. The hydraulic oil chamber A is divided into a pressure side oil chamber 127A at a lower side than the piston 40 inside the cylinder tube 51, and an extension side oil chamber 127B between the inner periphery of the inner tube 12 and the outer periphery of the cylinder tube 51. .

  In the front fork 10 as the telescopic cylinder of the present embodiment, the compression side oil chamber channel 57A is formed on the compression side oil chamber 127A side, the extension side oil chamber channel 57B is formed on the extension side oil chamber 127B side, and the air In the chamber S, a lubricating oil hole 12 a is provided that allows lubricating oil to flow into and out of the annular gap between the outer tube 11 and the inner tube 12.

  The guide tube 52 is erected on the guide tube fixing portion 54b so as to form an annular gap e2 between the inner periphery of the cylinder tube 51 and the outer periphery of the guide tube 52. The lower end of the guide tube 52 is abutted against and fixed to the lowermost bottom portion 54 d of the axle holder 50. The lowermost bottom portion 54d is formed to be positioned below the above-described annular abutting portion 54c.

A cylindrical guide collar 52 </ b> A that allows the extension rod 16 to enter the guide tube 52 is attached to the upper end side of the guide tube 52. A seal member 52a is provided on the inner periphery of the guide collar 52A so as to be slidable while maintaining a liquid-tight state with the outer periphery of the extension rod 16. The seal member 52a is made of, for example, a rubber O-ring, X-ring or the like. The outer periphery of the guide collar 52A is supported by the inner periphery of the cylinder tube 51 and is formed in a petal shape in a cross-sectional view so that the working oil K can be distributed on the outer periphery side of the guide collar 52A.
The inner peripheral side of the guide tube 52 communicates with a through hole 55 provided in the axle holder 50 so as to be released to the atmosphere. Thereby, even if the piston 40 having the piston member 80 moves in the cylinder tube 51, the volume change corresponding to the advance / retreat of the piston rod 15 to the hydraulic oil chamber A is compensated by the advance / retreat of the extension rod 16. A change in pressure in the hydraulic oil chamber A during the operation is prevented.

  The outer circumference of the axle holder 50 is provided with the pressure side oil chamber channel 57A communicating with the annular gap e2 and the extension side oil chamber channel 57B communicating with the annular gap e1. Therefore, the pressure-side oil chamber flow path 57A through which the hydraulic oil K from the above-described pressure-side oil chamber 127A flows and the expansion-side oil chamber flow path 57B through which the hydraulic oil K from the expansion-side oil chamber 127B flows are opened. A damping force generator 140 that generates a damping force is provided between the pressure side oil chamber channel 57A and the extension side oil chamber channel 57B.

  As shown in FIG. 3, the damping force generator 140 includes a cylinder Ma integrally formed with the axle holder 50 so as to protrude from the side portion of the axle holder 50 corresponding to the compression side oil chamber flow path 57 </ b> A, and an extension. Corresponding to the side oil chamber flow path 57B, the communication path Mb is formed integrally with the axle holder 50, and a damping force generation unit 140A. The cylindrical body Ma is formed with a cylindrical valve accommodating hole 114A having one end opening. The valve housing hole 114A communicates with the pressure side oil chamber flow path 57A at the bottom 114b, and is connected to the communication path Mb having the extension side oil chamber flow path 57B at the side of the opening end side opposite to the bottom 114b.

The damping force generation unit 140A includes a compression side damping force generation unit 250 that generates a damping force when the front fork 10 is compressed, an extension side damping force generation unit 260 that generates a damping force when the front fork 10 is extended, and damping during compression and extension. A damping force adjusting unit 270 that enables force adjustment is provided, and the compression side damping force generating unit 250, the extension side damping force generating unit 260, and the damping force adjusting unit 270 are small with a cylindrical valve piece 141 as a base. It is constructed by assembling.
The valve piece 141 includes a large-diameter portion 142 made of a large-diameter cylindrical body and a small-diameter portion 143 made of a small-diameter cylindrical body that projects coaxially from one end of the large-diameter portion 142. The damping force generator 250 and the extension-side damping force generator 260 are provided with the damping force adjusting unit 270 in the large-diameter hollow portion 142a of the large-diameter portion 142 and the small-diameter hollow portion 143a of the small-diameter portion 143, respectively.

The extension-side damping force generator 260 includes a disk-like extension-side flow regulating body 160 having an extension-side channel 160A and a compression-side channel 160B that regulate the flow rate in the compression-side stroke and the extension-side stroke, and the extension-side stroke. An expansion side damping valve 161 for controlling the flow rate flowing out from the expansion side flow path 160A, and a pressure side check valve 152 that closes the pressure side flow path 160B in the expansion side stroke and allows the flow of the pressure side flow path 160B in the compression side stroke, The pressure side check valve 152, the extension side flow regulating body 160, and the extension side damping valve 161 are mounted on the outer periphery of the small diameter portion 143 in order from the large diameter portion 142 side of the valve piece 141.
Between the extension-side flow restricting body 160 and the outer stepped surface 141C, a collar 163 for positioning the extension-side flow restricting body 160, and a spring 164 is provided on the outer periphery of the collar 163. One end of the spring 164 is seated on the stepped surface 141 </ b> C via the spring seat 165, and the other end is seated on the pressure-side check valve 152, thereby urging the pressure-side check valve 152 toward the expansion-side flow regulating body 160. A shim 166 having a predetermined thickness is provided adjacent to the expansion side damping valve 161, and a center plate 145 is provided adjacent to the shim 166.

The center plate 145 is an annular member that is inserted on the outer periphery of the small diameter portion 143. The center plate 145 has an annular recess 145A that is recessed in the outer diameter direction at the center portion in the thickness direction of the inner periphery, and a plurality that communicates from the annular recess 145A to the outer periphery. Channel passage hole 145B. The center plate 145 is assembled such that the inner circumferential annular recess 145A surrounds the plurality of flow path holes 143A formed in the small diameter portion 143. This assembly position is adjusted by a shim 166, for example.
On the outside of the center plate 145, a compression-side damping force generation unit 250 is provided on the center plate 145 via a shim 167 having a predetermined thickness.

  The compression-side damping force generation unit 250 includes a disk-shaped compression-side flow regulating body 150 having a compression-side flow path 150A and an expansion-side flow path 150B that regulate the flow rate in the compression-side stroke and the expansion-side stroke, and the pressure-side flow path in the compression-side stroke. A compression-side damping valve 151 that controls the flow rate flowing out from 150A, and an expansion-side check valve 162 that blocks the flow of the expansion-side channel 150B in the compression-side stroke and allows the flow of the expansion-side channel 150B in the expansion-side stroke, In order from the center plate 145 side, a pressure side damping valve 151, a pressure side flow regulating body 150, and an extension side check valve 162 are mounted. Further, the small diameter portion 143 is provided with a collar 153 for positioning the pressure side flow regulating body 150, a spring 154 for biasing the extension side check valve 162, and a spring seat 155 on which the spring 154 is seated until the collar 153 comes into contact. The nut 200 is fastened to the screw part 143C, and the compression side damping force generation part 250 and the extension side damping force generation part 260 are integrally assembled on the outer peripheral side of the valve piece 141.

The damping force adjusting unit 270 is inserted into the needle hole 143B constituting the needle valve mechanism in the small-diameter hollow portion 143a of the small-diameter portion 143, and the bypass channel 141A from the large-diameter portion 142 side, and the opening 144A of the needle hole 143B. A needle shaft 272 that adjusts a gap n1 between the opening 144B of the bypass flow channel 141A and the needle shaft 272, and a needle shaft 272 that surrounds the outer periphery of the needle shaft 272. The flow rate adjusting means 273 includes a flow rate adjusting body 279 that adjusts the inflow amount of the hydraulic oil K flowing into the bypass channel 141A from the gap n2 on the rear end side of the needle shaft 272.
The bypass passage 141A configured by the valve piece 141 includes a large-diameter hollow portion 142a that houses the flow rate adjusting body 279, a small-diameter hollow portion 143a that extends on the same axis as the large-diameter hollow portion 142a side, and a small-diameter hollow portion 143a. It consists of a needle hole 143B extending from the tip of the hollow portion 143a to the same axis.

  The damping force generation unit 140A that is assembled as described above is accommodated with the nut 200 facing the bottom 114b in the axial direction of the valve accommodation hole 114A. When the damping force generating unit 140A is housed in the valve housing hole 114A, the seal member 160C; 150C provided on the outer periphery of the extension side flow restricting body 160 and the outer periphery of the pressure side flow restricting body 150 is inside the valve housing hole 114A. In close contact with the circumference, the pressure-side flow regulating body 150 and the pressure-side oil chamber flow path 57A side communicate with the pressure-side oil chamber 127A, and the pressure-sharing common flow path 146A and the extension-side flow restriction body 160 and the extension in the valve housing hole 114A. An annular space around the center plate 145 defined by a pressure expansion common flow channel 146B communicating with the pressure side oil chamber 127A, a pressure side flow restriction body 150, and an extension side flow restriction body 160, with the space on the side oil chamber flow path 57B side. Is formed as an intermediate chamber 149. An oil reservoir chamber 132 (reservoir chamber) communicates with the intermediate chamber 149 through an oil reservoir chamber flow path 114B. The oil reservoir chamber 132 is provided with a pressurizing chamber 132A defined by a free piston 133 on the opposite side, and is pressurized by a gas sealed in the pressurizing chamber 132A. Gas is sealed in the pressurizing chamber 132A at a predetermined pressure through a valve (not shown), and the volume change accompanying the temperature change of the hydraulic oil K is absorbed by the displacement of the free piston 133, so that the outside air temperature and the front fork are absorbed. A stable damping force can be obtained without depending on the temperature rise of the hydraulic oil K caused by the operation 10.

  4A to 4D are views showing the operation of the front fork 10 in the extension side stroke. Hereinafter, the operation of the oil lock mechanism in the extension stroke will be described with reference to FIG. In addition, the meter display of P0-P3 shown below each figure shows the state with respect to the hydraulic pressure in the oil pressure chamber L of Fig.4 (a) thru | or (d).

[Stretching process]
FIG. 4A shows a state where the piston 40 has completed the compression stroke. When the compression side stroke is completed, the front fork 10 is extended by the urging force of the suspension spring 14 when the front side fork 10 extends to the extension side stroke, and the piston 40 interlocked with the outer tube 11 is connected to the cylinder tube. Move upward in 51.
At this time, the piston 40 pressurizes the hydraulic oil K in the extension side oil chamber 127B, and the pressurized hydraulic oil K in the extension side oil chamber 127B flows from the extension side oil chamber 127B into the extension side oil chamber flow path. Via 57B, the damping force generator 140 moves to the pressure side oil chamber 127A via the pressure side oil chamber flow path 57A while generating a damping force in the extension side stroke by the function of the damping force generator 140.

  Here, as shown in FIG. 4B, when the upper end side of the piston member 80 above the piston 40 enters the oil pressure chamber L so as to close the opening of the oil pressure chamber L of the cylinder member 70, the oil pressure chamber L The pressure of the hydraulic oil K inside is slightly higher than the pressure of the hydraulic oil K in the extension side oil chamber 127B.

Next, as shown in FIG. 4C, when the extension side stroke of the front fork 10 is continued and the piston member 80 further enters the oil pressure chamber L of the cylinder member 70, the pressure in the oil pressure chamber L is increased. Will rise further. At this time, an upward force from the piston member 80 of the piston 40 through the hydraulic oil K in the oil pressure chamber L, a downward biasing force by the rebound spring 64, and an oil path from the oil pressure chamber L to the cylinder member 70. 78 flows into the hydraulic chamber 75 through 78, the back surface of the braking member 73 is pressed by the pressurized pressure of the oil pressure chamber L, the braking member 73 bends inwardly, presses against the outer periphery of the piston rod 15, and friction force Will act.
When the pressure in the oil pressure chamber L pressurized by the rise of the piston 40 exceeds the urging force of the rebound spring 64, the cylinder member 70 moves upward while pushing and contracting the rebound spring 64, while the oil pressure chamber L This is decelerated by the frictional force of the braking member 73 that is bent and pressed in the direction of the piston rod 15 by the hydraulic pressure. That is, the urging force of the rebound spring 64 and the frictional force of the braking member 73 pressed against the piston rod 15 by the pressure of the oil pressure chamber L are balanced against the upward force of the piston 40.
Therefore, the speed at which the cylinder member 70 moves upward changes according to the speed at which the piston member 80 that rises together with the piston 40 enters the oil pressure chamber L.

  Further, as shown in FIG. 4D, when the extension side stroke of the front fork 10 continues and the piston member 80 completely enters the oil pressure chamber L, the rebound spring is moved together with the moving speed of the piston 40. 64 is compressed, and the extension speed is reduced by the urging force of the rebound spring 64. At this time, the extension speed of the front fork 10 is decelerated at a constant speed by the spring constant of the rebound spring 64.

  As described above, the piston member 80 of the cylinder mechanism Z that moves together with the piston 40 is provided and is configured to enter the cylinder member 70, so that the oil pressure depends on the moving speed of the piston 40 as the front fork 10 extends. Since the pressure of the chamber L changes, when the moving speed of the piston 40 is fast, the braking member 73 is pressed against the piston rod 15 with a strong force by the large pressure of the oil pressure chamber L that has rapidly increased, and the moving speed of the piston 40 is increased. A braking force that suddenly decelerates acts. When the moving speed of the piston 40 is slow, the braking member 73 is pressed against the outer periphery of the piston rod 15 by the pressure of the oil pressure chamber L that slowly rises, and the moving speed of the piston 40 is slowly decelerated. Since it changes to the extension speed according to the moving speed of piston 40, steering stability can be improved.

  In the present invention, the cylinder member 70 may be provided on the piston 40 side, the piston member 80 may be provided on the rebound spring 64 side, and the positions thereof may be switched.

Embodiment 2
In the present embodiment, the problem of the first embodiment is solved. That is, in the first embodiment, as shown in FIG. 4 (d), there is a problem that it is difficult for the piston member 80 to come out of the cylinder member 70 when the piston member 80 enters the oil pressure chamber L. Therefore, in the second embodiment, as shown in FIGS. 5 and 6, a collar 84 having a shorter length than the piston member 80 is provided on the outer periphery of the piston member 80 with a gap F. A fastener 85 as a retaining means is provided above the front end of the outer periphery.
That is, in FIG. 5 and FIG. 6, the piston member 80 is in contact with the tip of the cylindrical collar 84 that is movable in the axial direction with respect to the outer periphery, so that the collar 84 does not come out of the piston member 80. A fastener 85 is provided as a retaining means for preventing the above.

In addition, the cylindrical piston member 80 is formed in the center side of the upper end of the piston 40, and the upper end of the piston 40 is formed as the level | step difference surface 40F as a plane. In this case, a gap E is formed between the inner circumference 71 a of the cylinder body 71 and the outer circumference of the collar 84, and a gap F is formed between the inner circumference of the collar 84 and the outer circumference of the piston member 80. That is, the collar 84 has an inner diameter that is larger than the outer diameter of the piston member 80, and an annular shape that allows the working oil to flow between the outer periphery of the piston member 80 and the inner periphery of the collar 84. The gap F is formed. The collar 84 is set shorter than the length of the piston member 80 so that the upper end side of the piston member 80 protrudes when inserted into the piston member 80.
A fastener 85 as a retaining means is provided at a position where the collar 84 has a predetermined play in the axial direction in the outer peripheral portion protruding from the collar 84 of the piston member 80. Therefore, the collar 84 is configured to be movable up and down between the step surface 40F and the fastener 85 as a retaining means, and a check valve function is configured between the step surface 40F as a flat surface.
The fastener 85 includes, for example, a cutout that allows the working oil to flow through a part of the outer periphery such as a C ring and an E ring, and a petal that allows the working oil to flow between the outer periphery of the oil lock body. An annular member having an outer shape is applied.

In the second embodiment, first, as shown in FIG. 6A, the collar 84 is in a state in which the lower end of the collar 84 is abutted against the step surface 40F by the resistance of the hydraulic oil in the oil pressure chamber L in the extension side stroke. Thus, the piston member 80 enters the oil pressure chamber L. Therefore, the hydraulic oil in the oil pressure chamber L does not flow out to the expansion side oil chamber 127B via the annular gap F between the outer periphery of the piston member 80 and the inner periphery of the collar 84, and the inner periphery of the oil pressure chamber L. It flows out only from an annular gap E as a clearance between 71a and the outer periphery of the collar 84.
Next, when the piston 40 descends and shifts from the extension stroke to the compression stroke, that is, when the piston member 80 is retracted, the piston 40 operates as shown in FIG.
That is, when the piston member 80 is withdrawn from the oil pressure chamber L, the collar 84 has an annular gap F, so that it does not follow the piston member 80 that descends with the piston 40, and the piston member 80 descends for a certain distance. In addition, the tip of the collar 84 is locked to the fastener 85 and starts to descend.
At this time, since the oil pressure chamber L is more negative than the pressure in the expansion side oil chamber 127B, the play amount in the vertical direction generated between the step surface 40F and the lower end of the collar 84 is indicated by an arrow in the figure. The hydraulic oil flows into the oil pressure chamber L from the extension side oil chamber 127B through the gap of the ring, the annular gap F, and the portion of the fastener 85 through which the hydraulic oil can flow, and the oil pressure chamber L and the extension side oil chamber The pressure with 127B becomes the same pressure. As a result, the piston member 80 is easily retracted from the oil pressure chamber L, and the transition from the extension side stroke to the pressure side stroke is smoothly performed without resistance.

Embodiment 3
Moreover, in the said Embodiment 1 and Embodiment 2, although the piston member 80 demonstrated with the form comprised integrally with the piston 40, you may comprise separately from the piston 40. FIG. In this case, it is important that the piston member 80 is fixed to the piston rod 15 in a stationary manner.

Embodiment 4
Further, a second rebound spring may be provided between the lower surface of the spring receiving portion 79 of the cylinder member 70 and the piston main body 81 of the piston 40. By comprising in this way, the pressure receiving stroke which receives a load at the time of an extension side process can fully be ensured.

10 front fork, 11 outer tube, 12 inner tube,
14 suspension springs, 15 piston rods, 40 pistons,
51 cylinder tube, 60 partition member, 70 cylinder member,
73 braking member, 78 oil passage, 80 piston member,
K hydraulic oil, L oil pressure chamber.

Claims (8)

A telescopic cylinder made of slidable inner and outer cylinders;
A partition member for partitioning the inside of the telescopic cylinder into a spring chamber and a hydraulic oil chamber;
A cylinder provided on the hydraulic oil chamber side;
A piston rod extending along the central axis of the cylinder from the cap side of the telescopic cylinder;
In the hydraulic shock absorber that is attached to the piston rod and includes a piston that slides in the cylinder in response to expansion and contraction of the expansion and contraction cylinder,
A cylinder mechanism that is located between the piston and the partition member and includes a piston member and a cylinder member in which the piston member advances and retreats from the opening;
The piston member is moved forward and backward relative to the cylinder member based on the operation of the piston, and configured to control the pressure of the oil pressure chamber in the cylinder member,
A braking member that abuts on the piston rod and applies a braking force is provided,
A hydraulic shock absorber in which the braking member is deformed and contacted in the direction of the piston rod based on the pressure in the oil pressure chamber so as to apply a braking force to the piston when extended. The piston member is provided on the partition member side of the piston,
The hydraulic shock absorber according to claim 1, wherein the cylinder member is supported by an elastic support portion attached to the partition member side. The braking member is formed as a cylinder surrounding the outer periphery of the piston rod,
The cylinder member is formed of a cylindrical cylinder main body that protrudes from a ring-shaped base material that surrounds the outer periphery of the piston rod, and a ring-shaped recess that houses the brake member is formed on the inner peripheral side of the base material. Forming a hydraulic chamber communicating with the oil pressure chamber of the cylinder member on the bottom surface side of the recess,
The pressure from the oil pressure chamber side is guided to the hydraulic chamber by the operation of the piston, the pressure is applied to the outer periphery of the braking member by the hydraulic pressure of the hydraulic chamber, and the braking member is bent in the piston rod direction and brought into contact. The hydraulic shock absorber according to claim 1 or claim 2.   The hydraulic shock absorber according to claim 3, wherein an axial dimension of the hydraulic chamber is set shorter than an axial length of the braking member.   The hydraulic shock absorber according to claim 3 or 4, wherein an oil passage for guiding pressure from the oil pressure chamber side to the hydraulic chamber is formed in the base material. The outer periphery of the piston member in the hydraulic shock absorber according to claim 1 is configured to be surrounded by a gap with a collar that is shorter in the axial direction than the piston member and moves up and down within a certain range,
When the piston member enters the cylinder member,
The lower end of the collar is pressed in close contact with the piston member and enters,
A hydraulic shock absorber in which the lower end of the collar is separated from the piston member when the piston member is withdrawn.   7. The hydraulic shock absorber according to claim 6, wherein a collar retaining means is provided at a position away from the upper end of the collar on the tip side of the piston member. 8. The hydraulic shock absorber according to claim 7, wherein the retaining means includes a fastener that has a length that does not contact the inner periphery of the cylinder member and projects from the piston member. 9.

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