JP2021173313A - Attenuation force generation device - Google Patents

Abstract

To provide an attenuation force generation device which can easily reduce a size of a back pressure chamber.SOLUTION: An attenuation force generation device comprises: a flow passage forming part 61 for forming a flow passage in which liquid flows; a back pressure chamber forming part 51 for forming a back pressure chamber between the flow passage forming part and itself; a valve part 53 having a valve for generating an attenuation force by being controlled so as to reduce a flow passage area of the liquid; a seal member which is arranged so as to be capable of suppressing the flow-out of the liquid in the back pressure chamber to the outside of the back pressure chamber; and an elastic member being an elastic body which can impart a force in a direction in which the seal member is made to tightly adhere to the back pressure chamber forming part. The seal member and the elastic member are integrated with each other.SELECTED DRAWING: Figure 2

Description

The present invention relates to a damping force generator used in a shock absorber.

Patent Document 1, for example, discloses a technique for sealing a sliding portion by providing a sealing structure on the sliding portion in the damping force generator of the shock absorber.

Patent Publication No. 2016-183702

In the piston structure disclosed in Patent Document 1, the damping force is adjusted by pressing the damping valve with the spool forming the back pressure chamber. Since a seal and a preset spring are arranged on this spool, the back pressure chamber tends to be large.
An object of the present invention is to provide a damping force generator that can easily reduce the size of the back pressure chamber.

As a result of diligent studies, the present inventor has made it easier to reduce the size of the back pressure chamber by integrating the seal member and the preset spring, and (2) integrate the seal member and the preset spring. As a result, it was found that these can be easily assembled. This disclosure has been completed based on these findings. Embodiments of the present disclosure will be described below.

In the embodiment of the present disclosure, a flow path forming portion forming a flow path through which a liquid flows, a back pressure chamber forming portion forming a back pressure chamber between the flow path forming portion, and a flow path area of the liquid are used. A valve portion having a main valve that generates a damping force by being controlled to be reduced, and a seal that is arranged so as to prevent the liquid in the back pressure chamber from flowing out of the back pressure chamber. A damping member comprising a member and an elastic member which is an elastic body capable of applying a force in a direction in which the seal member is brought into close contact with the back pressure chamber forming portion, and the seal member and the elastic member are integrated with each other. It is a force generator.
The elastic member may be any of a spiral coil spring, a wave spring, and a flexible leaf spring.
The constituent material of the elastic member may be the same as or different from the constituent material of the sealing member.
The elastic member may be sandwiched between the pair of the sealing members.

According to the present invention, it is possible to provide a damping force generator that makes it easy to miniaturize the back pressure chamber.

It is an overall view of the hydraulic shock absorber of 1st Embodiment. It is sectional drawing of the damping part apparatus of 1st Embodiment. It is a figure explaining the damping part and the damping force generator of 1st Embodiment. It is a figure explaining the seal structure. It is a figure explaining the modification of the seal structure. It is a figure explaining the modification of the seal structure. This is a modified example of the seal structure in the damping force adjusting device of the first embodiment. It is sectional drawing of the outer damping part provided in the damping force adjusting apparatus of 2nd Embodiment.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
<First Embodiment>
[Configuration / function of hydraulic shock absorber 1]
FIG. 1 is an overall view of a hydraulic shock absorber 1 including an outer damping unit 100, which is a damping force generating device of the first embodiment.
In the following description, the longitudinal direction of the cylinder portion 10 shown in FIG. 1 (the vertical direction of the paper surface in FIG. 1) is referred to as an "axial direction". Further, the lower side of the cylinder portion 10 in the axial direction is referred to as "one side", and the upper side of the cylinder portion 10 is referred to as "the other side".
Further, the left-right direction of the cylinder portion 10 shown in FIG. 1 (the left-right direction of the paper surface in FIG. 1) is referred to as a "radial direction". The side of the central axis CL1 in the radial direction is referred to as "inside in the radial direction", and the side away from the central axis CL1 is referred to as "outside in the radial direction".

As shown in FIG. 1, the hydraulic shock absorber 1 includes a cylinder portion 10 for accommodating oil and a rod 20 having the other side protruding from the cylinder portion 10 and one side slidably inserted into the cylinder portion 10. Be prepared. Further, the hydraulic shock absorber 1 includes a piston portion 30 provided at one end of the rod 20 and a bottom portion 40 provided at one end of the cylinder 10. Further, the hydraulic shock absorber 1 includes an outer damping portion 100 provided outside the cylinder portion 10 to generate a damping force.

As shown in FIG. 1, the shock absorber 1 has a triple tube structure including a first cylinder 11, a second cylinder 12, and an outer tube 13 in the radial direction. The cylinder portion 10 is a cylinder 11 for accommodating oil, an outer cylinder 12 provided on the outer side in the radial direction of the cylinder 11, and a damper case 13 provided on the outer side in the radial direction of the cylinder 11 and further on the outer side in the radial direction of the outer cylinder 12. And have.

The cylinder 11 is cylindrical and has a cylinder opening 11H on the other side. The outer cylinder 12 has a cylindrical shape. Then, the outer cylinder body 12 forms a connecting path L with the cylinder 11. Further, the outer cylinder 12 has an outer cylinder opening 12H and an outer connecting portion 12J at positions facing the outer damping portion 100. The outer connecting portion 12J has an oil flow path and projects outward in the radial direction to form a connecting portion with the outer damping portion 100.

The damper case 13 has a cylindrical shape. Then, the damper case 13 forms a reservoir chamber R in which oil is collected between the damper case 13 and the outer cylinder body 12. The reservoir chamber R absorbs the oil in the cylinder 11 and supplies the oil into the cylinder 11 as the rod 20 moves relative to the cylinder 11. Further, the reservoir chamber R stores the oil that has flowed out from the outer damping portion 100. Further, the damper case 13 has a case opening 13H at a position facing the outer damping portion 100.

[Structure / function of rod 20]
The rod 20 is a rod-shaped member that extends long in the axial direction. The rod 20 is connected to the piston portion 30 on one side. Further, the rod 20 is connected to, for example, a vehicle body on the other side via a connecting member (not shown) or the like.

[Structure / function of piston portion 30]
The piston portion 30 is a spring provided between a piston body 31 having a plurality of piston oil passage ports 311 and a piston valve 32 that opens and closes the other side of the piston oil passage openings 311 and one end of the piston valve 32 and the rod 20. It has 33 and. Then, the piston portion 30 divides the oil in the cylinder 11 into the first oil chamber Y1 and the second oil chamber Y2.

[Structure / function of bottom portion 40]
The bottom portion 40 has a valve seat 41, a check valve portion 43 provided on the other side of the valve seat 41, and a fixing member 44 provided on one side of the valve seat 41. Then, the bottom portion 40 separates the first oil chamber Y1 and the reservoir chamber R.

[Structure / Function of Outer Damping Unit 100]
In the following description, the longitudinal direction of the outer damping portion 100 shown in FIG. 2 is referred to as a "second axis direction", and the second axis is referred to as a second axis CL2. Further, in the direction of the second axis CL2, the side closer to the damper case 13 is referred to as "inside the second axis", and the side far from the damper case 13 is referred to as "outside the second axis". In the present embodiment, the direction of the second axis CL2 is the crossing direction intersecting the central axis CL1 (see FIG. 1). Further, in the description with reference to FIG. 2, the direction of the central axis CL1 is also referred to as a "second radial direction". In the second radial direction, the side along the second radial direction CL2 is referred to as "inside in the second radial direction", and the side away from the central axis along the second axis CL2 is referred to as "outside in the second radial direction".

As shown in FIG. 2, the outer damping portion 100 has an outer housing 110 that accommodates various components in the outer damping portion 100. Further, the outer damping unit 100 has a main valve unit 50 that generates a main damping force in the hydraulic shock absorber 1, and a damping force adjusting unit 60 that adjusts the damping force generated by the hydraulic shock absorber 1. Further, the outer damping portion 100 has an inner housing 120 that holds the main valve portion 50 and the damping force adjusting portion 60.

(Outer housing 110)
The outer housing 110 is a member having a substantially cylindrical shape. The outer housing 110 is fixed to the side surface of the damper case 13 by welding or the like.
Further, the outer housing 110 forms an inter-housing flow path 130, which is an oil flow path in the outer housing 110, on the outer side in the second radial direction of the main valve portion 50 and the damping force adjusting portion 60. Then, the inter-housing flow path 130 is connected to the reservoir chamber R.

(Main valve part 50)
As shown in FIGS. 2 and 3, the main valve portion 50 generates a damping force together with the back pressure chamber forming member 51, the seal ring 52, and the back pressure chamber forming member 51, which are examples of the back pressure chamber forming portion. It includes a valve member 53.

The back pressure chamber forming member 51 includes an inflow flow path 512 for flowing oil into the back pressure chamber 60P formed between the back pressure chamber forming member 51 and the flow path forming portion 61 described later, and the valve portion 53. It has a main valve 514 that generates a damping force by reducing the cross-sectional area of the flow path. The main valve 514 has an annular surface facing the seat portion 530.

The valve portion 53 includes a main valve 532 that generates a damping force by controlling so as to narrow the area of the oil flow path formed between the main valve 514 and the valve portion 53, and a main valve 532 on which the main valve 532 is seated. It has a valve seat 531 and.

A seal ring 52, which is an example of the seal member, is arranged on the outside of the second shaft of the back pressure chamber forming member 51. The oil flow that tends to flow out from between the flow path forming member 61 that functions as the flow path forming portion and the back pressure chamber forming member 51 to the outside of the back pressure chamber 60P is suppressed by the seal ring 52.

The inflow flow path 512 is the main flow path of the back pressure chamber 60P arranged outside the second shaft of the back pressure chamber forming member 51 and the main valve seat 531 arranged inside the second shaft of the back pressure chamber forming member 51. Connect with 533. That is, the inflow flow path 512 forms a path through which oil flows from the main flow path 533 into the back pressure chamber 60P.

The main valve 514 adjusts the damping force by changing the distance of the valve portion 53 with respect to the main valve 532 in the second axial direction.

The seal ring 52 is provided outside the main valve 514 in the second radial direction. An elastically deformable resin material such as rubber can be used for the seal portion 52B of the seal ring 52, which is an example of the seal member. Further, the seal ring 52 movably contacts the main valve 514 with the flow path forming member 61 in the second axial direction. When a force is applied to the seal ring 52 by the elastic member 52A, the seal portion 52B comes into close contact with the back pressure chamber forming member 51. The elastic member 52A and the seal portion 52B are integrally formed.

The elastic member 52A also applies a force in the direction from the outside of the second shaft to the inside of the second shaft to the main valve 514 via the seal portion 52B. For example, a compression coil spring or the like can be applied to the elastic member 52A.

The main valve seat 531 has a seat portion 530 in contact with the main valve 514 and a main flow path 533 which is a main flow path in the outer damping portion 100. Further, the main valve seat 531 is connected to the main flow path 533 to form an oil flow path at low speed, and the oil flowing between the main valve 514 and the main valve 532 flows through the first low speed flow path 534. It has an outflow flow path 535.

The seat portion 530 is formed in a substantially annular shape and protrudes toward the outside of the second axis. Then, the seat portion 530 forms a portion where the main valve 514 is seated when it comes into contact with the main valve 514.

The main flow path 533 constitutes a parallel flow path with respect to the first low speed flow path 534. The main flow path 533 is connected to the outer cylinder opening 12H on the inside of the second shaft and faces the main valve 514 on the outside of the second shaft. Further, the main flow path 533 is provided inside the second radius of the seat portion 530.

The first low speed flow path 534 is provided so as to extend in the second radial direction. The first low-speed flow path 534 connects the main flow path 533 and the second low-speed flow path 613.
The outflow flow path 535 is provided so as to extend in the second axial direction. The outflow flow path 535 connects the facing portion between the main valve 514 and the seat portion 530 and the case opening 13H.

(Damping force adjusting unit 60)
As shown in FIGS. 2 and 3, the damping force adjusting portion 60 includes the flow path forming member 61, which is an example of the flow path forming portion forming the oil flow path in the inner housing 120, and the pressure of the back pressure chamber 60P. It has an adjustment valve 62 for controlling the adjustment valve 62 and an adjustment valve seat 63 on which the adjustment valve 62 is seated. Further, the damping force adjusting unit 60 controls the pressure of the back pressure chamber 60P via the adjusting valve 62 and the moving valve 64 for controlling the oil flow in the third low speed flow path 614 described later, and the moving valve 64 is second. It has a second spring 65 that urges the outside of the shaft. Further, the damping force adjusting unit 60 includes a solenoid unit 66 that drives the moving valve 64, and a non-energized control unit 67 that controls the flow of oil when the solenoid unit 66 is not energized.

As shown in FIG. 3, the flow path forming member 61 has a main valve accommodating portion 611 accommodating the main valve 514 and an adjusting valve holding portion 612 holding the adjusting valve 62 and the adjusting valve seat 63. Further, the flow path forming member 61 has a second low speed flow path 613 and a third low speed flow path 614 that form a flow path of oil at low speed. The flow path forming member 61 has a merging flow path 615 connected to the back pressure chamber 60P and the third low speed flow path 614, and a first outflow flow path 616 from which oil flows out from the merging flow path 615.

The main valve accommodating portion 611 is provided inside the second shaft of the flow path forming member 61. Then, the main valve accommodating portion 611 holds the main valve 514 movably in the direction of the second axis CL2 via the seal ring 52. Further, the main valve accommodating portion 611 of the present embodiment forms the back pressure chamber 60P of the main valve 514 together with the back pressure chamber forming member 51.

The adjusting valve holding portion 612 is provided outside the second axis of the main valve accommodating portion 611 and inside the second axis of the merging flow path 615. Then, the adjusting valve holding portion 612 holds the adjusting valve 62 and the adjusting valve seat 63 so as not to move in the second axial direction by press-fitting at least the adjusting valve seat 63.

The second low-speed flow path 613 is provided on the outside of the flow path forming member 61 in the second radial direction. Further, the second low speed flow path 613 is formed so as to extend in the second axial direction. Then, the second low-speed flow path 613 connects the first low-speed flow path 534 and the third low-speed flow path 614.

The third low speed flow path 614 is provided so as to extend in the second radial direction. Then, the third low-speed flow path 614 connects the second low-speed flow path 613 and the merging flow path 615. A plurality of third low-speed flow paths 614 are provided in the outer damping portion 100 of the present embodiment.

The merging flow path 615 forms a region in which the moving valve 64 can move along the second axial direction. Further, the merging flow path 615 forms a region in which the moving valve 64 displaces the adjusting valve 62. The merging flow path 615 includes a region where oil flows in from the third low speed flow path 614 and a region where oil flowing out from the back pressure flow path 632 of the adjustment valve seat 63 flows in. At the merging flow path 615, the oil flowing through the third low speed flow path 614 and the back pressure flow path 632 merge.

Further, the merging flow path 615 has a valve facing portion 641 with the moving valve 64 at the connection point with the third low speed flow path 614. The valve facing portion 641 has a cylindrical inner peripheral surface. Specifically, the valve facing portion 641 moves the moving valve 64 in the second axial direction to open and close the flow path openings, which are the ends of the plurality of third low-speed flow paths 614 described above.

The first outflow flow path 616 is provided so as to extend in the second axial direction. The first outflow flow path 616 connects the merging flow path 615 and the second outflow flow path 123 of the inner housing 120.

As shown in FIG. 2, the solenoid unit 66 has a coil 661 that is excited by being energized, a magnet 662 that moves depending on the excited state of the coil 661, and a plunger 663 that is fixed to the magnet 662. Then, the solenoid unit 66 drives the moving valve 64 in the second axial direction according to the energized state.

The solenoid unit 66 pushes the plunger 663 toward the inside of the second shaft when the coil 661 is energized. The extruded plunger 663 extrudes the moving valve 64 connected to the inner end of the second shaft of the plunger 663 toward the inner side of the second shaft, and further pushes the second spring 65 in contact with the moving valve 64. Press it toward the adjusting valve 62. Further, the plunger 663 controls the amount of movement inward of the second shaft according to the amount of energization of the coil 661. Therefore, the amount of movement of the moving valve 64 changes according to the amount of energization of the coil 661.

On the other hand, in the solenoid unit 66, when the coil 661 is in a non-energized state, the plunger 663 is pushed back to the outside of the second shaft by the spring force of the second spring 65. In this case, the moving valve 64 is returned toward the outside of the second axis as the plunger 663 moves. Then, when the coil 661 is in the non-energized state, the second spring 65 moves the moving valve 64 to a position where the flow path area of the oil flowing out from the merging flow path 615 is narrowed compared to the case where the coil 661 is in the energized state.

As shown in FIGS. 2 and 3, the non-energized control unit 67 is a disk-shaped member having an opening 671 inside in the second radial direction. The non-energized control unit 67 is provided on the outside of the second axis of the flow path forming member 61. Then, the non-energized control unit 67 is held by being sandwiched between the flow path forming member 61 and the inner housing 120.
The inner diameter of the opening 671 is larger than the outer diameter of the side surface 641 of the moving valve 64. Since the moving valve 64 has a shape in which the width in the second radial direction changes according to the portion in the second axial direction, the distance between the inner peripheral surface of the opening 671 and the side surface portion 641 is the first of the moving valve 64. It changes according to the position in the biaxial direction.

(Inner housing 120)
As shown in FIG. 2, the inner housing 120 includes a first holding portion 121 that holds the solenoid portion 66, a second holding portion 122 that holds the main valve portion 50 and the damping force adjusting portion 60, and the inside of the inner housing 120. It has a second outflow flow path 123 for flowing oil from the outside to the outside.

The first holding portion 121 is provided outside the second holding portion 122 with respect to the second holding portion 122. In the inner housing 120 of the present embodiment, the first holding portion 121 and the second holding portion 122 are integrally formed.
The second outflow flow path 123 is formed so as to extend in the second radial direction. As shown in FIGS. 2 and 3, the second outflow flow path 123 connects the first outflow flow path 616 and the inter-housing flow path 130 via the opening 671 of the non-energized control unit 67.

The structure of the seal ring 52 will be described with reference to FIGS. 4A, 4B, 4C, and 5.
The seal ring 52 shown in FIG. 4A includes an elastic member 52A which is a metal coil spring, and seal portions 52B and 52B which are arranged at the upper and lower ends thereof and are formed of a resin or the like having a sealing function. Have. The elastic member 52A and the seal portion 52B are integrated. FIG. 4A shows a form having one elastic member 52A, but the number of elastic members 52A sandwiched by the pair of sealing portions 52B and 52B is not limited to this. Two or more elastic members 52A may be sandwiched between the pair of sealing portions 52B and 52B.

The seal ring 52X shown in FIG. 4B has an elastic member 521X which is a coil spring made of resin, and seal portions 522X and 522X formed of a resin having a sealing function arranged at the upper end and the lower end thereof, respectively. .. The elastic member 521X and the seal portion 522X are integrated. The constituent material of the elastic member 521 and the constituent material of the seal portion 522X may be the same or different. The elastic member 521X and the sealing portion 522X can be formed of, for example, a fluororesin such as PTFE or PEEK, a polyamide resin, or a phenol resin. The elastic member 52A can also be formed of these resins.

The seal ring 52Y shown in FIG. 4C is a seal portion 522Y and 522Y formed of an elastic member 521Y which is a wave spring made of metal or resin and a resin or the like having a sealing function arranged at the upper end and the lower end thereof, respectively. And have. The elastic member 521Y and the seal portion 522Y are integrated.

In the above description, the seal ring having a seal portion at the upper end and the lower end of the elastic member has been described, but the seal ring that can be used in the present invention is not limited to this form. In the present invention, it is also possible to use a seal ring in which an elastic member and a seal portion arranged at one of the upper end or the lower end thereof are integrated.

The seal ring 52Z shown in FIG. 5 includes an elastic member 521Z which is a leaf spring made of metal or resin and has a hole through which oil can pass, and a resin or the like having a sealing function arranged so as to surround the elastic member 521Z. It has a seal portion 522Z formed by the above. The elastic member 521Z and the seal portion 522Z are integrated. As shown in FIG. 5, the elastic member in the present invention may be a leaf spring.

<Second Embodiment>
Subsequently, the damping force generator of the second embodiment will be described.
FIG. 6 is an enlarged cross-sectional view showing a part of the damping force generator 200 of the second embodiment.
In the description of the second embodiment, the same components as those of the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. The damping force generator 200 has a function as a so-called frequency response type damping force adjusting device that utilizes the pressure in the back pressure chamber without using an actuator or the like.

Unlike the first embodiment, the damping force generator 200 of the second embodiment is provided inside the first cylinder 11, and the piston portion 210 provided on the piston rod 20 generates a damping force.
The piston portion 210 has a piston 211, and the piston 211 has a through hole through which the piston rod 20 penetrates, and a flow path 212 and a flow path 213 through which the piston 211 penetrates the first cylinder 11 in the axial direction. The upper end of the flow path 212 is closed by the valve 214, and the valve 215 is arranged at the lower end of the flow path 213. A damping force is generated when the oil flowing through the flow path 212 flows through the gap between the upper end opening of the flow path 212 and the valve 214, which is formed by opening the valve 214. At least a part of the oil that has passed through the flow path 213 passes between the inner peripheral surface of the valve 215 and the rod 20 and flows into the flow path 221 described later. A damping force is generated when the oil flows through the gap between the lower end opening of the flow path 213 and the valve 215, which is formed by opening the valve 215 with the rest of the oil passing through the flow path 213.

A sub-piston 220 is arranged below the valve 215. The sub-piston 220 has a through hole through which the piston rod 20 penetrates, and the inner peripheral surface of the through hole and the outer peripheral surface of the piston rod 20 define a flow path 221 extending in the axial direction of the cylinder 11. The valve 222 is arranged so as to close the lower end opening of the sub-piston 220 including the lower end opening of the flow path 221. When the oil that has moved in the flow path 221 from the valve 215 side flows through the gap between the valve 222 and the lower end opening of the sub-piston 220, which is formed by opening the valve 222, a damping force is applied. Occurs.

A spool 230 is arranged below the valve 222. The spool 230 has a piston nut 231 having a through hole through which the piston rod penetrates, and an outer edge portion 232 formed so as to surround the piston nut 231 from the outside at a predetermined interval. A seal ring 233 is fitted between the piston nut 231 and the outer edge portion 232, a pressing member 234 is provided on the lower side of the seal ring 233, and a support portion 235 is provided on the upper side of the seal ring 233. ing. The seal ring 233 is in close contact with the support portion 235 by being pushed by the pressing member 234 from below. The spool 230 further has a valve 222, a piston nut 231 and an outer edge 232, a seal ring 233, and a back pressure chamber 236, which is a region defined by the support 235. The back pressure chamber 236 has a function of adjusting the opening degree of the valve 222 (the size of the gap between the upper end surface of the valve 222 and the lower end surface of the sub-piston 220).

The valve 222 abuts on a round surface of the sub-piston 220 (not shown), and the flow path 221 and the back pressure chamber 236 are connected via an orifice flow path 223 extending in the radial direction of the valve 222. The oil flowing through the flow path 221 flows into the back pressure chamber 236 through the orifice flow path 223.

The seal ring 233 can have the same shape as the seal rings 52, 52X, 52Y shown in FIGS. 4A to 4C, for example. In the damping force generator 200, the seal ring 233 has a sealing function and acts as a free piston. The opening / closing timing of the sub valve 222 is adjusted by delaying the pressure rise of the back pressure chamber 236 by the seal ring 233.

In the above description, a damping force generator provided outside the cylinder and a damping force generator that also functions as a frequency response type damping force adjusting device have been exemplified, but the damping force generator of the present invention has these modes. Not limited to. Other shapes and other configurations may be used as long as they satisfy the function of generating a damping force.
Further, the damping force generator of the present invention may have a structure in which a part of the configuration of the damping force generator 100 and a part of the configuration of the damping force generator 200 are combined. For example, the back pressure chamber in the present invention may be a back pressure chamber that applies a force in the direction of closing the valve that the flowing oil tries to open during the process of increasing the distance between the vehicle body and the wheels. Often, it may be a back pressure chamber applied to the bottom portion.

Further, the function of the outer damping portion 100 provided on the outside of the cylinder 11 may be provided on the piston sliding inside the cylinder 11 or may be provided on the bottom portion. Further, the shock absorber to which the damping force generator of the present invention is applied is not limited to the triple tube structure having three cylinders arranged concentrically as shown in FIG. The damping force generator of the present invention can also be applied to a shock absorber having a double tube structure having two cylinders arranged concentrically.

1 ... Hydraulic shock absorber, 11 ... Cylinder, 13 ... Outer tube, 20 ... Rod, 30 ... Piston part, 40 ... Bottom part, 51 ... Back pressure chamber forming member (back pressure chamber forming part), 52A ... Elastic member, 52B ... Seal part (seal member), 53 ... Valve part, 60 ... Damping force adjusting part, 60P ... Back pressure chamber, 61 ... Flow path forming part, 100 ... Outer damping part (damping force generator), 200 ... Damping force generation Device, 532 ... valve

Claims (7)

A flow path forming part that forms a flow path through which a liquid flows,
A back pressure chamber forming portion that forms a back pressure chamber between the flow path forming portion and the back pressure chamber forming portion.
A valve portion having a valve that generates a damping force by being controlled so as to reduce the flow path area of the liquid.
A sealing member arranged so as to prevent the liquid in the back pressure chamber from flowing out of the back pressure chamber.
An elastic member, which is an elastic body capable of applying a force in a direction in which the seal member is brought into close contact with the back pressure chamber forming portion, is provided.
A damping force generator in which the sealing member and the elastic member are integrated. The damping force generator according to claim 1, wherein the elastic member is a spiral coil spring. The damping force generator according to claim 1, wherein the elastic member is a wave spring. The damping force generator according to claim 1, wherein the elastic member is a leaf spring having flexibility. The damping force generator according to any one of claims 1 to 3, wherein the constituent material of the elastic member is the same as the constituent material of the sealing member. The damping force generator according to any one of claims 1 to 4, wherein the constituent material of the elastic member is different from the constituent material of the sealing member. The damping force generating device according to any one of claims 1 to 6, wherein the elastic member is sandwiched between the pair of the sealing members.

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