JPH1182606A - Hydraulic buffer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid the increase in a production cost following the increase in manufacturing man-hours, in an usual hydraulic buffer assembled with a rebound cushion. SOLUTION: This device is provided with a piston 15 for partitioning the inside of a cylinder 16 to two liquid rooms 13, 14, a piston rod 18 on which a small diameter part 32 continuing to this large diameter part 30 through the large diameter part 30 and a step part 31 is formed and the piston 15 is fixed to this small diameter part 32 and also for penetrating slidably an end plate 19 on which the large diameter part 30 is mounted to the cylinder 16, a stopper sheet 34, fitted to the small diameter part 32 so as to be engagingly locked to the step part 31, for receiving the piston 15, a rebound stopper 39 fitted to the large diameter part 30 so that its one end surface is contacted with the stopper sheet 34 and a rebound cushion 40 fitted to the large diameter part 30 so as to be contacted with this rebound stopper 39 and contacted with the end plate 19 and formed by an elastic body which can regulate the slide end of the piston 15 to the end plate 19 side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic shock absorber incorporating a rebound cushion for regulating a sliding end of a piston toward an end plate of a cylinder when a piston rod extends from the cylinder.

[0002]

2. Description of the Related Art A cylinder filled with a buffering liquid is partitioned into two liquid chambers by a piston, and a piston is slid in the cylinder via a piston rod connected to the piston to thereby form two liquid chambers. In a hydraulic shock absorber in which the movement of the liquid generated between the chambers is suppressed so as to have a shock absorbing function, it may be necessary to define the stroke end of the piston rod.
A hydraulic shock absorber as disclosed in JP-A-14328 is known.

In this hydraulic shock absorber, a piston rod extends from a cylinder between an end plate closing one end of a cylinder and a piston fitted to one end of a piston rod slidably penetrating the end plate. A rebound cushion formed of a rubber-like elastic body that abuts on the end plate to reduce the impact at the stroke end when the piston rod is welded to the piston rod. It is in a state held in.

[0004] By providing the rebound cushion, the distance from the end plate at one stroke end of the piston rod to the piston can be set longer than when the rebound cushion is not provided. Radial stress acting on the end plate due to the radial lateral force
This has the advantage that the life of the end plate that slidably holds the piston rod can be extended.

[0005]

Problems to be Solved by the Invention
In the conventional hydraulic shock absorber disclosed in Japanese Patent Application Laid-Open Publication No. H11-157, it is necessary to weld a metal flange-shaped stopper to the piston rod in order to position the rebound cushion with respect to the piston rod. In addition, prior to the welding, the fitting position of the stopper to the piston rod must be defined, and it is necessary to devise any means for positioning, for example, to prepare a dedicated positioning jig.
As a result, in the conventional hydraulic shock absorber incorporating the rebound cushion, there is a problem that the manufacturing cost is increased as the number of manufacturing steps is increased.

[0006]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulic shock absorber which can easily and inexpensively incorporate a rebound cushion.

[0007]

According to a first aspect of the present invention, there is provided a cylinder filled with a buffering liquid, and the cylinder is slidably fitted in the cylinder. A piston that partitions the inside of the cylinder into two liquid chambers, and a small-diameter portion that follows the large-diameter portion through a large-diameter portion and a step portion are formed. The piston is fixed to the small-diameter portion, and the large-diameter portion is A hydraulic pressure having a piston rod slidably penetrating an end plate mounted on a cylinder, and a stopper sheet fitted to the small diameter portion to receive the piston so as to be engaged with the step portion of the piston rod. A shock absorber, wherein one end face is fitted to the large-diameter portion of the piston rod so as to contact the stopper sheet, and the other end face contacts the end plate to slide the piston toward the end plate. Elastic body that can regulate the moving end In the hydraulic shock absorber, characterized in that it comprises a rebound cushion which is formed Te.

According to the present invention, the stopper sheet for receiving the piston also functions as a stopper for receiving the rebound cushion. At one stroke end of the piston rod, the rebound cushion hits the end plate with elastic deformation, and the impact is reduced. Be relaxed.

According to a second aspect of the present invention, there is provided a cylinder having a buffer liquid filled therein,
A piston which is slidably fitted in the cylinder and partitions the inside of the cylinder into two liquid chambers, and a small diameter portion following the large diameter portion through a large diameter portion and a step portion are formed. The piston is fixed, and the large-diameter portion is slidably penetrated through an end plate mounted on the cylinder, and is fitted to the small-diameter portion so as to be engaged with the step portion of the piston rod. A rebound stopper fitted to the large diameter portion of the piston rod such that one end surface abuts the stopper sheet, and
One end face is fitted to the large-diameter portion of the piston rod so as to abut the other end face of the rebound stopper, and the other end face abuts the end plate and slides the sliding end of the piston toward the end plate. And a rebound cushion formed of an elastic body that can be regulated.

According to the present invention, the rebound stopper abutting on the stopper sheet positions the rebound cushion at an appropriate position with respect to the piston rod. In addition, the stopper sheet that receives the piston also functions as a stopper that receives the rebound cushion via the rebound stopper, and the rebound cushion hits the end plate with elastic deformation at one stroke end of the piston rod, reducing the impact Is done.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the hydraulic shock absorber according to the first aspect of the present invention, as described in the second aspect of the present invention, the rebound cushion is fitted to the large-diameter portion of the piston rod with an interference. In this case, as described in claim 3 of the present invention, the rebound cushion has an inner peripheral wall having an inner diameter larger than the large diameter portion of the piston rod and a circumferential direction extending from the inner peripheral wall. And at least three projections projecting at equal intervals and pressing against the large diameter portion of the piston rod.

Further, as described in claim 4 of the present invention,
The rebound cushion may have a notch on its outer periphery. In this case, as described in claim 5 of the present invention, a plurality of notches are provided at equal intervals along the circumferential direction. Is desirable.

Further, as described in claim 6 of the present invention, the rebound cushion may be formed such that one end and the other end are symmetrical with respect to the center in the longitudinal direction.

On the other hand, in the hydraulic shock absorber according to the second aspect of the present invention, as described in claim 8 of the present invention, even if the rebound stopper is formed of an elastic body harder than the rebound cushion. Good.

[0015] According to a ninth aspect of the present invention,
The rebound stopper may be fitted to the large-diameter portion of the piston rod with an interference, and in this case, as described in claim 10 of the present invention, the rebound stopper is larger than the large-diameter portion of the piston rod. May have an inner peripheral wall having a large inner diameter, and at least three protruding portions that project from the inner peripheral wall at equal intervals along the circumferential direction and press against the large diameter portion of the piston rod.

Further, as described in claim 11 of the present invention, the rebound stopper may have a notch on its outer periphery. In this case, claim 1 of the present invention
As described in 2, it is preferable that a plurality of notches are provided at equal intervals along the circumferential direction.

Further, as described in claim 13 of the present invention, the one end and the other end of the rebound stopper may be formed symmetrically with respect to the longitudinal center.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which a hydraulic damper according to the present invention is applied to a vehicle shock absorber will be described in detail with reference to FIGS. 1 to 8, but the present invention is not limited to such an embodiment. These can be further combined, or applied to technologies in other fields that include similar problems.

As shown in FIG. 1 showing a schematic structure of the vehicle shock absorber in the present embodiment, the vehicle shock absorber of the present embodiment interposed between a link connected to wheels (not shown) and the vehicle body. A lower end of the outer cylinder 11 is rotatably attached to a link (not shown) connected to wheels via an eyebush 12. A piston that partitions the interior into an upper chamber 13 and a lower chamber 14 is provided in the outer cylinder 11. 1
An inner cylinder 16 as a cylinder accommodating slidably accommodated therein is accommodated coaxially. End plates 1 partitioning the lower chamber 14 are provided at lower end portions of the outer cylinder 11 and the inner cylinder 16.
7 is fixed. Similarly, at the upper end of the inner cylinder 16,
A substantially cylindrical rod guide 19 as an end plate of the present invention, in which a piston rod 18 slidably penetrates and partitions the upper chamber 13.
The rod guide 19 is also fitted to the upper end of the outer cylinder 11.

The end plate 17 is provided with a pair of passages 22 and 23 which can communicate a cylindrical reservoir chamber 21 formed between the outer cylinder 11 and the inner cylinder 16 with the lower chamber 14. ,
An elastically deformable disk valve 24 having an appropriate bending rigidity is attached to one of the passages 22, and the other passage 2
A check valve 25 is attached to 3. The disc valve 24 is moved from the lower chamber 14 to the disc valve 24.
Only the movement of the working fluid to the reservoir chamber 21 is permitted through the above, but at this time, a damping force is generated by utilizing the elastic bending of the valve disk 24, and constitutes a so-called base valve. Further, the check valve 25 is connected to the lower chamber 14 via the check valve 25 from the reservoir chamber 21.
Only the movement of the working fluid is allowed.

A gap 27 surrounded by the rod guide 19 and the guide holder 20 and a seal plate 26 mounted on the upper end of the outer cylinder 11 forms an upper chamber through a gap between the piston rod 18 and the rod guide 19. 13.

A passage 29 is formed in the rod guide 19 to communicate the gap 27 with the reservoir chamber 21.
The upper chamber 13 and the lower chamber 14 described above are filled with a working fluid for buffering (not shown), and an appropriate amount of working fluid is stored in the reservoir chamber 21.

The upper end of the piston rod 18 is supported on the vehicle body via an insulator (not shown). A spring (not shown) is mounted between an upper spring mount (not shown) connected to the upper end of the piston rod 18 and a lower spring mount 28 fitted to the upper end of the outer cylinder 11. The vertical movement of the wheels following the irregularities is not transmitted to the vehicle body due to the expansion and contraction of the spring.

The piston rod 18 has a large diameter portion 30
And a small-diameter portion 3 following the large-diameter portion 30 via a step portion 31.
2 is formed, and the piston 15 is interposed between the annular stopper sheet 34 fitted to the small-diameter portion 32 so as to be locked to the step portion 31 by the lock nut 33 screwed into the tip of the small-diameter portion 32. Piston rod 1 while pinched
8 is fixed to the small diameter portion 32.

A pair of passages 37, 3 through which the upper chamber 13 and the lower chamber 14 can communicate with each other through the piston 15 via an upper disk valve 35 and a lower disk valve 36, respectively.
8 are formed.

During the compression stroke in which the piston rod 18 enters the inner cylinder 16, the upper disc valve 35
4, the working fluid in the lower chamber 14 flows through the passage 37.
Flows directly into the upper chamber 13 via the upper disk valve 35, and at this time, a damping force corresponding to the bending rigidity of the upper disk valve 35 is generated. Furthermore, the piston rod 1
8 is inserted into the inner cylinder 16, the volume in the inner cylinder 16 changes. Therefore, the working fluid in the lower chamber 14 flows into the reservoir chamber 21 via the disc valve 24 from the passage 22 provided in the end plate 17 for constituting the base valve, and the disc valve is thus displaced. The damping force corresponding to the flexural rigidity of 24 is also generated at the same time.

On the other hand, in the extension stroke in which the piston rod 18 projects from the inner cylinder 16, the pressure in the upper chamber 13 increases, and the working fluid in the upper chamber 13 flows directly from the passage 38 to the lower chamber 14 via the lower disk valve 36. At this time, a damping force corresponding to the bending rigidity of the lower disk valve 36 is generated. Furthermore, the volume in the inner cylinder 16 changes by the amount that the piston rod 18 protrudes out of the inner cylinder 16. Therefore, the working fluid corresponding to the change in volume has the passage 2 forming a part of the base valve.
From 3, the working fluid in the reservoir chamber 21 flows into the lower chamber 14 via the check valve 25.

Here, since the check valve 25 has almost no bending rigidity, the check valve 25 hardly generates a damping force.

In the above-described embodiment, when the piston 15 is in the compression stroke, the upper disk valve 35 provided on the piston 15 and the end plate 17 for forming the base valve are used.
Although the damping force is generated by both the disk valve 24 provided with the piston, a check valve is provided on the piston 15 and only the disk valve 24 provided on the end plate 17 for forming the base valve is used. A damping force may be generated.

An annular rebound stopper 39 and a rebound cushion 40 are attached to the large diameter portion 30 of the piston rod 18 facing the upper chamber 13.
Rebound stopper 39 made of rubber-like elastic material
Are fitted to the large-diameter portion 30 with an interference in a state of contacting the stopper sheet 34. That is, the stopper sheet 3
4 also functions as a stopper for the rebound stopper 39 in addition to the stopper function of the upper disc valve 35, and a special stopper is provided for the piston rod 18 as in the related art.
This eliminates the need for welding. Further, the rebound cushion 40 formed of a rubber-like elastic material softer than the rebound stopper 39 abuts on the rod guide 19 at the stroke end of the extension stroke to reduce the impact when the piston rod 18 is fully extended. It has become.

In this case, a compressive force to the piston 15 acts on the rebound stopper 39 and the rebound cushion 40. The compressive force is received by the stopper sheet 34, and the rebound stopper 39 and the rebound cushion 40 are moved by the piston rod. There is no problem such as displacement of the position 18 along the longitudinal direction. When the above-described rebound cushion 40 is provided, the rebound stopper 39 may be formed of a resin, a metal, or the like that does not elastically deform.

In this embodiment, the rebound stopper 39 is used.
As shown in FIG. 2 showing the planar shape of the piston rod 18 and FIG. 3 showing the sectional structure taken along the line III-III, both ends of the inner peripheral wall 41 having an inner diameter larger than the large diameter portion 30 of the piston rod 18 are provided with piston rods. A plurality of (three in this embodiment) protrusions 42 pressing against the large diameter portion 30 of the inner peripheral wall 4
1 and are provided at equal intervals along the circumferential direction. That is, the radius from the axis of the rebound stopper 39 to the inner peripheral end of the protrusion 42 is set smaller than the radius of the large diameter portion 30 of the piston rod 18, and these protrusions 42 Is pressed against the large-diameter portion 30.

As described above, since the rebound stopper 39 is fitted to the large diameter portion 30 of the piston rod 18 with a tight allowance, the rebound stopper 39 can be firmly fixed to the piston rod 18. Further, since the inner peripheral wall 41 does not contact the large diameter portion 30 of the piston rod 18, the resistance when the rebound stopper 39 is pressed into the piston rod 18 can be reduced, and the workability can be improved. .

In this embodiment, since the rebound stopper 39 is formed of a rubber-like elastic material which is harder than the rebound cushion 40, the degree of freedom in the design of the bending characteristics is greater than when this is made of a rigid material such as metal. Can be increased. That is, as shown in FIG. 4 showing the relationship between the amount of flexure when the rebound cushion 40 is compressed and its compression load, when the rebound stopper 39 is formed of a rubber-like elastic body, only the rebound cushion 40 is An arbitrary bending characteristic can be obtained in a range from the state shown by the solid line where the bending deformation occurs to the state where the rebound stopper 39 also bends and deforms in the middle, for example, as shown by the two-dot chain line.

In order to reduce the material cost due to the weight reduction of the rebound stopper 39 and to obtain appropriate bending characteristics of the rebound stopper 39, a cutout portion such as a hollow portion is formed on the outer peripheral surface of the rebound stopper 39. You may.

FIG. 5 shows a plan view of another embodiment of such a rebound stopper 39 according to the present invention.
FIG. 6 shows a cross-sectional structure taken along the line VI. However, the same reference numerals are used for the parts having the same functions as those of the previous embodiment, and the overlapping description will be omitted. That is, both ends of the rebound stopper 39 are left in a flange shape so that the strength required for the rebound stopper 39 can be secured, and a plurality of the rebound stoppers 39 are provided on the outer peripheral surface at equal intervals along the circumferential direction. A notch 43 is formed. By these notches 43, it is possible to reduce the material cost due to the weight reduction and obtain the desired bending characteristics while securing the necessary strength.

In the above embodiment, the notch 43 is formed intermittently on the outer peripheral surface of the rebound stopper 39.
If the required strength can be satisfied, it may be formed over the entire circumference.

FIG. 7 shows a plan view of another embodiment of such a rebound stopper 39 according to the present invention.
FIG. 8 shows a cross-sectional structure taken along the line VIII of FIG. 8, and portions having the same functions as those in the previous embodiment will be denoted by the same reference numerals, and redundant description will be omitted. That is, a notch 43 is formed on the entire outer peripheral surface of the rebound stopper 39 so that the thickness of the rebound stopper 39 is increased toward the center so as to form a drum shape as a whole. I have. In this embodiment, as in the previous embodiment, the cutout 43 can reduce the material cost due to the weight reduction and obtain the desired bending characteristics while securing the necessary strength.

When the rebound stopper 39 is mounted on the piston rod 18, in order to improve the operability by eliminating the mounting direction, the rebound stopper 39 is, as in all the rebound stoppers 39 described above, positioned at the center in the longitudinal direction. It is desirable that one end and the other end are formed symmetrically.

In the above-described embodiment, the rebound stopper 39 and the rebound cushion 40 are overlapped and brought into contact with the stopper sheet 34. However, since the rebound stopper 39 can be formed of a rubber-like elastic body, By forming the rebound stopper 39 of a relatively soft material to give an appropriate bending characteristic, it is also possible to use this as a rebound cushion. In this case, since it is not necessary to use the rebound cushion 40, the manufacturing cost can be reduced with a reduction in the number of parts.

[0041]

According to the hydraulic shock absorber of the present invention corresponding to the first aspect, the rebound cushion is brought into contact with the existing stopper sheet to position the same.
It is not necessary to weld a stopper for supporting the rebound cushion to the piston rod, so that the number of parts and man-hours can be reduced and the manufacturing cost can be reduced.

According to the second aspect of the present invention, since the rebound cushion is fitted to the large-diameter portion of the piston rod with a tight allowance, the rebound cushion is more tightly fitted to the piston rod. Can be fixed firmly.

According to the hydraulic shock absorber of the present invention, the inner peripheral wall having an inner diameter larger than the large diameter portion of the piston rod, and the piston protruding from the inner peripheral wall at equal intervals along the circumferential direction. Since the rebound cushion has at least three protrusions that press against the large diameter portion of the rod,
The resistance at the time of press-fitting the rebound cushion into the piston rod can be reduced, and the workability can be improved.

According to the fourth aspect of the present invention, since the notch is provided on the outer periphery of the rebound cushion, the material cost can be reduced, and the weight of the rebound cushion can be further reduced. It becomes possible.

According to the hydraulic pressure absorbing device of the present invention corresponding to claim 5, by providing a plurality of notches at equal intervals along the circumferential direction on the outer periphery of the rebound cushion, the strength can be improved by the portions without the notches. And material costs can be reduced.

According to the hydraulic shock absorber of the present invention corresponding to claim 6, by forming the one end side and the other end side symmetrically with respect to the longitudinal center of the rebound cushion,
Since the directionality when assembling the rebound cushion to the piston rod is eliminated, erroneous assembly can be prevented and workability can be improved.

On the other hand, according to the hydraulic shock absorber of the present invention, the rebound stopper is brought into contact with the existing stopper sheet, and the rebound cushion is received via the rebound stopper. It is not necessary to weld a stopper for supporting the piston rod to the piston rod, and the number of parts and man-hours can be reduced, and the manufacturing cost can be reduced.

According to the hydraulic shock absorber of the present invention corresponding to claim 8, since the rebound stopper is formed of an elastic body harder than the rebound cushion, the rebound stopper can have the function of the rebound cushion, The design flexibility with respect to the bending characteristics of the rebound cushion is increased, and the weight can be reduced as compared with the case where the rebound stopper is made of metal.

According to the hydraulic pressure damping device of the present invention corresponding to claim 9, since the rebound stopper is fitted to the large-diameter portion of the piston rod with an interference, the rebound stopper can be attached to the piston rod more. Can be fixed firmly.

According to the hydraulic shock absorber of the present invention corresponding to claim 10, the inner peripheral wall having an inner diameter larger than the large diameter portion of the piston rod, and the piston protruding from the inner peripheral wall at equal intervals along the circumferential direction. Since the rebound stopper has at least three protrusions that press against the large diameter portion of the rod,
The resistance at the time of press-fitting the rebound stopper into the piston rod can be reduced, and the workability can be improved.

According to the hydraulic shock absorber of the present invention, since the notch is provided on the outer periphery of the rebound stopper, the material cost can be reduced and the weight can be further reduced. .

According to the hydraulic pressure damping device of the present invention, a plurality of notches are provided on the outer periphery of the rebound stopper at equal intervals along the circumferential direction, so that the strength can be improved by the portions without the notches. And material costs can be reduced.

According to the hydraulic shock absorber of the present invention, one end and the other end of the rebound stopper are formed symmetrically with respect to the longitudinal center of the rebound stopper.
Since the directionality when assembling the rebound stopper to the piston rod is eliminated, erroneous assembly can be prevented, and workability can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of an embodiment in which a hydraulic shock absorber according to the present invention is applied to a vehicle shock absorber.

FIG. 2 is a plan view of a rebound stopper in the embodiment shown in FIG.

FIG. 3 is a sectional view taken along the line III-III in FIG. 2;

FIG. 4 is a graph showing the relationship between the amount of deflection of the rebound cushion and the compression load.

FIG. 5 is a plan view of another embodiment of the rebound stopper according to the present invention.

6 is a sectional view taken along the line VI-VI in FIG.

FIG. 7 is a plan view of another embodiment of the rebound stopper according to the present invention.

8 is a sectional view taken along the line VIII-VIII in FIG.

[Explanation of symbols]

 Reference Signs List 13 Upper chamber 14 Lower chamber 15 Piston 16 Inner cylinder (cylinder) 18 Piston rod 19 Rod guide (end plate) 30 Large diameter part 31 Step part 32 Small diameter part 34 Stopper sheet 39 Rebound stopper 40 Rebound cushion 41 Inner peripheral wall 42 Projecting part 43 Notch

Claims (13)

[Claims] 1. A cylinder filled with a buffering liquid therein, a piston slidably fitted in the cylinder to partition the cylinder into two liquid chambers, and a large diameter portion and a step portion. A small-diameter portion following the large-diameter portion is formed, the piston is fixed to the small-diameter portion, and the large-diameter portion slidably penetrates an end plate mounted on the cylinder; A stopper sheet fitted to the small-diameter portion so as to be engaged with the stepped portion of the piston rod and receiving the piston, wherein the piston has one end face abutting on the stopper sheet. A rebound cushion formed of an elastic body fitted to the large-diameter portion of the rod, the other end surface of which is in contact with the end plate to regulate the sliding end of the piston toward the end plate; Features That hydraulic shock absorber. 2. The hydraulic shock absorber according to claim 1, wherein the rebound cushion is fitted to the large-diameter portion of the piston rod with an interference. 3. The rebound cushion includes an inner peripheral wall having an inner diameter larger than the large diameter portion of the piston rod,
At least 3 projecting from the inner peripheral wall at equal intervals along the circumferential direction and pressing against the large diameter portion of the piston rod
3. The hydraulic shock absorber according to claim 2, comprising two protrusions. 4. The hydraulic pressure damper according to claim 1, wherein the rebound cushion has a notch on an outer periphery thereof. 5. The hydraulic shock absorber according to claim 4, wherein a plurality of the notches are provided at equal intervals along a circumferential direction. 6. The liquid according to claim 1, wherein one end and the other end of the rebound cushion are formed symmetrically with respect to the center in the longitudinal direction. Pressure buffer. 7. A cylinder filled with a buffering liquid therein, a piston slidably fitted in the cylinder to partition the cylinder into two liquid chambers, and a large diameter portion and a step portion. A small-diameter portion following the large-diameter portion is formed, the piston is fixed to the small-diameter portion, and the large-diameter portion slidably penetrates an end plate mounted on the cylinder; A stopper sheet fitted to the small-diameter portion so as to be engaged with the stepped portion of the piston rod and receiving the piston, wherein the piston has one end face abutting on the stopper sheet. A rebound stopper fitted to the large-diameter portion of the rod; and a rebound stopper fitted to the large-diameter portion of the piston rod such that one end surface is in contact with the other end surface of the rebound stopper, and the other end surface is the other end. Contact with the hydraulic shock absorber, characterized in that it comprises a rebound cushion which is formed of an elastic body capable of regulating the sliding end of the piston to the end plate side. 8. The hydraulic shock absorber according to claim 7, wherein the rebound stopper is formed of an elastic body that is harder than the rebound cushion. 9. The hydraulic shock absorber according to claim 7, wherein the rebound stopper is fitted to the large-diameter portion of the piston rod with an interference. 10. The rebound stopper comprises: an inner peripheral wall having an inner diameter larger than the large diameter portion of the piston rod;
At least 3 projecting from the inner peripheral wall at equal intervals along the circumferential direction and pressing against the large diameter portion of the piston rod
10. The hydraulic shock absorber according to claim 9, wherein the hydraulic shock absorber has two protrusions. 11. The hydraulic pressure damper according to claim 7, wherein the rebound stopper has a notch on the outer periphery thereof. 12. The apparatus according to claim 1, wherein a plurality of the notches are provided at equal intervals along a circumferential direction.
2. The hydraulic shock absorber according to 1. 13. The liquid according to claim 7, wherein one end and the other end of the rebound stopper are formed symmetrically with respect to the center in the longitudinal direction. Pressure buffer.