JP2002266924A - Damping valve part structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To optimize an application, for example, to a vehicle-mounted hydraulic shock absorber by generating damping force according to setting even when a piston speed shifts from a low-speed range state to a high-speed range state. SOLUTION: A damping valve part structure has an annular spacer 8 disposed between an annular support 6 disposed on the back side of an annular leaf valve 5 and an annular valve stopper 7 disposed on the back side of the annular support 6 to restrict the lift of the annular support 6, in order to allow a lift of the annular leaf valve 5 and the annular support 6. An annular elastic plate material 11 is disposed between the annular spacer 8 and the valve stopper 7, and a surface of the valve stopper 7 opposite to the spacer 8 is provided with an annular recess S for allowing a flexure of the inner circumferential side of the annular elastic plate material 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damping valve structure, and more particularly to an improvement in a damping valve structure in a hydraulic shock absorber.

[0002]

2. Description of the Related Art There have been various proposals for a damping valve portion structure in a hydraulic shock absorber. Among them, for example, a damping valve portion structure shown in FIG. It is embodied in a piston section (not shown).

More specifically, the piston section has a piston 3 as a valve seat member connected to a distal end, which is a lower end in the drawing, of a piston rod 2 that is inserted into and retracted from the cylinder 1. Become.

[0004] The piston 3 is provided with an expansion port 3a and a compression port 3b.
Assuming that the downstream end, which is the lower end in FIG. 3A, is openably closed by the extension side damping valve 4 and the downstream end, which is the upper end of the compression side port 3b, is openably closed by the compression side damping valve 5. I have.

Incidentally, the piston 3 is slidably housed in the cylinder 1 and has an upper oil chamber R1 above the piston 3 in the figure and a lower part of the piston 3 in the figure. A lower oil chamber R2 is defined.

On the other hand, the expansion-side damping valve 4 is composed of a laminated annular leaf valve, and the outer circumference is bent while the inner circumference is fixed, and the outer circumference is bent by hydraulic action from the expansion port 3a. When the damping force is set.

On the other hand, in the pressure-side damping valve 5 which is also composed of laminated annular leaf valves, the outer peripheral side is on the bending side, but the inner peripheral end is not fixed.
It is said that it will be fixed in a floating state.

That is, the damping valve section structure having the stacked annular leaf valve, ie, the pressure side damping valve 5, is as follows.
An annular support 6 disposed on the back side of the compression-side damping valve 5 and allowing a large deflection on the outer peripheral side of the compression-side damping valve 5, and a lift on the outer peripheral end of the annular support 6 disposed on the rear side of the annular support 6 An annular valve stopper 7 for regulating the amount, and a lift between the inner peripheral end of the compression side damping valve 5 and the inner peripheral end of the annular support 6 which is disposed between the inner peripheral side of the valve stopper 7 and the inner peripheral side of the annular support 6. And an allowable spacer 8.

The annular support 6 is disposed adjacent to the compression damping valve 5 via an annular seat 9 adjacent to the inner peripheral side thereof, and is configured to lift together with the compression damping valve 5 when lifted.

The spacer 8 is made of an O-ring made of an elastic material such as oil-resistant rubber, for example, as shown in the figure, and is collapsed when the annular support 6 is lifted by an external force. This is allowed, and when the external force for lifting the annular support 6 disappears, the annular support 6 is restored to the old state and the annular support 6 is pushed back.

The pressure-side damping valve 5, the ring seat 9, the annular support 6, and the spacer 8 are connected to a guide member 10 provided on the outer periphery of the tip fitting portion 2a of the piston rod 2.
Is mounted on the outer periphery of the vehicle so as to be able to move up and down.

Therefore, in this damping valve portion structure, when the hydraulic pressure when the piston speed is in the low speed range acts on the outer peripheral side of the compression side damping valve 5 via the compression side port 3b, the O-ring as the spacer 8 is formed. A slight collapse will allow the annular support 6, ie the compression damping valve 5, to be lifted, albeit slightly.

As a result, a gap is formed between the outer peripheral side of the compression-side damping valve 5 and the valve seat portion 3c of the piston 3, and the oil passes through the gap, whereby a low damping force can be generated. Become.

When the hydraulic pressure acting on the compression-side damping valve 5 increases as the piston speed increases, the amount of deflection on the outer peripheral side of the compression-side damping valve 5 increases, and a relatively large damping force can be generated. become.

Furthermore, when the amount of deflection on the outer peripheral side of the compression side damping valve 5 increases, the outer peripheral side comes into contact with the annular support 6, and when the outer peripheral side of the annular support 6 also bends, the damping becomes larger. When a force is generated and the bending of the outer peripheral side of the annular support 6 is restricted by the valve stopper 7, the maximum damping force is generated.

That is, in the above-described conventional damping valve structure, the damping force when the piston speed is in the low speed region can be generated as set, and the damping force when the piston speed is in the middle and high speed region. Will be higher.

[0017]

However, in the above-described conventional damping valve structure, the damping force when the piston speed is in the low speed region can be generated as set, but the piston speed is in the high speed region. It may be pointed out that the resulting damping force becomes abnormally high.

That is, in the above-described conventional damping valve structure, the O-ring serving as the spacer 8 has a characteristic of reducing the restoring force against a slight crush, that is, the repulsive force, but extremely increasing the repulsive force against a large crush. There is.

Therefore, in the spacer 8 composed of the O-ring, the annular support 6 cannot be lifted largely due to its large collapse, that is, in other words, the spacer 8 tends to prevent a large lift in the compression side damping valve 5. Become.

Therefore, even if the oil pressure when the piston speed is in the high speed range acts on the compression damping valve 5, the O-ring serving as the spacer 8 is not significantly collapsed.
In the case of the compression-side damping valve 5, although it is through the annular support 6, the valve stopper 7 is prevented from being lifted any more. Will be passed.

As a result, in the above-described conventional damping valve portion structure, the damping force when the piston speed is in the low speed range can be generated as set, but the piston speed exceeds the low speed range, and especially when the piston speed exceeds the low speed range. The damping force in the region becomes abnormally high.

When the hydraulic shock absorber having the damping valve portion structure is mounted on a vehicle, for example, there is a concern that the vehicle may not only improve the ride comfort but also deteriorate.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a damping device that can properly adjust the damping speed even when the piston speed changes from a low speed range to a high speed range. An object of the present invention is to provide a damping valve portion structure that enables generation of a force and is optimally used for a hydraulic shock absorber mounted on a vehicle, for example.

[0024]

SUMMARY OF THE INVENTION In order to achieve the above-mentioned object, the present invention basically comprises an annular leaf valve which generates a damping force at the time of bending on an outer peripheral side, and a back surface of the annular leaf valve. An annular support that is arranged on the side and allows a large deflection on the outer peripheral side of the annular leaf valve; an annular valve stopper that is arranged on the rear side of the annular support and regulates a lift amount of an outer peripheral end of the annular support; In a damping valve part structure having a spacer that is disposed between the inner peripheral side of the valve stopper and the inner peripheral side of the annular support and that allows a lift of the inner peripheral end of the annular leaf valve and the annular support, While the annular elastic plate is disposed between the spacer and the valve stopper, the annular elastic plate is disposed on the side of the valve stopper facing the spacer. Annular recess to permit deflection of the circumferential side and is formed.

In the above structure, more specifically, the annular concave portion is formed by retreating an inner peripheral side of a surface of the valve stopper facing the spacer to an appropriate depth. It is assumed that an annular sheet body having an appropriate thickness is formed adjacent to the outer peripheral side of the surface facing the spacer.

The spacer is made of an O-ring made of an elastic material such as oil-resistant rubber or a cylindrical body made of a hard material which does not elastically deform such as metal.

Further, the elastic plate member is assumed to be a single sheet formed in the shape of an annular leaf valve, or a laminate of a plurality of sheets formed in the shape of an annular leaf valve having the same diameter.

It is preferable that the annular leaf valve is formed by stacking a plurality of annular leaf valves having different diameters. At this time, on the rear side, the diameter gradually increases from the outer peripheral end toward the inner peripheral end. It is assumed that the diameter is set to be small.

The annular support is formed in the same manner as the annular leaf valve. At this time, the diameter of the annular support gradually increases from the outer peripheral end toward the inner peripheral end on the surface facing the back surface of the annular leaf valve. It is assumed that the diameter is set to be small.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described based on the illustrated embodiment. However, as shown in FIG. 1, even in the damping valve portion structure according to the present invention, basically,
It has the same configuration as the conventional damping valve structure shown in FIG.

Therefore, the parts having the same structure in the damping valve part structure according to the present invention as those in the conventional damping valve part structure are designated by the same reference numerals in the drawings only, and unless necessary. A detailed description is omitted, and the following description focuses on features that are characteristic of the present invention.

That is, according to the present invention, first, while the annular elastic plate 11 is disposed between the spacer 8 and the annular valve stopper 7, the surface of the valve stopper 7 facing the spacer 8 It is assumed that an annular concave portion S is formed to allow the inner peripheral side of the elastic plate member 11 to bend.

At this time, as shown in the figure, the elastic plate member 11 is formed by laminating a plurality of sheets formed in the shape of an annular leaf valve having the same diameter. It states that the spring force can be changed.

Therefore, as long as the elastic plate member 11 can have a predetermined spring force, although it is not shown, it is a matter of course that the elastic plate member 11 may be formed as a single annular leaf valve.

As described above, according to the present invention, the elastic plate 11
Therefore, even if the same spring force can be obtained, compared to the case of using a coil spring, not only the characteristics are stable, but also there is no need to prepare many types of coil springs with different spring forces. In addition to this, it is advantageous in that the number of sheets can be increased without requiring a large space.

On the other hand, the annular concave portion S
The valve stopper 7 is formed by retreating by cutting the inner peripheral side of the surface facing the spacer 8 to an appropriate depth.

In the meantime, the annular concave portion S has an appropriate thickness of an annular portion on the outer surface of the surface of the valve stopper 7 facing the spacer 8, that is, the lower surface in FIG. It is described that the sheet is formed by adjoining the sheet members 12.

Therefore, the position shown in FIG. 1 is advantageous in that a component called the annular seat body 12 is not required, and the position shown in FIG. 2 is advantageous in that a so-called groove is not required in the valve stopper 7. Becomes

By the way, as for the spacer 8, as shown in the drawing, as in the case of the conventional example shown in FIG. 3, it is assumed that the spacer 8 is made of an O-ring made of an elastic material such as oil-resistant rubber. Therefore, the spacer 8 formed of the O-ring can be expected to slightly collapse when an external force acts, and therefore, the cracking pressure in the compression-side damping valve 5 can be set low.

The pressure-side damping valve 5 is preferably formed by stacking a plurality of annular leaf valves having different diameters.
At this time, it is assumed that the diameter is set to gradually decrease from the outer peripheral end toward the inner peripheral end on the back side.

Thus, in the compression side damping valve 5, when the outer peripheral side is bent to generate a damping force, the rigidity increases as the bending increases, and a high damping force can be generated.

The annular support 6 is formed in the same form as the compression-side damping valve 5. At this time, the diameter of the annular support 6 is changed from the outer peripheral end to the inner peripheral end on the surface facing the back surface of the compression-side damping valve 5. It is assumed that the diameter is gradually set to gradually decrease.

As a result, when the compression-side damping valve 5 is bent, the contact position of the annular support 6 serving as a fulcrum is sequentially changed, so that the set damping characteristic can be realized.

Therefore, in the damping valve portion structure formed as described above, when the inner peripheral side of the elastic plate member 11 is bent, the inner peripheral side enters the annular concave portion S. The spacer 8 adjacent to the elastic plate member 11 slides along the outer periphery of the guide member 10 and escapes into the annular concave portion S.

Since the spacer 8 escapes, that is, retreats, a large lift in the annular support 7 adjacent to the spacer 8 becomes possible,
Therefore, a large lift in the compression side damping valve 5 becomes possible.

As a result, for example, when the oil pressure in the medium to high speed region of the piston speed acts on the compression-side damping valve 5, the outer peripheral side thereof is greatly bent and the O-ring is largely collapsed. The O-ring retreats so as to escape into the annular groove S due to the bending of the elastic plate material 11.

Therefore, the annular support 6 can be greatly lifted together with the compression-side damping valve 5, and in the above-described conventional example, the O-ring as the spacer 8 cannot be retracted, so that the O-ring is significantly crushed. As a result, the present invention generates a damping force having a proper height which is not too high, in comparison with the fact that the damping force becomes extremely high.

Next, in the embodiment shown in FIG. 2, as described above, the annular concave portion S is formed by adjoining the annular sheet member 12 having an appropriate thickness on the outer peripheral side of the surface of the valve stopper 7 opposed to the spacer 8. On the other hand, the spacer 8 is made of a cylindrical body made of a hard material that does not elastically deform, such as metal.

Therefore, in this embodiment, the spacer 8 cannot be expected to be slightly crushed when an external force is applied as in the case of the O-ring, so that the piston speed in the compression side damping valve 5 is low. The attenuation characteristic when in the region can be set to a relatively large gradient.

Also in this embodiment, when an external force from the compression-side damping valve 5 acts and the inner peripheral side of the elastic plate 11 bends, the inner peripheral side enters the annular concave portion S. Then, the cylindrical body serving as the spacer 8 adjacent to the elastic plate member 11 slides along the outer periphery of the guide member 10 and escapes into the annular concave portion S.

Further, the cylindrical body escapes, that is,
The retraction allows a large lift in the annular support 7 adjacent to this cylinder and thus a large lift in the compression damping valve 5.

When the hydraulic pressure acting on the compression-side damping valve 5 increases as the piston speed increases, the amount of deflection on the outer peripheral side of the compression-side damping valve 5 increases, and a large set damping force can be generated. .

That is, even with the damping valve portion structure of the present invention, the damping force when the piston speed is in the low speed range can be generated as set, and the damping force when the piston speed is in the middle speed range can also be generated. It can be generated as set, and the damping force when the piston speed is in the high-speed range can be appropriately increased without unnecessarily increasing.

As described above, the case where the damping valve portion structure is embodied in the piston portion of the hydraulic shock absorber and the case where the annular leaf valve is a compression side damping valve have been described as examples. From an intended point, the annular leaf valve may be an extension damping valve in a piston portion, and the annular leaf valve may be a compression damping valve in a base valve portion in a cylinder. Of course, in that case, it goes without saying that the function and effect of the damping valve portion structure are the same.

[0055]

As described above, according to the present invention, the spacer adjacent to the rear side of the annular leaf valve via the annular support is locked from behind by the elastic plate, while the elastic plate is Makes the flexible side penetrate into the annular recess formed on the back side, so that the spacer retreats and escapes, so that the spacer cannot be retreated, so that a very large repulsive force is not generated. Therefore, it is possible to avoid a situation in which the annular leaf valve generates a so-called excessively high damping force.

In addition, when the spacer is formed of a so-called crushable O-ring, the O-ring is slightly crushed by the hydraulic pressure acting on the annular leaf valve. Therefore, the cracking pressure in the annular leaf valve is set low. This is advantageous in that, for example, a low damping force can be smoothly generated in a range from a very low piston speed to a low piston speed.

When the spacer is formed of a so-called non-crushable cylinder, the damping characteristic of the annular leaf valve when the piston speed is in a low speed region can be set to a relatively large gradient, and a high damping force can be obtained from the beginning of operation. Is advantageous in that it can be adapted for use when expecting to occur.

In the present invention, if the annular concave portion is formed by adjoining an annular sheet member having an appropriate thickness on the outer peripheral side of the surface of the valve stopper facing the spacer, Just the placement work is enough,
When the annular recess is formed by retreating the inner peripheral side of the surface of the valve stopper facing the spacer to an appropriate depth or the like, it is only necessary to form a so-called groove in the valve stopper. There is.

As a result, according to the present invention, even when the piston speed changes from the low speed range to the high speed range, it is possible to generate the damping force as set, for example, to utilize the piston in a hydraulic shock absorber mounted on a vehicle. And the versatility can be expected to be improved.

[Brief description of the drawings]

FIG. 1 is a partial longitudinal sectional view showing a state in which a damping valve section structure according to the present invention is embodied in a piston section in a cylinder.

FIG. 2 is a diagram showing another embodiment in the same manner as FIG. 1;

FIG. 3 is a view showing a structure of a conventional damping valve section, similarly to FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cylinder 2 Piston rod 2a Lower end fitting part 3 Piston 3a Extension port 3b Compression port 3c Valve seat part 4 Extension damping valve 5 Compression damping valve 6 Annular support 7 Valve stopper 8 Spacer 9 Ring seat 10 Guide member 11 Elastic plate material 12 Annular sheet body R1 Upper oil chamber R2 Lower oil chamber S Annular recess

Claims (5)

[Claims] 1. An annular leaf valve that generates a damping force when flexing on an outer peripheral side, an annular support disposed on a back side of the annular leaf valve and allowing a large flexure on an outer peripheral side of the annular leaf valve, and an annular support An annular valve stopper disposed behind the support to regulate a lift amount of an outer peripheral end of the annular support; and an annular leaf disposed between an inner peripheral side of the valve stopper and an inner peripheral side of the annular support. In a damping valve portion structure having a valve and a spacer that allows the inner peripheral end of the annular support to be lifted, an annular elastic plate material is disposed between the spacer and the valve stopper, while the spacer in the valve stopper is An annular concave portion is formed on an opposing surface side of the annular elastic plate so as to allow the inner peripheral side to bend. 2. The damping valve part structure according to claim 1, wherein the annular concave portion is formed by retreating an inner peripheral side of a surface of the valve stopper facing the spacer to an appropriate depth. 3. The damping valve part structure according to claim 1, wherein the annular concave portion is formed by adjoining an annular seat body having an appropriate thickness on an outer peripheral side of a surface of the valve stopper facing the spacer. 4. The damping valve part structure according to claim 1, wherein the spacer is formed of an O-ring formed of a material having high elasticity such as oil-resistant rubber. 5. The damping valve part structure according to claim 1, wherein the spacer is formed of a cylindrical body made of a hard material that does not elastically deform such as metal.