JPH08170678A - Non-return valve structure - Google Patents

Abstract

PURPOSE: To make utilization optimum in a hydraulic shock absorber by having a reinforcing member of impeding deforming a distortion end side of a non- return valve into a wave shape, when open operated the non-return valve, in the distortion end side of the non-return valve. CONSTITUTION: In a back surface in a distortion end side, which is a peripheral end side of an annular leaf valve 1, a floating annular leaf valve 5, which is a reinforcing member, is placed adjacent, to apparently increase a thickness in the distortion end side of the annular leaf valve 1. Accordingly, energizing force from a pawl-type leaf spring 3 acts in a back side of the floating annular leaf valve 5. As a result, in the case of distorting the annular leaf valve 1, the floating annular leaf valve 5 only rises while being adjacent to a distorted end of the annular leaf valve 1, to prevent impeding a distortion characteristic of the annular leaf valve 1 itself. Further here without deforming the distortion end side of the annular leaf valve 1 into a wave shape, a prescribed suction function by the annular leaf valve 1 can be displayed with no obstacle.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a non-retan valve structure which is most suitable for use in a hydraulic shock absorber such as a shock absorber or a front fork.

[0002]

2. Description of the Related Art Generally, in a hydraulic shock absorber such as a shock absorber or a front fork, a main valve provided in a piston portion, a base valve portion, or the like is used to set a predetermined expansion side and a compression side when the expansion / contraction operation is performed. It is configured to generate a damping force.

In this case, a so-called non-return valve is generally arranged in the piston part and the base valve part together with the main valve. In this case, the non-return valve structure is, for example, as shown in FIG. There is a structure as shown in.

That is, in this conventional example, the non-return valve is composed of an annular leaf valve 1, and the annular leaf valve 1 is a valve seat member, that is, in the illustrated example,
It is assumed that the piston body 2 constituting the piston portion P slidably accommodated in the cylinder C is adjoined to one end surface which is an upper end surface in the drawing in a detachable and seatable manner.

Incidentally, the annular leaf valve 1 is arranged in a manner of fixing the inner peripheral end, and its outer peripheral end side is set to the flexible end side which is adjacent to the one end surface of the piston body 2 so as to be detachably seated. The flexible end has a port for opening the piston body 2, that is,
In the illustrated example, the outer peripheral side pressure side port 2b parallel to the inner peripheral side expansion side port 2a is configured to openably close the downstream side end that is the upper end in the figure.

The annular leaf valve 1 is urged by its urging member from the rear side of its flexible end side, that is, in the illustrated example, a claw leaf spring 3 which is a tripod type spring. Then, a predetermined initial load is applied.

The annular leaf valve 1 has a plurality of through holes 1a in the inner peripheral side portion thereof which face the extension side port 2a.
have.

Therefore, in the above-described conventional non-return valve structure, the annular leaf valve 1 which is a non-return valve is set to have a thin tendency, so that the non-return valve easily bends and smoothly exhibits a predetermined suction performance. You will get it.

However, in the above-mentioned conventional example,
When the annular leaf valve 1 is set to be thin,
Since the claw-shaped leaf spring 3 is a three-legged spring, when the opening operation of the annular leaf valve 1 is started,
A situation in which the portion that is not directly receiving the urging force from the claw-shaped leaf spring 3 opens first and then opens entirely, that is, the phenomenon that the bending end side of the annular leaf valve 1 deforms into a waveform become.

As a result, the characteristics of the non-return valve composed of the annular leaf valve 1 may become unstable, and when the hydraulic shock absorber having the non-return valve structure is mounted in the vehicle, the riding comfort of the vehicle is improved. It is also feared that it will be a factor that worsens.

Therefore, it may be proposed to prevent the above-mentioned waveform deformation on the bending end side by setting the annular leaf valve 1 to have a thick wall tendency, but in this case, the plate thickness of the annular leaf valve 1 is large. Therefore, there is a fear that the rigidity is increased, the rapid opening operation of the annular leaf valve 1 cannot be expected, and conversely, a vacuum phenomenon due to insufficient suction is likely to be caused.

The present invention was devised in view of the above-mentioned circumstances, and an object thereof is to exhibit a predetermined suction function without causing waveform deformation on the bending end side of a non-retan valve. The purpose of the present invention is to provide a non-return valve structure that is optimal for use in hydraulic shock absorbers such as shock absorbers and front forks.

[0013]

In order to achieve the above-mentioned object, the structure of the present invention has a valve seat member in which an outer peripheral side port parallel to an inner peripheral side port is opened, and an inner peripheral end is fixed. A non-return valve which is disposed on a flexible end side of which the outer peripheral end side is adjoined to one end surface of the valve seat member so as to be separably seated, and the downstream end of the outer peripheral side port is openly closed. A non-return valve structure comprising: a non-return valve structure, which is disposed on the back side of the non-return valve and biases the non-return valve so that the non-return valve is seated on one end surface of the valve seat member. A non-return valve structure having a reinforcing member on the flexible end side of the valve for preventing the flexible end side of the non-return valve from being deformed into a waveform when the non-return valve is opened. , The non-return valve is an annular leaf valve, the reinforcing member is a floating annular leaf valve, and the biasing member is a claw leaf spring, and the floating annular leaf valve can float on the back surface of the annular leaf valve. And is formed so that the biasing force from the claw-shaped leaf spring acts on the back surface of the floating annular leaf valve.

[0014]

Therefore, the non-return valve flexes so as to overcome the urging force of the urging member at the time of its opening operation so that its outer peripheral end is separated from the one end face of the valve seat member.

At this time, in the case where the reinforcing member disposed on the rear surface on the flexible end side which is the outer peripheral end side of the non-retan valve is adjacent to the rear surface on the flexible end side of the non-retan valve, the non-retan valve is provided. It does not hinder the opening operation of the non-return valve because it is simply raised during the opening operation.

Further, when the urging force of the urging member is appropriately selected, it is possible to improve the suction property by the non-return valve structure, or the non-return valve structure can be diverted to the back valve structure.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention will be described below with reference to the illustrated embodiment. The hydraulic shock absorber according to this embodiment, as shown in FIG. 1, seems to be a hydraulic shock absorber of this kind. In addition, the piston rod P is inserted into the cylinder C so that the piston rod R can be retracted and retracted.

The piston portion P is slidably accommodated in the cylinder C, and the rod side oil chamber A is accommodated in the cylinder C.
1 and a piston-side oil chamber A2 are defined to have a piston body 2 which is set as a valve seat member. It has a non-return valve.

That is, the non-return valve is composed of an annular leaf valve 1 (see FIG. 2), is arranged in a manner of fixing the inner peripheral end, and its outer peripheral side is adjacent to one end surface of the piston body 2 so as to be seated and detachable. The downstream side end, which is the upper end in the drawing, of the outer peripheral side compression side port 2b that is set to the flexible end side and is parallel to the inner peripheral side expansion side port 2a opened in the piston body 2 can be opened. It is configured to close.

In this embodiment, the annular leaf valve 1 has a plurality of through holes 1a facing the extension side port 2a in the inner peripheral side portion thereof (see FIG. 2). The downstream side end, which is the lower end in the figure of the side port 2a, is openably closed by an expansion side damping valve 4, which is a main valve on the expansion side.

The non-return valve, that is, the annular leaf valve 1 is basically a biasing member whose flexible end side is arranged on the back side thereof, that is, in the illustrated example, a three-legged type. It is assumed that the leaf spring 3 is urged by the urging force of the claw-shaped leaf spring 3 as a spring and a predetermined initial load is applied.

However, in this embodiment, the urging force from the pawl type leaf spring 3 is directly applied to the annular leaf valve 1.
It does not act on the back surface side of the above, but rather on the back surface side of the reinforcing member adjacent to the back surface on the flexible end side of the annular leaf valve 1.

That is, in this embodiment, a floating type annular leaf valve 5 serving as a reinforcing member is adjacent to the rear surface of the annular leaf valve 1 on the side of the outer peripheral end, which is the bending end. By adjoining the mold annular leaf valve 5,
The wall thickness of the annular leaf valve 1 on the flexible end side is apparently increased.

Therefore, in this embodiment, the biasing force from the claw-shaped leaf spring 3 acts on the rear surface side of the floating annular leaf valve 5 which is adjacent to the rear surface of the annular leaf valve 1 on the flexible end side. I am trying.

The floating annular leaf valve 5 is arranged so that it can be moved up and down by using a spacer 6 that holds the inner peripheral end of the annular leaf valve 1 between the inner peripheral end of the piston body 2 and the inner peripheral end as a guide member. As shown in FIG. 3, a plurality of guide portions 5a adjacent to the outer circumference of the spacer 6 and a through hole portion 5b defined by the guide portions 5a are formed on the inner peripheral side thereof, as shown in FIG. To have.

Incidentally, it goes without saying that the through hole 1a of the annular leaf valve 1 is aimed at the through hole portion 5b.

As described above, in this embodiment, since the floating type annular leaf valve 5 is adjacent to the rear face of the annular leaf valve 1 which is the outer peripheral end side of the annular leaf valve 1, the annular leaf valve 1 bends. The wall thickness on the end side is apparently thickened and reinforced.

As a result, when the annular leaf valve 1 bends, the floating annular leaf valve 5 becomes the annular leaf valve 1.
Although it is adjacent to the bending end of the annular leaf valve 1, it only rises and does not hinder the bending characteristics of the annular leaf valve 1 itself.

When the annular leaf valve 1 bends,
Since the floating annular leaf valve 5 is adjacent to the flexible end of the annular leaf valve 1, it is possible to prevent the waveform deformation from occurring on the flexible end side of the annular leaf valve 1 in advance.

Therefore, when the annular leaf valve 1 is set to be thin, the bending characteristics of the annular leaf valve 1 itself are not changed, and at that time, the bending end side of the annular leaf valve 1 undergoes waveform deformation. Therefore, the predetermined suction function of the annular leaf valve 1 can be exhibited without any obstacle.

By the way, the floating type annular leaf valve 5 is used.
In the illustrated example, the outer diameter is set so as to match the outer diameter of the annular leaf valve 1 which is a non-return valve, but from the role of the floating annular leaf valve 5, that is, the reinforcing member. If so, it goes without saying that the outer diameter does not have to match the outer diameter of the annular leaf valve 1.

Therefore, the outer diameter of the floating annular leaf valve 5 may be so-called recessed from the outer diameter of the annular leaf valve 1 as long as it exerts a predetermined function as a reinforcing member, and the annular leaf valve 1 Needless to say, they may be projected as long as they do not hinder the operation (see FIG. 4).

As described above, in the present invention, the wall thickness of the annular leaf valve 1 is not made thick as a whole, but only the wall thickness at the bending end side is apparently made thicker. It suffices to prevent the waveform from being deformed as if only increasing the rigidity. Therefore, the following embodiment may be used instead of the above embodiment.

That is, first, as shown in FIG. 4, it is assumed that the floating annular leaf valve 5 as a reinforcing member has an annular flange portion 5c set downward at the outer peripheral end thereof. The outer peripheral end of the annular leaf valve 1, which is a non-return valve, may be set to be close to the inner periphery of the portion 5c.

In the case of this embodiment, since the floating annular leaf valve 5 is guided by the outer peripheral end of the annular leaf valve 1, in the floating annular leaf valve 5 as in the above-mentioned embodiments. Guide part 5a on the inner peripheral side
(See FIG. 3) does not have to be formed, and the inner peripheral side can be set to the through hole portion 5b over the entire circumference.

As a result, in the case of this embodiment, there is an advantage that the mobility which is different to the spacer 6 on the inner peripheral side is improved, and the flowability of the hydraulic oil into the extension side port 2a is improved. There are advantages.

Next, as shown in FIG. 5, the arrangement positions of the non-return valve and the reinforcing member may be reversed upside down.

In the case of this embodiment, the pressure side port 2
Floating type annular leaf valve 5 whose downstream end of b is a reinforcing member
In view of the fact that the floating annular leaf valve 5 is generally formed to be thicker than the annular leaf valve 1 which is a non-return valve, the waveform on the outer peripheral end side of the non-return valve is closed. This is advantageous in that deformation is less likely to be exhibited.

Further, although not shown, for example, in the embodiment shown in FIG. 1, a reinforcing member may be integrated with the rear surface of the non-return valve on the outer peripheral end side by welding or using an adhesive material.

According to this embodiment, the non-return valve and the reinforcing member can be assembled in a single operation.
This is advantageous in that the number of assembling steps can be reduced.

In each of the above-mentioned embodiments, the non-return valve is arranged in the piston portion P in the cylinder C and functions as a so-called extension side check valve, but instead of this, as shown in FIG. , Non-return valve is cylinder C
Needless to say, it may be set to function as a so-called pressure side check valve in the base valve portion B disposed inside the lower end of the.

In this case, the non-return valve is the annular leaf valve 1 (see FIG. 2) as in the case of the embodiment shown in FIG.
A flexible end that is adjacent to the one end surface that is the upper end surface in the figure of the valve block 11 that is arranged in a manner of fixing the inner peripheral end and the outer peripheral end side thereof is set as the valve seat member so as to be detachably seated. Is set to the side.

In the non-return valve, that is, the annular leaf valve 1, the expansion side port 11b on the outer peripheral side in which the flexible end side is parallel to the pressure side port 11a on the inner peripheral side opened in the valve block 11 is shown. It is set to openably close the downstream end that is the upper end.

The downstream side end, which is the lower end of the pressure side port 11a in the figure, is the pressure side damping valve 1 which is the main valve on the pressure side.
It is closed so that it can be opened at 2.

It is assumed that a floating type annular leaf valve 5 (see FIG. 3), which is a reinforcing member, is adjacent to the rear surface of the annular leaf valve 1 on the side of the outer peripheral end, which is the bending end, of the floating type annular leaf valve 5. Due to the adjacency, the wall thickness of the annular leaf valve 1 on the flexible end side is apparently increased.

On the back surface of the floating annular leaf valve 5, an urging member, that is, in the illustrated example, an urging force from a claw leaf spring 3 which is a tripod spring is applied. Then, a predetermined initial load is applied to the flexible end side of the annular leaf valve 1 via the floating annular leaf valve 5.

In this embodiment, although not shown, an outer cylinder is provided outside the cylinder C, and a reservoir chamber is formed between the outer cylinder and the cylinder C. It is assumed that the base valve portion B, that is, the non-return valve and the pressure side main valve communicate with the piston side oil chamber A2 in the cylinder C.

Therefore, in this embodiment as well, similar to the case of the above-described embodiment, the predetermined suction function of the non-retan valve is of course exhibited, and the urging force of the urging member is appropriately adjusted. By adjusting, the non-return valve can also function as a back valve.

Also in this embodiment, it is possible to change the structure of the non-return valve like the embodiment shown in FIGS. 4 and 5 and the above-mentioned embodiments not shown. Of course.

In each of the above-mentioned embodiments, the urging member is
Although it is assumed that the leaf spring 3 is a claw-shaped leaf spring that is a three-legged spring, it may be a conical spring instead.

In this case, generally, the conical spring tends to weaken the biasing force as compared with the claw leaf spring 3, so that it is suitable for use when giving priority to the suction function of the non-return valve.

In each of the above-described embodiments, the reinforcing member is formed separately from the non-return valve and is set adjacent to the non-return valve. The object of the invention is not to cause the corrugated deformation on the bending end side of the non-return valve, so that the biasing member including the claw-shaped leaf spring 3 may also serve as the reinforcing member.

When the urging member also serves as the reinforcing member, the non-retan valve is directly urged by the urging member, so that the number of members is not increased as compared with the conventional structure. Further, it is advantageous in that the predetermined performance can be improved without causing so-called design change.

[0054]

As described above, according to the present invention, the non-return valve structure may be set to be relatively thin, and the non-return valve structure is set to be relatively thick on the flexible end side which is the outer peripheral end side. Since the reinforcing members that are
In a state where the bending characteristics of the non-return valve itself are not changed, the waveform deformation at the bending end side is prevented, and there is an advantage that the suction function of the non-return valve is exhibited as set.

Further, according to the present invention, when the biasing member is a claw leaf spring which is a tripod type spring, the so-called back pressure in the non-retan valve is compared to the case where it is a conical spring. There is an advantage that the setting can be made higher and the non-return valve structure can be diverted to the back valve structure.

According to the present invention, when a conical spring is used instead of the pawl type leaf spring as the urging member, the urging force of the urging member is weakened as compared with the pawl type leaf spring. Is possible, and there is an advantage that it is effective for use when the above-mentioned suction property is prioritized.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view mainly showing a piston portion in a hydraulic shock absorber according to an embodiment of the present invention.

FIG. 2 is a plan view showing an annular leaf valve that is a non-return valve.

FIG. 3 is a plan view showing a floating annular leaf valve that is a reinforcing member.

FIG. 4 is a partial vertical cross-sectional view showing, in an enlarged manner, another embodiment of the non-return valve portion.

FIG. 5 is a partial vertical cross-sectional view showing still another embodiment of the non-return valve portion similarly to FIG.

FIG. 6 is a vertical cross-sectional view mainly showing a base valve portion of a hydraulic shock absorber according to another embodiment of the present invention.

FIG. 7 is a vertical cross-sectional view showing a piston portion in a hydraulic shock absorber as a conventional example, similar to FIG.

[Explanation of symbols]

 1 Non-return valve, annular leaf valve 2 Valve seat member, piston body 2a Inner side port, expansion side port 2b, Outer side port, pressure side port 3 Biasing member, claw leaf spring 5 Reinforcing member, floating type annular leaf valve 11 Valve seat member Valve block 11a Inner peripheral side port Pressure side port 11b Outer peripheral side port Expansion side port

Claims (2)

[Claims] 1. A valve seat member in which an outer peripheral port parallel to an inner peripheral port is opened, and an inner peripheral end is fixed to the valve seat member, and the outer peripheral end is seated on one end surface of the valve seat member. A non-retan valve which is adjacent to the non-retan valve and is arranged on the back side of the non-retan valve so as to openably close the downstream end of the outer peripheral port, and the non-retan valve disposed on the back side of the non-retan valve. In a non-return valve structure that includes a biasing member that biases the seat member to be seated on one end surface thereof, a non-retan valve is provided on a flexible end side of the non-retan valve when the non-retan valve is opened. Non-return valve structure having a reinforcing member that prevents the flexible end side from being deformed into a corrugated shape 2. The non-return valve is an annular leaf valve, the reinforcing member is a floating annular leaf valve, the biasing member is a claw leaf spring, and the floating annular leaf valve is an annular leaf valve. 2. A floatable adjoining rear surface of the floating annular leaf valve, wherein the biasing force of the pawl leaf spring is formed so as to act on the rear surface of the floating annular leaf valve.
Non-return valve structure