KR20120134783A - Valve structure of shock absorber - Google Patents

Abstract

PURPOSE: A valve structure of a shock absorber is provided to gradually open a flow path by a reciprocating speed becoming faster and to reduce a blow-off, thereby improving the comfort ride and steering stability. CONSTITUTION: A valve structure of a shock absorber comprises a shock absorber(100), a main piston valve assembly(200), and an auxiliary piston valve assembly(300). The shock absorber comprises a cylinder(110) and a piston rod(120). The cylinder is charged with a working fluid. The piston rod is embedded in the cylinder, thereby reciprocating along a longitudinal direction of the cylinder. The main piston assembly is mounted in one side of the piston rod, thereby dividing the cylinder into an upper chamber(111) and a lower chamber(112). The main piston assembly is interlocked to the reciprocating motion of the piston rod and opened/closed depending on a reciprocating speed of the piston rod, thereby varying damping force. The auxiliary piston assembly is opened/closed with the main piston valve assembly depending on the reciprocating speed of the piston, thereby varying the damping force. The auxiliary piston assembly is mounted in the other end of the piston rod.

Description

VALVE STRUCTURE OF SHOCK ABSORBER}

The present invention relates to a valve structure of a shock absorber, and more particularly, as the reciprocating speed of the piston repeats compression and tension is increased, the flow path is opened step by step to reduce blow-off to improve ride comfort and adjustment stability. It relates to a valve structure of a shock absorber.

The shock absorber generally operates according to the vibration of the vehicle according to the road surface condition, and the damping force generated by the shock absorber varies depending on whether the shock absorber is fast or slow.

It is very important to control the damper force characteristics of the shock absorber when designing the vehicle, because it is possible to control the ride comfort and driving stability of the vehicle according to how the damper force characteristics generated in the shock absorber are adjusted.

The piston valve installed in the conventional shock absorber is designed to have a constant damping characteristic at high speed, medium speed, and low speed by using a single flow path. Therefore, when it is desired to improve ride comfort by lowering damping force at low speed, This can affect the damping force of.

In particular, when changing from low speed to medium speed, blow-off occurs, which acts as one of the factors that hinder ride comfort.

Thus, the damping force which is changed only by the speed change of the piston generates the same damping force according to various road surface conditions, and therefore, it is very difficult to satisfy the riding comfort and adjustment stability at the same time.

Therefore, it is necessary to continuously research and develop a shock absorber valve structure that can satisfy the riding comfort and adjustment stability of the vehicle while reducing the phenomenon such as blow-off due to the variable damping force according to the speed change of the piston.

The present invention has been invented to improve the above problems, and as the reciprocating speed of the piston repeats compression and tension is increased, the flow path is opened step by step to reduce the blow-off to improve ride comfort and adjustment stability. It is to provide a valve structure of the shock absorber.

In order to achieve the above object, the present invention includes a shock absorber including a cylinder filled with a working fluid and a piston rod reciprocating along a longitudinal direction of the cylinder, and mounted on one side of the piston rod to seal the cylinder in an upper chamber. And a main piston valve assembly for dividing into the lower chamber and interlocking with the reciprocation of the piston rod to open and close according to the reciprocating speed of the piston rod to change the damping force, and an inner space of the housing fixed to the lower portion of the main piston valve assembly and having an inner space formed therein. And a connecting passage formed inside the piston rod to communicate with the upper chamber and the lower chamber, and includes an auxiliary piston valve assembly that changes the damping force while opening and closing according to the reciprocating speed of the piston rod in association with the reciprocating speed of the piston rod. Reciprocating speed of the piston rod As the secondary speed increases, the auxiliary piston valve assembly and the main piston valve assembly may be sequentially opened, and thus the embodiment of the present invention may be applied to a structure that reduces blow off.

Here, the main piston valve assembly includes a main piston body having at least one main compression passage through which the working fluid passes when the shock absorber is compressed, and at least one main rebound passage through which the working fluid passes when the shock absorber is extended, and an upper portion of the main piston body. A main compression valve means for generating a damping force against the pressure of the working fluid passing through the main compression passage, and a damping force against the pressure of the working fluid disposed below the main piston body and passing through the main rebound passage. It is preferred to include a main rebound valve means.

At this time, the auxiliary piston valve assembly further includes a housing fixed to the lower portion of the main piston valve assembly and the inner space is formed, and a connecting passage formed inside the piston rod to communicate with the inner space of the housing and the upper chamber and the lower chamber. Application of the embodiment is possible.

In addition, the auxiliary piston valve assembly includes at least one auxiliary compression passage through which the working fluid passes when the shock absorber is compressed, and at least one auxiliary rebound passage through which the working fluid passes when the shock absorber is extended, and is connected through the connecting passage of the piston rod. An auxiliary piston body in communication with the lower chamber, an auxiliary compression valve means disposed above the auxiliary piston body to generate a damping force against the pressure of the working fluid passing through the auxiliary compression passage; It is preferable to include an auxiliary rebound valve means for generating a damping force against the pressure of the working fluid passing through the rebound passage.

Here, the auxiliary compression valve means are arranged on the upper portion of the auxiliary piston body and each of which is sequentially stacked on the upper surface of the slit disk and the upper surface of the slit disk, the slit disk having a slit formed from the edge toward the outer peripheral surface side of the piston rod at a position corresponding to the auxiliary compression passage. And a spring which allows the elastic deformation in which the edge rises to the upper side of the auxiliary piston body by the pressure of the working fluid, and the working fluid first passes through the slit, and the reciprocating speed of the piston rod is gradually increased. Application of the embodiment of pushing the edge of the auxiliary piston body up is possible.

At this time, the auxiliary rebound valve means is disposed in the lower portion of the auxiliary piston body and a plurality of slits are sequentially stacked on the lower surface of the slit disk and the slit disk with slits formed from the edge toward the outer circumferential surface side of the piston rod, respectively, at positions corresponding to the auxiliary rebound passages. And a spring which allows the elastic deformation of the disk by the pressure of the working fluid, the edge of which is lowered to the lower side of the auxiliary piston body. The working fluid first passes through the slit, and the reciprocating speed of the piston rod is gradually increased. It is possible to apply the embodiment of pushing the edge of the auxiliary piston body down.

Further, in addition to the above-described embodiment, the auxiliary compression valve means is disposed on the upper portion of the auxiliary piston body and is formed on the upper surface of the slit disk and the slit disk, each of which has a slit formed from the edge toward the outer circumferential surface side of the piston rod at a position corresponding to the auxiliary compression passage. It includes a coil spring mounted to support the slit disk in close contact with the auxiliary piston body and allow elastic deformation to contract by the pressure of the working fluid, the working fluid initially passes through the slit, the reciprocating speed of the piston rod is gradually increased It is of course also possible to apply the embodiment of pushing up the edge of the ground slit disk to the top of the auxiliary piston body.

According to the present invention having the above-described configuration, the following effects can be achieved.

First, the present invention minimizes the blow-off that may occur when the auxiliary piston valve assembly and the main piston valve assembly are converted from low speed to medium speed while opening the flow path step by step as the reciprocating speed of the piston rod reciprocating inside the cylinder is increased. Can be.

Therefore, the ride comfort and the adjustment stability can be improved by the valve structure of the shock absorber according to the embodiment described above.

1 is a cross-sectional conceptual view showing a valve structure of a shock absorber according to an embodiment of the present invention.
Figure 2 is a cross-sectional conceptual view showing an operating state from the valve structure of the shock absorber according to an embodiment of the present invention
3 is a partial cross-sectional conceptual view showing a structure of an auxiliary piston valve assembly which is a main part in a valve structure of a shock absorber according to another embodiment of the present invention;

Hereinafter, with reference to the accompanying drawings will be described a preferred embodiment of the present invention.

1 is a cross-sectional conceptual view showing a valve structure of a shock absorber according to an embodiment of the present invention.

As shown in the present invention, the main piston valve assembly 200 and the auxiliary piston valve assembly 300 in the shock absorber 100 gradually open the flow path to divide the flow path into a plurality so that the pressure of the working fluid is constantly increased. It can be seen that the structure for minimizing the driving comfort deterrent including the blow-off generated in the reciprocating speed of the piston rod 120, in particular in the section from low speed to medium speed.

The shock absorber 100 includes a cylinder 110 in which a working fluid is filled, and a piston rod 120 embedded in the cylinder 110 to reciprocate in the longitudinal direction of the cylinder 110.

The main piston valve assembly 200 is mounted on one side of the piston rod 120 to divide the cylinder 110 into the upper chamber 111 and the lower chamber 112, and interlock with the reciprocation of the piston rod 120. The opening and closing operation according to the reciprocating speed of the piston rod 120 serves to change the damping force.

In addition, the auxiliary piston valve assembly 300 is mounted to the other end of the piston rod 120 and acts in conjunction with the reciprocation of the piston rod 120 opening and closing operation according to the reciprocating speed of the piston rod 120 serves to change the damping force. To perform.

That is, the main piston valve assembly 200 and the auxiliary piston valve assembly 300 are successively mounted toward the lower end side of the piston rod 120.

Here, 'top' and 'bottom' refer to the upper and lower portions of the drawings, respectively.

Although not shown in particular, the upper end of the piston rod 120 is capable of sliding on the rod guide and the oil seal and at the same time penetrates fluidly and extends out of the cylinder 110.

Here, as the reciprocating speed is gradually increased, the piston rod 120 minimizes the factors that hinder ride comfort such as blow-off as the auxiliary piston valve assembly 300 and the main piston valve assembly 200 are sequentially opened, that is, the change in the damping force. Assuming that the curve is shown on the graph, the damping force is changed to draw a smooth damping force change curve by reducing the severe up and down deviation at the time of blow off.

The present invention can be applied to the embodiments described above, and the following various embodiments are also applicable.

As described above, the main piston valve assembly 200 changes the damping force while being opened and closed according to the reciprocating speed of the piston rod 120, and the main piston body 210, the main compression valve means 220, and the main rebound valve means. It can be seen that the structure including (230).

The main piston body 210 includes one or more main compression passages 212 through which the working fluid passes upon compression of the shock absorber 100 and one or more main rebound passages 214 through which the working fluid passes upon expansion of the shock absorber 100. Is formed.

The main compression valve means 220 is disposed above the main piston body 210 and serves to generate a damping force against the pressure of the working fluid passing through the main compression passage 212, the slit disk 222 And a spring 224.

The main rebound valve means 230 is disposed under the main piston body 210 to generate a damping force against the pressure of the working fluid passing through the main rebound passage 214, the slit disk 232 and the spring 234 ) Is a member including.

The slit disk 222 of the main compression valve means 220 is disposed above the main piston body 210 so as to face the outer circumferential surface side of the piston rod 120 from the edge at a position corresponding to the main compression passage 212. (Not shown).

The spring 224 is composed of a plurality of disks 223 stacked on the slit disk 222, the elastic deformation to push the edge to the upper side of the main piston body 210 with the slit disk 222 against the pressure of the working fluid. It is a member that acts like a leaf spring to allow.

When the piston rod 120 reciprocates at a low speed, the main compression valve means 220 passes a small amount of working fluid through the slit of the slit disk 222 described above, but the reciprocating speed of the piston rod 120 gradually increases. As a result, the flow rate through which the working fluid passes also increases, which leads to an increase in pressure applied to the surface of the slit disk 222.

Therefore, when the reciprocating speed of the piston rod 120 increases at medium and high speeds, the main compression valve means 220 has an edge of the slit disk 222 and the spring 224 as the flow rate of the working fluid increases. 210 is pushed up to the upper side.

The slit disk 232 of the main rebound valve means 230 is disposed below the main piston body 210 and slit from the edge toward the outer peripheral surface side of the piston rod 120 at positions corresponding to the main rebound passage 214, respectively. This is a formed member.

The spring 234 is composed of a plurality of disks 233 stacked on top of the slit disk 232, the elastic deformation to push the edge to the lower side of the main piston body 210 with the slit disk 222 against the pressure of the working fluid. It is a member that acts like a leaf spring to allow.

When the piston rod 120 reciprocates at a low speed, the main rebound valve means 230 passes a small amount of working fluid through the slit of the slit disk 232 described above, but the reciprocating speed of the piston rod 120 gradually increases. As a result, the flow rate through which the working fluid passes also increases, which leads to an increase in pressure applied to the surface of the slit disk 232.

Accordingly, when the reciprocating speed of the piston rod 120 increases at medium speed and high speed, the main rebound valve means 230 may have an edge of the slit disk 232 and the spring 234 along with an increase in the flow rate of the working fluid. 210 is pushed down to the lower side.

On the other hand, the auxiliary piston valve assembly 300 to change the damping force while the opening and closing operation in accordance with the reciprocating speed of the piston rod 120 with the main piston valve assembly 200 as described above, the communication with the connecting passage 320 It can be seen that the mounting in the housing 310.

The housing 310 is fixed to the lower part of the main piston valve assembly 200, that is, the main piston body 210, and an inner space 311 is formed, and the connection passage 320 is an inner space 311 of the housing 310. And a flow path of a working fluid formed inside the piston rod 120 to communicate with the upper chamber 111 and the lower chamber 112.

Here, it will be understood that the auxiliary piston valve assembly 300 is a structure in which the auxiliary compression valve means 340 and the auxiliary rebound valve means 350 are mounted on upper and lower portions of the auxiliary piston body 330 mounted to the housing 310, respectively. Can be.

The auxiliary piston body 330 may include one or more auxiliary compression passages 332 through which the working fluid passes upon compression of the shock absorber 100 and one or more auxiliary rebound passages 334 through which the working fluid passes upon expansion of the shock absorber 100. Is formed, it is in communication with the lower chamber 112 through the connection passage 320 of the piston rod 120.

The auxiliary compression valve means 340 is disposed above the auxiliary piston body 330 to generate a damping force against the pressure of the working fluid passing through the auxiliary compression passage 332, the slit disk 342 and the spring 344 ) Is a member including.

The auxiliary rebound valve means 350 is disposed below the auxiliary piston body 330 to generate a damping force against the pressure of the working fluid passing through the auxiliary rebound passage 334. The slit disk 352 and the spring 354 ) Is a member including.

The slit disk 342 of the auxiliary compression valve means 340 is disposed above the auxiliary piston body 330 and slit from the edge toward the outer peripheral surface side of the piston rod 120 at positions corresponding to the auxiliary compression passages 332, respectively. It is a member in which (not shown) was formed.

The spring 344 is composed of a plurality of disks 343 sequentially stacked on the upper surface of the slit disk 342 to allow the elastic deformation of the edge rising to the upper side of the auxiliary piston body 320 by the pressure of the working fluid. It is a member that acts like a spring.

When the piston rod 120 reciprocates at a low speed, the auxiliary compression valve means 340 passes a small amount of working fluid through the slit of the slit disk 342 described above, but the reciprocating speed of the piston rod 120 gradually increases. As a result, the flow rate through which the working fluid passes also increases, which leads to an increase in pressure applied to the surface of the slit disk 342.

Therefore, when the reciprocating speed of the piston rod 120 is increased at medium speed and high speed, the auxiliary compression valve means 340 increases the flow rate of the working fluid, so that the edges of the slit disk 342 and the spring 344 become the auxiliary piston body ( 330 is pushed to the upper side.

Here, the rigidity of the spring 344 is slightly smaller than that of the spring 224 of the main compression valve means 220 so that the piston rod 120 is lowered to the lower side of FIG. 1 in the course of reciprocating the inside of the cylinder 110. At the time of stroke, when the descending speed of the piston rod 120 gradually increases, the principle of reducing blow-off by increasing the flow rate of the working fluid while allowing elastic deformation before the spring 224 of the main compression valve means 220 is increased. to be.

Of course, it would appear that the auxiliary compression valve means 340 and the main compression valve means 220 sequentially open when the piston rod 120 reciprocates at high speed so that it cannot be seen visually. .

However, as described above, by applying a product in which the difference between the spring 344 and the spring 224 stiffness of the main compression valve means 220 is properly adjusted, vibration and shock are directly applied to the vehicle body in response to various road conditions and driving environments. It can be prevented from being delivered to.

The slit disk 352 of the auxiliary rebound valve means 350 is disposed below the auxiliary piston body 330 and slit from the edge toward the outer peripheral surface side of the piston rod 120 at positions corresponding to the auxiliary rebound passages 334, respectively. This is a formed member.

The spring 354 is composed of a plurality of disks 353 sequentially stacked on the lower surface of the slit disk 352 to allow the elastic deformation of the edge lowered to the lower side of the auxiliary piston body 330 by the pressure of the working fluid. It is a member that acts like a spring.

When the piston rod 120 reciprocates at a low speed, the auxiliary rebound valve means 350 passes a small amount of the working fluid through the slit of the slit disk 352 described above, but the reciprocating speed of the piston rod 120 gradually increases. As a result, the flow rate through which the working fluid passes also increases, which leads to an increase in pressure applied to the surface of the slit disk 352.

Therefore, when the reciprocating speed of the piston rod 120 is increased at medium speed and high speed, the auxiliary rebound valve means 350 has an edge of the slit disk 352 and the spring 354 along with the increase in the flow rate of the working fluid. 330 is pushed down to the lower side.

Here, the rigidity of the spring 354 is slightly smaller than that of the spring 234 of the main rebound valve means 230, so that the piston rod 120 rebounds to the upper side of FIG. At the time of stroke, when the ascending speed of the piston rod 120 gradually increases, the principle of reducing blow-off by increasing the flow rate of the working fluid while allowing elastic deformation before the spring 234 of the main rebound valve means 230 is increased. to be.

Of course, it would appear that the auxiliary rebound valve means 350 and the main rebound valve means 230 sequentially open when the piston rod 120 reciprocates at high speed so that it cannot occur visually. .

However, as described above, by applying a product in which the difference between the spring 354 and the spring 234 stiffness of the main rebound valve means 230 is properly adjusted, vibrations and shocks are directly applied to the vehicle body in response to various road conditions and driving environments. It can be prevented from being delivered to.

On the other hand, the auxiliary compression valve means 340 can also be applied to the embodiment including the coil spring 346 as shown in FIG.

That is, the auxiliary piston body 330 and the auxiliary compression valve means 340 and the auxiliary rebound valve means 350 are all fixed by the fixing pin 390 integrally, the auxiliary compression valve means 340 is fixed pin ( It can be seen that the locking head 392 of the upper end, and the auxiliary rebound valve means 350 is fixed to the finishing piece 394 of the upper end of the fixing pin 390, respectively.

Since the structure of the auxiliary rebound valve means 350 is the same as the embodiment shown in Figure 1, it is omitted for convenience.

The auxiliary compression valve means 340 has a structure including a slit disk 342 and a coil spring 346, the slit disk 342 is disposed above the auxiliary piston body 330 and corresponds to the auxiliary compression passage 332 It is a member in which the slit was formed toward the outer peripheral surface side of the piston rod 120 from the edge at each position.

The coil spring 346 is mounted on the upper surface of the slit disk 342 so that the upper end is fixed to the locking head 392, and the lower end supports the slit disk 342 in close contact with the auxiliary piston body 330 and the pressure of the working fluid It is a member that allows elastic deformation to contract.

When the piston rod 120 reciprocates at a low speed, the auxiliary compression valve means 340 passes a small amount of working fluid through the slit of the slit disk 342 described above, but the reciprocating speed of the piston rod 120 gradually increases. As a result, the flow rate through which the working fluid passes also increases, which leads to an increase in pressure applied to the surface of the slit disk 342.

Therefore, when the reciprocating speed of the piston rod 120 increases at medium and high speeds, the auxiliary compression valve means 340 increases the flow rate of the working fluid in accordance with the pressure of the working fluid exceeding the elastic repulsive force of the coil spring 346. The edge of the slit disk 342 is pushed up to the upper side of the auxiliary piston body 330 while contracting.

Here, the rigidity of the coil spring 346 is slightly smaller than the spring 224 of the main compression valve means 220 so that the piston rod 120 is lowered to the lower side of FIG. 1 in the course of reciprocating the inside of the cylinder 110. In the compression stroke, when the descending speed of the piston rod 120 is gradually increased, the blow-off is increased by increasing the flow rate of the working fluid while allowing the elastic deformation to contract before the spring 224 of the main compression valve means 220. The principle is to reduce.

Of course, it would appear that the auxiliary compression valve means 340 and the main compression valve means 220 sequentially open when the piston rod 120 reciprocates at high speed so that it cannot be seen visually. .

However, as described above, by applying a product in which the difference between the stiffness of the spring 224 of the coil spring 346 and the main compression valve means 220 is appropriately adjusted, vibrations and shocks are applied to the vehicle body in response to various road conditions and driving environments. It can be prevented from being delivered directly.

Hereinafter, the opening and closing operation according to the reciprocating motion including the compression and the tension stroke of the piston rod 120 from the valve structure of the shock absorber according to an embodiment of the present invention will be briefly described with reference to FIG. 3.

For reference, in the center line of FIG. 3, the left side represents the main piston valve assembly 200 and the auxiliary piston when the piston rod 120 rebounds during the reciprocating motion of the piston rod 120, that is, when the piston rod 120 rises above the cylinder 110. The behavior of the valve assembly 300, the right side of the center line is the compression stroke during the reciprocating motion of the piston rod 120, that is, the main piston valve assembly in the case of the piston rod 120 descends to the lower side of the cylinder 110 ( 200 and the behavior of the auxiliary piston valve assembly 300, respectively.

Reference numerals not shown in FIG. 3 refer to FIGS. 1 and 2, in which the arrows indicated by the dashed-dotted line indicate the flow direction C of the working fluid during the compression stroke, and the arrows indicated by the dashed-dotted line indicate the rebound stroke. The flow direction R of the working fluid is respectively shown.

First, the compression stroke shown on the right side with respect to the center line will be described.

When the piston rod 120 is a low speed section, as shown in FIG. 1, the slit disk 342 of the auxiliary compression valve means 340 and the slit disk 222 of the main compression valve means 220 are respectively the auxiliary piston body 330 and Maintaining close contact with the upper side of the main piston body 210, the flow rate of the working fluid through the main compression passage 212 and the auxiliary compression passage 332 will also be a small amount.

Thus, the working fluid moves to the upper chamber 111 through the slits of the respective slit disks 222 and 342.

Then, when the piston rod 120 is a medium speed and high speed section, the pressure of the working fluid applied to each of the slit disks 222 and 342 increases as shown in FIG. Each of the slit disks 222 and 342 and each of the springs 224 and 344 is pushed upwards while allowing the elastic deformations 224 and 344.

At this time, the spring 344 of the auxiliary compression valve means 340 is pushed up first, and the spring 224 of the main compression valve means 220 is pushed up subsequently as described above.

On the other hand, the rebound stroke shown on the left side with respect to the center line will be described.

When the piston rod 120 is a low speed section, as shown in FIG. 1, the slit disk 352 of the auxiliary rebound valve means 350 and the slit disk 232 of the main rebound valve means 230 are respectively the auxiliary piston body 330 and Maintaining close contact with the lower side of the main piston body 210, the flow rate of the working fluid through the main rebound passage 214 and the auxiliary rebound passage 334 will also be a small amount.

Thus, the working fluid moves to the lower chamber 112 through the slits of the respective slit disks 232 and 352.

Then, when the piston rod 120 is a medium speed and high speed section, the pressure of the working fluid applied to each of the slit disks 232 and 352 increases as shown in FIG. 3, and each spring is stacked below each of the slit disks 232 and 352. Each of the slit disks 232 and 352 and each of the springs 234 and 354 is pushed down to the lower side while allowing the elastic deformation 234 and 354.

At this time, the spring 354 of the auxiliary rebound valve means 350 is pushed down first, and the spring 234 of the main rebound valve means 230 is pushed up as described above.

As described above, the present invention provides a shock absorber valve structure for improving the riding comfort and adjustment stability by opening the flow path step by step as the reciprocating speed of the piston repeats compression and tension is increased. It can be seen that the basic technical idea.

It will be apparent to those skilled in the art that many other modifications and applications are possible within the scope of the basic technical idea of the present invention.

100 ... Shock absorber 200 ... Main piston valve assembly
300 ... Auxiliary Piston Valve Assembly

Claims (6)

A shock absorber comprising a cylinder filled with a working fluid, and a piston rod embedded in the cylinder and reciprocating along a longitudinal direction of the cylinder;
A main piston valve assembly mounted on one side of the piston rod for dividing the cylinder into an upper chamber and a lower chamber, the main piston valve assembly changing the damping force while being opened and closed according to the reciprocating speed of the piston rod while interlocking with the reciprocating of the piston rod; And
A piston rod fixed to the lower portion of the main piston valve assembly and having an inner space formed therein, and a connecting passage formed inside the piston rod to communicate with the inner space of the housing and the upper chamber and the lower chamber; And an auxiliary piston valve assembly configured to change a damping force while being opened and closed according to the reciprocating speed of the piston rod in association with a reciprocating speed of the piston rod.
And as the reciprocating speed of the piston rod is gradually increased, the auxiliary piston valve assembly and the main piston valve assembly are sequentially opened, thereby reducing blow-off valve structure.
The method according to claim 1,
The main piston valve assembly,
A main piston body having at least one main compression passage through which the working fluid passes when the shock absorber is compressed, and at least one main rebound passage through which the working fluid passes when the shock absorber is extended;
A main compression valve means disposed above the main piston body to generate a damping force against the pressure of the working fluid passing through the main compression passage;
And a main rebound valve means disposed under the main piston body to generate a damping force against the pressure of the working fluid passing through the main rebound passage.
The method according to claim 1,
The auxiliary piston valve assembly,
One or more auxiliary compression passages through which the working fluid passes when the shock absorber is compressed and one or more auxiliary rebound passages through which the working fluid passes when the shock absorber is extended are formed, and communicate with the lower chamber through the connection passage of the piston rod. With the auxiliary piston body,
An auxiliary compression valve means disposed above the auxiliary piston body to generate a damping force against the pressure of the working fluid passing through the auxiliary compression passage;
And an auxiliary rebound valve means disposed under the auxiliary piston body to generate a damping force against the pressure of the working fluid passing through the auxiliary rebound passage.
The method according to claim 3,
The auxiliary compression valve means,
A slit disk disposed on an upper portion of the auxiliary piston body and having slits formed from an edge toward an outer circumferential surface side of the piston rod, respectively, at a position corresponding to the auxiliary compression passage;
Comprising a plurality of disks sequentially stacked on the upper surface of the slit disk includes a spring to allow the elastic deformation of the edge rises to the upper side of the auxiliary piston body by the pressure of the working fluid,
The working fluid initially passes through the slit, and when the reciprocating speed of the piston rod is gradually increased, the valve structure of the shock absorber, characterized in that for pushing up the edge of the spring to the upper portion of the auxiliary piston body.
The method according to claim 3,
The auxiliary rebound valve means,
A slit disk disposed below the auxiliary piston body and having slits formed from an edge toward an outer circumferential surface side of the piston rod, respectively, at a position corresponding to the auxiliary rebound passage;
Comprising a plurality of disks sequentially stacked on the lower surface of the slit disk includes a spring to allow the elastic deformation of the edge lowered to the lower side of the auxiliary piston body by the pressure of the working fluid,
The working fluid initially passes through the slit, and when the reciprocating speed of the piston rod is gradually increased, the valve structure of the shock absorber, characterized in that for pushing the edge of the spring to the lower portion of the auxiliary piston body.
The method according to claim 3,
The auxiliary compression valve means,
A slit disk disposed on an upper portion of the auxiliary piston body and having slits formed from an edge toward an outer circumferential surface side of the piston rod, respectively, at a position corresponding to the auxiliary compression passage;
A coil spring mounted on an upper surface of the slit disk to support the slit disk in close contact with the auxiliary piston body and to allow elastic deformation to contract by pressure of a working fluid;
The working fluid initially passes through the slit, and when the reciprocating speed of the piston rod is gradually increased, the valve structure of the shock absorber, which pushes up the edge of the slit disk to the upper portion of the auxiliary piston body.

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