KR100623276B1 - Valve structure for shock absorber - Google Patents

Abstract

It is an object of the present invention to provide a damping force variable shock absorber having a relatively simple coupling relationship and a rigid mounting end, without being limited to the mounting portion by using a control tube coupled to surround the piston rod.

Such a damping force variable shock absorber of the present invention has an inner tube (20) equipped with a lower valve assembly (1) and an operating chamber (30) formed by the inner tube (20) to control the flow of filled oil. A piston rod 50 coupled to move the piston valve assembly 40 in the axial direction, and having an oil passage 55 and a first orifice 60 penetrated in the radial direction at the lower axis, and an outer cylinder 21. ). The damping force variable shock absorber of the present invention is formed in a hollow shaft shape to form a second orifice 90 at a position corresponding to the axial center of the first orifice 60, and surround the outer circumferential surface of the piston rod 50 The upper surface includes a control tube 80 fixed to the circular disk-shaped handle disk 88, the control tube 80 is rotated at a finite angle by the handle disk 88 and the stopper 59, Thus, the oil flow path 55 and the orifices 60 and 90 are opened and closed to vary the damping force, but the control tube 80 and the piston rod 50 rotate the control tube 80 and the fluid Ring engaging grooves 57 and 87 are formed to engage O-rings 58 for sealing.

The damping force variable shock absorber of the present invention has the advantage that the damping force is variable by a control tube coupled to surround the piston rod, and since the mounting ring is directly fixed to the upper surface of the piston rod, it can be stably mounted on the mounting portion of the vehicle. There is this.

Description

Variable structure shock absorber {Valve structure for shock absorber}             

1 is a cross-sectional view for explaining the configuration of a damping force variable shock absorber according to the prior art,

2 and 3 are cross-sectional views for explaining the operation relationship of important parts of the damping force variable shock absorber shown in FIG.

Figure 4 is a cross-sectional view for explaining the configuration of the damping force variable shock absorber according to an embodiment of the present invention,

5 is a plan view for explaining the shape of the important portion of the damping force variable shock absorber shown in FIG.

6 and 7 are cross-sectional views for explaining the operation relationship of important parts of the damping force variable shock absorber shown in FIG.

    ♣ Explanation of symbols for main part of drawing ♣

    20: inner tube 21: outer cylinder

    30: operation chamber 40: piston valve assembly

    50: piston rod 52: mounting ring

    55: oil path 57, 87: ring coupling groove                 

    58: O-ring 59: stopper

    60: first orifice 80: control tube

88: handle disc 90: second orifice

The present invention relates to a damping force variable shock absorber, and more particularly, to a damping force variable shock absorber for varying the damping force of the shock absorber by rotating the control rod to adjust the total cross-sectional area of the orifice.

In general, shock absorbers are an important element of the suspension system of an automobile. Here, the suspension device of the vehicle means a device that connects the axle and the frame and absorbs vibration or shock received from the road surface while driving to improve ride comfort and safety of the vehicle. The shock absorber, which is part of such suspension, serves to absorb the up and down vibration of the vehicle body. In addition, the shock absorber plays a role such as vibration absorption of the spring generated by the road surface, fatigue reduction of the spring, improvement of ride comfort and road holding.

There are two types of shock absorbers, a telescopic type and a lever type, depending on the shape. Here, the shock absorber of the cylindrical type is classified into oil and compressed gas types according to the operation method, the structure and the enclosed fluid, and the shock absorber of the lever type is classified into various types such as rotary wing type or piston type.

In addition, a type of shock absorber includes a damping force variable shock absorber capable of adjusting the magnitude of the damping force by variably controlling the overall cross-sectional area of the orifice through which oil passes. Here, the damping force variable shock absorber is classified as an electronically controlled suspension used in an electronically controlled suspension (ECS). Such a damping force variable shock absorber is very different in its structure according to the manufacturer and type, but compared with the general shock absorber, the piston rod is hollow, and the control rod formed integrally with the rotary valve is installed therein. Have In addition, the difference between the electronically controlled and the manual type is in the presence or absence of an actuator such as a step motor that rotates the control rod at an angle left and right.

The damping force variable shock absorber according to the prior art is a manual type, as shown in Fig. 1, an inner tube (2) equipped with a lower valve assembly (1), and an operating chamber (3) formed by such an inner tube (2). It consists of a piston rod 5 and an outer cylinder (not shown) coupled to move the piston valve assembly 4 in the axial direction.

First, the piston rod 5 is formed in hollow shaft shape. The first orifice 6 penetrates the piston rod 5 in the radial direction. Moreover, the control rod 7 is arrange | positioned in the oil flow path 19 which is the inner diameter of the piston rod 5. The shutter 8 is coupled to the lower end of the control rod 7 arranged in this way. The second orifice 9 is formed to penetrate the shutter 8 in the radial direction.

The piston valve assembly 4 is inserted into the lower end of the piston rod 5 formed as described above. Here, the piston valve assembly 4 is the first piston valve 12 and the second piston valve 13. The first piston valve 12 includes first check valves 10 at upper and lower portions, and forms an orifice 11 inclined therethrough. In addition, the second piston valve 13 controls the flows (a, b) of oil flowing in the oil passage (19) of the piston rod (5) during the compression automatic and rebound operation of the piston valve assembly (4). The third orifice 14 and the second check valve 15 are provided. The second piston valve 13 is seated inside the extension tube 16, and the extension tube 16 is fixed to the end of the piston rod 5 so as to contact the lower surface of the first piston valve 12. have.

In addition, as shown in Figure 2, the damping force variable shock absorber according to the prior art is coupled to the shutter (8) formed on the control rod to be manually rotated in the oil passage (19) of the piston rod (5) of the hollow shaft shape I'm making it.

In the conventional damping force variable shock absorber coupled as described above, when the soft and relatively small damping force is generated, the second orifice 9 of the shutter 8 and the first orifice 6 of the piston rod 5 coincide with each other. The oil passage 19 of the piston rod 5 is open.

In addition, as shown in Figure 3, in the case of generating a rigid and relatively increased damping force in the conventional damping force variable shock absorber, it is only necessary to manually rotate the control rod at a finite angle. At this time, the shutter 8 integrally formed on the control rod rotates at a finite angle, and at the same time, the second orifice 9 of the shutter 8 and the first orifice 6 of the piston rod 5 coincide with each other. You will not. Thus, the oil passage 19 of the piston rod 5 is sealed.

However, since the damping force variable shock absorber according to the prior art has a structure in which a control rod is inserted into the piston rod, a stroke and a mounting portion are limited.

In particular, the conventional damping force variable shock absorber has a disadvantage in that it can not be mounted to a mounting portion such as a driver seat due to the coupling relationship between the control rod and the piston rod.

In addition, the conventional damping force variable shock absorber has a relatively unstable mounting structure because both mounting ends formed to be fixed to the hinge coupling portion of the vehicle cannot be directly attached to the end portions of the piston rod, There is a disadvantage of having a complicated coupling relationship.

The present invention devised to solve this problem is to provide a damping force variable shock absorber having a relatively simple coupling relationship and a rigid mounting end without being limited to the mounting portion using a control tube coupled to surround the piston rod. The purpose.

The object of the present invention described above is combined with an inner tube equipped with a lower valve assembly to move the piston valve assembly in an axial direction in an operating chamber formed by the inner tube to control the flow of filled oil, In a piston rod having a first orifice penetrating in an oil channel and a radial direction, and a damping force variable shock absorber having an outer cylinder, a second orifice is formed at a position coinciding with the axis of the first orifice. It comprises a control tube formed in a hollow shaft shape to surround the outer circumferential surface of the fixed disk in the circular frame shape on the top surface, the control tube is rotated at a finite angle by the handle disk and the stopper, therefore, the The oil flow path and the orifices are opened and closed to vary the damping force, but the control tube 80 and the piston rod A damping force variable shock absorber characterized in that a ring coupling groove is formed to engage the rotation of the control tube and the O-ring for sealing the fluid.

In addition, according to the present invention, it is preferable that the handle disc is integrally formed with a handle formed by bending vertically in the cut groove so that the user can easily rotate the control tube.

According to the present invention, it is preferable that the control tube and the piston rod are formed with a ring coupling groove so as to couple the rotation of the control tube and the O-ring for sealing the fluid.

Further, according to the present invention, it is preferable that the long hole is formed on the outer circumference of the stopper so that the handle of the handle disc can be restrained to move at a finite rotation angle.

Hereinafter, the damping force variable shock absorber according to a preferred embodiment of the present invention will be described in detail with reference to FIGS. 4 to 7.                     

In the drawings, Figure 4 is a cross-sectional view for explaining the configuration of the damping force variable shock absorber according to an embodiment of the present invention, Figure 5 is a view for explaining the shape of the important portion of the damping force variable shock absorber shown in FIG. 6 and 7 are cross-sectional views for explaining the operation relationship of important parts of the damping force variable shock absorber shown in FIG.

As shown in FIG. 4, the damping force variable shock absorber of the present invention can fill a gas by maintaining a predetermined interval with the inner tube 20 equipped with a lower valve assembly (not shown) and the inner tube 20. The outer cylinder 21 and the rod guide 22 which is mounted on the upper end of the inner tube 20 to induce the axial movement of the piston rod 50 and the control tube 80 of the hollow shaft shape.

In addition, the damping force variable shock absorber of the present invention bends the upper end of the outer cylinder 21 inward to fix the oil seal 23 disposed above the rod guide 22.

The damping force variable shock absorber of the present invention couples the piston rod 50 to move the piston valve assembly 40 in the axial direction in the operation chamber 30 formed by the inner tube 20.

First, the piston rod 50 is an actual axis, and forms an oil flow path 55 formed at a predetermined depth in the upper direction of the shaft center at the lower end. The first orifice 60 penetrates in the radial direction in the piston rod 50 where the oil passage 55 ends. The first circumferential surface of the piston rod 50 is formed with a first ring coupling groove 57 to mount an O-ring 58. Here, the O-ring 58 can rotate the control tube 80, and serves to prevent the outflow of oil. In addition, the upper end surface of the piston rod 50 fixes the ring bolt mounting ring 52 using a welding joint method. Here, the mounting ring 52 is a portion coupled to the mounting portion of the vehicle. The mounting ring 52 fixed in this way has a rigid mounting structure by directly applying a load in the axial direction of the piston rod 50.

In addition, the control tube 80 surrounding the piston rod 50 forms a second orifice 90 penetrating radially at a position corresponding to the axis of the first orifice 60. The upper inner circumferential surface of the control tube 80 forms a second ring coupling groove 87 for mounting the O-ring 58. The outer circumferential surface of such a control tube 80 is in surface contact with the inner diameters of the rod guide 22 and the oil seal 23, so that oil filled in the operation chamber 30 does not flow out. In addition, the handle disk 88 of the circular frame shape is fixed to the upper surface of the control tube (80).

Here, the handle disk 88 is formed integrally with the handle 88a formed by vertically bent in the groove 88b in which a portion of the circular frame portion is cut.

As shown in FIG. 5, the handle disc 88 is integrated with the handle 88a at the long hole 59a of the stopper 59, so that the control tube can be rotated at a finite angle. On the top of such a stopper 59 is expressed a "soft" mark (not shown) indicating where a relatively small amount of damping force is generated and a "hard" mark indicating where a relatively large amount of damping force is generated. Can be.

In the following, an operation method of the damping force variable shock absorber of the present invention as described in detail above will be described.                     

First, in the damping force variable shock absorber of the present invention, the handle 88a of the handle disc 88 is disposed near the "soft" mark on the stopper 59.

In this case, the second orifice 90 of the control tube 80 and the first orifice 60 of the piston rod 50 coincide with each other, as shown in FIG. 6, and the oil flow path of the piston rod 50 ( 55) is opened. At this time, as shown in Figure 4, when an impact is applied to the piston rod 50 from the outside, the piston rod 50 is in a compression operation.

When the piston rod 50 is compressed in this manner, the oil in the operating chamber 30 is inclined orifice of the piston valve assembly 40 and the oil passage 55 of the piston rod 50 as indicated by the solid line. And flows through the first orifice 60 and the second orifice 90.

Therefore, the damping force variable shock absorber of the present invention generates a soft and relatively small damping force.

In the damping force variable shock absorber of the present invention, the oil indicated by the dotted line at the time of the rebound operation is an inclined orifice of the piston valve assembly 40, an oil channel 55 of the piston rod 50, and a first orifice 60. ), And flows in the second orifice 90.

In addition, when the user rotates the handle disk 88 toward the "hard" mark by using the handle 88a of the handle disk 88, the control tube 80 integrally formed with the handle disk 88 is finite It will rotate at an angle. In this case, the second orifice 90 of the control tube 80 and the first orifice 60 of the piston rod 50 do not coincide with each other, and the oil flow path 55 of the piston rod 50 is sealed. In this case, as described above, when the piston rod 50 performs the compression operation and the rebound operation, the oil may flow only through the inclined orifice of the piston valve assembly 40.

Accordingly, the damping force variable shock absorber of the present invention generates a hard and relatively increased damping force.

As described in detail above, the damping force variable shock absorber of the present invention varies the damping force by a control tube coupled to surround the piston rod, and since the mounting ring is directly fixed to the upper surface of the piston rod, it is stably mounted on the mounting portion of the vehicle. There is an advantage that can be.

In addition, the damping force variable shock absorber of the present invention has the advantage of having a rigid structure and a simple coupling relationship between the components.

In addition, the damping force variable shock absorber of the present invention has an advantage that the damping force can be easily changed by using a control tube having a stopper and a handle disc.

In addition, the damping force variable shock absorber of the present invention has the advantage of being able to easily rotate the control tube in the piston rod using the oil, to seal the outflow of oil.

In addition, the damping force variable shock absorber of the present invention has the advantage that can be reduced in accordance with improved design freedom, light weight.

Although the technical idea of the damping force variable shock absorber of the present invention described above has been described with the accompanying drawings, this is for illustrative purposes only and not for limiting the present invention. In addition, it is obvious that any person skilled in the art can make various modifications and imitations without departing from the scope of the technical idea of the present invention.

Claims (4)

To control the flow of the filled fluid to move the piston valve assembly 40 in the axial direction in the inner tube 20 with the lower valve assembly and in the operating chamber 30 formed by the inner tube 20. In the damping force variable shock absorber provided with a piston rod (50) having an oil cylinder (55) and a radially penetrating first orifice (60) formed at a lower shaft and an outer cylinder (21), The second orifice 90 is formed at a position corresponding to the axis of the first orifice 60, It includes a control tube 80 formed in a hollow shaft shape to surround the outer circumferential surface of the piston rod 50 and fixed to the upper end surface of the circular disk-shaped handle disk 88, the control tube 80 is the handle The disk 88 and the stopper 59 are rotated at a finite angle c, whereby the oil passage 55 and the orifices 60, 90 are opened and closed to vary the damping force, Ring control grooves (57, 87) are formed in the control tube (80) and the piston rod (50) to couple the O-ring (58) for the rotation of the control tube (80) and the sealing of the fluid. Damping force variable shock absorber characterized by. The method of claim 1, Damping force, characterized in that the handle disk 88 is formed integrally with the handle 88a formed by bending vertically in the cut groove (88b) so that the user can easily rotate the control tube (80). Variable shock absorber. delete The method of claim 1, A damping force variable shock absorber, characterized in that a long hole (59a) is formed on the outer circumference of the stopper (59) to restrain the handle (88a) of the handle disk (88) to move at a finite rotation angle.

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