KR101254303B1 - Valve structure of a shock absorber - Google Patents

Valve structure of a shock absorber Download PDF

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Publication number
KR101254303B1
KR101254303B1 KR1020100100941A KR20100100941A KR101254303B1 KR 101254303 B1 KR101254303 B1 KR 101254303B1 KR 1020100100941 A KR1020100100941 A KR 1020100100941A KR 20100100941 A KR20100100941 A KR 20100100941A KR 101254303 B1 KR101254303 B1 KR 101254303B1
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South Korea
Prior art keywords
shock absorber
rebound
valve
working fluid
piston body
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KR1020100100941A
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Korean (ko)
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KR20120039301A (en
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박인수
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주식회사 만도
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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • General Engineering & Computer Science (AREA)

Abstract

The present invention relates to a shock absorber, and more particularly, to a valve structure of a shock absorber installed in a shock absorber to control damping force.
According to the present invention, in the valve structure of the shock absorber having a piston valve installed at the end of the piston rod and operating in a state bisecting the cylinder to generate a damping force, the piston valve is a working fluid during compression of the shock absorber. A piston body having at least one compression passage therethrough and at least one rebound passage through which the working fluid passes upon expansion of the shock absorber; Compression valve means disposed above the piston body to generate a damping force against pressure of the working fluid passing through the compression passage; Rebound valve means disposed under the piston body to generate a damping force against pressure of the working fluid passing through the rebound passage; Includes, the piston body, the slit forming portion that can adjust the damping force through the slit formed on the edge and the thickness variable portion that can adjust the damping force according to the thickness, wherein the slit forming portion and the thickness variable portion the piston body Provided is a valve structure of a shock absorber, which is formed integrally with the shock absorber.

Description

VALVE STRUCTURE OF A SHOCK ABSORBER}

The present invention relates to a shock absorber, and more particularly, to a valve structure of a shock absorber installed in a shock absorber to control damping force.

In general, a shock absorber is provided between the vehicle body side and the wheel side to absorb various vibrations or shocks transmitted from the wheels in contact with the road surface while driving to improve the vehicle ride comfort and driving stability.

1 is a cross-sectional view showing a conventional general shock absorber.

The shock absorber 10 includes a cylinder 1 filled with a working fluid therein. The piston rod (2) is installed in the cylinder (1) so as to reciprocate, and generates a damping force in accordance with the movement of the working fluid in the cylinder (1) during the reciprocating movement of the piston rod (2).

The cylinder 1 is composed of an inner tube 1a and an outer tube 1b outside thereof. The inner tube 1a is filled with a working fluid, that is, oil, and the outer tube 1b is filled with a working fluid for compensating the pressure in the inner tube 1a.

An upper cap 3 penetrating the upper portion of the piston rod 2 is coupled to an upper portion of the outer tube 1b, and an oil seal 4 for preventing leakage of oil is coupled therein. In addition, a lower portion of the oil seal 4 supports the piston rod 2, and a rod guide 5 for guiding the shanghai movement of the piston rod 2 is coupled.

In addition, a piston rod 2 is installed in the inner tube 1a of the cylinder 1 so as to reciprocate, and is divided into a tension chamber 6 and a compression chamber 7. In addition, a piston valve 9 is installed at the end of the piston rod 2 to control the flow of the working fluid between the tension chamber 6 and the compression chamber 7.

On the other hand, the base cap 8 is coupled to the lower portion of the cylinder 1, that is, the end of the outer tube 1b. The base cap 8 is welded to the inner circumferential surface of the outer tube 1b and sealed. In addition, the body valve 20 for controlling the flow of the working fluid is coupled to the end of the inner tube (1a).

Meanwhile, a plurality of through holes 11 and 21 are formed in the piston valve 9 and the body valve 20. In addition, the through holes 11 and 21 each form an orifice, the compression orifices 11a and 21a disposed on a circle close to the center, and the tension orifices disposed on an outer circle of the compression orifices 11a and 11a. 11b, 21b).

In addition, the piston valve 9 and the body valve 20 is provided with a plurality of disks (12, 13, 22, 23) on each of the upper and lower surfaces. The plurality of disks 12, 13, 22, 23 control the opening and closing of the compression orifices 11a, 21a or the tension orifices 11b, 21b so that a damping force is generated.

2 is a cross-sectional view showing a conventional dual flow valve structure installed at the end of a piston rod. 3 is a perspective view illustrating a rebound disk and a pilot case of the dual flow valve structure shown in FIG. 2.

The shock absorber is provided with a piston rod (2) installed reciprocally in the cylinder (1) and one end of the piston rod (2), and the inside of the cylinder (1) to the upper and lower chambers (6, 7). And a piston valve 20 that operates in a bisected state to generate a damping force. The piston valve 20 is fitted to the end of the piston rod 2 and is fixed by a fastening member such as a nut 27 or the like.

The piston valve (20) includes a piston body (24) in which at least one compression passage (26) through which the working fluid passes during compression of the shock absorber and at least one rebound passage (25) through which the working fluid passes during the expansion of the shock absorber ).

The piston valve 20 also includes compression valve means 40 disposed at the top of the piston body 24 for generating a damping force against the pressure of the working fluid that has passed through the compression passage 26, And rebound valve means (30) disposed at a lower portion of the rebound passage (25) for generating a damping force against the pressure of the working fluid passing through the rebound passage (25).

The rebound valve means 30 is mounted on the bottom surface of the piston body 24 and has a rebound disk 31 having an opening 31a (see FIG. 3), and an opening 33a being formed and rebounding according to the pressure of the working fluid. A pilot case 33 forming a rebound back pressure chamber 33b for pressurizing the disk 31 from the rear, and attached to a lower portion of the rebound disk 31 to seal between the rebound disk 31 and the pilot case 33. It includes a rebound seal portion 32, and a rebound valve 35 that is seated on the lower portion of the pilot case (33).

In the rebound stroke of the piston rod 2, the working fluid passes through the rebound passage 25 and passes through the slit 53 formed in the pilot disk-S 52. The opening 31a above the rebound disk 31 is shown in FIG. 3. Enter the rebound back pressure chamber 33b). The working fluid exits through the slit formed in the rebound valve 35 through the opening 33a of the pilot case 33 as shown by arrow a.

Further, when the speed of the piston rod 2 is increased to increase the pressure of the working fluid, the working fluid presses the rebound disk 31 and flows to the lower portion of the cylinder 1 as shown by the arrow b. In addition, some of the working fluid enters the rebound back pressure chamber 33b through the opening 31a in the upper portion of the rebound disk 31 via the slit 53 formed in the pilot disk-S 52. When the amount of working fluid filled in the rebound back pressure chamber (33b) is increased, the filled working fluid acts as a back pressure for pressing the rebound disc (31) backward. As a result, the flow path formed between the rebound disk 31 and the piston body 24 is closed, and the working fluid mainly flows out through the opening 33a of the pilot case 33.

When the pressure of the working fluid is further increased, the working fluid presses the rebound valve 35 to open the rebound valve 35 in the form of a disk so that a greater amount of working fluid escapes through the flow path therebetween.

The compression valve means 40 also includes a compression disc 41, a pilot case 43, a compression seal 42 and a compression valve 45 similar to the rebound valve means 30. The operation of the conventional dual flow type valve structure at the time of the compression stroke of the piston rod 2 is the same as that of the above-mentioned rebound stroke in view of the characteristics of the valve structure formed up and down symmetrically, and thus the detailed description thereof is omitted.

The piston valve 20 has the effect of reducing the damping force in the extremely low speed region and the high speed region by making the flow path of the working fluid according to the speed of the piston rod 2, thereby improving the ride comfort. This type of valve structure is referred to as a dual flow damper valve structure.

4 is an exploded perspective view of a conventional piston body.

As shown in FIG. 4, the pilot body 51 and the pilot disc-S 52 are sequentially stacked on the piston body 24 in the up and down symmetry. In addition, a plurality of slits 53 are formed in the pilot disk-S 52 so that the working fluid can flow through the slits 53.

However, if such a laminated structure has a risk of productivity and quality problems due to many valve parts. That is, referring again to FIG. 2, the piston disk 24 and the pilot disk-S 52, as well as the compression disk 41, the pilot case 43, the compression valve 45, and the plurality of upper portions of the piston body 24, are provided. Disks are stacked, and the lower portion of the piston body 24 includes a pilot disk 51 and a pilot disk-S 52, as well as a rebound disk 31, a pilot case 33, a rebound valve 35, and a plurality of disks. Are stacked. This stacking of multiple valve-related components not only reduces productivity but also makes it difficult to maintain the same quality.

Furthermore, since the pilot disk-S 52, which is a separate part from the piston body 24, is manufactured through press working due to its thin thickness, there is a limit to varying the shape of the slit 53, and thus there is a limitation in tuning the damping force characteristics. There was no choice but to be.

Accordingly, research and development on the valve structure of the shock absorber, which can prevent misassembly of the valve and improve productivity, needs to be continuously made.

In order to solve these problems, the present invention does not combine the pilot disk and the pilot disk-S to the piston body, but instead manufactures the pilot disk, the pilot disk-S, and the piston body as an integrated shock absorber having improved productivity and quality. To provide a valve structure of.

According to the present invention for achieving the above object, in the valve structure of the shock absorber having a piston valve which is installed at the end of the piston rod and operates in a state in which the inside of the cylinder is bisected to generate a damping force, the piston valve is, A piston body having at least one compression passage through which the working fluid passes during compression, and at least one rebound passage through which the working fluid passes upon expansion of the shock absorber; Compression valve means disposed above the piston body to generate a damping force against pressure of the working fluid passing through the compression passage; Rebound valve means disposed under the piston body to generate a damping force against pressure of the working fluid passing through the rebound passage; Includes, the piston body, the slit forming portion that can adjust the damping force through the slit formed on the edge and the thickness variable portion for adjusting the damping force according to the thickness, wherein the slit forming portion and the thickness variable portion the piston body Provided is a valve structure of a shock absorber, which is formed integrally with the shock absorber.

Preferably, the thickness variable portion and the slit forming portion are integrally formed with the piston body through sintering.

Here, the slits are preferably formed separately through processing after the sintering is finished.

Preferably, the slit forming part and the thickness varying part are present both vertically and symmetrically based on the piston body.

According to the present invention as described above, the valve structure of the shock absorber formed integrally with the pilot disk, the pilot disk-S and the piston body can be provided.

Accordingly, according to the present invention, since the pilot disk and the pilot disk-S do not need to be separately assembled to the piston body, the quality due to misassembly can be prevented from being degraded and workability can be improved.

In addition, according to the present invention, since the piston body is integral, even pressure is distributed during operation, thereby making it possible to compensate for the weak part of the piston valve.

In addition, in the conventional case, the pilot disk-S was manufactured through press working, but there was a big limitation in varying the shape of the slit. The degree of freedom in tuning the damping force characteristic can be increased.

1 is a cross-sectional view showing a conventional shock absorber.
2 is a cross-sectional view showing a valve structure of a dual flow type installed at the end of a conventional piston rod.
3 is a perspective view showing a rebound disk and a pilot case of the dual flow valve structure shown in FIG.
Figure 4 is an exploded perspective view of a conventional piston body.
Figure 5 is a cross-sectional view showing a dual flow valve structure according to the present invention.
6 is an enlarged view of a portion A of FIG. 5.
7 is a perspective view of a piston body applied to the dual flow valve structure according to the present invention.

Hereinafter, a valve structure of a shock absorber according to a preferred embodiment of the present invention will be described in detail with reference to the drawings.

5 is a cross-sectional view showing a dual flow type valve structure according to the present invention.

As shown in FIG. 5, the valve structure of the shock absorber according to the present invention has a piston rod 102 installed in the cylinder 101 so as to be reciprocated in the cylinder 101, and is installed at the end of the piston rod 102 and has a cylinder. It includes a piston valve 120 to operate in a state divided into the tension chamber 106 and the compression chamber 107 to generate a damping force.

The piston valve 120 includes a piston body 124 having one or more compression passages 126 through which the working fluid passes when the shock absorber is compressed and one or more rebound passages 125 through which the working fluid passes when the shock absorber is extended. ).

In addition, the piston valve 120 is disposed above the piston body 124, the compression valve means 140 for generating a damping force against the pressure of the working fluid passing through the compression passage 126, and the piston body 124 It is disposed in the lower portion of the includes a rebound valve means 130 for generating a damping force against the pressure of the working fluid passing through the rebound passage (125).

The rebound valve means 130 includes a rebound disk 131, a pilot case 133, a rebound seal 132, and a rebound valve 135.

The rebound disk 131 is seated on the bottom surface of the piston body 124 to cover the rebound passage 125. The rebound disk 131 is formed with a disc opening (not shown) corresponding to the rebound passage 125 (see 31A in FIG. 3).

The pilot case 133 is provided with a rebound back pressure chamber 133b for closing the flow path through the rebound disk 131 by pressing the rebound disk 131 from the rear according to the pressure of the working fluid. The pilot case 133 is formed with a pilot opening 133a connected to the rebound valve 135.

A rebound seal 132 is positioned on the wall of the pilot case 133 to provide fluid sealing between the rebound disk 131 and the pilot case 133.

The rebound valve 135 is seated at the bottom of the pilot case 133 to cover the pilot opening 133a to provide a passage for the working fluid therethrough.

In the rebound stroke of the piston rod 102, the working fluid passes through the rebound passage 125 and passes through the slit 153 in the slit forming portion 152 (see FIG. 6) to open the disk opening (top) of the rebound disk 131. It enters the rebound back pressure chamber 133b through 131a. The working fluid exits through the slit formed in the rebound valve 135 through the pilot opening 133a of the pilot case 133 as shown by arrow a.

In addition, when the speed of the piston rod 102 is increased to increase the pressure of the working fluid, the working fluid presses the rebound disk 131 and flows down the cylinder 101 as shown by the arrow b. In addition, some of the working fluid enters the rebound back pressure chamber 133b through the slit 153 in the slit forming part 152 through the disk opening 131a on the upper part of the rebound disk 131. When the amount of the working fluid filled in the rebound back pressure chamber 133b is increased, the filled working fluid acts as a back pressure for pressing the rebound disk 131 from the rear side. Accordingly, the flow path formed between the rebound disk 131 and the piston body 124 is closed and the working fluid mainly exits through the pilot opening 133a of the pilot case 133.

As the pressure of the working fluid is further increased, the working fluid pressurizes the rebound valve 135 so that the rebound valve 135 in the form of a disc is opened so that a larger amount of working fluid is forced out through the flow path therebetween.

The compression valve means 140 also includes a compression disc 141, a pilot case 143, a compression seal 142 and a compression valve 145 similar to the rebound valve means 130. The operation of the valve structure of the present invention at the time of the compression stroke of the piston rod 102 is the same as the above-mentioned rebound stroke in view of the characteristics of the valve structure formed symmetrically, and thus the detailed description thereof will be omitted.

FIG. 6 is an enlarged view of portion A of FIG. 5, and FIG. 7 is a perspective view of a piston body applied to the dual flow valve structure according to the present invention.

6 and 7, in the piston body 124 applied to the present invention, the variable thickness part 151 and the slit forming part 152 are integrally formed. In addition, as shown in FIG. 5, since the upper and lower sides of the piston body 124 are symmetrical, the lower part of the piston body 124 is not shown in FIG. 7, but the thickness variable part 151 and the slit forming part 152 are naturally integrated in the lower part. It is formed.

delete

Piston body 124 according to a preferred embodiment of the present invention can be manufactured in one piece through sintering. At this time, since all of the plurality of slits 153 in the slit forming part 152 are manufactured by sintering, the shape of the slit 153 can be varied. Therefore, it is easy to change the flow path of the working fluid flowing through the slit 153, it is possible to increase the tuning freedom of the damping force characteristics.

In addition, the piston body 124, the variable thickness portion 151 and the slit forming portion 152 without the slit integrally sintered and then manufactured by the method of forming the slit 153 in the slit forming portion 152 through processing. It may be. In the case of forming the slit 153 by processing, since the slit 153 having a more complicated shape can be obtained than in the case of forming the slit 153 through sintering, according to the shape of the slit 153 to be obtained Can be selected as appropriate.

As mentioned above, the valve structure of the shock absorber which concerns on this invention was demonstrated with reference to the preferred embodiment of this invention. However, it should be understood that the present invention is not limited to the above-described embodiments and drawings, and various modifications and changes may be made by those skilled in the art without departing from the scope of the present invention.

101: cylinder 102: piston rod
120: piston valve 124: piston body
125: rebound passage 126: compression passage
130: rebound valve means 131: rebound disk
132: rebound seal portion 133: pilot case
133a: pilot opening 133b: rebound back pressure chamber
135: rebound valve 140: compression valve means
141: compression disk 142: compression seal portion
143: pilot case 145: compression valve
151: variable thickness portion 152: slit forming portion
153: slit

Claims (4)

In the valve structure of the shock absorber having a piston valve 120 which is installed at the end of the piston rod 102 and operates in a state bisecting the inside of the cylinder 101 to generate a damping force,
The piston valve 120,
A piston body 124 having one or more compression passages 126 through which the working fluid passes when the shock absorber is compressed, and one or more rebound passages 125 through which the working fluid passes when the shock absorber is extended;
Compression valve means (140) disposed above the piston body (124) to generate a damping force against the pressure of the working fluid passing through the compression passage (126);
Rebound valve means (130) disposed under the piston body (124) to generate a damping force against pressure of the working fluid passing through the rebound passage (125); Including,
The piston body 124,
And a slit forming portion 152 that can adjust the damping force through the slit 153 formed at the edge and a thickness variable portion 151 that can adjust the damping force according to the thickness. Part 151 is the valve structure of the shock absorber, characterized in that formed integrally through the piston body 124 through sintering. delete The method according to claim 1,
The slit 153 is a valve structure of the shock absorber, characterized in that formed separately through the processing after finishing the sintering. The method according to claim 1,
The slit forming portion (152) and the thickness variable portion 151 is a valve structure of the shock absorber, characterized in that both exist up and down symmetry relative to the piston body (124).
KR1020100100941A 2010-10-15 2010-10-15 Valve structure of a shock absorber KR101254303B1 (en)

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KR1020100100941A KR101254303B1 (en) 2010-10-15 2010-10-15 Valve structure of a shock absorber

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Application Number Priority Date Filing Date Title
KR1020100100941A KR101254303B1 (en) 2010-10-15 2010-10-15 Valve structure of a shock absorber

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KR20120039301A KR20120039301A (en) 2012-04-25
KR101254303B1 true KR101254303B1 (en) 2013-04-12

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL237405B1 (en) * 2017-10-12 2021-04-19 Akademia Gorniczo Hutnicza Im Stanislawa Staszica W Krakowie Fluid spring with variable damping force
US11427337B2 (en) * 2019-01-30 2022-08-30 Goodrich Corporation Radial slit disc energy attenuation system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004125023A (en) 2002-09-30 2004-04-22 Tokico Ltd Hydraulic buffer
JP2005344911A (en) 2004-06-07 2005-12-15 Hitachi Ltd Hydraulic shock absorber
JP2006275216A (en) 2005-03-30 2006-10-12 Hitachi Ltd Piston structure of hydraulic shock absorber
JP2009108984A (en) 2007-10-31 2009-05-21 Hitachi Ltd Hydraulic shock absorber

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004125023A (en) 2002-09-30 2004-04-22 Tokico Ltd Hydraulic buffer
JP2005344911A (en) 2004-06-07 2005-12-15 Hitachi Ltd Hydraulic shock absorber
JP2006275216A (en) 2005-03-30 2006-10-12 Hitachi Ltd Piston structure of hydraulic shock absorber
JP2009108984A (en) 2007-10-31 2009-05-21 Hitachi Ltd Hydraulic shock absorber

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