Oil seal guide seal structure for a high-pressure type shock absorber

Abstract

The application discloses an oil seal guide sealing structure of a high-pressure type shock absorber, which comprises a cylinder, a piston rod, a guide body and an oil seal assembly, the guide body is installed in the cylinder, the oil seal assembly is connected between the cylinder and the guide body, the guide body and the oil seal assembly are arranged outside the piston rod, a first concave ring groove is arranged in the guide body, an O-shaped ring and a first Gley ring are arranged in the first concave ring groove, a second concave ring groove is arranged in the oil seal assembly, and a second Gley ring is arranged in the second concave ring groove. In the process that the piston rod is elongated outward, the first Gley ring is extruded under the action of friction and has a rolling tendency by means of the O-shaped ring, so that the first Gley ring is further tightly attached to the outer wall of the piston rod and the sealing is strengthened; in the process that the piston rod is contracted inward, the second Gley ring is extruded and matched with the second concave ring groove in a wedge shape under the action of friction, so that the second Gley ring is further tightly attached to the outer wall of the piston rod and the sealing is strengthened, and the pressure can reach more than 20Mpa without leakage.

Description

Technical Field

[0001] This invention relates to the field of shock absorber technology, and specifically to an oil seal guide sealing structure for a high-pressure type shock absorber. Background Technology

[0002] Shock absorbers are used to suppress the oscillations caused by the rebound of springs after absorbing shocks and to absorb impacts from the road surface. They are widely used in automobiles to accelerate the attenuation of vibrations in the chassis and body, thereby improving the ride comfort of the vehicle. When the chassis and axle reciprocate relative to each other, the piston moves back and forth within the cylinder of the shock absorber. The oil in the cylinder housing repeatedly flows from one inner cavity to another through narrow orifices. Due to the throttling effect of the orifices, the friction between the orifice wall and the oil, as well as the friction within the liquid molecules, creates a damping force against the vibration. This converts the vibration energy of the vehicle body and chassis into heat energy, which is absorbed by the oil and the shock absorber housing and then dissipated into the atmosphere. Existing shock absorbers can basically meet the needs of daily use, but there are still some shortcomings that need to be improved.

[0003] Patent document 202110649691.8 discloses an assembly method for a shock absorber guide and oil seal, including the following steps: A. Fitting an auxiliary mounting ring onto the outside of an annular boss; B. Pre-positioning the oil seal and guide, i.e., partially fitting the annular sealing body onto the outside of the auxiliary mounting ring, with an axial gap between the annular sealing body and the guide; C. Pressing the oil seal and guide together into the outer cylinder. After the guide is positioned, continue applying pressure to the oil seal until the axial gap is eliminated and the annular sealing body is press-fitted with the inner wall of the outer cylinder. This invention, by using a rubber auxiliary mounting ring to assist in the pre-positioning of the guide and oil seal, reduces the number of pressing operations during the assembly of the guide and oil seal, thereby improving the assembly efficiency of the shock absorber.

[0004] In existing shock absorbers such as those described in the aforementioned patent, the sealing structure between the oil seal and the piston rod is simple and suitable for shock absorption in traditional passenger cars. However, with the current development of new energy passenger cars, the average weight of passenger cars has increased, and the existing shock absorber sealing structure cannot withstand higher pressure conditions. Therefore, there is an urgent need for a high-pressure type shock absorber oil seal guide sealing structure to solve the above problems. Summary of the Invention

[0005] The purpose of this invention is to provide an oil seal guide sealing structure for high-pressure type vibration dampers to overcome the above-mentioned shortcomings in the prior art.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A sealing structure for an oil seal guide in a high-pressure type vibration damper includes a cylinder, a piston rod, a guide body, and an oil seal assembly. The guide body is installed inside the cylinder, and the oil seal assembly is connected between the cylinder and the guide body. The guide body and the oil seal assembly are sleeved on the outside of the piston rod. A first concave annular groove is provided inside the guide body, and an O-ring and a first Glyd ring are provided inside the first concave annular groove. The first Glyd ring is located inside the O-ring and is pressed against the outer wall of the piston rod during the elongation process by pressing against the O-ring. A second concave annular groove is provided inside the oil seal assembly, and a second Glyd ring is provided inside the second concave annular groove. The second Glyd ring is pressed against the outer wall of the piston rod during the contraction process by wedge-shaped pressing against the second concave annular groove.

[0008] Preferably, the oil seal assembly includes an outer oil seal, an inner oil seal, and an oil seal cover. The outer oil seal includes a first metal skeleton and a first rubber body that are vulcanized into one piece. The inner oil seal includes a second metal skeleton and a second rubber body that are vulcanized into one piece. A second concave annular groove is disposed on the inner side of the second rubber body that abuts against one end of the first rubber body. The oil seal cover is sealed to the cylinder.

[0009] Preferably, the first rubber body is provided with a first elastic band on the outer side and a first sealing lip that is interference-fitted with the piston rod on the inner side.

[0010] Preferably, the second rubber body has a second elastic band on its outer side and a second sealing lip that is interference-fitted with the piston rod on its inner side.

[0011] Preferably, a third concave annular groove is provided on the outer side of the guide body, and a sealing ring is provided in the third concave annular groove. The oil seal cap is embedded between the cylinder and the guide body, and the guide body and the sealing ring are tightly held together by the interference fit with the cylinder.

[0012] Preferably, the inner side of the first glyph is configured as a wedge-shaped surface, and the inner diameter of the wedge-shaped surface increases from the inside of the cylinder to the outside of the cylinder. The minimum inner diameter of the wedge-shaped surface is configured to be interference-fitted with the piston rod.

[0013] Preferably, the outer side of the second glyph engages with the second concave annular groove in a wedge shape, and the outer diameter of the second glyph increases from inside the cylinder to outside the cylinder.

[0014] Preferably, the guide body is provided with a docking groove that communicates with the first concave annular groove, a cover plate is installed in the docking groove, and a limiting component for limiting the position of the cover plate is provided in the guide body.

[0015] Preferably, the limiting component includes an L-shaped groove provided in the guide body, an insert block provided on the cover plate that matches the L-shaped groove, an elastic groove provided on one side of the L-shaped groove, a stop block provided elastically in the elastic groove, and the insert block being held in place by the stop block after being inserted into the L-shaped groove.

[0016] Preferably, the guide body is provided with a through hole connecting the inside of the cylinder and the L-shaped groove, the cover plate is provided with an oil return hole, one end of the oil return hole passes through the side wall of the insert block near the through hole, and the abutment block is provided with an extension piece for blocking the oil return hole.

[0017] In the above technical solution, the beneficial effects of the present invention are:

[0018] The oil seal guide sealing structure of this high-pressure type vibration damper utilizes the following: during the outward extension of the piston rod, the first Glyd ring is compressed under friction and rolls with the help of the O-ring, thus further tightening its contact with the outer wall of the piston rod and strengthening the seal. During the inward retraction of the piston rod, the second Glyd ring is wedge-shaped and pressed against the second concave annular groove under friction, further tightening its contact with the outer wall of the piston rod and strengthening the seal. This sealing structure can achieve pressure above 20 MPa without leakage. Furthermore, the friction between the first and second Glyd rings and the piston rod during the extension and retraction process is minimal in non-specified directions, extending its service life.

[0019] It should be understood that the foregoing general description and the following detailed description are exemplary and illustrative only, and are not intended to limit this disclosure.

[0020] This application provides an overview of various implementations or examples of the technology described in this disclosure, and is not a full disclosure of the entire scope or all features of the disclosed technology. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this invention. For those skilled in the art, other drawings can be obtained based on these drawings.

[0022] Figure 1 This is a frontal cross-sectional view of the present invention.

[0023] Figure 2 This is a schematic diagram of the guide body structure of the present invention;

[0024] Figure 3 This is a schematic diagram of the guide body assembly structure of the present invention;

[0025] Figure 4 This is a side cross-sectional view of the guide body through hole of the present invention.

[0026] Figure 5 For the present invention Figure 4 Enlarged structural diagram at point A;

[0027] Figure 6 This is a top view cross-sectional structural diagram of the guide body of the present invention.

[0028] Explanation of reference numerals in the attached figures:

[0029] 1. Cylinder body; 2. Piston rod; 3. Guide body; 4. First concave annular groove; 5. O-ring; 6. First Glyd ring; 7. Second concave annular groove; 8. Second Glyd ring; 9. Outer oil seal; 10. Inner oil seal; 11. Oil seal cover; 12. First metal skeleton; 13. First rubber body; 14. Second metal skeleton; 15. Second rubber body; 16. First elastic band; 17. First sealing lip; 18. Second elastic band; 19. Second sealing lip; 20. Third concave annular groove; 21. Sealing ring; 22. Butt groove; 23. Cover plate; 24. L-shaped groove; 25. Insert block; 26. Elastic groove; 27. Abutment block; 28. Through hole; 29. ​​Oil return hole; 30. Extension plate. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this disclosure. All other embodiments obtained by those skilled in the art based on the described embodiments of this disclosure without creative effort are within the scope of protection of this disclosure.

[0031] Please see Figure 1-6 This invention provides a sealing structure for an oil seal guide of a high-pressure type vibration damper, comprising a cylinder 1, a piston rod 2, a guide body 3, and an oil seal assembly. The guide body 3 is installed inside the cylinder 1, and the oil seal assembly is connected between the cylinder 1 and the guide body 3. The guide body 3 and the oil seal assembly are sleeved on the outside of the piston rod 2. A first concave annular groove 4 is provided inside the guide body 3, and an O-ring 5 and a first Glyd ring 6 are provided inside the first concave annular groove 4. The first Glyd ring 6 is located inside the O-ring 5 and is pressed against the outer wall of the piston rod 2 during the elongation process by pressing against the O-ring 5. A second concave annular groove 7 is provided inside the oil seal assembly, and a second Glyd ring 8 is provided inside the second concave annular groove 7. The second Glyd ring 8 is pressed against the outer wall of the piston rod 2 during the contraction process by wedge-shaped pressing against the second concave annular groove 7.

[0032] Specifically, a piston connected to a piston rod 2 is installed inside the cylinder 1. The side of the piston connected to the piston rod 2 is the first chamber inside the cylinder 1, and the other side is the second chamber. When the piston rod 2 extends outward, the pressure in the first chamber increases and the pressure in the second chamber decreases. When the piston rod 2 retracts inward, the pressure in the first chamber decreases and the pressure in the second chamber increases. The piston rod 2 is coaxial with the cylinder 1. A bushing is installed inside the guide body 3 between it and the piston rod 2. The bushing ensures coaxial guidance of the piston rod 2 and has a certain degree of sealing. The oil seal assembly is located outside the guide body 3, sealing one end of the cylinder 1 and providing axial movable sealing between it and the piston rod 2. The first concave groove 4 is formed on the inner wall of the guide body 3; the O-ring 5 is coaxial with the first glyph 6 and their axial positions correspond. The cross-section of the O-ring 5 is O-shaped. The inner side of the first glyph 6 is set as a wedge-shaped surface, and the inner diameter of the wedge-shaped surface increases from the inside of the cylinder 1 to the outside of the cylinder 1. The minimum inner diameter of the wedge-shaped surface is interference-fitted with the piston rod 2. The axial range of the wedge-shaped surface on the first glyph 6 is greater than half of the overall axial range of the first glyph 6, and it is located at the end of the first glyph 6 further away from the cylinder 1; the O-ring 5 is elastic and provides continuous radial preload to ensure that it is in a low-pressure or no-pressure state. The initial seal is achieved, but under high pressure, the O-ring 5 deforms to compress the first glyph 6, making the first glyph 6 fit more tightly against the surface of the piston rod 2; the outer side of the second glyph 8 wedges with the second concave annular groove 7, and the outer diameter of the second glyph 8 increases from the inside of the cylinder 1 to the outside of the cylinder 1. The inner side of the second glyph 8 is in full contact with the surface of the piston rod 2. During the retraction of the piston rod 2, the frictional force causes the second glyph 8 to tend to move into the cylinder 1, thereby generating a wedge-shaped compression effect between the second glyph 8 and the second concave annular groove 7, making the second glyph 8 fit more tightly against the surface of the piston rod 2. In practical use, as the piston rod 2 extends outward, the pressure in the first chamber increases, increasing the pressure on the O-ring 5. This causes the first glyph 6 to fit more tightly against the surface of the piston rod 2. Furthermore, under the friction of the piston rod 2, the first glyph 6 tends to roll outward due to the cross-sectional shape of the O-ring 5, further tightening the smallest inner diameter against the outer wall of the piston rod 2, enhancing the seal. Conversely, as the piston rod 2 retracts inward, the pressure in the first chamber decreases, and the first glyph 6 relaxes but still receives radial preload from the O-ring 5 to maintain a seal. Meanwhile, the second glyph 8, under the friction with the piston rod 2, wedges with the second concave annular groove 7, further tightening against the outer wall of the piston rod 2 and strengthening the seal. In summary, this sealing structure can achieve pressures above 20 MPa without leakage. Moreover, the friction between the first and second glyph 6 and the piston rod 2 during extension and retraction is minimal in non-specified directions, extending their service life.

[0033] Compared with the prior art, the oil seal guide sealing structure of the high-pressure type shock absorber proposed in this embodiment of the invention achieves a stronger seal by having the first Gladius ring 6 squeezed under friction and roll with the help of the O-ring 5 during the outward extension of the piston rod 2. During the inward retraction of the piston rod 2, the second Gladius ring 8 wedges with the second concave annular groove 7 under friction, further strengthening the seal. This allows the sealing structure to achieve a pressure of over 20 MPa without leakage. Furthermore, the friction between the first Gladius ring 6 and the second Gladius ring 8 and the piston rod 2 during the extension and retraction process is small in non-specified directions, extending the service life.

[0034] As a preferred embodiment, the oil seal assembly includes an outer oil seal 9, an inner oil seal 10, and an oil seal cover 11. The outer oil seal 9 includes a vulcanized first metal skeleton 12 and a first rubber body 13. The inner oil seal 10 includes a vulcanized second metal skeleton 14 and a second rubber body 15. A second recessed annular groove 7 is disposed on the inner side of the second rubber body 15 abutting against one end of the first rubber body 13. The oil seal cover 11 is sealed to the cylinder 1. Specifically, the separate structure of the outer oil seal 9 and the inner oil seal 10 facilitates the assembly of the second glyph 8 between them. The first metal skeleton 14... The outer oil seal 9 has a stable inner and outer diameter to ensure stable assembly within the oil seal cover 11 and to ensure that the outer oil seal 9 is sealed against the outer wall of the piston rod 2. The second metal skeleton 14 has a stable inner and outer diameter to ensure stable assembly within the oil seal cover 11 and to ensure that the inner oil seal 10 is sealed against the outer wall of the piston rod 2. It also ensures that the shape of the second concave annular groove 7 meets the requirement of wedge-shaped fit with the second Glyd ring 8. The first rubber body 13 and the second rubber body 15 respectively ensure the sealing performance of the outer oil seal 9 and the inner oil seal 10 through their elasticity. The first rubber body 13 has a first elastic band 16 on its outer side and a first sealing lip 17 that is interference-fitted with the piston rod 2 on its inner side. The second rubber body 15 has a second elastic band 18 on its outer side and a second sealing lip 19 that is interference-fitted with the piston rod 2 on its inner side. The first sealing lip 17 and the second sealing lip 19 ensure the sealing performance between the oil seal assembly and the piston rod 2.

[0035] As a preferred technical solution of this embodiment, a third concave annular groove 20 is provided on the outer side of the guide body 3, and a sealing ring 21 is provided in the third concave annular groove 20. The oil seal cover 11 is embedded between the cylinder 1 and the guide body 3, and the guide body 3 and the sealing ring 21 are tightly bound together by the interference fit with the cylinder 1. Specifically, the oil seal cover 11 seals between the outer wall and the cylinder 1 by the interference fit with the cylinder 1, and at the same time, it seals between the inner wall and the guide body 3 by inwardly binding the guide body 3 and the sealing ring 21. In addition, a wedge-shaped platform is provided on the outer side of the guide body 3, and the end of the oil seal cover 11 embedded in the cylinder 1 presses against the wedge-shaped platform, thereby ensuring that the assembly position between the cylinder 1, the guide body 3 and the oil seal cover 11 is fixed.

[0036] In actual use of the above embodiments, since the first concave annular groove 4 is located on the inner wall of the guide body 3, it is difficult to assemble the O-ring 5, whose outer diameter is larger than the inner diameter of the guide body 3, and the first glyph 6 into the first concave annular groove 4. The following embodiments are proposed to solve this problem.

[0037] In another embodiment of the present invention, the guide body 3 is provided with a mating groove 22 communicating with the first concave annular groove 4. A cover plate 23 is installed in the mating groove 22. A limiting component for limiting the position of the cover plate 23 is provided in the guide body 3. Specifically, when the O-ring 5 and the first glyph 6 are assembled, the cover plate 23 is separated from the mating groove 22, thereby exposing the first concave annular groove 4. This facilitates the installation of the O-ring 5 and the first glyph 6 into the first concave annular groove 4. Then, the cover plate 23 is embedded into the mating groove 22, and the limiting component limits the cover plate 23 to prevent detachment during the assembly process.

[0038] As a preferred embodiment, the limiting component includes an L-shaped groove 24 disposed within the guide body 3, an insert 25 on the cover plate 23 that matches the L-shaped groove 24, an elastic groove 26 on one side of the L-shaped groove 24, and a stop block 27 elastically and movably disposed within the elastic groove 26. The insert 25 is inserted into the L-shaped groove 24 and held in place by the stop block 27. Specifically, one end of the L-shaped groove 24 connects to the mating groove 22, and the other end extends into the guide body 3 and bends. The L-shaped groove 24 has an arc around the axis of the guide body 3, and at least two L-shaped grooves 24 are symmetrically arranged around the axis of the guide body 3. The elastic groove 26 is arc-shaped and... Block 27 matches the elastic groove 26. An elastic element is provided in the elastic groove 26 to connect the abutment block 27. The elastic element keeps pushing the abutment block 27 so that the abutment block 27 tends to approach the L-shaped groove 24. A shovel-shaped part is provided on one side of the insertion block 25. The insertion block 25 can be slidably inserted into the L-shaped groove 24 by means of the shovel-shaped part. After the cover plate 23 is fully embedded in the mating groove 22, the shovel-shaped part corresponds to the bending direction of the L-shaped groove 24. The abutment block 27 pushes against the insertion block 25 from the opposite side of the bending direction of the L-shaped groove 24. As a result, the cover plate 23 rotates at a small angle. The shovel-shaped part forms a hook at the bending position of the L-shaped groove 24, thereby limiting the cover plate 23 in the mating groove 22.

[0039] As a further preferred technical solution of this embodiment, the guide body 3 is provided with a through hole 28 connecting the inside of the cylinder 1 and the L-shaped groove 24, and the cover plate 23 is provided with an oil return hole 29. One end of the oil return hole 29 passes through the side wall of the insert block 25 near the through hole 28, and the abutment block 27 is provided with an extension piece 30 for blocking the oil return hole 29. Specifically, due to the repeated extension and retraction of the piston rod 2, oil inevitably enters the cavity between the guide body 3 and the oil seal assembly along with the surface of the piston rod 2. The continuous accumulation of oil in the cavity will greatly affect the sealing effect and service life of the oil seal assembly. The through hole 28 is directly connected to the first chamber inside the cylinder 1, and the oil pressure is consistent. One end of the through hole 28 that connects to the L-shaped groove 24 is located on the opposite side of the bending direction of the L-shaped groove 24. The return oil hole 29 is directly connected to the cavity between the guide body 3 and the oil seal assembly, and the oil pressure is consistent. The extension piece 30 is blocked between the through hole 28 and the return oil hole 29. That is, the two sides of the extension piece 30 are affected by the oil pressure in the first chamber and the oil pressure in the cavity between the guide body 3 and the oil seal assembly, respectively. When the stop block 27 presses against the insert block 25, the extension piece 30 is attached to the insert block 25 and cannot move or bend closer to the insert block 25. However, the extension piece 30 can move or bend towards the through hole 28. In practical use, when the piston rod 2 extends, the oil pressure in the first chamber increases, which in turn increases the oil pressure acting on the through hole 28 side of the extension plate 30. The extension plate 30 then tightly fits against the return oil hole 29 side, ensuring that oil does not enter the cavity between the guide body 3 and the oil seal assembly through the through hole 28 and the return oil hole 29. When the piston rod 2 retracts, the oil pressure in the first chamber decreases, which in turn decreases the oil pressure acting on the through hole 28 side of the extension plate 30. However, if not enough oil has accumulated in the cavity between the guide body 3 and the oil seal assembly, the oil pressure on the through hole 28 side of the extension plate 30 is still greater than the oil pressure on the return oil hole 29 side. Therefore, the extension plate... The extension plate 30 remains tightly fitted to the side of the return oil hole 29, ensuring that the oil does not enter the cavity between the guide body 3 and the oil seal assembly through the through hole 28 and the return oil hole 29. When the piston rod 2 retracts and enough oil accumulates in the cavity between the guide body 3 and the oil seal assembly, the oil pressure on the side of the through hole 28 of the extension plate 30 is less than the oil pressure on the side of the return oil hole 29 of the extension plate 30. As a result, the extension plate 30 moves or bends in the direction of the through hole 28, and the oil accumulated in the cavity between the guide body 3 and the oil seal assembly returns to the first chamber through the return oil hole 29 and the through hole 28, thereby avoiding the continuous accumulation of oil and oil pressure in the cavity between the guide body 3 and the oil seal assembly.

[0040] The foregoing has only described certain exemplary embodiments of the present invention by way of illustration. Undoubtedly, those skilled in the art can modify the described embodiments in various ways without departing from the spirit and scope of the present invention. Therefore, the foregoing drawings and descriptions are illustrative in nature and should not be construed as limiting the scope of protection of the claims of the present invention.

Claims

1. A sealing structure for an oil seal guide of a high-pressure type vibration damper, comprising a cylinder (1), a piston rod (2), a guide body (3), and an oil seal assembly, wherein the guide body (3) is installed inside the cylinder (1), the oil seal assembly is connected between the cylinder (1) and the guide body (3), and the guide body (3) and the oil seal assembly are sleeved on the outside of the piston rod (2), characterized in that, The guide body (3) is provided with a first concave annular groove (4), and an O-ring (5) and a first glyph (6) are provided in the first concave annular groove (4). The first glyph (6) is located inside the O-ring (5). The first glyph (6) is pressed against the outer wall of the piston rod (2) during the elongation process by pressing against the O-ring (5). The oil seal assembly is provided with a second concave annular groove (7), and a second glyph (8) is provided in the second concave annular groove (7). The second glyph (8) is pressed against the outer wall of the piston rod (2) during the contraction process by wedge-shaped pressing against the second concave annular groove (7).

2. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 1, characterized in that, The oil seal assembly includes an outer oil seal (9), an inner oil seal (10), and an oil seal cover (11). The outer oil seal (9) includes a first metal skeleton (12) and a first rubber body (13) vulcanized together. The inner oil seal (10) includes a second metal skeleton (14) and a second rubber body (15) vulcanized together. A second concave annular groove (7) is provided on the inner side of the second rubber body (15) abutting against one end of the first rubber body (13). The oil seal cover (11) is sealed to the cylinder (1).

3. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 2, characterized in that, The first rubber body (13) has a first elastic band (16) on its outer side and a first sealing lip (17) that is interference-fitted with the piston rod (2) on its inner side.

4. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 2, characterized in that, The second rubber body (15) has a second elastic band (18) on its outer side and a second sealing lip (19) on its inner side that is interference fit with the piston rod (2).

5. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 2, characterized in that, The guide body (3) is provided with a third concave annular groove (20) on the outside, and a sealing ring (21) is provided in the third concave annular groove (20). The oil seal cap (11) is embedded between the cylinder (1) and the guide body (3), and the guide body (3) and the sealing ring (21) are held tightly by the interference fit with the cylinder (1).

6. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 1, characterized in that, The inner side of the first glyph (6) is set as a wedge-shaped surface, and the inner diameter of the wedge-shaped surface increases from the inside of the cylinder (1) to the outside of the cylinder (1). The minimum inner diameter of the wedge-shaped surface is press-fitted with the piston rod (2).

7. The sealing structure of the oil seal guide of the high-pressure type vibration damper according to claim 1, characterized in that, The outer side of the second glyph (8) is wedge-shapedly fitted with the second concave annular groove (7), and the outer diameter of the second glyph (8) is set to increase from the inside of the cylinder (1) to the outside of the cylinder (1).

8. The oil seal guide sealing structure of the high-pressure type vibration damper according to claim 1, characterized in that, The guide body (3) is provided with a docking groove (22) that connects to the first concave annular groove (4), a cover plate (23) is installed in the docking groove (22), and a limiting component for limiting the position of the cover plate (23) is provided in the guide body (3).

9. The oil seal guide sealing structure of the high-pressure type vibration damper according to claim 8, characterized in that, The limiting component includes an L-shaped groove (24) provided in the guide body (3), an insert (25) matching the L-shaped groove (24) provided on the cover plate (23), an elastic groove (26) provided on one side of the L-shaped groove (24), and a stop block (27) elastically and movably provided in the elastic groove (26). After the insert block (25) is embedded in the L-shaped groove (24), it is held in place by the stop block (27).

10. The oil seal guide sealing structure of the high-pressure type vibration damper according to claim 9, characterized in that, The guide body (3) is provided with a through hole (28) connecting the inside of the cylinder (1) and the L-shaped groove (24). The cover plate (23) is provided with an oil return hole (29). One end of the oil return hole (29) passes through the side wall of the insert block (25) near the through hole (28). The abutment block (27) is provided with an extension piece (30) for blocking the oil return hole (29).

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