A vibration damper piston structure

Abstract

This application discloses a piston structure for a shock absorber, including a body, a rubber sleeve formed by vulcanization on the outer circumference of the body, and a throttling orifice disposed on the body. The body has a mounting hole at its center for mounting a piston rod. Both ends of the body have axially protruding bosses, which are frustoconical and have concave annular guide grooves on their end faces. The bosses, guide grooves, and mounting holes are coaxial. The throttling orifice extends axially from the bottom of the guide groove through the body and opens to the outer side of the small end edge of the opposite boss. The structure also includes valve plate assemblies symmetrically disposed at both ends of the body and a force-applying component that applies pre-pressure to the valve plate assemblies to unidirectionally close the guide groove opening. The force-applying component includes at least a guide plate symmetrically disposed relative to the body and located axially outside the valve plate assemblies. A guide ring is disposed on the outer circumference of the guide plate for sliding engagement with the inner wall of the cylinder of the shock absorber.

Description

Technical Field

[0001] This application relates to the field of vibration damper technology, specifically to a vibration damper piston structure. Background Technology

[0002] Hydraulic shock absorbers are core components of automotive suspension systems, primarily used to dampen vibrations of the vehicle body and wheels, improving ride comfort and handling stability. The core working principle of a shock absorber involves the reciprocating motion of a piston within a hydraulically filled cylinder. This forces the fluid through throttling orifices or valves on the piston, creating throttling resistance and converting the mechanical energy of vibration into heat energy, which is then dissipated. During operation, in addition to the axial reciprocating motion, the geometric characteristics of the suspension guiding mechanism, the lateral acceleration during vehicle cornering, and the lateral impact caused by road unevenness generate lateral forces on the piston rod. Existing piston structures are prone to fracture and failure under these lateral forces, indicating relatively weak resistance to lateral loads, necessitating improvement. Utility Model Content

[0003] The purpose of this application is to provide a shock absorber piston structure to solve the problems in the prior art.

[0004] To achieve the above objectives, this application provides the following technical solution: a shock absorber piston structure, comprising a body 2, a rubber sleeve 10 vulcanized on the outer circumference of the body 2, and a throttling orifice 201 disposed on the body 2. The body 2 has a mounting hole 204 at its center for mounting a piston rod 3. Both ends of the body 2 have axially protruding bosses 203, each boss 203 being a frustum and having an inwardly concave annular guide groove 202 on its end face. The bosses 203, guide grooves 202, and mounting hole 204 are coaxial. The throttle orifice 201 extends axially through the bottom of the guide groove 202 and then opens onto the outer side of the small end edge of the opposite boss 203. It also includes valve plate groups symmetrically arranged at both ends of the body 2 and a force-applying component that applies pre-pressure to the valve plate groups to make the valve plate groups unidirectionally close the opening of the guide groove 202. The force-applying component includes at least a guide plate 4 symmetrically arranged relative to the body 2 and located on the outer side of the valve plate group. A guide ring 8 is provided on the outer circumference of the guide plate 4 for sliding cooperation with the inner wall of the cylinder 1 of the shock absorber.

[0005] Furthermore, an overflow cavity 11 is formed between the guide plate 4 and the body 2, and overflow holes 401 are evenly distributed along the circumference of the guide plate 4 to connect the outer side of the guide plate 4 with the overflow cavity 11.

[0006] Furthermore, the outer circular surface of the guide ring 8 includes a cylindrical guide surface 801 located at the axial center and slidingly engaged with the inner wall of the cylinder 1 of the damper, and inclined surfaces 802 extending from both ends of the guide surface 801 toward both ends of the guide ring 8 and away from the inner wall of the cylinder 1. The inclined surfaces 802 are used to introduce hydraulic oil into the space between the inner wall of the cylinder 1 and the guide surface 801 to form a pressure oil film when the guide plate 4 moves along the cylinder 1.

[0007] Furthermore, the outer end of the piston rod 3 has a coaxial optical axis section 301 and a threaded section 302. The diameter of the optical axis section 301 is smaller than the diameter of the piston rod 3. The body 2 is sleeved on the optical axis section 301, and valve plate groups and guide plates 4 are respectively installed on both sides of the optical axis section 301. The force application component also includes a nut 9 screwed into the threaded section 302. The nut 9 applies axial preload to an adjacent guide plate 4, which fixes the body 2 and the valve plate groups and guide plates 4 on both sides to the end of the piston rod 3, while making the valve plate groups unidirectionally close the opening of the guide groove 202.

[0008] Furthermore, the outer end face of the threaded section 302 is axially recessed to form a hexagonal countersunk hole 303.

[0009] Furthermore, the angle D between the generatrix of the inclined surface 802 and the generatrix of the inner wall surface of the cylinder 1 is 12°~17°.

[0010] The beneficial technical effects of this application are as follows: The shock absorber piston structure provided by this application effectively increases the thickness of the body by setting bosses at both ends of the body. While enhancing its own strength, it also increases the length of the connection with the piston rod, which is conducive to improving the ability to resist lateral loads. By setting guide plates at both ends of the body, the length of the piston structure is increased axially, and the body is sandwiched in the middle, which further enhances the ability to resist lateral loads. Attached Figure Description

[0011] Figure 1 This is a partial view of the shock absorber piston and cylinder block after assembly according to this application; Figure 2 for Figure 1 Enlarged view of a portion of point A in the middle; Figure 3 This is a schematic diagram of the body of the shock absorber piston of this application; In the diagram: 1. Cylinder block; 2. Body; 201. Throttling orifice; 202. Guide groove; 203. Boss; 204. Mounting hole; 3. Piston rod; 301. Optical shaft section; 302. Threaded section; 303. Countersunk hole; 4. Guide plate; 401. Flow hole; 5. Back pressure plate; 6. Secondary valve plate; 7. Primary valve plate; 8. Guide ring; 801. Guide surface; 802. Inclined surface; 9. Nut; 10. Rubber sleeve; 11. Escape chamber. Detailed Implementation

[0012] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0013] Please see Figure 1-3 A shock absorber piston structure includes a body 2, a rubber sleeve 10 vulcanized on the outer circumference of the body 2, and a throttling orifice 201 disposed on the body 2. The body 2 has a mounting hole 204 for mounting a piston rod 3 at its center. Both ends of the body 2 have axially protruding bosses 203, which are frustoconical and have concave annular guide grooves 202 on their end faces. The bosses 203, guide grooves 202, and mounting holes 204 are coaxial. The throttling orifice 201 extends axially from the bottom of the guide groove 202 through the body 2 and opens to the outer side of the small end edge of the opposite boss 203. The structure also includes valve plate groups symmetrically disposed at both ends of the body 2 and a force-applying component that applies pre-pressure to the valve plate groups to unidirectionally close the opening of the guide groove 202. The force-applying component includes at least a guide plate 4 symmetrically disposed relative to the body 2 and located axially outside the valve plate groups. A guide ring 8 is disposed on the outer circumference of the guide plate 4 for sliding cooperation with the inner wall of the cylinder 1 of the shock absorber.

[0014] With the above-mentioned configuration, the shock absorber piston structure provided in this application effectively increases the thickness of the solid body by setting bosses 203 at both ends of the body 2, forming a structure that is thick in the center and thin at the edges. While enhancing its own strength, it also increases the length of the connection with the piston rod 3, which is beneficial to improving the ability to resist lateral loads. By setting guide plates 4 at both ends of the body 2, the length of the piston structure is increased axially, and the body 2 is sandwiched in the middle, which further enhances the ability to resist lateral loads and fundamentally avoids the hidden danger of the body 2 breaking and being damaged.

[0015] In a further preferred embodiment, an overflow cavity 11 is formed between the guide plate 4 and the body 2. Flow holes 401 are evenly distributed circumferentially on the guide plate 4 to connect the outer side of the guide plate 4 with the overflow cavity 11. Thus, through the circumferential connection of the overflow cavity 11, the hydraulic oil, after flowing out of the throttle hole 201, is distributed through the overflow cavity 11 to each of the flow holes 401 and discharged into the cylinder 1 on the corresponding side (the body 2 divides the cylinder 1 into two parts, located on both sides of the body 2). This not only enhances the overall structural strength of the piston but also facilitates the flow of hydraulic oil when the piston moves continuously during the recovery and compression strokes during operation. It avoids obstructing the flow of hydraulic oil through channels other than the throttle hole 201, ensuring vibration damping performance. In this embodiment, the flow holes 401 can be set to 6 or 8 evenly distributed circumferentially around the axis of the guide plate 4.

[0016] In a further preferred embodiment, the outer circular surface of the guide ring 8 includes a cylindrical guide surface 801 located at the axial center and slidingly engaging with the inner wall of the cylinder 1 of the damper, and inclined surfaces 802 extending from both ends of the guide surface 801 toward both ends of the guide ring 8 and away from the inner wall of the cylinder 1. The inclined surfaces 802 are used to introduce hydraulic oil into the space between the inner wall of the cylinder 1 and the guide surface 801 to form a pressure oil film when the guide plate 4 moves along the cylinder 1. This ensures effective lubrication between the inner wall of the cylinder 1 and the guide surface 801, guarantees the smoothness of the piston during movement, further improves the damping sensitivity, and thus improves the damping effect.

[0017] More preferably, the outer end of the piston rod 3 has a coaxial optical axis section 301 and a threaded section 302. The diameter of the optical axis section 301 is smaller than the diameter of the piston rod 3. The body 2 is sleeved on the optical axis section 301, and valve plate assemblies and guide plates 4 are respectively mounted on both sides of the optical axis section 301. The force-applying component also includes a nut 9 screwed into the threaded section 302. The nut 9 applies axial preload to an adjacent guide plate 4, fixing the body 2 and the valve plate assemblies and guide plates 4 on both sides to the end of the piston rod 3 while causing the valve plate assembly to unidirectionally close the opening of the guide groove 202. In this embodiment, the valve plate assembly includes back pressure plates that abut against each other in sequence. 5. Secondary valve plate 6 and primary valve plate 7, wherein the back pressure plate 5 abuts against the guide plate 4 at the other end face of the secondary valve plate 7, and the primary valve plate 7 covers the opening face of the guide channel 202 for unidirectional sealing of the opening face of the guide channel 202. Through the above arrangement, the back pressure plate 5, secondary valve plate 6, primary valve plate 7, body 2, guide plate 4 and piston rod 3 are connected as a whole to form a stable piston structure. Furthermore, the guide plate 4 and body 2 are independent parts, which fundamentally eliminates the stress concentration phenomenon and effectively avoids the hidden danger of existing pistons breaking under lateral force, ensuring reliability and service life.

[0018] In a further preferred embodiment, the outer end face of the threaded section 302 is axially recessed to form a hexagonal countersunk hole 303. In this way, during assembly, a tool such as a hexagonal wrench can be inserted into the countersunk hole 303 to provide a reaction force nearby when tightening or loosening the nut 9, making the assembly work simple and easy to operate.

[0019] More preferably, the angle D between the generatrix of the inclined surface 802 and the generatrix of the inner wall surface of the cylinder 1 is 12°~17°. In this embodiment, the angle D is 15°. Thus, when the guide plate 4 moves with the piston rod 3, the axial resistance of the inclined surface 802 to the hydraulic oil is smaller, making it easier for the hydraulic oil to be squeezed into the space between the inner wall of the cylinder 1 and the guide surface 801 to form a stable pressure oil film, thereby improving lubrication performance. It can be understood that the inclined surface 802 forms a cone shape on the outer circumference of the guide ring 8. The guide ring 8 can be made of a polymer wear-resistant material such as nylon or Teflon, while the guide plate 4 is made of metal. First, an annular groove is machined on the outer circumference of the guide plate 4, and then injection molding or other existing technologies are used. The guide ring 8 is wrapped around the circumferential surface of the guide plate 4 and mechanically inlaid with the annular groove. Then, through machining methods such as turning, a tapered shape is formed to constitute the inclined surface 802 and a guide surface 801 for sliding fit, ensuring the coaxiality of the inner hole on the guide plate 4 that mates with the optical axis section 301, the inclined surface 802, and the guide surface 801. It can be understood that the back pressure plate 5, the secondary valve plate 6, and the primary valve plate 7 all have inner holes that mate with the optical axis section 301, and these inner holes are coaxial with the axes of the back pressure plate 5, the secondary valve plate 6, and the primary valve plate 7 themselves. Let the diameter of the back pressure plate 5 be d1, the diameter of the secondary valve plate 6 be d2, and the diameter of the primary valve plate 7 be d3, then d1 < d2 < d3.

[0020] It should be noted that, in this document, the terms “comprising,” “including,” or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus.

[0021] Furthermore, any content not described in detail in this specification is existing technology known to those skilled in the art.

[0022] Although embodiments of this application have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A shock absorber piston structure, comprising a body (2), a rubber sleeve (10) vulcanized on the outer circumference of the body (2), and a throttling orifice (201) disposed on the body (2), wherein a mounting hole (204) for mounting a piston rod (3) is provided at the center of the body (2), characterized in that: Both ends of the body (2) are axially protruding to form bosses (203). The bosses (203) are truncated cones and have concave annular guide grooves (202) on their end faces. The bosses (203), guide grooves (202) and mounting holes (204) are coaxial. Throttling holes (201) axially and obliquely penetrate the body (2) from the bottom of the guide grooves (202) and open on the outer side of the small end edge of the opposite bosses (203). The body also includes valve plate groups symmetrically arranged at both ends of the body (2) and force application components that apply pre-pressure to the valve plate groups to make the valve plate groups unidirectionally close the opening of the guide grooves (202). The force application components include at least a guide plate (4) symmetrically arranged relative to the body (2) and located on the outer side of the valve plate groups. A guide ring (8) is provided on the outer circumference of the guide plate (4) for sliding cooperation with the inner wall of the cylinder (1) of the damper.

2. The damper piston structure according to claim 1, characterized in that: An overflow cavity (11) is formed between the guide plate (4) and the body (2). Flow holes (401) are evenly distributed along the circumference of the guide plate (4) to connect the outside of the guide plate (4) with the overflow cavity (11).

3. The shock absorber piston structure according to claim 2, characterized in that: The outer circular surface of the guide ring (8) includes a cylindrical guide surface (801) located in the middle of the axial direction and slidingly engaging with the inner wall of the cylinder body (1) of the damper, and inclined surfaces (802) extending from both ends of the guide surface (801) toward both ends of the guide ring (8) and away from the inner wall of the cylinder body (1). The inclined surfaces (802) are used to introduce hydraulic oil into the space between the inner wall of the cylinder body (1) and the guide surface (801) to form a pressure oil film when the guide plate (4) moves along the cylinder body (1).

4. The damper piston structure according to claim 1, characterized in that: The piston rod (3) has a coaxial optical axis section (301) and a threaded section (302) at its outer end. The diameter of the optical axis section (301) is smaller than that of the piston rod (3). The body (2) is fitted on the optical axis section (301). The optical axis section (301) is located on both sides of the body (2) and valve plate groups and guide plates (4) are respectively fitted. The force application component also includes a nut (9) screwed into the threaded section (302). The nut (9) applies axial preload to an adjacent guide plate (4). While fixing the body (2) and the valve plate groups and guide plates (4) on both sides to the end of the piston rod (3), the valve plate groups unidirectionally close the opening of the guide groove (202).

5. The damper piston structure according to claim 4, characterized in that: The outer end face of the threaded section (302) is axially recessed to form a hexagonal countersunk hole (303).

6. The damper piston structure according to claim 3, characterized in that: The angle D between the inclined surface (802) generatrix and the inner wall surface generatrix of the cylinder (1) is 12°~17°.

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