A type of air spring anti-rotation structure

Abstract

This utility model relates to the field of air spring technology, specifically to an air spring anti-rotation structure, including an air spring piston, a damper oil reservoir, and an anti-rotation ring. The anti-rotation ring is disposed between the inner side of the piston and the outer side of the oil reservoir, and one end of the piston has a conical opening. The anti-rotation ring includes a first section, a second section, and a third section. The first section has a protrusion in the radial direction, and the protrusions are arranged in an array along the circumferential direction of the first section. The second section is a conical shape adapted to the inner wall of the conical opening of the piston, and the small end of the second section is connected to the first section. The third section is annularly protruding along the radial direction of the anti-rotation ring, and the inner side of the third section has a groove for fitting and engaging with the mounting plate of the damper. The air spring anti-rotation structure provided by this utility model can further avoid or reduce the relative displacement between the air spring piston and the damper oil reservoir, and eliminate frictional noise caused by relative displacement.

Description

Technical Field

[0001] This utility model relates to the field of air spring technology, specifically to an air spring anti-rotation structure. Background Technology

[0002] As the automotive industry moves towards higher comfort and handling stability, air suspension is gradually replacing traditional passive damping structures and becoming the mainstream choice for mid-to-high-end models. Air springs, with their high load-bearing capacity, variable stiffness, and small space occupation, improve the overall vehicle vibration isolation while optimizing chassis layout. However, the stability of the connection between the air spring piston and the shock absorber remains a challenge for the industry.

[0003] The current mainstream solution uses a conical disc with a rubber retaining ring for fixation. Although the rubber elasticity can reduce some noise, the inherent elasticity of the rubber causes the piston to have slight displacement in six degrees of freedom, including translation along the X, Y, and Z axes and rotation along the RX, RY, and RZ axes. This can easily cause friction noise between the piston and the protective cover and oil reservoir, seriously affecting the overall NVH performance (noise, vibration, and acoustic roughness). In addition, the elastic deformation of the rubber parts will produce clearances as the operating conditions fluctuate, and the reliability of the limit will decrease after long-term use. Utility Model Content

[0004] In view of the shortcomings of the prior art, the purpose of this utility model is to provide an air spring anti-rotation structure, which can further avoid or reduce the relative displacement between the piston of the air spring and the oil reservoir of the shock absorber, and eliminate frictional noise caused by relative displacement.

[0005] To achieve the above and other related objectives, this utility model provides an air spring anti-rotation structure, including an air spring piston, a damper oil reservoir, and an anti-rotation ring. The anti-rotation ring is disposed between the inner side of the piston and the outer side of the oil reservoir, and one end of the piston has a tapered opening. The anti-rotation ring includes:

[0006] The first section is cylindrical in shape, and a protrusion is provided in the radial direction of the first section. A plurality of the protrusions are arranged along the circumferential direction of the first section, and the first section is interference-fitted with the inner wall of the piston.

[0007] The second section is a cone shape adapted to the inner wall of the cone-shaped opening of the piston, and the small end of the second section is connected to the first section;

[0008] The third section is connected to the large end of the second section and extends radially outward along the anti-rotation ring, and the inner side of the third section has a groove for fitting and engaging with the mounting plate of the shock absorber.

[0009] In one embodiment of the present invention, the anti-rotation ring is provided with multiple slots in the radial direction that penetrate the inner and outer walls of the anti-rotation ring itself. The multiple slots are arranged along the circumferential direction of the anti-rotation ring, and the slots extend from the first section to the third section.

[0010] In one embodiment of this utility model, along the circumferential direction of the anti-rotation ring, a predetermined number of protrusions are evenly spaced between any two adjacent slots.

[0011] In one embodiment of the present invention, a limiting part for limiting the mounting plate is provided in the radial direction of the third section, and the limiting part is a point protrusion or a pin.

[0012] In one embodiment of the present invention, the piston has a first plane at one end with a conical opening, and the third section has a second plane at one end near the second section, with the first plane and the second plane being arranged parallel to each other.

[0013] In one embodiment of this utility model, the protrusion is a rib extending along the axial direction of the first section, and there are 6 to 18 ribs, and the interference fit between the rib and the inner wall of the piston is 0.3-0.8 mm.

[0014] In one embodiment of the present invention, an annular groove is provided between the first section and the second section.

[0015] In one embodiment of this utility model, the anti-rotation ring is made of a rigid material.

[0016] In one embodiment of this utility model, the outer wall of the anti-rotation ring is in direct contact with the inner wall of the piston, and the inner wall of the anti-rotation ring is in direct contact with the outer wall of the oil reservoir.

[0017] In one embodiment of this utility model, the anti-rotation ring is configured with an interference fit with the oil reservoir.

[0018] In summary, the first section of this invention, through its cylindrical structure and circumferentially arrayed protrusions, is interference-fitted with the inner wall of the piston. The radial compression of the protrusions directly restricts the piston's translation in the X and Y directions and its rotation around the X and Y axes (RX and RY directions). The conical structure of the second section fits tightly against the inner wall of the piston's conical opening. The wedge-shaped amplification effect of the conical surface generates a radial clamping force, effectively suppressing the piston's rotation around the oil reservoir axis (RZ direction) and axial movement (Z direction). The annular protrusion structure and inner groove of the third section rigidly engage with the damper mounting plate, forming a mechanical hard limit, further enhancing the reliability of axial positioning. This invention, through multi-dimensional limiting settings, combined with a rigid interference-fit connection and a non-elastic component structure that eliminates the rubber retainer ring, achieves a stable connection between the piston and the damper in all dimensions, fundamentally eliminating the risk of abnormal noise caused by multi-directional relative movement. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the air spring anti-rotation structure before the improvement of this utility model;

[0021] Figure 2 This is a schematic diagram of the air spring anti-rotation structure in one embodiment of the present utility model;

[0022] Figure 3 This is a schematic diagram of the anti-rotation ring structure in one embodiment of the present invention;

[0023] Figure 4 This is a schematic diagram of the piston and protective cover installation in one embodiment of the present invention;

[0024] Component labeling: Piston 1, Conical opening 11, First plane 111, Oil reservoir 2, Anti-rotation ring 3, First section 31, Protrusion 311, Groove 312, Annular groove 313, Second section 32, Third section 33, Slot 331, Limiting part 332, Second plane 333, Mounting plate 4, Protective cover 5, Rubber retaining ring 6, Sealing ring 7, Vibration damper piston rod 8. Detailed Implementation

[0025] The following specific examples illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification. This utility model can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this utility model. It should be noted that, in the absence of conflict, the following embodiments and features in the embodiments can be combined with each other. It should also be understood that the terminology used in the embodiments of this utility model is for describing specific implementation schemes and not for limiting the scope of protection of this utility model. Test methods in the following embodiments that do not specify specific conditions are generally performed under conventional conditions or according to the conditions recommended by the respective manufacturers.

[0026] Please see Figures 1 to 4 It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and are not intended to limit the scope of this invention. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and purpose of this invention, should still fall within the scope of the technical content disclosed in this invention. Furthermore, the terms such as "upper," "lower," "left," "right," "middle," and "one" used in this specification are merely for clarity and are not intended to limit the scope of this invention. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of this invention.

[0027] When numerical ranges are given in the embodiments, it should be understood that, unless otherwise stated in this invention, both endpoints of each numerical range and any value between the two endpoints may be selected. Unless otherwise defined, all technical and scientific terms used in this invention, as well as the prior art known to those skilled in the art and the description of this invention, may be implemented using any prior art methods, devices, and materials similar to or equivalent to those described, used, or made of materials in the embodiments of this invention.

[0028] Replacing the original coil springs with air springs saves chassis layout space while effectively improving the vehicle's vibration isolation and comfort. However, in the installation and assembly of the air spring body and the shock absorber, the current mainstream solution uses a conical disc and rubber retaining ring 6 to achieve fixation and eliminate the risk of abnormal noise. See the specific solution below. Figure 1The rubber retaining ring can effectively reduce noise, but it cannot provide sufficient limiting support. Due to the elasticity of the rubber retaining ring 6, the piston moves in the six directions of X, Y, Z, RX, RY, and RZ, causing friction between the piston 1 and the protective cover 5, which generates noise and causes great trouble to the NVH of the whole vehicle.

[0029] Please see Figure 2-3 This utility model provides an air spring anti-rotation structure, including an air spring piston 1, a damper oil reservoir 2, and an anti-rotation ring 3. The anti-rotation ring 3 is disposed between the inner side of the piston 1 and the outer side of the oil reservoir 2. One end of the piston 1 has a tapered opening 11. The anti-rotation ring 3 includes a first section 31, a second section 32, and a third section 33. The first section 31 is cylindrical, and a protrusion 311 is provided in the radial direction of the first section 31. A plurality of the protrusions 311 are arranged along the... The first section 31 is evenly arranged in a circumferential array, and the first section 31 is interference-fitted with the inner wall of the piston 1; the second section 32 is a cone shape adapted to the inner wall of the cone opening 11 of the piston 1, and the small end of the second section 32 is connected to the first section 31; the third section 33 is connected to the large end of the second section 32 and extends outward along the radial direction of the anti-rotation ring 3, and the inner side of the third section 33 is formed with a groove 331 for fitting and engaging with the mounting plate 4 of the shock absorber.

[0030] It should be noted that the anti-rotation ring 3, as an intermediate connecting component, has its inner and outer sides respectively forming a mating relationship with the inner wall of piston 1 and the outer wall of oil reservoir 2, constituting the force transmission path between piston 1 and oil reservoir 2. The cylindrical structure of the first section 31 is in direct contact with the inner wall of piston 1. The circumferentially arrayed protrusions 311 (such as ribs or protrusion structures) generate radial compression through interference fit, restricting the translation of piston 1 in the horizontal direction (X, Y axes) and its rotation around the horizontal axis (RX, RY directions). The number of protrusions 311 can be adjusted according to actual needs (such as 8-16), and their cross-sectional shape can be rectangular, trapezoidal, or arc-shaped to adapt to different interference requirements. The conical shape of the second section 32 forms a surface contact fit with the conical opening 11 of the piston 1. Its taper is consistent with or similar to the taper of the piston 1 opening (e.g., cone angle 30°-60°). Through the wedging effect of the conical surface, a radial expansion force is generated when the piston 1 is pressed down, tightly fitting the outer wall of the oil reservoir 2 and suppressing the rotation (RZ direction) and axial movement (Z direction) of the piston 1 around the axis of the oil reservoir 2. This conical fit can be achieved through rigid metal-to-metal contact, or by applying a wear-resistant coating (e.g., nylon coating) to the conical surface to reduce wear. The third section 33 extends radially outward along the anti-rotation ring 3. Its inner groove 331 forms a mechanical engagement with the damper mounting plate 4 (e.g., the annular groove 331 engages with the edge of the disc-shaped mounting plate 4, or the segmented groove 331 engages with the positioning pin of the mounting plate 4), directly restricting the axial movement (Z direction) of the damper. The mounting plate 4 rigidly connects the anti-rotation ring 3 to the damper body, enhancing the overall torsional stiffness.

[0031] This structure achieves full-dimensional restriction of the piston 1's six degrees of freedom through the coordinated action of the three sections of the anti-rotation ring 3: the protrusion 311 of the first section 31 has an interference fit with the inner wall of the piston 1, directly constraining the piston 1's translation in the X and Y axes and rotation in the RX and RY axes through rigid contact; the conical surface of the second section 32 uses the wedge principle to convert the axial pressure of the piston 1 into radial clamping force, constraining the rotation in the RZ direction and the axial movement in the Z direction; the slot 331 of the third section 33 engages with the damper mounting plate 4, forming an axial mechanical limit, further strengthening the positioning in the Z direction. The combination of these three elements allows the piston 1 to be fixed in multiple directions through pure rigid fit without the rubber retaining ring 6, avoiding displacement gaps caused by elastic deformation, and eliminating frictional noise caused by relative motion from the root.

[0032] This design utilizes a multi-section structure to restrict the multi-directional movement of piston 1, avoiding friction between piston 1 and oil reservoir 2 and protective cover 5, thus significantly improving the overall vehicle NVH performance. The rubber retaining ring is eliminated, and a purely rigid connection with interference fit and mechanical engagement is adopted to prevent limit failure caused by aging of the rubber retaining ring 6, improving long-term stability. By reducing the number of rubber retaining rings 6 and integrating the anti-rotation ring 3 into a single unit, multi-functional integration is achieved, reducing parts procurement and assembly costs. Furthermore, through the positioning and engagement of the slot 331 and the mounting plate 4, precise control of the pressing depth can be achieved with the help of specialized equipment (such as ensuring proper installation by checking the dimensions after installation), improving assembly efficiency and consistency.

[0033] Please see Figure 2-3 As an optional embodiment of this case, the anti-rotation ring 3 is provided with multiple slots 312 in the radial direction that penetrate the inner and outer walls of the anti-rotation ring 3 itself. The multiple slots 312 are arranged along the circumferential direction of the anti-rotation ring 3, and the slots 312 extend from the first section 31 to the third section 33.

[0034] It should be noted that the slot 312 is a strip structure that runs radially through the anti-rotation ring 3. Its number can be adjusted according to the size of the anti-rotation ring 3 (e.g., 6-12 slots), and it is evenly distributed circumferentially to ensure balanced stress. The slot 312 extends from the first section 31 (cylindrical section) to the third section 33 (annular protrusion section), forming a through-slot structure that penetrates the main body of the anti-rotation ring 3. The cross-sectional shape of the slot 312 is rectangular, trapezoidal, or arc-shaped; the slot 312 can be straight or slightly inclined in the axial direction to adapt to different press-fitting process requirements; the bottom of the slot 312 can be chamfered or rounded to reduce stress concentration. To improve assembly compatibility while ensuring a rigid connection, enhance the clamping force on the oil reservoir 2, and further eliminate the risk of abnormal noise caused by multi-directional relative movement, this design utilizes the slot 312 to give the anti-rotation ring 3 a limited elastic deformation capability in the radial direction. When the anti-rotation ring 3 is press-fitted between the piston 1 and the oil reservoir 2, the material at the slot 312 can slightly expand or contract radially, enhancing the fit with the inner wall of the piston 1 and the outer wall of the oil reservoir 2 through an elastic clamping effect. Especially during the tapered engagement process of the second section 32, the slot 312 allows the anti-rotation ring 3 to undergo slight deformation under radial pressure, further amplifying the wedging effect of the tapered surface, creating a tighter clamping force between the anti-rotation ring 3 and the oil reservoir 2, thereby effectively suppressing the rotation (RZ direction) and axial movement (Z direction) of the piston 1 around the axis of the oil reservoir 2. Furthermore, the slot 312 extends to the third section 33, which can help release the stress during press-fitting and prevent assembly difficulties or material damage caused by excessive rigidity of the anti-rotation ring 3.

[0035] Please see Figure 2-3 As an optional embodiment of this case, along the circumferential direction of the anti-rotation ring 3, a predetermined number of protrusions 311 are evenly spaced between any two adjacent slots 312.

[0036] It should be noted that the protrusions 311 are strip-shaped structures disposed on the outer wall of the anti-rotation ring 3, located circumferentially between adjacent slots 312, and their number matches the number of slots 312 (e.g., when there are 6 slots 312, there can be 6 sets of protrusions 311), with uniform spacing angles (e.g., 60° intervals). The protrusions 311 can be cylindrical, prismatic, or hemispherical, and their height is adapted to the interference fit between the outer wall of the anti-rotation ring 3 and the inner wall of the piston 1, generating radial pressure through the interference fit with the inner wall of the piston 1. The protrusions 311 are evenly distributed circumferentially, forming an alternating structure of rigid support and elastic deformation with the slots 312: the corresponding positions of the protrusions 311 provide rigid anti-rotation force through interference fit, restricting the piston 1 from translation in the X and Y axis directions and rotation in the RX and RY directions; the corresponding positions of the slots 312 enhance the clamping force through elastic deformation. The two work together to make the anti-rotation ring 3 have both a rigid limiting fulcrum in the circumferential direction and the ability to adapt to assembly errors through deformation.

[0037] Please see Figure 2-3 As an optional embodiment of this case, the third section 33 is provided with a limiting part 332 for limiting the mounting plate 4 in the radial direction. The limiting part 332 is a point protrusion or a pin.

[0038] It should be noted that the limiting part 332 is a positioning structure that extends radially from the third section 33 (annular protrusion section). The point protrusion is a local protrusion (such as a hemispherical boss), and the pin is a columnar protrusion (such as a cylindrical pin). Both are adapted to engage with the grooves or holes of the damper mounting plate 4. The limiting part 332 can be evenly distributed circumferentially along the third section 33 (such as 3-6), and its height or length is based on the mechanical stop formed after being inserted into the corresponding structure of the mounting plate 4. By directly engaging the limiting part 332 (point protrusion or pin) of the third section 33 with the mounting plate 4, an axial (Z direction) mechanical hard limit is formed, which transforms the axial displacement constraint of the anti-rotation ring 3 into a rigid connection between the mounting plate 4 and the damper body, further suppressing the piston 1's tendency to move along the Z axis and rotate around each axis, and enhancing anti-rotation reliability and NVH performance.

[0039] Please see Figure 2-3 As an optional embodiment of this case, the piston 1 has a first plane 111 at one end with a conical opening 11, and the third section 33 has a second plane 333 at one end near the second section 32. The first plane 111 and the second plane 333 are arranged in parallel and spaced apart.

[0040] It should be noted that the first plane 111 is the annular plane at the end of the conical opening 11 of the piston 1, extending radially along the piston 1, forming the positioning reference surface of the lower end of the piston 1; the second plane 333 is the end face of the third section 33 (annular protrusion section) near the conical second section 32, also extending radially along the anti-rotation ring 3, parallel to the first plane 111 and with a gap (i.e., an axial gap is formed between the two). The parallel and spaced arrangement of the first plane 111 and the second plane 333 forms an axial positioning reference between the piston 1 and the anti-rotation ring 3: when the piston 1 is pressed into the design position, the distance between the two planes corresponds to the preset assembly depth. By controlling this distance, it can be ensured that the conical second section 32 of the anti-rotation ring 3 is completely fitted with the conical opening 11 of the piston 1, while ensuring that the groove 331 of the third section 33 is correctly engaged with the damper mounting plate 4. It should be understood that the first plane 111 and the second plane 333 are parallel and spaced apart, and the minimum distance of this gap can be zero. By aligning the mechanical reference surfaces, the failure of the tapered fit or misalignment of the slot 331 due to excessively deep or shallow pressing is avoided, ensuring that the functions of each section of the anti-rotation ring 3 are realized synchronously, thereby effectively limiting the axial movement of the piston 1 in the Z-axis direction and its rotation in the RZ-axis direction. The distance between the two parallel planes can be directly verified by feeler gauge measurement or visual inspection, providing an intuitive basis for judging assembly quality, avoiding reliance on complex testing equipment, and improving production efficiency.

[0041] Please see Figure 2-3 As an optional embodiment of this case, the protrusion 311 is a rib structure extending along the axial direction of the first section 31, the rib structure is provided with 6 to 18 ribs, and the interference between the rib and the inner wall of the piston 1 is 0.3-0.8mm.

[0042] It should be noted that the protrusion 311 is specifically defined as a rib structure extending axially along the first section 31 (cylindrical section), with its extension direction parallel to the axis of piston 1, forming a longitudinal ridge. The number of ribs can be adjusted within the range of 6-18 (such as the common 12 ribs), and they are evenly distributed circumferentially to ensure balanced pressure on the inner wall of piston 1. The interference fit range (0.3-0.8mm) is set according to the fitting accuracy requirements of piston 1 and oil reservoir 2. For example, 0.5mm generates friction by radially pressing the inner wall of piston 1 through the ribs, restricting the translation of piston 1 in the X and Y axis directions and the rotation in the RX and RY axis directions.

[0043] Please see Figure 2-3 As an optional embodiment of this case, an annular groove 313 is provided between the first section 31 and the second section 32.

[0044] It should be noted that the annular groove 313 is a groove structure that surrounds the anti-rotation ring 3 in a circumferential direction, located between the cylindrical first section 31 and the conical second section 32. The function of the annular groove 313 is to reduce stress transmission between the first section 31 and the second section 32, reduce mutual interference between the first section 31 and the second section 32 when under force, avoid insufficient fit clearance or deformation due to stress superposition, and improve the accuracy of movement restriction in all directions.

[0045] As an optional embodiment of this case, the anti-rotation ring 3 is made of a rigid material.

[0046] It should be noted that the anti-rotation ring 3 is not made of elastic materials such as rubber or silicone, but rather of metal (aluminum alloy, steel) or rigid plastic (nylon, polyoxymethylene). This material ensures a rigid connection with interference fit, conical wedging, and locking groove 331, preventing multi-directional displacement of the piston 1 due to material elasticity. The rigidity of the non-elastic material allows the anti-rotation ring 3 to directly transmit loads through mechanical structures (protrusion 311, conical surface, locking groove 331) when engaging with the piston 1 and oil reservoir 2, rather than relying on frictional forces generated by material elastic deformation. This purely rigid connection precisely restricts the movement of the piston 1 in the six degrees of freedom (X, Y, Z, RX, RY, RZ), thereby eliminating the locking failure problem caused by deformation hysteresis or aging of traditional rubber retaining rings 6, ensuring the long-term stability of the anti-rotation function.

[0047] Please see Figure 2-3 As an optional embodiment of this case, the outer wall of the anti-rotation ring 3 is in direct contact with the inner wall of the piston 1, and the inner wall of the anti-rotation ring 3 is in direct contact with the outer wall of the oil reservoir 2.

[0048] It should be noted that the anti-rotation ring 3, as the intermediate layer between the piston 1 and the oil reservoir 2, has direct contact between its outer wall and the inner wall of the piston 1, and between its inner wall and the outer wall of the oil reservoir 2 without any intermediate medium, forming a rigid connection chain of piston 1-anti-rotation ring 3-oil reservoir 2. This eliminates the need for elastic intermediate components such as rubber retaining ring 6 in traditional solutions, and transmits load through direct contact between metals (or non-metallic rigid materials).

[0049] Please see Figure 2-3 As an optional embodiment of this case, the anti-rotation ring 3 is configured with an interference fit with the oil reservoir 2.

[0050] It should be noted that the inner wall of the anti-rotation ring 3 is connected to the outer wall of the oil reservoir 2 by an interference fit, that is, the inner diameter of the anti-rotation ring 3 is slightly smaller than the outer diameter of the oil reservoir 2, which generates a radial clamping force after pressing. The interference fit is set according to the load requirements, so that static friction is formed between the anti-rotation ring 3 and the oil reservoir 2, preventing relative rotation (RZ direction) and axial movement (Z direction) between the two.

[0051] Please see Figure 2-4 In this case, the upper part of the anti-rotation ring 3 is in linear contact with the piston 1, and the lower conical structure provides support for the piston 1. Through the six slots 312, a large clamping force is generated on the damper oil reservoir 2 during pressing, restricting movement in the RZ direction. At the bottom of the anti-rotation ring 3, it engages with the damper mounting plate 4 through a slot 331 and point protrusions or pins, providing positioning. The piston 1 and protective cover 5, through a partial interference design, restrict the shaking or tilting of the piston 1 top during operation, preventing abnormal noise. This case eliminates the rubber retainer ring; the absence of the rubber retainer ring 6 provides a more stable fit. The anti-rotation ring 3 is assembled by using specialized equipment to press-fit the piston 1 at the first section 31 and the third section 33. After pressing, it is identified through a re-detection method. Figure 4 The size of the H in the middle is used to determine whether it should be pressed into the designed position.

[0052] This case, through the design of a fixed ring, restricts the movement of the fluctuating piston in six directions (X, Y, Z, RX, RY, RZ) without increasing the overall volume of the air spring, thereby reducing the risk of abnormal noise and improving the NVH performance of the entire vehicle. Furthermore, it solves the problem of abnormal noise while reducing the number of parts, and also provides a reference case for saving costs in air spring design.

[0053] In summary, this utility model effectively overcomes some practical problems in the prior art, thus having high utilization value and significance.

[0054] The above embodiments are merely illustrative of the principles and effects of this utility model and are not intended to limit the scope of this utility model. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of this utility model. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in this utility model should still be covered by the claims of this utility model.

Claims

1. A spring stop structure, characterized by comprising: The device includes an air spring piston, a shock absorber reservoir, and an anti-rotation ring. The anti-rotation ring is disposed between the inner side of the piston and the outer side of the reservoir. One end of the piston has a tapered opening. The anti-rotation ring comprises: The first section is cylindrical in shape, and a protrusion is provided in the radial direction of the first section. A plurality of the protrusions are arranged along the circumferential direction of the first section, and the first section is interference-fitted with the inner wall of the piston. The second section is a cone shape adapted to the inner wall of the cone-shaped opening of the piston, and the small end of the second section is connected to the first section; The third section is connected to the large end of the second section and extends radially outward along the anti-rotation ring, and the inner side of the third section has a groove for fitting and engaging with the mounting plate of the shock absorber.

2. The spring stop structure according to claim 1, characterized by The anti-rotation ring has multiple slots in its radial direction that penetrate the inner and outer walls of the anti-rotation ring itself. The multiple slots are arranged along the circumferential direction of the anti-rotation ring, and the slots extend from the first section to the third section.

3. The spring stopper structure according to claim 2, characterized by Along the circumferential direction of the anti-rotation ring, a predetermined number of protrusions are evenly spaced between any two adjacent slots.

4. The spring stopper structure according to claim 1, characterized by The third section is provided with a limiting part for limiting the mounting plate in the radial direction. The limiting part is a point protrusion or a pin.

5. The spring stopper structure according to claim 1, characterized by The piston has a first plane at one end with a tapered opening, and the third section has a second plane at one end near the second section. The first plane and the second plane are arranged parallel to each other and spaced apart.

6. The air spring anti-rotation structure according to claim 1, characterized in that, The protrusion is a rib extending along the axial direction of the first section. There are 6 to 18 ribs, and the interference fit between the rib and the inner wall of the piston is 0.3-0.8 mm.

7. The air spring anti-rotation structure according to claim 1, characterized in that, An annular groove is provided between the first section and the second section.

8. The air spring anti-rotation structure according to claim 1, characterized in that, The anti-rotation ring is made of a rigid material.

9. The air spring anti-rotation structure according to claim 1, characterized in that, The outer wall of the anti-rotation ring is in direct contact with the inner wall of the piston, and the inner wall of the anti-rotation ring is in direct contact with the outer wall of the oil reservoir.

10. The air spring anti-rotation structure according to claim 1, characterized in that, The anti-rotation ring is configured with an interference fit with the oil reservoir.

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