A method for improving the ultimate load stiffness of marine vibration isolators

Abstract

The present invention discloses a method for improving the ultimate load stiffness of a marine vibration isolator. The vibration isolator includes an upper mounting seat, a lower mounting seat and a rubber body. The upper mounting seat includes an upper seat plate and a downwardly protruding conical circular boss arranged on the bottom surface of the upper seat plate. The lower mounting seat includes a lower seat plate and a conical sleeve arranged on the top surface of the lower seat plate. The conical circular boss is inserted into the conical sleeve and is vulcanized and bonded between the outer conical surface of the conical circular boss and the inner conical surface of the conical sleeve by using the rubber body. The bottom of the rubber body is set to be concave. The groove formed at the bottom of the concave rubber body is the bottom space A of the rubber body; a space B is formed between the top surface of the rubber body and the bottom surface of the upper seat plate. The method is to reduce the spatial volume of the bottom space A of the bottom of the rubber body so that when subjected to the ultimate load, the bottom of the rubber body expands, deforms and contacts in the reduced bottom space A, thereby improving the lateral stiffness and vertical stiffness of the vibration isolator, thereby improving the ultimate load stiffness of the vibration isolator.

Description

Technical Field

[0001] The invention relates to a method for improving the stiffness of a vibration isolator, in particular to a method for improving the ultimate load stiffness of a marine vibration isolator, and belongs to the technical field of vibration reduction. Background Art

[0002] Marine vibration isolators are vibration isolation devices designed specifically for ships. They aim to reduce and eliminate the vibration forces and vibrations transmitted to the hull by marine engines, mechanical equipment or other external factors, thereby improving the stability of the hull, the comfort of the crew, and protecting the equipment and cargo on board.

[0003] Marine vibration isolators are springs that combine metal and rubber to reduce vibration and resist extreme loads. Both the metal and rubber have a conical structure, and are characterized by large load capacity, large displacement, low frequency, and high damping. The isolator is installed between the equipment and the hull to provide support and reduce vibration. The conical metal parts and rubber are vulcanized into a single unit using adhesive at a certain temperature and pressure. The vulcanized rubber acts as a vibration reducer, while the metal parts serve as a support and mounting interface. Because the equipment requires vibration reduction, the natural frequency is required to be small, and thus the dynamic stiffness requirements are small. However, the extreme load is large, so a larger extreme load stiffness needs to be designed. Generally, the extreme load stiffness / dynamic stiffness is required to be ≥1 to achieve the extreme load resistance function. The quality of its design will directly affect the reliability of the equipment on board.

[0004] Existing vibration isolators, such as Figure 1 As shown, it includes an upper mounting seat 1, a lower mounting seat 2 and a rubber body 3, the upper mounting seat 1 includes an upper seat plate 111 and a downwardly protruding conical circular boss 112 arranged on the bottom surface of the upper seat plate 111, the lower mounting seat 2 includes a lower seat plate 211 and a conical sleeve 212 arranged on the top surface of the lower seat plate 211, the conical circular boss 112 is inserted into the conical sleeve 212 and is vulcanized and bonded between the outer conical surface of the conical circular boss 112 and the inner conical surface of the conical sleeve 212 by the rubber body 3, thereby connecting the upper mounting seat 1 and the lower mounting seat 2 through the rubber body 3, the rubber body 3 is in the shape of a conical sleeve, the top surface of the upper seat plate 111 is connected to the equipment 4 to be protected, the bottom surface of the lower seat plate 211 is connected to the frame 5 below the hull, and the equipment is vibration-isolated and protected by the vibration isolator.

[0005] The problem with existing vibration isolators is that the nonlinearity of stiffness is weak, and the stiffness under large deformation and small deformation is not much different, that is, the ultimate load stiffness / dynamic stiffness is generally less than 0.8, which does not meet the requirement of ultimate load stiffness / dynamic stiffness ≥ 1. Therefore, if the ratio between ultimate load stiffness and dynamic stiffness needs to be increased, the ultimate load stiffness must be increased.

[0006] The Chinese utility model patent with authorization announcement number CN2752538Y and authorization announcement date January 18, 2006 discloses a low-frequency, high-load rubber vibration isolator, including an upper iron piece, a lower iron piece and a rubber body, the rubber body is clamped in the middle by the upper iron piece and the lower iron piece, the upper iron piece is in a "T"-shaped structure, including a top plate and a middle baffle connected under the top plate; the lower iron piece is in a "U"-shaped structure, including a bottom plate and two side baffles connected on both sides of the bottom plate; the upper part of the rubber body is provided with a structure adapted to the upper iron piece and connected to the bottom of the upper iron piece, and the upper two side surfaces of the rubber body are concave arc-shaped; the lower part of the rubber body is provided with a structure adapted to the lower iron piece and embedded in the "U"-shaped body of the lower iron piece, and an arc groove is provided in the middle of the lower part of the rubber body that runs through along the length direction.

[0007] The vibration isolator in the above patent document has the problem of failing to achieve ultimate load stiffness / dynamic stiffness ≥ 1.

[0008] Therefore, how to design a method to improve the ultimate load stiffness of marine vibration isolators so that the ultimate load stiffness of the vibration isolators can be improved, so that the ratio of ultimate load stiffness to dynamic stiffness reaches the requirement of ≥1, the function of the vibration isolators to resist ultimate loads can be improved, and the reliability of the equipment on board can be better guaranteed. This is a technical problem that needs to be solved urgently. Summary of the Invention

[0009] The technical problem to be solved by the present invention is to address the defects existing in the prior art and provide a method for improving the ultimate load stiffness of a ship vibration isolator. The method can improve the ultimate load stiffness of the vibration isolator, so that the ratio of the ultimate load stiffness to the dynamic stiffness reaches the requirement of ≥1, thereby improving the function of the vibration isolator in resisting the ultimate load and better ensuring the reliability of the equipment on board.

[0010] To solve the above technical problems, the technical solution adopted by the present invention is: a method for improving the ultimate load stiffness of a marine vibration isolator, the vibration isolator comprising an upper mounting seat, a lower mounting seat and a rubber body, the upper mounting seat comprising an upper seat plate and a downwardly protruding conical circular boss arranged on the bottom surface of the upper seat plate, the lower mounting seat comprising a lower seat plate and a conical sleeve arranged on the top surface of the lower seat plate, the conical circular boss being inserted into the conical sleeve and being vulcanized and bonded between the outer conical surface of the conical circular boss and the inner conical surface of the conical sleeve by the rubber body, the bottom of the rubber body being configured to be concave, the groove formed by the concave bottom of the rubber body being the bottom space A of the rubber body; a space B being formed between the top surface of the rubber body and the bottom surface of the upper seat plate, the method being by reducing the spatial volume of the bottom space A of the bottom of the rubber body so that when subjected to an ultimate load, the bottom of the rubber body expands, deforms and contacts in the reduced bottom space A, thereby improving the lateral stiffness and vertical stiffness of the vibration isolator, and further improving the ultimate load stiffness of the vibration isolator.

[0011] Preferably, the spatial volume of the bottom space A at the bottom of the rubber body is reduced by providing an extension portion on the bottom end surface of the conical circular boss, so that the extension portion extends into the bottom space A, thereby reducing the spatial volume of the bottom space A.

[0012] Preferably, the inner surface of the bottom of the concave rubber body is designed to be a three-segment oblique line structure, including an oblique line segment 1 surface, an oblique line segment 2 surface, and an oblique line segment 3 surface, wherein the oblique line segment 1 surface, the oblique line segment 2 surface, and the oblique line segment 3 surface are sequentially connected end to end;

[0013] When subjected to the ultimate load, the first oblique line segment profile is in contact with the outer peripheral surface of the extension portion to provide lateral stiffness, and the second oblique line segment profile is in contact with the bottom end surface of the extension portion to provide vertical stiffness.

[0014] Preferably, the lateral stiffness and vertical stiffness of the vibration isolator are adjusted by adjusting the lengths of the first oblique line segment profile and the second oblique line segment profile.

[0015] Preferably, the lengths of the oblique line segment 1 profile and the oblique line segment 2 profile are increased to increase the lateral stiffness and vertical stiffness of the vibration isolator; and the lengths of the oblique line segment 1 profile and the oblique line segment 2 profile are shortened to reduce the lateral stiffness and vertical stiffness of the vibration isolator.

[0016] Preferably, an acute angle a is formed between the three-shaped surface of the oblique line segment and the horizontal line; when the acute angle a is reduced, the lateral stiffness and vertical stiffness of the vibration isolator are improved; when the acute angle a is increased, the lateral stiffness and vertical stiffness of the vibration isolator are reduced.

[0017] Preferably, the method further includes reducing the spatial volume of the space B at the top of the rubber body, so that when subjected to an extreme load, the top of the rubber body expands, deforms and contacts within the reduced space B, thereby increasing the lateral stiffness and vertical stiffness of the isolator, and further increasing the extreme load stiffness of the isolator.

[0018] Preferably, the volume of the space B at the top of the rubber body is reduced by providing a flange portion on the bottom surface of the upper seat plate so that the flange portion extends into the space B, thereby reducing the volume of the space B.

[0019] Preferably, the profile of the top of the rubber body is designed to be a two-segment oblique line structure, including an oblique line segment four profile and an oblique line segment five profile, wherein the oblique line segment four profile and the oblique line segment five profile are sequentially connected end to end;

[0020] When subjected to the action of the ultimate load, the four profiles of the oblique line segment are in contact with the bottom end surface of the flange portion to provide vertical rigidity.

[0021] Preferably, the slopes of the oblique line segment four profile and the oblique line segment five profile are set to be different, so that the oblique line segment four profile is inclined toward the bottom end surface close to the flange portion, while the oblique line segment five profile is inclined toward the bottom end surface away from the flange portion.

[0022] The beneficial effects of the present invention are that when the displacement during vibration reduction is small, generally less than 5 mm, and the displacement during ultimate load resistance is large, generally greater than 25 mm, the vibration isolator of the present invention can achieve an ultimate load stiffness / dynamic stiffness ratio of ≥ 1, achieving the effect of lower stiffness at small displacements and higher stiffness at large displacements. By reducing the bottom space A at the bottom of the rubber body and the space B at the top of the rubber body, the bottom and top of the rubber body can expand and deform more quickly within the reduced spaces, thereby improving the lateral and vertical stiffness of the vibration isolator, that is, improving the ultimate load stiffness of the vibration isolator, so that the ratio of ultimate load stiffness to dynamic stiffness reaches the requirement of ≥ 1, improving the vibration isolator's ability to resist ultimate loads and better ensuring the reliability of onboard equipment. An extension is provided on the bottom end surface of the tapered circular boss, which extends into the bottom space A, thereby reducing the spatial volume of the bottom space A. A flange is provided on the bottom surface of the upper seat plate, so that the flange extends into the space B, thereby reducing the spatial volume of the space B. The inner surface of the concave rubber body's bottom is designed as a three-segment diagonal structure. Adjusting this structure allows for further adjustment of the lateral and vertical stiffnesses, allowing for flexible adjustment of these values ​​based on actual operating conditions, thereby improving practicality. The top surface of the rubber body is designed as a two-segment diagonal structure. This design not only increases the isolator's vertical stiffness but also prevents the top of the rubber body from being cut by adjacent components when it expands and deforms, further extending the isolator's service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a schematic diagram of the axial cross-sectional structure of a marine vibration isolator in the prior art;

[0024] Figure 2 Schematic diagram of the axial cross-sectional structure of a marine vibration isolator in an embodiment of the present invention;

[0025] Figure 3 for Figure 2 Schematic diagram of the enlarged structure of the middle C part;

[0026] Figure 4 for Figure 2 The enlarged structural diagram of the middle E part;

[0027] In the figure: 1. Upper mounting seat, 111. Upper seat plate, 1111. Flange portion, 11111. Bottom end surface of flange portion, 112. Conical circular boss, 1121. Extension portion, 11211. Outer peripheral surface of extension portion, 11212. Bottom end surface of extension portion, 2. Lower mounting seat, 211. Lower seat plate, 212. Conical sleeve, 2121. Inner recess, 3. Rubber body, 311. Oblique line segment 1 profile, 312. Oblique line segment 2 profile, 313. Oblique line segment 3 profile, 314. Oblique line segment 4 profile, 315. Oblique line segment 5 profile, 4. Equipment, 5. Structure below hull. DETAILED DESCRIPTION

[0028] The technical solution of the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0029] The ultimate load stiffness mainly includes the lateral stiffness and vertical stiffness provided by the vibration isolator under the action of the ultimate load (i.e. impact load). Figure 1 As shown, the height direction of the vibration isolator is set as the vertical direction (Z direction), and the horizontal direction perpendicular to the vertical direction (Z direction) is set as the lateral direction (X direction). In conventional vibration isolators, when subjected to extreme loads, the rubber body 3 in the vibration isolator deforms primarily in two locations: one at the bottom of the rubber body. Specifically, the bottom of the rubber body 3 is concave, and the groove formed in the concave bottom of the rubber body 3 is the bottom space A of the rubber body 3. The other is located at the top of the rubber body, namely, the space B between the top surface of the rubber body 3 and the bottom surface of the upper seat plate 111. When subjected to extreme loads, the rubber body 3 in the vibration isolator undergoes rapid expansion and deformation within the bottom space A and space B, thereby causing the vibration isolator to deform and provide lateral and vertical stiffness. Example 1

[0030] The applicant has found through research that if the ultimate load stiffness needs to be increased, it is necessary to find a way to increase the lateral stiffness and vertical stiffness of the vibration isolator under the ultimate load.

[0031] like Figure 2As shown, the vibration isolator in this embodiment also includes an upper mounting seat 1, a lower mounting seat 2 and a rubber body 3, the upper mounting seat 1 includes an upper seat plate 111 and a downwardly protruding conical circular boss 112 arranged on the bottom surface of the upper seat plate 111, the lower mounting seat 2 includes a lower seat plate 211 and a conical sleeve 212 arranged on the top surface of the lower seat plate 211, the conical circular boss 112 is inserted into the conical sleeve 212 and is vulcanized and bonded between the outer conical surface of the conical circular boss 112 and the inner conical surface of the conical sleeve 212 by the rubber body 3, thereby connecting the upper mounting seat 1 and the lower mounting seat 2 through the rubber body 3, the rubber body 3 is in the shape of a conical sleeve, and the bottom of the rubber body 3 is set to be concave, and the groove formed at the bottom of the concave rubber body 3 is the bottom space A of the rubber body 3; a space B is formed between the top surface of the rubber body 3 and the bottom surface of the upper seat plate 111. The top surface of the upper seat plate 111 is connected to the equipment to be protected (not shown in the figure), and the bottom surface of the lower seat plate 211 is connected to the frame below the hull (not shown in the figure). The equipment is protected by vibration isolation through the vibration isolator.

[0032] The applicant has improved the vibration isolator as follows:

[0033] like Figure 3 As shown, the applicant has provided an extension 1121 on the bottom end surface of the tapered circular boss 112, extending into the bottom space A. This reduces the volume of the bottom space A, allowing the bottom of the rubber body 3 to expand and deform within the bottom space A (as indicated by the hollow arrow in the figure), contacting the extension 1121 and providing lateral and vertical stiffness. This confines the expansion and deformation of the rubber body bottom to a smaller space, allowing it to contact the extension more quickly under the action of the ultimate load, thereby improving the lateral and vertical stiffness of the isolator, and thus, the ultimate load stiffness of the isolator. Furthermore, the bottom of the bottom space A is connected to the lower hull frame, ensuring that the volume of the reduced bottom space A is constant. However, due to the incompressibility of the rubber, its stiffness increases rapidly under large displacements, thereby achieving a ratio of ultimate load stiffness to dynamic stiffness of ≥1. This improves the isolator's ability to withstand ultimate loads and better ensures the reliability of the ship's equipment. In this embodiment, the extension portion 1121 is configured to be cylindrical.

[0034] like Figure 4As shown, the applicant has made further improvements by providing a flange portion 1111 on the bottom surface of the upper seat plate 111. This flange portion 1111 extends into the space B, thereby reducing the volume of space B. Under the action of a critical load, the top of the rubber body 3 expands and deforms within the bottom space B (as indicated by the hollow arrow in the figure), contacting the flange portion 1111 and providing vertical stiffness. This confines the expansion and deformation of the top of the rubber body to a smaller space, allowing it to contact the flange portion 1111 more quickly under the action of a critical load, thereby improving the vertical stiffness of the vibration isolator and further enhancing the critical load stiffness of the vibration isolator.

[0035] like Figure 3 As shown, the inner surface of the bottom of the concave rubber body is designed as a three-segment oblique line structure, including oblique line segment 1 surface 311, oblique line segment 2 surface 312, and oblique line segment 3 surface 313. These oblique line segment 1 surface 311, oblique line segment 2 surface 312, and oblique line segment 3 surface 313 are connected end-to-end. When subjected to a limit load, oblique line segment 1 surface 311 contacts the outer peripheral surface 11211 of the extension, supporting the upper mounting seat in the transverse (X) direction to provide lateral rigidity. Oblique line segment 2 surface 312 contacts the bottom end surface 11212 of the extension, supporting the upper mounting seat in the vertical (Z) direction to provide vertical rigidity. Here, when the lateral and vertical stiffnesses need to be adjusted, this can be achieved by adjusting the lengths of the first oblique segment profile 311 and the second oblique segment profile 312. For example, when a greater lateral and vertical stiffness is required, the lengths of the first oblique segment profile 311 and the second oblique segment profile 312 can be appropriately increased. Conversely, when a smaller lateral and vertical stiffness is required, the lengths of the first oblique segment profile 311 and the second oblique segment profile 312 can be appropriately decreased. In this way, the lateral and vertical stiffnesses can be flexibly adjusted according to actual working conditions, thereby improving the practicality of this embodiment. In addition, the lateral and vertical stiffness of the vibration isolator can also be adjusted by adjusting the oblique segment three-shaped surface 313. That is, an acute angle a is formed between the oblique segment three-shaped surface 313 and the horizontal line. When the acute angle a is reduced, the total volume of the rubber body 3 is increased, thereby further improving the lateral and vertical stiffness of the vibration isolator; conversely, when the acute angle a is increased, the total volume of the rubber body 3 is reduced, thereby further reducing the lateral and vertical stiffness of the vibration isolator.

[0036] An inner concave portion 2121 is further provided at the bottom end of the cone sleeve 212 and on the inner circumferential surface. By providing the inner concave portion 2121 here, stress concentration on the rubber body is avoided, thereby increasing the service life of the vibration isolator.

[0037] like Figure 4As shown, the top surface of the rubber body is designed as a two-segment oblique line structure, including oblique line segment 4 surface 314 and oblique line segment 5 surface 315. These oblique line segment 4 surface 314 and oblique line segment 5 surface 315 are connected end to end. When subjected to a limit load, oblique line segment 4 surface 314 contacts the bottom end surface 11111 of the flange, supporting the upper mounting seat vertically (in the Z direction) to provide vertical stiffness.

[0038] The above-mentioned oblique line segments are transitioned with rounded corners. As the vertical load increases, they slowly come into contact with the upper mounting seat. This surface design can not only reduce rubber stress, avoid rubber wrinkles, and greatly improve product reliability, but also achieve variable stiffness under large displacement. By adjusting the slope and length of the straight line segment, the size and position of the stiffness change can be adjusted. Increasing the number of straight line segments can achieve multiple stiffness changes.

[0039] Here, since the corner D of the flange portion 1111 is located at the profile of the top of the rubber body, in order to avoid contact and cutting of the corner of the flange portion 1111 when the top of the rubber body expands and deforms, the slopes of the oblique segment fourth profile 314 and the oblique segment fifth profile 315 are set to be different, so that the oblique segment fourth profile 314 is inclined toward the side close to the bottom end surface 11111 of the flange portion, and the oblique segment fifth profile 315 is inclined toward the side away from the bottom end surface 11111 of the flange portion, thereby avoiding contact and cutting of the oblique segment fifth profile 315 by the corner of the flange portion 1111 when expanding and deforming, thereby further improving the service life of the vibration isolator.

[0040] In summary, when the displacement during vibration reduction is small, generally less than 5mm, and the displacement for resisting the ultimate load is large, generally greater than 25mm, the vibration isolator of the present invention can achieve an ultimate load stiffness / dynamic stiffness ≥ 1, achieving the effect of lower stiffness under small displacement and higher stiffness under large displacement. By reducing the bottom space A at the bottom of the rubber body and the space B at the top of the rubber body, the bottom and top of the rubber body can expand and deform more quickly in the reduced space, thereby improving the lateral stiffness and vertical stiffness of the vibration isolator, that is, improving the ultimate load stiffness of the vibration isolator, so that the ratio of the ultimate load stiffness to the dynamic stiffness reaches the requirement of ≥ 1, improving the vibration isolator's ability to resist ultimate loads, and better ensuring the reliability of the onboard equipment. An extension is provided on the bottom end surface of the conical circular boss, which extends into the bottom space A by extension, thereby reducing the spatial volume of the bottom space A. A flange is provided on the bottom surface of the upper seat plate, so that the flange extends into the space B, thereby reducing the spatial volume of the space B. The inner surface of the concave rubber body's bottom is designed as a three-segment diagonal structure. Adjusting this structure allows for further adjustment of the lateral and vertical stiffnesses, allowing for flexible adjustment of these values ​​based on actual operating conditions, thereby improving practicality. The top surface of the rubber body is designed as a two-segment diagonal structure. This design not only increases the isolator's vertical stiffness but also prevents the top of the rubber body from being cut by adjacent components when it expands and deforms, further extending the isolator's service life.

[0041] The term "plurality" in this embodiment refers to "two or more." The above embodiments are intended to illustrate the present invention only and are not intended to limit the present invention. Persons skilled in the art may make various modifications or alterations without departing from the spirit and scope of the present invention. Therefore, all equivalent technical solutions are intended to fall within the scope of protection of the present invention, which is defined by the claims.

Claims

1. A method for improving the ultimate load stiffness of a marine vibration isolator, the vibration isolator comprising an upper mounting seat, a lower mounting seat, and a rubber body, the upper mounting seat comprising an upper seat plate and a downwardly protruding conical circular boss disposed on the bottom surface of the upper seat plate, the lower mounting seat comprising a lower seat plate and a tapered sleeve disposed on the top surface of the lower seat plate, the tapered circular boss being inserted into the tapered sleeve and being vulcanized and bonded to the rubber body between the outer conical surface of the conical circular boss and the inner conical surface of the tapered sleeve, the bottom of the rubber body being concave, the groove formed by the concave bottom of the rubber body being the bottom space A of the rubber body; and a space B being formed between the top surface of the rubber body and the bottom surface of the upper seat plate, characterized in that: The method is to reduce the volume of the bottom space A at the bottom of the rubber body so that when subjected to an ultimate load, the bottom of the rubber body expands, deforms, and contacts within the reduced bottom space A, thereby increasing the lateral stiffness and vertical stiffness of the vibration isolator, and further increasing the ultimate load stiffness of the vibration isolator; The volume of the bottom space A at the bottom of the rubber body is reduced by providing an extension portion on the bottom end surface of the conical circular boss so that the extension portion extends into the bottom space A, thereby reducing the volume of the bottom space A; The inner surface of the bottom of the concave rubber body is designed to be a three-segment oblique line structure, including an oblique line segment 1 surface, an oblique line segment 2 surface, and an oblique line segment 3 surface arranged from top to bottom, wherein the oblique line segment 1 surface, the oblique line segment 2 surface, and the oblique line segment 3 surface are connected end to end in sequence; When subjected to the ultimate load, the first oblique line segment profile is in contact with the outer peripheral surface of the extension portion to provide lateral rigidity, and the second oblique line segment profile is in contact with the bottom end surface of the extension portion to provide vertical rigidity; The lengths of the first and second oblique line segments are increased to increase the lateral and vertical stiffness of the vibration isolator; the lengths of the first and second oblique line segments are shortened to reduce the lateral and vertical stiffness of the vibration isolator; An acute angle a is formed between the three-shaped surface of the oblique line segment and the horizontal line; when the acute angle a is reduced, the lateral stiffness and vertical stiffness of the vibration isolator are improved; when the acute angle a is increased, the lateral stiffness and vertical stiffness of the vibration isolator are reduced.

2. The method according to claim 1, wherein: The method further includes reducing the volume of the space B at the top of the rubber body, so that when subjected to an ultimate load, the top of the rubber body expands, deforms, and contacts within the reduced space B, thereby increasing the lateral stiffness and vertical stiffness of the vibration isolator, and further increasing the ultimate load stiffness of the vibration isolator.

3. The method according to claim 2, wherein: The volume of the space B at the top of the rubber body is reduced by providing a flange portion on the bottom surface of the upper seat plate so that the flange portion extends into the space B, thereby reducing the volume of the space B.

4. The method according to claim 3, wherein: The top surface of the rubber body is designed to be a two-segment oblique line structure, including oblique line segment four and oblique line segment five, wherein the oblique line segment four and oblique line segment five are connected end to end in sequence; When subjected to the action of the ultimate load, the four profiles of the oblique line segment are in contact with the bottom end surface of the flange portion to provide vertical rigidity.

5. The method according to claim 4, characterized in that: The slopes of the oblique line segment four profile and the oblique line segment five profile are set to be different, so that the oblique line segment four profile is inclined toward the bottom end surface close to the flange part, while the oblique line segment five profile is inclined toward the bottom end surface away from the flange part.

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