Rigidity-adjustable isolation type anti-vibration pad structure

Abstract

The utility model relates to the technical field of urban rail transit, and discloses a rigidity-adjustable isolation type anti-vibration pad structure which comprises a first plate body, a second plate body and a plurality of vibration reduction units arranged between the first plate body and the second plate body in an array mode. The vibration reduction unit comprises a first boss and a second boss, the first boss and the second boss are integrally formed, the bottom face of the first boss is fixedly connected with the first plate body, and the bottom face of the second boss is fixedly connected with the second plate body; the height sum between the first boss and the second boss is not changed, and the height ratio can be adjusted, so that the surface supporting rigidity of the vibration reduction unit is adjusted; according to the utility model, the height ratio of the first platform body to the second platform body is adjusted, so that the rigidity of the vibration reduction units at different positions of the vibration reduction pad structure can be adaptively adjusted, the rigidity of the vibration reduction units can be adjusted in sections such as track bending or transition, steel rail abrasion can be avoided, the track transition smoothness can be improved, the over-vibration reduction phenomenon can be avoided, and the service life of the vibration reduction pad structure can be prolonged. Rail corrugation is delayed, and wheel track noise is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of urban rail transit, in particular to an isolated vibration-damping pad structure with adjustable stiffness. Background Art

[0002] With the rapid development of urban rail transit construction in recent years, the speed of rail transit has been continuously improved, and the noise impact on buildings near subway lines has become more and more prominent. In order to reduce the noise impact caused by the operation of subway trains on surrounding buildings, according to the requirements of environmental impact assessment, vibration-damping ballasts are set up in sensitive sections of buildings. Among them, the isolated vibration-damping pad floating plate ballast is a technical solution with better effect among the vibration-damping technologies currently used. The isolated vibration-damping pad track is a mass-spring vibration isolation system. Compared with the steel spring floating plate integral ballast, it has the technical characteristics of low engineering cost, convenient construction and good noise reduction effect. Its main principle is to float the concrete ballast plate with a certain mass and stiffness on the vibration-damping pad, and isolate the ballast plate from the surrounding structures through the vibration-damping pad to form a mass-spring vibration isolation system. The force acting on the rail is transmitted to the ballast plate on the floating vibration-damping pad. The ballast plate can provide sufficient inertial mass to offset the dynamic load generated by the vehicle. Only the static load and a small amount of residual dynamic load will be transmitted to the foundation cushion through elastic support. When the roadbed plate is subjected to force, the force is evenly distributed on the vibration damping pad under the action of inertia, and then the vibration damping pad is used for buffering and absorbing energy to achieve the purpose of vibration isolation and vibration reduction.

[0003] However, the isolated vibration-damping pad floating plate used in the existing technology still has many problems. On the one hand, the superelevation is set by raising the outer rail in the curved section of urban rail transit. Since the actual superelevation is over-superelevation or under-superelevation, the vertical force of the inner and outer rails will be unbalanced, which will lead to increased rail wear and increase the frequency of track replacement. On the other hand, for different vibration reduction requirements, the isolated vibration-damping pad floating plate adopts a uniform stiffness, and the vibration reduction effect is relatively large in the section with lower vibration reduction requirements. The vibration reduction transition treatment section is prone to aggravate the development of corrugation, increase the noise inside the car, and affect the ride comfort. Utility Model Content

[0004] The technical problem to be solved by the utility model is: how to adjust the stiffness of the vibration damping pad. In order to solve the above technical problem, the utility model provides an isolated vibration damping pad structure with adjustable stiffness, comprising a first plate body and a second plate body arranged in parallel and a plurality of vibration damping units arranged in an array between the first plate body and the second plate body, wherein the vibration damping units are perpendicular to the first plate body;

[0005] The vibration reduction unit comprises a first boss and a second boss, the first boss and the second boss are integrally formed, both the first boss and the second boss are platform structures, the bottom surface of the first boss is fixedly connected to the first plate body, and the bottom surface of the second boss is fixedly connected to the second plate body;

[0006] The height sum between the first boss and the second boss remains unchanged, but the height ratio can be adjusted, thereby adjusting the surface support stiffness of the vibration reduction unit.

[0007] Preferably, the elastic modulus of the first boss is defined as Ea, and the height is defined as Ha; the elastic modulus of the second boss is defined as Eb, and the height is defined as Hb; the calculation formula for the surface support stiffness Ka of the first boss is:

[0008]

[0009] The calculation formula of the surface support stiffness Kb of the second boss is:

[0010]

[0011] The surface support stiffness K of a single damping unit 减振单元 The calculation formula is:

[0012]

[0013] The surface support stiffness K of the isolated vibration damping pad structure 减振垫结构 The calculation formula is:

[0014] K 减振垫结构 =∑K 减振单元 .

[0015] Preferably, the height ratio of the first boss to the second boss in different vibration reduction units is adjusted along the track width direction, so that when the track is in a curved section, the stiffness of the track load-increasing area is greater than the stiffness of the non-load-increasing area.

[0016] Preferably, the height ratio between the first boss and the second boss in different vibration reduction units is gradually adjusted along the length direction of the track, so that the stiffness change of the track in the transition section is smoother.

[0017] Preferably, the adjustment range of the first boss height Ha and the second boss height Hb are both 10 mm to 20 mm.

[0018] Preferably, when the first boss and the second boss are prisms, the edge length of the top surface of the first boss and the second boss ranges from 10mm to 30mm, and the edge length of the bottom surface ranges from 40mm to 60mm; when the first boss and the second boss are frustum, the diameter of the top surface of the first boss and the second boss ranges from 10mm to 30mm, and the diameter of the bottom surface ranges from 40mm to 60mm.

[0019] Preferably, the area and shape of the top surface of the first boss are the same as the area and shape of the top surface of the second boss, and the area and shape of the bottom surface of the first boss are the same as the area and shape of the bottom surface of the second boss.

[0020] Preferably, the interval between adjacent vibration-damping units is no greater than 1.5 times the bottom edge length or bottom diameter of the first boss.

[0021] Preferably, the first boss and the second boss are both made of rubber material; the first boss and the second boss have different formulations, so that the elastic modulus of the first boss is different from the elastic modulus of the second boss.

[0022] Preferably, the first plate body and the first boss and the second plate body and the second boss are integrally formed; the surface of the first plate body away from the first boss is provided with an adhesive layer, and the adhesive layer is used to glue and fix the first plate body to the track body; the second plate body is a high-strength fiber layer, and the second plate body is used to prevent the steel bars or stone particles in the track base from traditionally damaging the vibration damping unit.

[0023] Compared with the prior art, the isolated vibration damping pad structure with adjustable stiffness provided in the embodiment of the utility model has the following beneficial effects:

[0024] In the present invention, the first plate body and the second plate body of the vibration-damping pad structure are respectively abutted against the track plate bed and the base of the track, and a plurality of vibration-damping units are distributed in the internal array of the vibration-damping pad structure, and the vibration-damping unit comprises two integrally formed platforms, wherein the height ratio between the first platform and the second platform can be adjusted according to actual needs, thereby adjusting the stiffness of the first platform and the second platform, and further enabling the stiffness of the vibration-damping units at different positions of the vibration-damping pad structure to be adaptively adjusted. By adjusting the stiffness of the vibration-damping units at specific positions in curved sections or transition sections of the track, it is possible to better avoid rail wear and improve the smoothness of track transition. In places where the demand for vibration reduction is small, targeted adjustment of the stiffness of the vibration-damping units can also avoid over-vibration reduction, thereby delaying rail corrugation and reducing wheel-rail noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 It is a schematic diagram of the cross-sectional structure of the vibration-damping pad structure of the utility model;

[0026] Figure 2 It is a schematic diagram of the cross-sectional structure of the vibration damping pad structure stiffness adjustment of the utility model.

[0027] In the figure: 1, first plate body; 2, second plate body; 3, vibration reduction unit; 31, first boss; 32, second boss. DETAILED DESCRIPTION

[0028] The following is a further detailed description of the specific implementation of the present invention in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention but are not intended to limit the scope of the present invention. Figure 1 and Figure 2 All of them are cross-sectional structures, but it should be known that in the vibration-damping pad structure, there are multiple vibration-damping unit plane arrays, and Figure 2 The schematic diagram of the stiffness adjustment change of the vibration damping pad structure in the track can represent both the adjustment along the track width direction and the adjustment along the track length direction, and the change in the height ratio between the first boss and the second boss, Figure 2 Although only the solution in which the height of the first boss gradually decreases and the height of the second boss gradually increases is shown, the technical solution in which the height of the first boss gradually increases and the height of the second boss gradually decreases should also be within the protection scope of the present utility model.

[0029] like Figure 1 and Figure 2 As shown, a preferred embodiment of the utility model provides an isolated vibration-damping pad structure with adjustable stiffness, which includes a first plate body 1 and a second plate body 2 arranged in parallel and a plurality of vibration-damping units 3 arranged in an array between the first plate body 1 and the second plate body 2, wherein the vibration-damping unit 3 is perpendicular to the first plate body 1; the vibration-damping unit 3 includes a first boss 31 and a second boss 32, the first boss 31 and the second boss 32 are integrally formed, and both the first boss 31 and the second boss 32 are platform structures in which the top surface area is smaller than the bottom surface area, the bottom surface of the first boss 31 is fixedly connected to the first plate body 1, and the bottom surface of the second boss 32 is fixedly connected to the second plate body 2; wherein the height sum between the first boss 31 and the second boss 32 remains unchanged, and the size of the height ratio can be adjusted, thereby adjusting the surface support stiffness of the vibration-damping unit 3.

[0030] Specifically, in actual use, the total height of the vibration damping unit 3 is unchanged, while the height between the first boss 31 and the second boss 32 therein is variable. When the height of the first boss 31 increases, the height of the second boss 32 decreases. When the elastic modulus of the first boss 31 and the second boss 32 are different, the stiffness of the first boss 31 and the second boss 32 can be adjusted by adjusting the height of the first boss 31 and the second boss 32, thereby adjusting the stiffness of the entire vibration damping unit 3. In this way, the stiffness of different positions of the vibration damping pad structure can be adjusted in a targeted manner, so that the vibration damping pad can maintain the most appropriate stiffness when facing more complex and changeable usage scenarios.

[0031] In some embodiments, the elastic modulus of the first boss 31 is defined as Ea, the height is defined as Ha, the elastic modulus of the second boss 32 is defined as Eb, the height is defined as Hb, and the calculation formula of the surface support stiffness Ka of the first boss 31 is:

[0032]

[0033] The calculation formula of the surface support stiffness Kb of the second boss 32 is:

[0034]

[0035] The surface support stiffness K of a single damping unit 3 is 减振单元 The calculation formula is:

[0036]

[0037] The surface support stiffness K of the isolated vibration damping pad structure 减振垫结构 The calculation formula is:

[0038] K 减振垫结构 =∑K 减振单元 .

[0039] Specifically, in this embodiment, the surface support stiffness of a single boss is related to its own height and elastic modulus, inversely proportional to the height and proportional to the elastic modulus. The higher the height, the smaller the surface support stiffness, and the larger the elastic modulus, the greater the surface support stiffness. The single damping unit 3 is calculated according to the spring series relationship and by changing the surface support stiffness of the two bosses inside the damping unit 3. The surface support stiffness of the entire isolated damping pad structure is calculated by adding up the surface support stiffness of all damping units 3 according to the spring parallel relationship. When adjustment is actually needed, the height of the first boss 31 or the second boss 32 is selectively increased according to the required stiffness and the installation direction of the damping pad structure. In fact, the upper and lower positions or left and right positions of the second boss 32 and the first boss 31 do not need to be clearly defined in the utility model. The installation of the isolated damping pad can be arranged according to the stiffness requirements of the actual construction on site, and the track will also be divided into left bending or right bending, etc.

[0040] In some embodiments, the height ratio of the first boss 31 to the second boss 32 in different vibration reduction units 3 is adjusted along the track width direction so that when the track is in a curved section, the stiffness of the track load-increasing area is greater than the stiffness of the non-load-increasing area.

[0041] Specifically, the superelevation of curved sections of urban rail transit is generally set by raising the outer rail, but in actual settings, there is often an over-superelevation or under-superelevation phenomenon. The over-superelevation will cause an increase in the load on the inner rail, and the under-superelevation will cause an increase in the load on the outer side of the rail, which will lead to an unbalanced vertical force on the inner and outer rails, further leading to increased rail wear. In the utility model, the surface support stiffness of a series of vibration reduction units 3 in the track width direction is adjusted, so that the stiffness of the increased load area is greater than that of the non-increased load area while ensuring that the overall stiffness of the vibration reduction pad structure remains unchanged, and a greater support stiffness is provided on the side of the rail with greater force to avoid increased rail wear.

[0042] In some embodiments, the height ratio of the first boss 31 to the second boss 32 in different vibration reduction units 3 is gradually adjusted along the length direction of the track, so that the stiffness change of the track in the transition section is smoother.

[0043] Specifically, it is generally necessary to adopt stiffness transition measures between the isolated vibration-damping pad floating plate track bed and other track beds, and the currently used transition scheme usually adopts a two-stage or three-stage transition, and the length of each transition section is at least a single track plate. In more cases, each transition section will use multiple transition track plates to make the transition process as smooth as possible. However, this technical solution still has the problem of uneven transition, and the setting cost is also high. In this embodiment, the height ratio of the first boss 31 and the second boss 32 is gradually adjusted along the length direction of the track, so that the stiffness of the vibration-damping pad gradually increases along the length direction of the track, thereby realizing stepless adjustment of the track stiffness in the transition section and improving the smoothness of the transition.

[0044] In addition, in the existing track vibration reduction technical solutions, the vibration reduction requirements of the track often change with the changes in the external environment, and its vibration reduction requirements are not single and unchanging. However, the vibration reduction pad structure usually adopts a single stiffness to meet the maximum vibration reduction requirement. This leads to over-vibration reduction in areas with smaller vibration reduction requirements, accelerates the parameters of rail wear, and increases wheel-rail noise. In the present invention, the surface support stiffness of a certain vibration damping unit 3 can be adjusted by finely adjusting the height ratio between the first boss 31 and the second boss 32. That is, the surface support stiffness of a single or multiple vibration damping units 3 can be adjusted to increase or decrease the surface support stiffness of a certain position of the vibration damping pad structure. In places where the vibration damping demand is small, the surface support stiffness of the vibration damping unit 3 at that location can be reduced, while in places where the vibration damping demand is large, the surface support stiffness of the vibration damping unit 3 at that location can be increased in a targeted manner. In this way, fine design can be carried out according to different vibration damping requirements, avoiding the over-vibration damping phenomenon caused by a single vibration damping pad stiffness, thereby delaying rail corrugation and reducing wheel-rail noise.

[0045] In some embodiments, the height Ha of the first boss 31 and the height Hb of the second boss 32 are both adjusted in the range of 10 mm to 20 mm. When the height of the first boss 31 increases or decreases, the height of the corresponding second boss 32 decreases or increases by the same amount, so as to keep the overall height of the single vibration reduction unit 3 unchanged, and the stiffness of the entire vibration reduction unit 3 is adaptively adjusted by adjusting the height of the bosses with different elastic moduli inside.

[0046] In some embodiments, when the first boss 31 and the second boss 32 are prisms, the edge length of the top surface of the first boss 31 and the second boss 32 ranges from 10 mm to 30 mm, and the edge length of the bottom surface ranges from 40 mm to 60 mm; when the first boss 31 and the second boss 32 are frustums, the diameter of the top surface of the first boss 31 and the second boss 32 ranges from 10 mm to 30 mm, and the diameter of the bottom surface ranges from 40 mm to 60 mm.

[0047] Furthermore, the area and shape of the top surface of the first boss 31 are the same as the area and shape of the top surface of the second boss 32 , and the area and shape of the bottom surface of the first boss 31 are the same as the area and shape of the bottom surface of the second boss 32 .

[0048] Furthermore, the size of the interval between adjacent vibration-damping units 3 is no greater than 1.5 times the bottom edge length or bottom diameter of the first boss 31 .

[0049] Specifically, in this embodiment, the first boss 31 and the second boss 32 are both prism or truncated cone structures, while in some other embodiments, prisms and bosses can be mixed; the top and bottom surfaces of the first boss 31 and the top and bottom surfaces of the second boss 32 have the same outer surface area, which is convenient for the production and manufacturing of the vibration reduction unit 3, simplifies the production process, and reduces the difficulty of production. On the other hand, it can also ensure the stability and accuracy of the surface support stiffness of the vibration reduction unit 3. Limiting the length range of the edge length or diameter of the top and bottom surfaces facilitates the guarantee of production quality in the subsequent production process and adapts to more use environments with different stiffness requirements. In addition, limiting the spacing distance between adjacent vibration reduction units 3 can effectively ensure the density of the vibration reduction unit 3 in the vibration reduction pad structure, so that the vibration reduction pad structure can maintain good vibration reduction performance.

[0050] In some embodiments, the first boss 31 and the second boss 32 are both made of rubber material; the formula of the first boss 31 and the second boss 32 are different, so that the elastic modulus of the first boss 31 is different from the elastic modulus of the second boss 32. Specifically, in the present invention, the first boss 31 and the second boss 32 are made of rubber material with good elasticity, and the rubber material will show different performances, that is, different elastic moduli, due to the different proportions of each component in the formula and the different parameters such as temperature. The elastic modulus of the first boss 31 and the second boss 32 are different, so that the surface support stiffness of each boss can be adjusted by adjusting the height of the two, and then the surface support stiffness of the vibration reduction unit 3 and the support stiffness of the entire vibration reduction pad structure can be adjusted.

[0051] In some embodiments, the first plate body 1 and the first boss 31 and the second plate body 2 and the second boss 32 are integrally formed; the surface of the first plate body 1 away from the first boss 31 is provided with an adhesive layer (not shown in the figure), and the adhesive layer is used to glue and fix the first plate body 1 to the rail body; the second plate body 2 is a high-strength fiber layer, and the second plate body 2 is used to prevent the steel bars or stone particles in the rail base from traditionally damaging the vibration damping unit.

[0052] Specifically, the first plate body 1, the first boss 31, the second boss 32 and the second plate body 2 are produced by vulcanization integrated molding, and the connection between the various components is tighter, the strength is better, and the stability is higher. The adhesive layer on the back of the first plate body 1 can make the connection between the vibration damping pad structure and the track body more stable, and can better disperse the vibration and pressure of the track body to each vibration damping unit 3, so as to achieve a better vibration damping effect; and the high-strength fiber layer of the second plate body 2 can be made of high-performance fibers, such as high-strength and high-modulus fibers, which can improve the strength and anti-penetration ability of the second plate body 2, and prevent the vibration damping pad structure from being penetrated by the steel bars or stone particles in the track base when the force is applied, thereby causing damage to the vibration damping unit 3.

[0053] In summary, the embodiment of the utility model provides an isolated vibration damping pad structure with adjustable stiffness, wherein the first plate body 1 and the second plate body 2 of the vibration damping pad structure are respectively abutted against the track bed and the base of the track, and a plurality of vibration damping units 3 are distributed in the internal array of the vibration damping pad structure, and the vibration damping unit 3 includes two integrally formed platforms, wherein the first platform and the second platform are made of rubber with different elastic moduli, and the height ratio therebetween can be adjusted according to actual needs, thereby adjusting the stiffness of the first platform and the second platform, and further enabling the stiffness of the vibration damping units 3 located at different positions of the vibration damping pad structure to be adaptively adjusted, and by adjusting the stiffness of the vibration damping units 3 at specific positions in curved sections or transition sections of the track, it is possible to better avoid rail wear and improve the smoothness of the track transition, and targeted adjustment of the stiffness of the vibration damping units 3 in places where the vibration damping demand is small can also avoid over-vibration damping, thereby delaying rail corrugation and reducing wheel-rail noise.

[0054] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and substitutions can be made without departing from the technical principle of the present invention. These improvements and substitutions should also be regarded as the protection scope of the present invention.

Claims

1. An isolated vibration damping pad structure with adjustable stiffness, characterized in that: It comprises a first plate body and a second plate body arranged in parallel and a plurality of vibration reduction units arranged in an array between the first plate body and the second plate body, wherein the vibration reduction units are perpendicular to the first plate body; The vibration reduction unit comprises a first boss and a second boss, the first boss and the second boss are integrally formed, both the first boss and the second boss are platform structures, the bottom surface of the first boss is fixedly connected to the first plate body, and the bottom surface of the second boss is fixedly connected to the second plate body; The height sum between the first boss and the second boss remains unchanged, but the height ratio can be adjusted, thereby adjusting the surface support stiffness of the vibration reduction unit.

2. The isolated vibration damping pad structure with adjustable stiffness according to claim 1, characterized in that: The elastic modulus of the first boss is defined as Ea, and the height is defined as Ha; the elastic modulus of the second boss is defined as Eb, and the height is defined as Hb. The calculation formula for the surface support stiffness Ka of the first boss is: The calculation formula of the surface support stiffness Kb of the second boss is: The surface support stiffness K of a single damping unit 减振单元 The calculation formula is: The surface support stiffness K of the isolated vibration damping pad structure 减振垫结构 The calculation formula is: K 减振垫结构 =∑K 减振单元 。 3. The isolated vibration damping pad structure with adjustable stiffness according to claim 2, characterized in that: The height ratio of the first boss to the second boss in different vibration reduction units is adjusted along the width direction of the track, so that when the track is in a curved section, the stiffness of the track load-increasing area is greater than the stiffness of the non-load-increasing area.

4. The isolated vibration damping pad structure with adjustable stiffness according to claim 2, characterized in that: The height ratio of the first boss to the second boss in different vibration reduction units is gradually adjusted along the length direction of the track, so that the stiffness change of the track in the transition section is smoother.

5. The isolated vibration damping pad structure with adjustable stiffness according to claim 1, characterized in that: The adjustment range of the first boss height Ha and the second boss height Hb is 10 mm to 20 mm.

6. The isolated vibration damping pad structure with adjustable stiffness according to claim 1, characterized in that: When the first boss and the second boss are prisms, the edge length of the top surface of the first boss and the second boss ranges from 10mm to 30mm, and the edge length of the bottom surface ranges from 40mm to 60mm; when the first boss and the second boss are frustum, the diameter of the top surface of the first boss and the second boss ranges from 10mm to 30mm, and the diameter of the bottom surface ranges from 40mm to 60mm.

7. The isolated vibration damping pad structure with adjustable stiffness according to claim 6, characterized in that: The area and shape of the top surface of the first boss are the same as the area and shape of the top surface of the second boss, and the area and shape of the bottom surface of the first boss are the same as the area and shape of the bottom surface of the second boss.

8. The isolated vibration damping pad structure with adjustable stiffness according to claim 7, characterized in that: The interval between adjacent vibration-damping units is no greater than 1.5 times the bottom edge length or bottom diameter of the first boss.

9. The isolated vibration damping pad structure with adjustable stiffness according to claim 1, characterized in that: The first boss and the second boss are both made of rubber material; the first boss and the second boss have different formulations, so that the elastic modulus of the first boss is different from the elastic modulus of the second boss.

10. The isolated vibration damping pad structure with adjustable stiffness according to claim 1, characterized in that: The first plate body and the first boss as well as the second plate body and the second boss are integrally formed; the surface of the first plate body away from the first boss is provided with an adhesive layer, and the adhesive layer is used to glue and fix the first plate body to the track body; the second plate body is a high-strength fiber layer, and the second plate body is used to prevent the steel bars or stone particles in the track base from traditionally damaging the vibration damping unit.

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