CN110285180B - Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator - Google Patents
Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator Download PDFInfo
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- CN110285180B CN110285180B CN201910628458.4A CN201910628458A CN110285180B CN 110285180 B CN110285180 B CN 110285180B CN 201910628458 A CN201910628458 A CN 201910628458A CN 110285180 B CN110285180 B CN 110285180B
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- 230000003068 static effect Effects 0.000 title claims abstract description 30
- 238000007667 floating Methods 0.000 claims abstract description 67
- 238000013016 damping Methods 0.000 claims description 32
- 238000007789 sealing Methods 0.000 claims description 7
- 230000033001 locomotion Effects 0.000 claims description 6
- 239000007788 liquid Substances 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 4
- 230000008602 contraction Effects 0.000 claims description 2
- 238000002955 isolation Methods 0.000 abstract description 45
- 230000000694 effects Effects 0.000 abstract description 15
- 238000006073 displacement reaction Methods 0.000 abstract description 11
- 230000009467 reduction Effects 0.000 abstract description 11
- 210000001503 joint Anatomy 0.000 abstract description 2
- 230000005540 biological transmission Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000003993 interaction Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000013178 mathematical model Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 201000010099 disease Diseases 0.000 description 1
- 208000037265 diseases, disorders, signs and symptoms Diseases 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005312 nonlinear dynamic Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B19/00—Protection of permanent way against development of dust or against the effect of wind, sun, frost, or corrosion; Means to reduce development of noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention provides a vibration isolator with high static and low dynamic stiffness characteristics and a track system with the vibration isolator, wherein the vibration isolator with high static and low dynamic stiffness characteristics comprises the following components: the positive rigidity component comprises a seat body and a first elastic piece arranged in a cavity of the seat body; the supporting part is in butt joint with the upper end of the first elastic piece; a floating part, which is connected with the supporting part in a matching way; the negative rigidity component comprises an elastic part and a bearing part which are matched with each other, the elastic part is connected with the supporting part and/or the floating part, and the bearing part is connected with the seat body; when the floating part bears the load and compresses the first elastic member, the direction of the acting force applied by the elastic part to the bearing part is inclined or vertical to the direction of the elastic force of the first elastic member. According to the technical scheme, the natural frequency of the existing track system can be reduced, the vibration isolation frequency range and the low-frequency vibration reduction effect of the existing vibration isolator and the track system can be improved, and meanwhile, the dynamic displacement of a train when passing through the track system can be effectively controlled.
Description
Technical Field
The invention relates to the technical field of vibration reduction and noise reduction of rails, in particular to a vibration isolator with high static and low dynamic stiffness characteristics and a rail system with the vibration isolator.
Background
The low-frequency vibration isolation is a great research hot spot and difficulty in the field of rail traffic vibration isolation. The structural vibration control can be divided into passive control, active control, semi-active control and hybrid control according to the need of external energy input, and adopts two technologies of active control vibration isolation and semi-active control vibration isolation to well isolate low-frequency vibration, but the structure is complex, the occupied space is large, the manufacturing cost is high, external energy supply is required, and the problems of instability, electromagnetic pollution and the like exist. In contrast, the conventional passive vibration isolation structure is simple, easy to implement, reliable in operation, and free from additional external energy consumption, but when the structure is once determined, the natural frequency is determined, and only when the excitation frequency is greater than a specific multiple of the natural frequency of the vibration isolation system, the vibration isolation effect can be achieved. In general, passive vibration isolation can better isolate middle-frequency vibration and high-frequency vibration, but has poor capability of isolating low-frequency vibration.
The vibration isolation system can be further classified into a linear vibration isolation system and a nonlinear vibration isolation system according to the characteristics of the vibration isolation system and the difference of mathematical models describing vibration. The linear vibration isolation system is a system in which the mass is kept unchanged, but the elastic force and the damping force of the linear vibration isolation system are in linear relation with the motion parameters, and the mathematical model of the linear vibration isolation system can be expressed by a linear constant coefficient ordinary differential equation. And a system which does not belong to the linear vibration isolation system is a nonlinear vibration isolation system. From vibration isolation theory, it is known that the transmissibility of a linear vibration isolation system has a close relationship with its stiffness k and damping c. When the damping ratio of the system is increased when the system damping is selected to be increased, the maximum value of the transmissibility corresponding to the resonance frequency of the system damping is reduced, but the transmissibility of the system damping in a high frequency band is increased; when the rigidity of the system is reduced, the natural frequency is reduced, the vibration isolation starting frequency is reduced, the vibration isolation frequency range is increased, but the static bearing capacity is reduced, and the static deformation is increased. Therefore, for the traditional linear vibration isolation system, a lower vibration isolation initial frequency and a higher static bearing capacity cannot be obtained at the same time, and the two are contradictory. This is also the main reason why the above-mentioned rail transit vibration damping measures are poor in low frequency vibration damping effect.
Therefore, the vibration isolation frequency range of the existing vibration isolator is narrow, and the vibration isolator capable of effectively isolating low-frequency vibration and simultaneously controlling dynamic displacement of a track is designed, so that the vibration isolator is necessary for low-frequency vibration isolation in the track traffic or other fields.
Disclosure of Invention
The invention mainly aims to provide the vibration isolator with high static and low dynamic stiffness characteristics and the track system with the vibration isolator, and on the premise of strictly controlling or reducing the dynamic displacement of the track, the natural frequency of the existing vibration isolator and the track system is reduced, and the low-frequency vibration reduction effect and the vibration isolation frequency range are improved.
In order to achieve the above object, according to one aspect of the present invention, there is provided a vibration isolator having high static and low dynamic stiffness characteristics, comprising: the positive rigidity component comprises a seat body and a first elastic piece arranged in a cavity of the seat body; the supporting part is in butt joint with the upper end of the first elastic piece; a floating part, which is connected with the supporting part in a matching way; the negative rigidity component comprises an elastic part and a bearing part which are matched with each other, the elastic part is connected with the supporting part and/or the floating part, and the bearing part is connected with the seat body; when the floating part bears the load and compresses the first elastic member, the direction of the acting force applied by the elastic part to the bearing part is inclined or vertical to the direction of the elastic force of the first elastic member.
Further, the elastic part comprises a second elastic piece and a pushing piece connected with the second elastic piece, the second elastic piece is in a compressed state, and the pushing piece is abutted with the bearing part.
Further, the bearing part is provided with a first curved surface, and the pushing piece can be abutted with different positions of the first curved surface in the stretching process of the second elastic piece.
Further, the pushing piece is provided with a second curved surface, and the position on the second curved surface is abutted with the position on the first curved surface.
Further, the bearing part comprises a connecting rod and a bearing piece, the lower end of the connecting rod is connected with the bottom of the seat body, the upper end of the connecting rod is connected with the bearing piece, and the pushing piece is abutted with the bearing piece.
Further, the connecting rod passes through at least a part of the supporting part, the supporting part is provided with an avoidance hole for avoiding the bearing member, and the bearing member is in threaded connection or welding with the connecting rod.
Further, the elastic part is connected with the supporting part and is arranged in the first cavity of the supporting part.
Further, the support portion includes: the bearing part passes through the frame body; the cover plate is arranged on the upper portion of the frame body, a first cavity is arranged between the cover plate and the frame body, the second elastic piece is connected with the side wall of the first cavity, and the floating portion is connected with the cover plate.
Further, the elastic part further includes: the guide structure is horizontally arranged in the first cavity, and the second elastic piece is arranged in the guide structure.
Further, the elastic parts are multiple, and the elastic parts are distributed in the circumferential direction of the bearing part.
Further, the floating part comprises a cylinder body and a supporting piece arranged on the inner wall of the cylinder body, the supporting piece is connected with the upper part of the supporting part, a second cavity is arranged above the supporting piece in the cylinder body, and the elastic part is arranged in the second cavity.
Further, the elastic part is connected with the floating part, the floating part further comprises a first fixing piece arranged on the inner wall of the cylinder body, the second cavity is located between the supporting piece and the first fixing piece, the elastic part further comprises a guide structure, the upper portion of the guide structure is connected with the first fixing piece, and the second elastic piece is arranged in the guide structure.
Further, the floating portion further includes: the lower part of the second fixing piece is connected with the supporting part, and the lower part of the guiding structure is connected with the upper part of the second fixing piece.
Further, the elastic part further includes: the limiting piece is arranged at the end part of the guide structure and used for limiting the second elastic piece.
Further, the supporting part and the seat body are arranged at intervals, the lower end face of the supporting part and the upper end face of the seat body are correspondingly arranged, the vibration isolator further comprises a sealing element, and the sealing element is sleeved on the supporting part and the seat body to seal a gap between the supporting part and the seat body.
Further, the floating part comprises a cylinder body and an annular supporting piece arranged on the inner wall of the cylinder body, and the supporting piece is provided with an avoidance groove; the supporting part can rotate relative to the floating part and axially move along the cylinder body, the supporting part comprises a frame body and a cover plate arranged on the frame body, and the cover plate can penetrate through the avoidance groove and move to a position abutting against the lower end face of the supporting piece through relative movement of the supporting part and the floating part.
Further, the vibration isolator further includes: damping fluid, set up in cavity of the seat body; the upper end of the damping piece is connected with the supporting part, and the lower end of the damping piece is immersed in damping liquid.
According to another aspect of the present invention, there is provided a rail system comprising a vibration isolator having high static and low dynamic stiffness characteristics, the vibration isolator being provided as described above.
By applying the technical scheme of the invention, the vibration isolator is provided with the positive stiffness component, the supporting part, the floating part and the negative stiffness component, the floating part is used for bearing load, the elastic part of the negative stiffness component is connected with the supporting part or the floating part, the bearing part is connected with the seat body, the first elastic piece contracts when the floating part bears load and compresses the first elastic piece, and the direction of the acting force exerted by the elastic part to the bearing part is inclined relative to the direction of the elastic force of the first elastic piece. Therefore, the elastic force generated by the cooperation of the positive stiffness component and the negative stiffness component is in a nonlinear relation with the displacement of the floating part, so that the vibration isolator can obtain a lower vibration isolation initial frequency and a higher static bearing capacity at the same time, namely has higher static stiffness and lower dynamic stiffness (short for high static and low dynamic), can isolate low-frequency vibration, and improves the vibration isolation frequency range of the vibration isolator. The vibration isolator is applied to a track system, so that the vibration isolation frequency range of the track system can be improved, low-frequency vibration transmission is reduced, and the influence on the surrounding environment is reduced.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
fig. 1 is a schematic view showing a structure of a vibration isolator according to a first embodiment of the present invention;
figure 2 shows a schematic view of the force of the elastomeric portion against the load bearing portion of the vibration isolator of figure 1 in operation;
fig. 3 shows a schematic layout of the elastic portion in the vibration isolator in fig. 1;
fig. 4 shows another arrangement schematic of the elastic portion in the vibration isolator in fig. 1;
fig. 5 is another schematic structural view showing the elastic portion in the vibration isolator of fig. 1;
figure 6 shows a top view of the vibration isolator of figure 1;
fig. 7 shows a schematic structural diagram of a vibration isolator according to a second embodiment of the present invention.
Wherein the above figures include the following reference numerals:
10. a positive stiffness component; 11. a base; 12. a first elastic member; 20. a support part; 21. a frame body; 22. a cover plate; 30. a floating part; 31. a cylinder; 32. a support; 321. an avoidance groove; 33. a first fixing member; 34. a second fixing member; 40. an elastic part; 41. a second elastic member; 42. a pushing member; 421. a second curved surface; 43. a guide structure; 44. a limiting piece; 50. a carrying part; 51. a first curved surface; 52. a connecting rod; 53. a carrier; 60. a seal; 70. and a damping member.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It will be apparent that the described embodiments are only some, but not all, embodiments of the invention. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
As shown in fig. 1 to 6, an embodiment of the present invention provides a vibration isolator having high static and low dynamic stiffness characteristics, including: a positive stiffness assembly 10, the positive stiffness assembly 10 comprising a seat 11 and a first elastic member 12 disposed within a cavity of the seat 11; a support portion 20, the support portion 20 being in contact with the upper end of the first elastic member 12; a floating part 30, wherein the floating part 30 is connected with the supporting part 20 in a matching way; the negative stiffness component comprises an elastic part 40 and a bearing part 50 which are matched with each other, the elastic part 40 is connected with the supporting part 20 and/or the floating part 30, and the bearing part 50 is connected with the seat body 11 of the positive stiffness component 10; when the floating portion 30 receives a load and compresses the first elastic member 12, the direction of the urging force applied to the bearing portion 50 by the elastic portion 40 is inclined or perpendicular to the direction of the urging force of the first elastic member 12. Specifically, the direction of the interaction force of the elastic portion 40 and the bearing portion 50 varies along the variation of the normal direction of the curved surface of the bearing portion 50.
By applying the technical solution of the present embodiment, the positive stiffness component 10, the supporting portion 20, the floating portion 30 and the negative stiffness component are provided in the vibration isolator, the floating portion 30 is used for bearing a load, the elastic portion 40 of the negative stiffness component is connected with the supporting portion 20 or the floating portion 30, the bearing portion 50 is connected with the base 11 of the positive stiffness component 10, the floating portion 30 contracts the first elastic member 12 under the condition that the bearing load is borne and the first elastic member 12 is compressed, and the direction of the acting force exerted by the elastic portion 40 to the bearing portion 50 is inclined relative to the direction of the elastic force of the first elastic member 12. In this way, the elastic force generated by the cooperation of the positive stiffness component 10 and the negative stiffness component is in a nonlinear relation with the displacement of the floating part 30, so that the vibration isolator can obtain a lower vibration isolation initial frequency and a higher static bearing capacity at the same time, namely has higher static stiffness and lower dynamic stiffness (short for high static and low dynamic), can isolate low-frequency vibration, and improves the vibration isolation frequency range of the vibration isolator. The vibration isolator is applied to a track system, so that the vibration isolation frequency range of the track system can be improved, low-frequency vibration transmission is reduced, and the influence on the surrounding environment is reduced.
In the present embodiment, the elastic portion 40 includes a second elastic member 41 and a pushing member 42 connected to the second elastic member 41, the second elastic member 41 is in a compressed state, and the pushing member 42 abuts against the bearing portion 50. Interaction force is generated with the bearing portion 50 by the cooperation of the second elastic member 41 and the pushing member 42. The direction of the urging force applied to the bearing portion 50 by the second elastic member 41 is inclined or perpendicular to the direction of the urging force of the first elastic member 12.
As shown in fig. 2, when the floating portion 30 receives a load, the floating portion 30 and the bearing portion 50 are relatively displaced, and the displacement of the bearing portion 50 causes the second elastic member 41 to extend, thereby exerting a force on the bearing portion 50. Through the arrangement, the component force variation of the acting force applied by the first elastic member 12 to the bearing portion 50 along the direction of the elastic force of the first elastic member 12 and the dimensional variation of the second elastic member 41 are in nonlinear relation, and the component force variation and the displacement of the floating portion 30 are also in nonlinear relation, so that the vibration isolator has higher static stiffness and lower dynamic stiffness characteristics, namely has the effect of high static and low motion, and can isolate low-frequency vibration and improve the vibration isolation frequency range of the vibration isolator compared with the conventional vibration isolator. The vibration isolator can isolate low-frequency vibration smaller than 20 Hz.
Specifically, in this embodiment, the first elastic member 12 may be disposed vertically, and the second elastic member 41 may be disposed horizontally (under the condition of not bearing), so that the vibration isolator may better perform vibration damping and noise reduction on the load in the vertical direction, and is relatively suitable for a track system.
As shown in fig. 1 or fig. 5, the bearing portion 50 has a first curved surface 51, and the pushing member 42 can abut against different positions of the first curved surface 51 during the expansion and contraction process of the second elastic member 41. By providing the first curved surface 51, the direction of the force applied to the bearing portion 50 by the second elastic member 41 can be changed as required to satisfy the nonlinear requirement, and the first curved surface 51 can be concave, convex, circular or the like.
In the present embodiment, the pushing member 42 has a second curved surface 421, and a position on the second curved surface 421 abuts against a position on the first curved surface 51. By matching the second curved surface 421 and the first curved surface 51, the nonlinear force requirement can be better realized, so that the effect of high static and low motion is realized.
In the present embodiment, the bearing portion 50 includes a link 52 and a bearing member 53, the lower end of the link 52 is connected to the bottom of the base 11, the upper end of the link 52 is connected to the bearing member 53, and the pushing member 42 abuts against the bearing member 53. Through the arrangement, the bearing part 50 can be connected with the positive stiffness component 10, so that the acting force of the negative stiffness component borne by the bearing part 50 can be conveniently transmitted to the positive stiffness component 10, the positive stiffness component 10 and the negative stiffness component are matched together to damp loads, meanwhile, the transmission of vibration to the surrounding environment is reduced, and the influence on the surrounding environment is reduced. Specifically, the force provided by the second elastic member 41 causes the direction of the interaction force generated by the pushing member 42 and the bearing member 53 to be along the normal direction of the bearing member 53.
It should be noted that, the bearing 53 on the bearing portion 50 and the first curved surface 51 on the bearing 53 may be designed into different shapes according to actual requirements, and the shape and sliding manner of the pushing member 42 in the elastic portion 40 may be changed in various manners, for example, a bearing is added to change sliding into rolling, or a bearing is added to the front end of the pushing member 42, so that the pushing member 42 and the first curved surface 51 of the bearing 53 may contact and slide into contact rolling. The principle of the method is that the method principle of the invention is adopted no matter how the shape and the mode are changed, and the method is within the protection scope.
Specifically, the link 52 is threaded through at least a portion of the support portion 20, the support portion 20 has relief holes for the relief carrier 53, and the carrier 53 is threaded or welded to the link 52. Through above-mentioned setting for isolator compact structure, small, and be convenient for the assembly.
In order to secure the stability of the carrier 53, it is necessary to install a lockwasher and locknut, the position of the carrier 53 on the link 52 may be adjusted, and when the carrier 53 is installed, the lower surface of the carrier 53 contacts the surface of the pusher 42 and provides a certain pressure, and the second elastic member 41 is compressed due to the existence of the pressure to provide a certain rigidity.
In the present embodiment, the elastic portion 40 is connected to the supporting portion 20, and the elastic portion 40 is disposed in the first cavity of the supporting portion 20. Therefore, the vibration isolator is compact in structure, and compared with the original vibration isolator, the vibration isolator is small in overall structure change, can reduce the influence on related parts, and is convenient to manufacture and assemble.
Specifically, the support portion 20 includes: a frame 21 through which the bearing part 50 passes; the cover plate 22 is arranged on the upper part of the frame body 21, a first cavity is arranged between the cover plate 22 and the frame body 21, the second elastic piece 41 is connected with the side wall of the first cavity, and the floating part 30 is connected with the cover plate 22. Therefore, the vibration isolator is compact in structure and has good vibration reduction and noise reduction effects.
In the present embodiment, the elastic portion 40 further includes: the guide structure 43, the guide structure 43 is horizontally disposed in the first cavity, and the second elastic member 41 is disposed in the guide structure 43. The contracting direction of the second elastic member 41 can be guided by the guide structure 43 to better control the direction of the acting force and to facilitate the assembly of the elastic portion 40. The guide structure 43 may be provided in a groove-like structure or a cylindrical structure.
As shown in fig. 3 and 4, the elastic portion 40 may be provided in plurality, and the plurality of elastic portions 40 are distributed in the circumferential direction of the bearing portion 50. Therefore, the integral influence of the negative stiffness component on the vibration isolator can be improved, the nonlinear characteristic effect is improved, and the vibration isolation frequency range of the vibration isolator is improved. Moreover, the load bearing portion 50 can be made relatively uniform in force.
In this embodiment, the supporting portion 20 is disposed at a distance from the base 11, the lower end surface of the supporting portion 20 is disposed corresponding to the upper end surface of the base 11, the vibration isolator further includes a sealing member 60, and the sealing member 60 is sleeved on the supporting portion 20 and the base 11 to seal the gap between the supporting portion 20 and the base 11. The supporting part 20 and the seat body 11 are arranged at intervals, so that the supporting part 20 and the floating part 30 can conveniently displace when bearing load, the lower end face of the supporting part 20 and the upper end face of the seat body 11 are correspondingly arranged, when the load is overlarge, the lower end face of the supporting part 20 and the upper end face of the seat body 11 can be in direct contact to play a limiting role, and therefore the overlarge displacement of the floating part 30 and the damage caused by plastic deformation due to overlarge deformation of the first elastic piece 12 can be avoided. In order to ensure effectiveness, the sealing member 60 of the present embodiment is a rubber seal ring, and is fixed to the seat 11 and the support 20 by a hose clamp, respectively.
As shown in fig. 1 and 6, the floating part 30 includes a cylinder 31 and an annular support member 32 provided on an inner wall of the cylinder 31, the support member 32 having a relief groove 321 thereon; the support portion 20 is rotatable relative to the floating portion 30 and moves in the axial direction of the cylinder 31, the support portion 20 includes a frame 21 and a cover plate 22 provided on the frame 21, and the cover plate 22 is capable of passing through the escape groove 321 and moving to a position abutting against the lower end surface of the support 32 by the relative movement of the support portion 20 and the floating portion 30. With the above arrangement, when the vibration isolator is assembled, the supporting portion 20 is rotated to enable the protruding portion on the cover plate 22 to correspond to the avoidance groove 321, then the supporting portion 20 is moved towards the inside of the cylinder 31, the supporting portion 20 can be penetrated below the supporting piece 32, then the supporting portion 20 is rotated again, the protruding portion on the cover plate 22 is misplaced with the avoidance groove 321, and therefore the cover plate 22 is abutted to the lower end face of the supporting piece 32, and accordingly assembly of the floating portion 30 and the supporting portion 20 is achieved, namely the supporting portion 20 supports the floating portion 30. In construction, the cylinder 31 may be prefabricated inside a concrete track slab.
As shown in fig. 1, the vibration isolator further includes: damping fluid, set up in the cavity of the seat 11; and a damping member 70, wherein an upper end of the damping member 70 is connected to the support portion 20, and a lower end of the damping member 70 is immersed in the damping liquid. With the above arrangement, when the support portion 20 receives a load, the generated vibration can be transmitted to the damping liquid through the damping member 70, and the vibration can be slowed down by the damping effect of the damping liquid, thereby achieving the effects of vibration reduction and noise reduction. Specifically, the damper 70 includes a rod-like member, an upper end of which is connected to the support portion 20, and a disk-like member disposed below the rod-like member. In order to improve the connection strength and the transmission effect, a plurality of rod-like members may be provided, and a plurality of rod-like members may be provided around the bearing part 50. The damping fluid is poured into the seat 11 at a certain height to provide the damping coefficient required by the system.
As shown in fig. 7, in the second embodiment of the present invention, unlike the above-described embodiment, the floating portion 30 includes the cylinder 31 and the support 32 provided on the inner wall of the cylinder 31, the support 32 is connected to the upper portion of the support 20, the cylinder 31 has the second cavity above the support 32, and the elastic portion 40 is provided in the second cavity. The elastic portion 40 may be connected to the structure in the floating portion 30 or may be connected to the structure in the supporting portion 20.
Specifically, in the present embodiment, the elastic portion 40 is connected to the floating portion 30, the floating portion 30 further includes a first fixing member 33 provided on an inner wall of the cylinder 31, the second cavity is located between the support member 32 and the first fixing member 33, the elastic portion 40 further includes a guide structure 43, an upper portion of the guide structure 43 is connected to the first fixing member 33, and the second elastic member 41 is provided in the guide structure 43. By the connection of the guide structure 43 with the first fixing member 33, the position setting of the second elastic member 41 and the guiding of the second elastic member 41 can be achieved.
In the present embodiment, the floating portion 30 further includes: and a second fixing member 34, wherein a lower portion of the second fixing member 34 is connected to the supporting portion 20, and a lower portion of the guide structure 43 is connected to an upper portion of the second fixing member 34. Through the arrangement, the components in the vibration isolator can be stably and firmly connected, so that the reliability of the vibration isolator is improved.
In the present embodiment, the elastic portion 40 further includes: the limiting piece 44, the limiting piece 44 sets up the tip at guide structure 43, and the limiting piece 44 is used for spacing second elastic component 41. The second elastic member 41 can be limited by the limiting member 44, so that the second elastic member 41 is limited and kept in a compressed state, and the second elastic member 41 is prevented from being separated from the guiding structure 43.
Another embodiment of the present invention provides a rail system, including a vibration isolator with high static and low dynamic stiffness characteristics, where the vibration isolator is provided by the foregoing embodiment.
In the prior art of vibration damping, a floating slab track structure is considered to be the track vibration damping form with the best vibration damping effect. However, the existing floating slab vibration isolator belongs to a linear vibration isolation system, and cannot have low vibration isolation initial frequency and high static bearing capacity due to structural limitations and material limitations, and cannot adjust vibration isolation performance in real time according to different running speeds of a train, track irregularity and other factors, so that vibration isolation frequency range and vibration isolation effect are unsatisfactory.
By applying the technical solution of the present embodiment, the positive stiffness component 10, the supporting portion 20, the floating portion 30 and the negative stiffness component are provided in the vibration isolator, the floating portion 30 is used for bearing a load, the elastic portion 40 of the negative stiffness component is connected with the supporting portion 20 or the floating portion 30, the bearing portion 50 is connected with the base 11 of the positive stiffness component 10, the floating portion 30 contracts the first elastic member 12 under the condition that the bearing load is borne and the first elastic member 12 is compressed, and the direction of the acting force exerted by the elastic portion 40 to the bearing portion 50 is inclined relative to the direction of the elastic force of the first elastic member 12. In this way, the elastic force generated by the cooperation of the positive stiffness component 10 and the negative stiffness component is in a nonlinear relation with the displacement of the floating part 30, so that the vibration isolator can obtain a lower vibration isolation initial frequency and a higher static bearing capacity at the same time, namely has higher static stiffness and lower dynamic stiffness (short for high static low dynamic), can isolate low-frequency vibration, improves the vibration isolation frequency range of the vibration isolator and the vibration isolation frequency range of a rail system, reduces low-frequency vibration transmission, and reduces the influence on the surrounding environment. By applying the technical scheme, on the premise of strictly controlling or reducing the dynamic displacement of the track, the natural frequency of the existing vibration isolator and the track system thereof is reduced, and the low-frequency vibration reduction effect and the vibration isolation frequency range are improved.
The cylinder 31 of the vibration isolator is prefabricated in a concrete track slab, when a train passes, the cylinder 31 moves downwards along with the track slab, then the supporting part 20, the guide structure 43, the second elastic piece 41 and the pushing piece 42 move downwards simultaneously, the base 11 is placed on a roadbed, then the connecting rod 52 and the bearing piece 53 are fixed, and the first elastic piece 12 with positive rigidity is compressed by pressure to provide rigidity. At this time, since the second elastic member 41 having negative rigidity is initially in a compressed state, the second elastic member 41 starts to relax as the pushing member 42 simultaneously descends, providing a pushing force to the bearing portion 50, and the front end of the pushing member 42 slides down along the surface of the bearing member 53.
When the train passes, the first elastic member 12 begins to relax to provide thrust, and then the supporting portion 20, the guiding structure 43, the second elastic member 41 and the pushing member 42 move upwards along with the cylinder 31, at this time, the front end of the pushing member 42 slides upwards along the surface of the bearing member 53, and the second elastic member 41 begins to compress to provide rigidity. The overall system provides a non-linear force due to the cooperation of the carrier 53 and the pusher 42. The schematic diagram of this embodiment is shown in fig. 2, where the negative stiffness assembly moves downward as the train passes, the relative positions of the carrier 53 and pusher 42 change, and the direction of the force provided by the negative stiffness assembly changes due to the change in shape of the contact surface. By utilizing the nonlinear dynamics characteristic of the vibration isolator, a high-performance track vibration reduction system with high static and low dynamic stiffness characteristics can be formed.
From the above description, it can be seen that the technical solution of the present invention achieves the following technical effects:
1) The low-frequency vibration isolation of the floating plate is realized, and the low-frequency transmission rate of the floating plate is reduced, so that the influence on the surrounding environment, people, buildings and precise instruments when the railway train such as a subway runs is optimized;
2) The dynamic displacement of a floating slab in the track system when a train passes through is reduced, the deformation of the track system is controlled, and the diseases such as rail wave grinding and the like caused by the large deformation of the track structure are reduced;
3) The integral structure has the characteristics of high static and low dynamic stiffness, has good integrity and is easy to install on site.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (14)
1. A vibration isolator with high static and low dynamic stiffness characteristics, comprising:
a positive stiffness assembly (10), the positive stiffness assembly (10) comprising a seat (11) and a first elastic member (12) disposed within a cavity of the seat (11);
a support portion (20), wherein the support portion (20) is in contact with the upper end of the first elastic member (12);
a floating part (30), wherein the floating part (30) is connected with the supporting part (20) in a matching way;
the negative stiffness assembly comprises an elastic part (40) and a bearing part (50) which are matched with each other, the elastic part (40) is connected with the supporting part (20) and/or the floating part (30), and the bearing part (50) is connected with the seat body (11);
the floating part (30) is inclined or vertical to the direction of the elastic force applied by the elastic part (40) to the bearing part (50) under the condition of bearing load and compressing the first elastic piece (12);
the elastic part (40) comprises a second elastic piece (41) and a pushing piece (42) connected with the second elastic piece (41), the second elastic piece (41) is in a compressed state, and the pushing piece (42) is abutted with the bearing part (50);
the bearing part (50) comprises a connecting rod (52) and a bearing piece (53), the lower end of the connecting rod (52) is connected with the bottom of the base body (11), the upper end of the connecting rod (52) is connected with the bearing piece (53), and the pushing piece (42) is abutted with the bearing piece (53);
the elastic part (40) is connected with the supporting part (20), and the elastic part (40) is arranged in the first cavity of the supporting part (20); or, the floating part (30) comprises a cylinder body (31) and a supporting piece (32) arranged on the inner wall of the cylinder body (31), the supporting piece (32) is connected with the upper part of the supporting part (20), a second cavity is arranged above the supporting piece (32) in the cylinder body (31), and the elastic part (40) is arranged in the second cavity.
2. The vibration isolator according to claim 1, characterized in that the carrier portion (50) has a first curved surface (51), and the pushing member (42) can abut against different positions of the first curved surface (51) during the expansion and contraction of the second elastic member (41).
3. The vibration isolator according to claim 2, characterized in that the pusher (42) has a second curved surface (421), a position on the second curved surface (421) being in abutment with a position on the first curved surface (51).
4. The vibration isolator according to claim 1, wherein the connecting rod (52) is threaded through at least a portion of the support portion (20), the support portion (20) having a relief hole for the bearing member (53), the bearing member (53) being threaded or welded to the connecting rod (52).
5. The vibration isolator according to claim 1, wherein the support portion (20) comprises:
the bearing part (50) penetrates through the frame body (21);
the cover plate (22) is arranged on the upper portion of the frame body (21), the first cavity is formed between the cover plate (22) and the frame body (21), the second elastic piece (41) is connected with the side wall of the first cavity, and the floating part (30) is connected with the cover plate (22).
6. The vibration isolator according to claim 1, wherein the elastic portion (40) further comprises:
the guide structure (43), the guide structure (43) is arranged in the first cavity horizontally, and the second elastic piece (41) is arranged in the guide structure (43).
7. The vibration isolator according to claim 1, wherein the elastic portion (40) is plural, and the plural elastic portions (40) are distributed in the circumferential direction of the bearing portion (50).
8. The vibration isolator according to claim 1, characterized in that the elastic portion (40) is connected to the floating portion (30), the floating portion (30) further comprises a first fixing member (33) provided on an inner wall of the cylinder (31), the second cavity is located between the support member (32) and the first fixing member (33), the elastic portion (40) further comprises a guide structure (43), an upper portion of the guide structure (43) is connected to the first fixing member (33), and the second elastic member (41) is provided in the guide structure (43).
9. The vibration isolator according to claim 8, wherein the floating portion (30) further comprises:
and the lower part of the second fixing piece (34) is connected with the supporting part (20), and the lower part of the guide structure (43) is connected with the upper part of the second fixing piece (34).
10. The vibration isolator according to claim 8, wherein the elastic portion (40) further comprises:
and the limiting piece (44), the limiting piece (44) is arranged at the end part of the guide structure (43), and the limiting piece (44) is used for limiting the second elastic piece (41).
11. The vibration isolator according to claim 1, characterized in that the supporting portion (20) is disposed at an interval with the base body (11), a lower end surface of the supporting portion (20) is disposed corresponding to an upper end surface of the base body (11), the vibration isolator further comprises a sealing member (60), and the sealing member (60) is sleeved on the supporting portion (20) and the base body (11) to seal a gap between the supporting portion (20) and the base body (11).
12. The vibration isolator according to claim 1, wherein,
the floating part (30) comprises a cylinder (31) and an annular supporting piece (32) arranged on the inner wall of the cylinder (31), wherein the supporting piece (32) is provided with an avoidance groove (321);
the support part (20) can rotate relative to the floating part (30) and move along the axial direction of the cylinder body (31), the support part (20) comprises a frame body (21) and a cover plate (22) arranged on the frame body (21), and the cover plate (22) can penetrate through the avoidance groove (321) and move to a position abutting against the lower end face of the support piece (32) through the relative movement of the support part (20) and the floating part (30).
13. The vibration isolator according to claim 1, further comprising:
damping fluid is arranged in the cavity of the seat body (11);
and the upper end of the damping piece (70) is connected with the supporting part (20), and the lower end of the damping piece (70) is immersed in the damping liquid.
14. A track system comprising a vibration isolator of high static and low dynamic stiffness characteristics, wherein the vibration isolator is the vibration isolator of any one of claims 1 to 13.
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| CN111041904B (en) * | 2019-12-30 | 2021-11-02 | 济南轨道交通集团有限公司 | Shock attenuation subway rail set |
| CN112871575B (en) * | 2021-01-12 | 2022-03-29 | 株洲时代新材料科技股份有限公司 | Vibration isolator damping agent pouring production line and production method |
| CN113124998B (en) * | 2021-03-26 | 2022-09-20 | 中铁二院工程集团有限责任公司 | Rail rigidity time-frequency measurement method based on P2 force vibration |
| CN114658749B (en) * | 2022-04-15 | 2024-01-12 | 维沃移动通信有限公司 | Hinge mechanism and electronic device |
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