CN110285180B - Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator - Google Patents

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

Vibration isolator with high static and low dynamic stiffness characteristics and track system having the same

Technical Field

The present invention relates to the technical field of track vibration reduction and noise reduction, and in particular to a vibration isolator with high static and low dynamic stiffness characteristics and a track system having the same.

Background technique

Low-frequency vibration isolation is a major research hotspot and difficulty in the field of rail transit vibration isolation. Structural vibration control can be divided into passive control, active control, semi-active control and hybrid control according to whether external energy input is required. Active control vibration isolation and semi-active control vibration isolation are two technologies that can effectively isolate low-frequency vibrations. However, their structures are complex, occupy a large space, and have high manufacturing costs. They both require energy from the outside world, and there are problems such as instability and electromagnetic pollution. In contrast, traditional passive vibration isolation structures are simple, easy to implement, reliable, and do not consume additional external energy. However, once its structure is determined, its natural frequency is determined, and the vibration isolation effect can only be achieved when the excitation frequency is greater than a specific multiple of the natural frequency of the vibration isolation system. In general, passive vibration isolation can better isolate medium and high frequency vibrations, but its ability to isolate low-frequency vibrations is poor.

According to the characteristics of the vibration isolation system and the mathematical model describing the vibration, the vibration isolation system can be divided into a linear vibration isolation system and a nonlinear vibration isolation system. Among them, the linear vibration isolation system refers to a system in which the mass remains unchanged, but its elastic force and damping force are linearly related to the motion parameters, and its mathematical model can be expressed by a linear constant coefficient ordinary differential equation. The system that does not belong to the linear vibration isolation system is a nonlinear vibration isolation system. According to the vibration isolation theory, the transmissibility of the linear vibration isolation system is closely related to its stiffness k and damping c. When the system damping is increased, its damping ratio increases, and the maximum transmissibility corresponding to its resonant frequency decreases, but its transmissibility in the high frequency band increases; when the system stiffness is reduced, its natural frequency decreases, the vibration isolation starting frequency decreases, and the vibration isolation frequency range increases, but its static bearing capacity decreases and the static deformation increases. Therefore, for the traditional linear vibration isolation system, it is impossible to obtain a lower vibration isolation starting frequency and a higher static bearing capacity at the same time, and the two are contradictory. This is also the main reason why the above-mentioned rail transit vibration reduction measures have poor low-frequency vibration reduction effects.

Therefore, the existing vibration isolators have a narrow vibration isolation frequency range. It is necessary to design a vibration isolator that can effectively isolate low-frequency vibrations and control the dynamic displacement of the track for low-frequency vibration isolation in rail transportation or other fields.

Summary of the invention

The main purpose of the present invention is to provide a vibration isolator with high static and low dynamic stiffness characteristics and a track system having the same, which can reduce the natural frequency of the existing vibration isolator and its track system and improve the low-frequency vibration reduction effect and vibration isolation frequency range under the premise of strictly controlling or reducing the dynamic displacement of the track.

In order to achieve the above-mentioned purpose, according to one aspect of the present invention, there is provided a vibration isolator with high static and low dynamic stiffness characteristics, comprising: a positive stiffness component, the positive stiffness component comprising a seat body and a first elastic member arranged in a cavity of the seat body; a support portion, the support portion abutting against the upper end of the first elastic member; a floating portion, the floating portion being cooperatively connected with the support portion; a negative stiffness component, the negative stiffness component comprising an elastic portion and a bearing portion that cooperate with each other, the elastic portion being connected to the support portion and/or the floating portion, and the bearing portion being connected to the seat body; when the floating portion bears a load and compresses the first elastic member, the direction of the force applied by the elastic portion to the bearing portion is inclined or vertically arranged relative to the direction of the elastic force of the first elastic member.

Further, the elastic part includes a second elastic member and a pushing member connected to the second elastic member, the second elastic member is in a compressed state, and the pushing member abuts against the bearing part.

Furthermore, the bearing portion has a first curved surface, and during the extension and retraction process of the second elastic member, the pushing member can abut against different positions of the first curved surface.

Furthermore, the pushing member has a second curved surface, and a position on the second curved surface abuts against a position on the first curved surface.

Furthermore, the bearing part includes a connecting rod and a bearing member, the lower end of the connecting rod is connected to the bottom of the seat body, the upper end of the connecting rod is connected to the bearing member, and the pushing member abuts against the bearing member.

Furthermore, the connecting rod passes through at least a portion of the supporting portion, and the supporting portion is provided with an escape hole for escaping the bearing member, and the bearing member is threadedly connected or welded to the connecting rod.

Further, the elastic part is connected to the supporting part, and the elastic part is arranged in the first cavity of the supporting part.

Furthermore, the support part includes: a frame, the bearing part passes through the frame; a cover plate, which is arranged on the upper part of the frame, a first cavity is provided between the cover plate and the frame, the second elastic member is connected to the side wall of the first cavity, and the floating part is connected to the cover plate.

Furthermore, the elastic part also includes: a guide structure, the guide structure is horizontally arranged in the first cavity, and the second elastic member is arranged in the guide structure.

Furthermore, there are multiple elastic parts, and the multiple elastic parts are distributed in the circumference of the bearing part.

Furthermore, the floating part includes a cylinder and a support member arranged on the inner wall of the cylinder, the support member is connected to the upper part of the support member, a second cavity is provided in the cylinder above the support member, and the elastic part is arranged in the second cavity.

Furthermore, the elastic part is connected to the floating part, the floating part also includes a first fixing part arranged on the inner wall of the cylinder, the second cavity is located between the support part and the first fixing part, the elastic part also includes a guide structure, the upper part of the guide structure is connected to the first fixing part, and the second elastic part is arranged in the guide structure.

Furthermore, the floating part also includes: a second fixing member, the lower part of the second fixing member is connected to the supporting part, and the lower part of the guide structure is connected to the upper part of the second fixing member.

Furthermore, the elastic part also includes: a limiting member, which is arranged at the end of the guide structure and is used to limit the second elastic member.

Furthermore, the support part and the seat body are spaced apart, the lower end surface of the support part is arranged corresponding to the upper end surface of the seat body, and the vibration isolator also includes a sealing member, which is sleeved on the support part and the seat body to seal the gap between the support part and the seat body.

Furthermore, the floating part includes a cylinder and an annular support member arranged on the inner wall of the cylinder, and the support member has an avoidance groove; the support part can rotate relative to the floating part and move along the axial direction of the cylinder, and the support part includes a frame body and a cover plate arranged on the frame body. Through the relative movement of the support part and the floating part, the cover plate can pass through the avoidance groove and move to a position abutting against the lower end surface of the support part.

Furthermore, the vibration isolator also includes: damping fluid, which is arranged in the cavity of the seat body; and a damping member, the upper end of which is connected to the supporting part, and the lower end of which is immersed in the damping fluid.

According to another aspect of the present invention, there is provided a track system, comprising a vibration isolator having high static and low dynamic stiffness characteristics, wherein the vibration isolator is the vibration isolator provided above.

According to the technical solution of the present invention, a positive stiffness component, a supporting part, a floating part and a negative stiffness component are arranged in the vibration isolator. The floating part is used to bear the load, the elastic part of the negative stiffness component is connected to the supporting part or the floating part, and the bearing part is connected to the seat body. When the floating part bears the load and compresses the first elastic part, the first elastic part contracts, and the direction of the force applied by the elastic part to the bearing part is inclined relative to the direction of the elastic force of the first elastic part. In this way, the elastic force generated by the cooperation of the positive stiffness component and the negative stiffness component is nonlinearly related to the displacement of the floating part. In this way, the vibration isolator can simultaneously obtain a lower vibration isolation starting frequency and a higher static bearing capacity, that is, it has a higher static stiffness and a lower dynamic stiffness characteristic (referred to as high static and low dynamic), can isolate low-frequency vibrations, and improve the vibration isolation frequency range of the vibration isolator. The vibration isolator is applied to the rail system to improve the vibration isolation frequency range of the rail system, reduce the transmission of low-frequency vibrations, and reduce the impact on the surrounding environment.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

FIG1 shows a schematic structural diagram of a vibration isolator provided in Embodiment 1 of the present invention;

FIG2 is a schematic diagram showing the force exerted by the elastic part on the bearing part of the vibration isolator in FIG1 when the vibration isolator is in operation;

FIG3 shows a schematic diagram of the arrangement of the elastic part in the vibration isolator in FIG1 ;

FIG4 shows another schematic diagram of the arrangement of the elastic part in the vibration isolator in FIG1 ;

FIG5 shows another schematic structural diagram of the elastic part in the vibration isolator in FIG1 ;

FIG6 shows a top view of the vibration isolator in FIG1 ;

FIG. 7 shows a schematic structural diagram of a vibration isolator provided in the second embodiment of the present invention.

The above drawings include the following reference numerals:

10. Positive stiffness component; 11. seat body; 12. first elastic member; 20. support part; 21. frame; 22. cover plate; 30. floating part; 31. cylinder body; 32. support member; 321. avoidance groove; 33. first fixing member; 34. second fixing member; 40. elastic part; 41. second elastic member; 42. pushing member; 421. second curved surface; 43. guide structure; 44. limiting member; 50. bearing part; 51. first curved surface; 52. connecting rod; 53. bearing member; 60. sealing member; 70. damping member.

Detailed ways

The technical solutions in the embodiments of the present invention will be described clearly and completely below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

As shown in FIGS. 1 to 6 , an embodiment of the present invention provides a vibration isolator with high static and low dynamic stiffness characteristics, including: a positive stiffness component 10, the positive stiffness component 10 includes a seat body 11 and a first elastic member 12 disposed in a cavity of the seat body 11; a support portion 20, the support portion 20 abuts against the upper end of the first elastic member 12; a floating portion 30, the floating portion 30 is cooperatively connected with the support portion 20; a negative stiffness component, the negative stiffness component includes an elastic portion 40 and a bearing portion 50 that cooperate with each other, the elastic portion 40 is connected to the support portion 20 and/or the floating portion 30, and the bearing portion 50 is connected to the seat body 11 of the positive stiffness component 10; when the floating portion 30 bears a load and compresses the first elastic member 12, the direction of the force applied by the elastic portion 40 to the bearing portion 50 is inclined or vertically arranged relative to the direction of the elastic force of the first elastic member 12. Specifically, the direction of the interaction force between the elastic portion 40 and the bearing portion 50 changes along the change of the normal direction of the curved surface of the bearing portion 50.

According to the technical solution of this embodiment, a positive stiffness component 10, a support part 20, a floating part 30 and a negative stiffness component are arranged in the vibration isolator. The floating part 30 is used to bear the load. The elastic part 40 of the negative stiffness component is connected to the support part 20 or the floating part 30. The bearing part 50 is connected to the seat 11 of the positive stiffness component 10. When the floating part 30 bears the load and compresses the first elastic part 12, the first elastic part 12 contracts, and the direction of the force applied by the elastic part 40 to the bearing part 50 is inclined relative to the direction of the elastic force of the first elastic part 12. In this way, the elastic force generated by the positive stiffness component 10 and the negative stiffness component is nonlinearly related to the displacement of the floating part 30. In this way, the vibration isolator can simultaneously obtain a lower vibration isolation starting frequency and a higher static bearing capacity, that is, it has a higher static stiffness and a lower dynamic stiffness characteristic (referred to as high static and low dynamic), can isolate low-frequency vibrations, and improve the vibration isolation frequency range of the vibration isolator. The vibration isolator is applied to the rail system, which can improve the vibration isolation frequency range of the rail system, reduce the transmission of low-frequency vibrations, and reduce the impact on the surrounding environment.

In this embodiment, the elastic part 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 part 50. The second elastic member 41 and the pushing member 42 cooperate to generate an interaction force with the bearing part 50. The direction of the force applied by the second elastic member 41 to the bearing part 50 is inclined or vertically arranged relative to the direction of the elastic force of the first elastic member 12.

As shown in FIG2 , when the floating part 30 is subjected to a load, the floating part 30 and the bearing part 50 are relatively displaced, and the displacement of the bearing part 50 causes the second elastic member 41 to extend, exerting a force on the bearing part 50. Through the above arrangement, the force component change along the direction of the elastic force of the first elastic member 12 exerted on the bearing part 50 is nonlinearly related to the change in the size of the second elastic member 41, and the change in the component force is also nonlinearly related to the displacement of the floating part 30, so that the vibration isolator has higher static stiffness and lower dynamic stiffness characteristics, that is, it has the effect of high static and low dynamic. Compared with conventional vibration isolators, it can isolate low-frequency vibrations and improve the vibration isolation frequency range of the vibration isolator. The vibration isolator can isolate low-frequency vibrations less than 20Hz.

Specifically, in this embodiment, the first elastic member 12 can be arranged vertically, and the second elastic member 41 can be arranged horizontally (under no load condition), so that the vibration isolator can better reduce vibration and noise of vertical loads, and is more suitable for rail systems.

As shown in FIG. 1 or FIG. 5 , the bearing portion 50 has a first curved surface 51. During the extension and retraction process of the second elastic member 41, the pusher 42 can abut against different positions of the first curved surface 51. By providing the first curved surface 51, the direction of the force applied by the second elastic member 41 to the bearing portion 50 can be changed as required to meet nonlinear requirements. The first curved surface 51 can be concave, convex, round, or the like.

In this embodiment, the pusher 42 has a second curved surface 421, and the position on the second curved surface 421 abuts against the position on the first curved surface 51. Through the cooperation of the second curved surface 421 and the first curved surface 51, the nonlinear force requirement can be better achieved, thereby achieving the effect of high static and low dynamic.

In this embodiment, the bearing part 50 includes a connecting rod 52 and a bearing member 53, the lower end of the connecting rod 52 is connected to the bottom of the seat body 11, the upper end of the connecting rod 52 is connected to the bearing member 53, and the pushing member 42 is in contact with the bearing member 53. Through the above arrangement, the bearing part 50 can be connected to the positive stiffness component 10, so that the force of the negative stiffness component borne by the bearing part 50 is transmitted to the positive stiffness component 10, so that the positive stiffness component 10 and the negative stiffness component cooperate to reduce the vibration of the load, and at the same time reduce the transmission of vibration to the surrounding environment, thereby reducing the impact on the surrounding environment. Specifically, the force provided by the second elastic member 41 makes the direction of the interaction force generated by the pushing member 42 and the bearing member 53 along the normal direction of the bearing member 53.

It should be noted that the bearing member 53 on the bearing part 50 and the first curved surface 51 on the bearing member 53 can be designed into different shapes according to actual needs, and the shape and sliding mode of the pusher 42 in the elastic part 40 can also be changed in many different ways, such as adding a bearing to change sliding into rolling, or adding a bearing to the front end of the pusher 42 to change the contact sliding between the pusher 42 and the first curved surface 51 of the bearing member 53 into contact rolling, etc. No matter how the shape and mode change, the principle is the method principle of the present invention, and it is within the protection scope.

Specifically, the connecting rod 52 passes through at least a portion of the support part 20, and the support part 20 has an escape hole for escaping the bearing member 53, and the bearing member 53 is threadedly connected or welded to the connecting rod 52. Through the above arrangement, the vibration isolator has a compact structure, a small volume, and is easy to assemble.

In order to ensure the stability of the supporting member 53, anti-loosening washers and anti-loosening nuts need to be installed. The position of the supporting member 53 on the connecting rod 52 can be adjusted. When the supporting member 53 is installed, the lower surface of the supporting member 53 contacts the surface of the pushing member 42 and provides a certain pressure. The second elastic member 41 is compressed due to the existence of pressure and provides a certain rigidity.

In this embodiment, the elastic part 40 is connected to the support part 20, and the elastic part 40 is disposed in the first cavity of the support part 20. This makes the vibration isolator structure compact, and compared with the original vibration isolator, the overall structure changes less, which can reduce the impact on related components and facilitate manufacturing and assembly.

Specifically, the support part 20 includes: a frame 21, the bearing part 50 is passed through the frame 21; a cover plate 22 is arranged on the upper part of the frame 21, a first cavity is provided between the cover plate 22 and the frame 21, the second elastic member 41 is connected to the side wall of the first cavity, and the floating part 30 is connected to the cover plate 22. In this way, the vibration isolator can be compact in structure and have a good effect of reducing vibration and noise.

In this embodiment, the elastic part 40 further includes: a guide structure 43, the guide structure 43 is horizontally arranged in the first cavity, and the second elastic member 41 is arranged in the guide structure 43. The contraction direction of the second elastic member 41 can be guided by the guide structure 43 to better control the direction of the force and facilitate the assembly of the elastic part 40. The guide structure 43 can be set as a groove structure or a cylindrical structure.

As shown in FIG3 and FIG4 , the elastic part 40 can be provided in plurality, and the plurality of elastic parts 40 are distributed in the circumferential direction of the bearing part 50. In this way, the overall influence of the negative stiffness component on the vibration isolator can be improved, the effect of the nonlinear characteristic can be improved, and the vibration isolation frequency range of the vibration isolator can be increased. Moreover, the force on the bearing part 50 can be made more uniform.

In this embodiment, the support part 20 is spaced apart from the seat body 11, and the lower end surface of the support part 20 is arranged corresponding to the upper end surface of the seat body 11. The vibration isolator also includes a sealing member 60, which is sleeved on the support part 20 and the seat body 11 to block the gap between the support part 20 and the seat body 11. The support part 20 is spaced apart from the seat body 11, which can facilitate the displacement of the support part 20 and the floating part 30 when bearing a load. The lower end surface of the support part 20 is arranged corresponding to the upper end surface of the seat body 11. When the load is too large, the lower end surface of the support part 20 can directly contact the upper end surface of the seat body 11 to play a limiting role, so as to avoid excessive displacement of the floating part 30 and excessive deformation of the first elastic member 12, resulting in plastic deformation and damage. In order to ensure effectiveness, the sealing member 60 of this embodiment uses a rubber sealing ring, and is fixed to the seat body 11 and the support part 20 respectively through a throat clamp.

As shown in Figures 1 and 6, the floating part 30 includes a cylinder 31 and an annular support member 32 arranged on the inner wall of the cylinder 31, and the support member 32 has 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 31. The support part 20 includes a frame 21 and a cover plate 22 arranged on the frame 21. Through the relative movement of the support part 20 and the floating part 30, the cover plate 22 can pass through the avoidance groove 321 and move to a position abutting against the lower end surface of the support member 32. With the above arrangement, when assembling the vibration isolator, the support part 20 is rotated so that the protruding part on the cover plate 22 corresponds to the avoidance groove 321, and then moved into the cylinder 31, so that the support part 20 can be inserted under the support member 32, and then the support part 20 is rotated again so that the protruding part on the cover plate 22 is misaligned with the avoidance groove 321, so that the cover plate 22 and the lower end surface of the support member 32 abut, thereby realizing the assembly of the floating part 30 and the support part 20, that is, the support part 20 supports the floating part 30. During construction, the cylinder 31 can be prefabricated inside the concrete track plate.

As shown in FIG1 , the vibration isolator further includes: a damping fluid, which is arranged in the cavity of the seat body 11; a damping member 70, the upper end of which is connected to the support portion 20, and the lower end of which is immersed in the damping fluid. Through the above arrangement, when the support portion 20 is subjected to a load, the vibration generated can be transmitted to the damping fluid through the damping member 70, and the damping effect of the damping fluid can slow down the vibration, thereby achieving the effect of reducing vibration and noise. Specifically, the damping member 70 includes a rod-shaped member and a disc-shaped member arranged below the rod-shaped member, and the upper end of the rod-shaped member is connected to the support portion 20. In order to improve the connection strength and the transmission effect, a plurality of rod-shaped members can be arranged, and the plurality of rod-shaped members are arranged around the bearing portion 50. The damping fluid is poured at a certain height in the seat body 11 to provide the damping coefficient required by the system.

As shown in FIG7 , in the second embodiment of the present invention, different from the above embodiments, the floating part 30 includes a cylinder 31 and a support member 32 disposed on the inner wall of the cylinder 31, the support member 32 is connected to the upper part of the support part 20, and the cylinder 31 has a second cavity above the support member 32, and the elastic part 40 is disposed in the second cavity. The elastic part 40 can be connected to the structure in the floating part 30, and can also be connected to the structure in the support part 20.

Specifically, in this embodiment, the elastic part 40 is connected to the floating part 30, the floating part 30 further includes a first fixing member 33 disposed on the inner wall of the cylinder 31, the second cavity is located between the support member 32 and the first fixing member 33, the elastic part 40 further includes a guide structure 43, the upper part of the guide structure 43 is connected to the first fixing member 33, and the second elastic member 41 is disposed in the guide structure 43. Through the connection between the guide structure 43 and the first fixing member 33, the position setting of the second elastic member 41 and the guidance of the second elastic member 41 can be achieved.

In this embodiment, the floating part 30 further includes: a second fixing member 34, the lower part of the second fixing member 34 is connected to the supporting part 20, and the lower part of the guide structure 43 is connected to the upper part of the second fixing member 34. Through the above arrangement, the components in the vibration isolator can be stably and firmly connected, thereby improving the reliability of the vibration isolator.

In this embodiment, the elastic part 40 further includes: a limiting member 44, which is disposed at the end of the guide structure 43 and is used to limit the second elastic member 41. The limiting member 44 can limit the second elastic member 41, so that the second elastic member 41 is limited to maintain a compressed state and prevent the second elastic member 41 from falling out of the guide structure 43.

Another embodiment of the present invention provides a track system, including a vibration isolator with high static and low dynamic stiffness characteristics, and the vibration isolator is the vibration isolator provided in the above embodiment.

Among the existing vibration reduction technologies, the floating plate track structure is considered to be the track vibration reduction form with the best vibration reduction effect. However, the existing floating plate isolator belongs to a linear vibration isolation system. Due to its structural limitations and material limitations, it cannot have a low vibration isolation starting frequency and a high static load-bearing capacity at the same time. It also cannot adjust its vibration isolation performance in real time according to factors such as different train running speeds and track unevenness. Its vibration isolation frequency range and vibration isolation effect are not satisfactory.

According to the technical solution of this embodiment, a positive stiffness component 10, a support part 20, a floating part 30 and a negative stiffness component are arranged in the vibration isolator. The floating part 30 is used to bear the load. The elastic part 40 of the negative stiffness component is connected to the support part 20 or the floating part 30. The bearing part 50 is connected to the seat 11 of the positive stiffness component 10. When the floating part 30 bears the load and compresses the first elastic part 12, the first elastic part 12 contracts, and the direction of the force applied by the elastic part 40 to the bearing part 50 is inclined relative to the direction of the elastic force of the first elastic part 12. In this way, the elastic force generated by the positive stiffness component 10 and the negative stiffness component is nonlinearly related to the displacement of the floating part 30. In this way, the vibration isolator can simultaneously obtain a lower vibration isolation starting frequency and a higher static bearing capacity, that is, it has a higher static stiffness and a lower dynamic stiffness characteristic (referred to as high static and low dynamic), can isolate low-frequency vibration, improve the vibration isolation frequency range of the vibration isolator and the vibration isolation frequency range of the track system, reduce the transmission of low-frequency vibration, and reduce the impact on the surrounding environment. By applying this technical solution, the natural frequency of the existing vibration isolator and its track system is reduced, and the low-frequency vibration reduction effect and vibration isolation frequency range are improved under the premise of strictly controlling or reducing the dynamic displacement of the track.

The cylinder 31 of the vibration isolator is prefabricated in the concrete track plate. When the train passes by, the cylinder 31 moves downward with the track plate, and the support part 20, the guide structure 43, the second elastic member 41, and the push member 42 move downward at the same time. The seat 11 is placed on the roadbed, and the connecting rod 52 and the bearing member 53 are fixed. The first elastic member 12 with positive stiffness is compressed by pressure to provide stiffness. At this time, because the second elastic member 41 with negative stiffness is originally in a compressed state, as the push member 42 simultaneously descends, the second elastic member 41 begins to relax, providing thrust to the bearing part 50, and the front end of the push member 42 slides downward along the surface of the bearing member 53.

When the train passes, the first elastic member 12 begins to relax and provide thrust, and the support part 20, the guide structure 43, the second elastic member 41, and the pusher 42 move upward simultaneously with the cylinder 31. At this time, the front end of the pusher 42 slides upward along the surface of the bearing member 53, and the second elastic member 41 begins to compress to provide stiffness. The entire system provides nonlinear force due to the cooperation between the bearing member 53 and the pusher 42. The schematic diagram of this embodiment is shown in Figure 2. When the train passes, the negative stiffness component moves downward, the relative positions of the bearing member 53 and the pusher 42 change, and the direction of the force provided by the negative stiffness component changes due to the change in the shape of the contact surface. By utilizing the nonlinear dynamic characteristics of the 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) Realize low-frequency vibration isolation of the floating plate and reduce its low-frequency transmission rate, thereby optimizing the impact of subway and other rail trains on the surrounding environment, people, buildings and precision instruments during operation;

2) Reduce the dynamic displacement of the floating plate in the track system when the train passes, control the deformation of the track system, and reduce the damage such as rail corrugation caused by large deformation of the track structure;

3) The overall structure has the characteristics of high static and low dynamic stiffness, good integrity and easy on-site installation.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall 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.