CN112030622A - Embedded track dynamic vibration absorber - Google Patents
Embedded track dynamic vibration absorber Download PDFInfo
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- CN112030622A CN112030622A CN202010943903.9A CN202010943903A CN112030622A CN 112030622 A CN112030622 A CN 112030622A CN 202010943903 A CN202010943903 A CN 202010943903A CN 112030622 A CN112030622 A CN 112030622A
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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
- E01B19/003—Means for reducing the development or propagation of noise
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Abstract
The invention discloses an embedded type track dynamic vibration absorber which comprises elastic units, mass units and damping units, wherein the elastic units, the mass units and the damping units are arranged on two sides of a rail web of a steel rail, the top of each elastic unit is provided with an opening, one side face of each elastic unit is in contact with the rail web and a bottom side wing of the steel rail, the mass units are filled in the elastic units and are distributed discretely, the mass units are filled with liquid rubber and then cured, the cured upper surfaces of the mass units are flush with two side walls of the elastic units, point contact exists between every two adjacent mass units, and the damping units are attached to the upper surfaces of the elastic units cured by the liquid rubber and the side faces of the elastic units. The dynamic vibration absorber disclosed by the invention adopts the discrete mass units and is solidified in the elastic units through the liquid rubber, so that the point contact among the steel balls is ensured, and the frequency ratio and the mass ratio are ensured. The invention has the advantages of simple structure, good vibration and noise reduction effect, stable performance and wider applicable frequency range, and simultaneously reduces the generation of rail corrugation and prolongs the service life of the steel rail.
Description
Technical Field
The invention relates to a dynamic vibration absorber, in particular to an embedded track dynamic vibration absorber.
Background
With the rapid development of economy and the acceleration of urbanization process, urban rail transit also enters a large development period. The rapid development of rail transit relieves the pressure of urban traffic, promotes the development of cities, but also brings about some problems, particularly noise problems. The noise sources during the operation of the rail train are various, mainly comprise wheel-rail noise, starting and braking noise, noise generated during air intake and exhaust of a compressor, pantograph noise, noise of an air conditioner and a ventilation device, traction noise, noise of a horn of the rail train, noise of a loudspeaker system and the like, wherein the noise sources with larger influence are the traction noise, the wheel-rail noise and the braking noise, the lower section of the running speed of the rail train is generally not more than 100km/h and the overhead line is not more than 120km/h in urban rail transit construction, and actual measurement shows that the wheel-rail noise accounts for the largest proportion in the radiation noise of the rail train at the moment.
The research at home and abroad considers that the wheel-rail noise mainly comprises rolling noise, impact noise and whistling sound. By adopting the wheel noise reduction damping vibration absorber, the squeal can be basically controlled, and by adopting an ultra-long seamless line, the steel rail joint is basically eliminated, so that the wheel rail impact sound is basically controlled, and the rolling sound becomes the main noise in the wheel rail noise. The noise and the vibration are linearly related within the frequency range of 500-2500Hz through analysis, and the steel rail is a main radiator in the range, so that the vibration of the steel rail is effectively inhibited, the vibration acceleration and the vibration frequency of the steel rail are reduced, and the key of noise reduction is realized.
In order to control the vibration and noise of the steel rail, engineers developed various types of vibration and noise reduction products, among which tuned mass vibration absorbers are common, and the method of dynamic vibration absorbers was proposed in 1928 by the aid of Ormond Roidede et al. The principle is that a mass spring resonance system is added on a vibrating object, and the reaction force generated by the additional system during resonance can reduce the vibration of the vibrating object. The dynamic vibration absorber is particularly useful when the excitation force is mainly single frequency or the frequency is very low, and a general vibration isolator is not suitable. It is also possible to cancel vibrations of different frequencies by adding a series of such vibration absorbers. Such as the tuned rail damper disclosed in patent application No. 200480019707.1, which achieves a certain vibration and noise reduction effect. However, in engineering applications, it is found that, since the elastic element is generally made of an elastic material such as rubber in the prior art solutions, and then a mass is built in the elastic element, the effect of the natural frequency ratio (α) on suppressing the vibration of the main system is not considered. In addition, the device only consists of mass and rubber elastic materials, and vibration is amplified by resonance of a secondary vibration system unlike a dynamic vibration absorber, and vibration energy is absorbed by damping, so that the vibration damping effect is reduced. The patent application No. 201310287329.6 discloses a rail vibration absorber, which comprises a connecting frame made into a shape consistent with the non-working surface of the steel rail, wherein the connecting frame comprises at least one vibration absorbing cavity, a mass block and an elastic element are arranged in the connecting frame, a coupling layer is required to be coated between the connecting frame and the non-working surface of the steel rail, and a non-mass-spring system is directly coupled with the steel rail to absorb vibration, so that the designed vibration absorbing frequency is possibly inconsistent with the actual working frequency. The dynamic vibration absorber disclosed in the patent application No. 201921890225.3 of the inventor is composed of an auxiliary mass block, an elastic element such as a metal spring, a damping material and a fastener, and has the advantages that the elastic element is convenient to mount and high in flexibility, mounting requirements under different conditions are met, a vibration absorbing structure with multiple degrees of freedom can be formed, and the like, but the problem of insufficient consideration of inherent frequency ratio exists. Meanwhile, the passive dynamic vibration absorber has obvious use limitation and has good inhibition effect only on single-frequency vibration or vibration with narrow frequency.
In summary, on the basis of the passive dynamic vibration absorber, a dynamic vibration absorber having a better suppression effect under a wider vibration response condition is developed, a larger natural frequency ratio can be obtained, and the suppression capability of a main vibration system is improved to the greatest extent.
Disclosure of Invention
In order to solve the technical problems, the invention provides an embedded track dynamic vibration absorber, so as to achieve the purposes of effectively improving the vibration absorbing effect, reducing the cost and being convenient to install.
In order to achieve the purpose, the technical scheme of the invention is as follows:
the utility model provides an embedded track dynamic vibration absorber, is including arranging elastic element, mass element and the damping unit in the web both sides of rail, elastic element open-top, a side and web and rail bottom flank contact, and inside packing has a plurality of mass elements of discrete distribution, and through the solidification after liquid rubber packing between a plurality of mass elements, and the upper surface after the solidification and elastic element's both sides wall parallel and level, there is the point contact between the adjacent mass element, the damping unit pastes and applies in the upper surface of elastic element after passing through the solidification of liquid rubber to and the non-contact side of elastic element and rail.
In the above scheme, a steel plate is attached to the outer side of the damping unit.
In the scheme, the wall thickness of the elastic unit is 5-20mm, and the elastic unit is made of silicon rubber.
In the scheme, the mass unit is a steel ball, and the diameter of the steel ball is 2-10 mm.
In a further technical scheme, the dynamic vibration absorber is fixed on wing plates on two sides of the steel rail through elastic connecting pieces.
In a further technical scheme, the elastic connecting piece is made of 65 manganese steel.
The invention provides an embedded track dynamic vibration absorber, which is a novel nonlinear damping dynamic vibration absorber-an embedded discrete mass unit dynamic vibration absorber on the basis of the idea of classical simple block type dynamic vibration absorber and particle damping vibration attenuation. The frequency band of the dynamic vibration absorber is expanded by utilizing the damping of the discrete mass unit (steel ball), namely, the discrete mass unit (steel ball) not only plays the role of a dynamic mass block, but also can provide the damping effect of expanding the frequency bandwidth of the dynamic vibration absorber by self friction and collision energy consumption, thereby achieving the effect of broadband vibration reduction. Meanwhile, the elastic unit of the dynamic vibration absorber is used for absorbing vibration and amplifying the motion of each mass unit, so that the vibration reduction capability of the whole mass unit is better exerted.
The elastic unit, the discrete mass unit (steel ball) and the damping unit are organically combined together, the characteristic of good elasticity of the elastic rubber (elastic unit) can be fully exerted, the discrete mass unit filled in the elastic unit provides a better energy consumption effect through collision and friction, and the selected material has the advantages of small influence of physical properties on the environment such as temperature and humidity, high efficiency and stability in vibration damping performance, long service life and the like. The key point is that each mass unit is embedded in the elastic unit and coupled with the main vibration system, and from the vibration absorption perspective, the elastic coupling vibration absorption of each discrete mass unit is formed, which is beneficial to improving the natural frequency ratio alpha of the vibration absorber in the rail main vibration system; and meanwhile, the sum of all the discrete mass units ensures the requirement of the mass ratio mu of the vibration absorber. Finally, from the energy absorption perspective, not only the liquid rubber filled in the gap of the discrete mass unit, but also the self friction and collision energy consumption of the discrete mass unit can provide the damping effect of expanding the frequency bandwidth of dynamic vibration absorption.
As is well known, three main parameters in the design of dynamic vibration absorbers are: mu (mass ratio),
(damping ratio), α (natural frequency ratio), and α has the greatest influence on the primary vibration system. The number and the diameter of the steel balls are determined according to mu (mass ratio) and alpha (natural frequency ratio of vibration of a main vibration system and a vibration absorber), and the method comprises the following specific steps:
the suppression of main system vibration by alpha is more than
The degree of the inhibition effect of alpha on the main system vibration is more than mu;
And has the following relationship:
in the formula (I), the compound is shown in the specification,
representing the amplitude of the primary system vibration, and λ representing the frequency ratio;strepresenting the vibration and static displacement of the main vibration system.
Therefore, the appropriate mu is selected,
alpha value of can
Minimum, i.e., the amplitude of the main system vibration is minimal.
Therefore, the embedded discrete mass unit dynamic vibration absorber effectively considers three main parameters in the design of the dynamic vibration absorber, particularly improves the inherent frequency ratio, and greatly improves the inhibiting capability of the vibration absorber on a main vibration system.
The invention realizes breakthrough on the integrated structure, can form auxiliary vibration systems with different frequencies by selecting rubber materials with different elastic moduli and small auxiliary discrete mass units (steel balls with different masses) with different masses, increases the bandwidth of the vibration absorber, and can form a multi-power vibration absorber structure.
The silicon rubber elastic structure (elastic unit) can transmit vibration energy to the steel balls inside in different directions, the steel balls reciprocate along with the system in the closed cavity, collision and friction between the steel balls, namely the steel balls and the steel balls, between boundaries can consume a large amount of system energy and enable the system to reduce vibration amplitude, and the steel ball group shows strong damping characteristics on the whole. The energy dissipation generated by the contact of the steel balls can be divided into three parts, namely normal, tangential and rolling. The smaller diameter of the steel ball can improve the energy dissipation rate to a certain extent and make the system tend to balance more quickly, but the effect is not obvious. Tests show that the steel ball has the best effect when the diameter is selected to be between 2 and 10 mm.
The elastic unit is convenient to install and high in flexibility, meets the installation requirements under different conditions, and can form a multi-freedom vibration absorption structure. More discrete mass units can be arranged under the same space condition, the mass ratio is increased, and the vibration reduction effect of the vibration absorption device is further effectively improved.
The discrete mass unit, the elastic unit and the damping unit can be independently designed according to a target vibration source, respective characteristic optimization is realized, mass production is facilitated, parameters are stable, the production process is simple, the cost is reduced to a great extent, and popularization and application are facilitated.
The vibration absorber is a finished product when leaving a factory according to the application direction, the effective working frequency range of the product can be set before leaving the factory, field debugging is not needed, and the vibration absorber is installed only by installing the elastic connecting piece, so that the vibration absorber is safe and reliable.
In conclusion, the dynamic vibration absorber has the advantages of simple structure, good vibration and noise reduction effects, stable performance, wider applicable frequency domain range, long service life and high cost performance, and simultaneously reduces the generation of rail corrugation and prolongs the service life of the steel rail. The dynamic vibration absorber can be applied to different occasions only by adjusting the shape of the whole structure and the connection mode of the dynamic vibration absorber, and has very wide market application prospect.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below.
Fig. 1 is a schematic structural diagram of an embedded track dynamic vibration absorber according to an embodiment of the present invention;
FIG. 2 is a schematic structural diagram of a cured elastic unit on the right side of a rail according to an embodiment of the present invention;
FIG. 3 is a schematic structural view of a left side of a rail with a cured resilient unit according to an embodiment of the present invention;
FIG. 4 is a schematic view of an embodiment of the disclosed elastic connecting member;
fig. 5 is a first schematic view illustrating an installation structure of an embedded track dynamic vibration absorber according to an embodiment of the present invention;
fig. 6 is a schematic view of a mounting structure of an embedded track dynamic vibration absorber according to an embodiment of the present invention.
In the figure, 1, an elastic unit; 2. a damping unit; 3. a steel plate; 4. a steel rail; 5. a steel ball; 6. an elastic connecting member; 7. liquid rubber.
Detailed Description
The technical solution 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.
The invention provides an embedded type track dynamic vibration absorber, which comprises an elastic unit 1, a damping unit 2 and a mass unit (steel ball 5) which are arranged on two sides of a rail web of a steel rail 4, as shown in figure 1.
Firstly, an elastic unit 1 is manufactured, the shape of the side surface and the bottom surface of the elastic unit 1, which are contacted with the rail web of the steel rail 4 and the side wing at the bottom of the steel rail, are the same as the surface shape of the steel rail 4, and the rest surfaces are planes, and the manufacturing is realized by hot-pressing vulcanization molding through a mold. The wall thickness of the elastic unit 1 is 5-20mm, the material is silicon rubber, and the elastic unit is empty before the steel ball 5 is filled. The selection of the Shore hardness and the elastic modulus is related to the size of the steel ball 5, and the combination of the Shore hardness and the elastic modulus determines the frequency and the bandwidth of the vibration absorber.
Then, filling discrete mass units, namely steel balls 5, the diameter of the steel balls 5 is 2-10mm, in the elastic unit 1, wherein the number and the diameter of the steel balls 5 are determined according to mu (mass ratio) and alpha (natural frequency ratio); the mass units may also be some other particulate matter. Then, the inside of the elastic unit 1 in which the steel balls 5 are placed is filled with liquid rubber 7 (the liquid rubber material can be the same as or different from the material of the elastic unit 1), the liquid rubber 7 is made to fill all gaps between the steel balls 5 and the upper end surface of the elastic unit 1 is made to be flat, finally, the liquid rubber is solidified into a whole, and when the filling material is added, the liquid filling material is made to fully fill the gaps between the steel balls through a vibrating device before solidification, and point contact between the steel balls is ensured. When the steel balls are solidified, whether the steel balls are solidified by heating or normal temperature, the filling material has the shrinkage rate of about 2-3% and can ensure the contact between the steel balls. Thus, not only can collision and friction be ensured at the time of forced vibration, but also damping absorption with the filler material is increased. As shown in fig. 2 and 3. When the liquid rubber 7 and the elastic unit 1 are made of the same material, they are cured into a whole, as shown in fig. 5 and 6, and when the material is different, as shown in fig. 1. In order to ensure that the structure is not deformed in the implementation process, the deformation is carried out in a mold, and the shape structure of the mold is consistent with the shape of the elastic unit 1.
The damping unit 2 has high viscosity and is attached to the top surface of the elastic unit 1 and the side surface which is not in contact with the steel rail, in order to further improve the system damping, organic micromolecules containing hydroxyl groups can be adopted for hybridization of the high-damping rubber composite material, the damping material not only improves the effective damping temperature range, but also can adjust the viscosity of the damping material by the organic micromolecules, the wettability of the damping material on a base material is improved, the bonding force is improved, the rubber material has good self-adhesion, and great convenience is brought to the forming processing and the site construction of the composite material.
The damping unit 2 adopts a saturated rubber material as a base material, has excellent ageing resistance and the characteristics of water resistance, ethanol resistance, chemical resistance and the like, and has the characteristics of chemical stability and good thermal stability to acid and alkali.
In order to effectively utilize the damping unit 2, a thin steel plate 3 is applied on the outside of the damping unit 2 to form the whole dynamic vibration absorber, and then the dynamic vibration absorber is fixed on a non-working surface along the vertical direction of the steel rail 4 or the transverse direction of the steel rail 4 through an elastic connecting piece 6.
In order to increase the reliability of the connection between the dynamic vibration absorber and the vibration surface of the rail 4, connection reinforcing structures may be further provided on both sides of the thin steel plate 3. The connection reinforcing structure comprises a surface convex-concave structure, a surface knurling structure or a surface galling structure.
During installation, the dynamic vibration absorbers are placed on the side wings at the bottom of the track, and are firstly clamped by a woodworking clamping tool and fixed by the elastic connecting pieces 6 shown in figure 4, and each group of dynamic vibration absorbers are respectively fixed by a pair of elastic connecting pieces 6 at two ends, and then the woodworking clamping tool is removed after the dynamic vibration absorbers are fixed as shown in figures 5 and 6. The elastic connecting piece 6 is made of 65 manganese steel, and the manufacturing process comprises the steps of annealing, forming into a required shape, quenching and normalizing.
The length of the dynamic vibration absorber is set according to the distance between sleepers, and is usually about half of the distance between sleepers. In practical application, the control of different frequencies and bandwidth vibration can be realized by optimizing the elastic modulus of the elastic unit 1 and the size and the number of the auxiliary mass bodies, namely the steel balls 5.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (6)
1. The utility model provides an embedded track dynamic vibration absorber, its characterized in that, is including arranging elastic element, mass element and the damping unit in the web of a rail both sides of rail, elastic element open-top, a side contacts with web of a rail and rail bottom flank, and inside packing has a plurality of mass element of discrete distribution, and through the solidification after liquid rubber packing between a plurality of mass element, and the upper surface after the solidification and the both sides wall parallel and level of elastic element, there is the point contact between the adjacent mass element, the damping unit pastes in the upper surface after the elastic element passes through the solidification of liquid rubber to and the non-contact side of elastic element and rail.
2. The embedded rail dynamic vibration absorber of claim 1, wherein a steel plate is attached to the outside of the damping unit.
3. The embedded rail dynamic vibration absorber of claim 1, wherein the wall thickness of the elastic unit is 5-20mm and the material is silicone rubber.
4. The embedded rail dynamic vibration absorber of claim 1 wherein the mass elements are steel balls having a diameter of 2-10 mm.
5. The embedded track power absorber according to any one of claims 1 to 4, wherein the power absorber is fixed to the two side flanges of the rail by elastic connecting members.
6. The embedded rail dynamic vibration absorber of claim 5 wherein said elastic connecting member is made of 65 manganese steel.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010943903.9A CN112030622A (en) | 2020-09-10 | 2020-09-10 | Embedded track dynamic vibration absorber |
| PCT/CN2021/108691 WO2022052655A1 (en) | 2020-09-10 | 2021-07-27 | Embedded rail dynamic vibration absorber |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010943903.9A CN112030622A (en) | 2020-09-10 | 2020-09-10 | Embedded track dynamic vibration absorber |
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| CN112030622A true CN112030622A (en) | 2020-12-04 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113106792A (en) * | 2021-04-19 | 2021-07-13 | 晟建科技集团有限公司 | Linear particle steel rail vibration absorber |
| WO2022052655A1 (en) * | 2020-09-10 | 2022-03-17 | 青岛声达技术有限公司 | Embedded rail dynamic vibration absorber |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2401139B (en) * | 2003-04-30 | 2006-07-12 | Corus Uk Ltd | Rail dampers |
| CN201722566U (en) * | 2010-07-14 | 2011-01-26 | 中国船舶重工集团公司第七二五研究所 | Vibration absorber for rail web of steel rail |
| CN105908581B (en) * | 2016-04-21 | 2018-06-29 | 同济大学 | A kind of composite particles damper for reducing rail vibration noise |
| CN211057515U (en) * | 2018-04-28 | 2020-07-21 | 洛阳双瑞橡塑科技有限公司 | Steel rail damper |
| CN210134297U (en) * | 2019-04-11 | 2020-03-10 | 陕西九域通创轨道系统技术有限责任公司 | Device for inhibiting vibration noise of steel rail |
| CN211285085U (en) * | 2019-11-05 | 2020-08-18 | 青岛声达技术有限公司 | Dynamic vibration absorber |
| CN212335660U (en) * | 2020-09-10 | 2021-01-12 | 青岛声达技术有限公司 | Embedded track dynamic vibration absorber |
| CN112030622A (en) * | 2020-09-10 | 2020-12-04 | 青岛声达技术有限公司 | Embedded track dynamic vibration absorber |
-
2020
- 2020-09-10 CN CN202010943903.9A patent/CN112030622A/en active Pending
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- 2021-07-27 WO PCT/CN2021/108691 patent/WO2022052655A1/en active Application Filing
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022052655A1 (en) * | 2020-09-10 | 2022-03-17 | 青岛声达技术有限公司 | Embedded rail dynamic vibration absorber |
| CN113106792A (en) * | 2021-04-19 | 2021-07-13 | 晟建科技集团有限公司 | Linear particle steel rail vibration absorber |
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| WO2022052655A1 (en) | 2022-03-17 |
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