WO2022052655A1 - 一种嵌入式轨道动力吸振器 - Google Patents
一种嵌入式轨道动力吸振器 Download PDFInfo
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- WO2022052655A1 WO2022052655A1 PCT/CN2021/108691 CN2021108691W WO2022052655A1 WO 2022052655 A1 WO2022052655 A1 WO 2022052655A1 CN 2021108691 W CN2021108691 W CN 2021108691W WO 2022052655 A1 WO2022052655 A1 WO 2022052655A1
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- rail
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- dynamic vibration
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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
Definitions
- the invention relates to a dynamic vibration absorber, in particular to an embedded track dynamic vibration absorber.
- wheel-rail noise is mainly composed of rolling noise, impact noise and screeching noise.
- the use of wheel noise reduction damping and vibration absorbers can basically control the whistling sound.
- the ultra-long seamless line is used to basically eliminate the rail joints, so that the wheel-rail impact sound is basically controlled, so the rolling sound becomes one of the wheel-rail noise.
- main noise The analysis shows that the noise and vibration are linearly related in the frequency range of 500-2500Hz, and the rail is the main radiator in this range. Therefore, effectively suppressing the vibration of the rail and reducing the vibration acceleration and frequency of the rail are the keys to noise reduction.
- 201310287329.6 includes a connection frame made in the same shape as the non-working surface of the rail, the connection frame includes at least one vibration absorbing cavity, the mass block and the elastic element are both arranged in the connection frame, and then The installation coupling layer needs to be coated between the connecting frame and the non-working surface of the rail, and the non-mass-spring system is directly coupled to the rail to absorb vibration, which may cause the design vibration absorption frequency to be inconsistent with the actual working frequency.
- a dynamic vibration absorber disclosed by myself in patent application No. 201921890225.3 is composed of elastic elements such as auxiliary mass blocks, metal springs, damping materials and fasteners. The elastic elements are easy to install and flexible, and meet the installation requirements under different conditions.
- this passive dynamic vibration absorber has obvious limitations in use, and only has a better effect on suppressing vibration response of a single frequency or a very narrow frequency.
- the present invention provides an embedded orbital dynamic vibration absorber, so as to effectively improve the vibration absorption effect, reduce the cost and facilitate installation.
- An embedded rail dynamic vibration absorber comprising elastic units, mass units and damping units arranged on both sides of a rail waist of a rail, the elastic unit is open at the top, one side is in contact with the rail waist and the bottom flanks of the rail, and the interior is filled with discrete Distributed multiple mass units, the multiple mass units are filled with liquid rubber and then cured, and the cured upper surface is flush with the two side walls of the elastic unit, and there is point contact between adjacent mass units, the damping The unit is attached to the upper surface of the elastic unit after being cured by the liquid rubber, and the side surface of the elastic unit which is not in contact with the rail.
- the outside of the damping unit is affixed with a steel plate.
- the wall thickness of the elastic unit is 5-20mm, and the material is silicone rubber.
- the mass unit is a steel ball, and the diameter of the steel ball is 2-10 mm.
- the dynamic vibration absorber is fixed on the two side wings of the rail through elastic connectors.
- the elastic connecting piece is made of 65 manganese steel.
- the embedded orbital dynamic vibration absorber provided by the present invention proposes a novel nonlinear damping dynamic vibration absorber, an embedded discrete mass unit dynamic vibration absorber, on the basis of the classical single-mass block type dynamic vibration absorber and particle damping vibration reduction ideas.
- the damping of the discrete mass element (steel ball) is used to expand the frequency band of the dynamic vibration absorber, that is, the discrete mass element (steel ball) not only acts as a dynamic mass block, but also can provide extended dynamic vibration absorption due to its own friction and collision energy consumption. Damping effect of frequency bandwidth, so as to achieve the effect of broadband vibration reduction.
- the elastic unit of the dynamic vibration absorber is used to absorb and amplify the movement of each mass unit, so as to better exert the vibration reduction capability of the overall mass unit.
- the invention organically combines the elastic unit, the discrete mass unit (steel ball) and the damping unit, which can give full play to the good elasticity of the elastic rubber (elastic unit), and the discrete mass unit filled in the elastic unit can pass through collision and friction. It can provide better energy consumption effect.
- the selected materials have the advantages of less physical properties affected by the environment such as temperature and humidity, more efficient and stable vibration reduction performance, and long service life.
- each mass element is embedded in the elastic element and coupled with the main vibration system. From the perspective of vibration absorption, the elastic coupling vibration absorption of each discrete mass element is formed, which is beneficial to the natural frequency ratio ⁇ of the vibration absorber in the orbit main vibration system.
- the sum of all discrete mass elements guarantees the requirement of the mass ratio ⁇ of the vibration absorber.
- ⁇ mass ratio
- ⁇ natural frequency ratio
- ⁇ natural frequency ratio
- the degree of influence on the suppression of the main system vibration is greater than ⁇ .
- ⁇ represents the frequency ratio
- ⁇ st represents the vibration static displacement of the main system.
- the embedded discrete mass unit dynamic vibration absorber of the device of the present invention effectively takes into account the three main parameters in the design of the dynamic vibration absorber, especially the improvement of the natural frequency ratio, which greatly improves the vibration absorber's effect on the main vibration.
- the inhibition ability of the system is
- the invention achieves a breakthrough in the integrated structure.
- a secondary vibration system with different frequencies can be formed, and a vibration absorber can be added.
- the bandwidth can form multiple dynamic vibration absorber structures.
- the silicone rubber elastic structure can transmit vibration energy to the inner steel ball in different directions.
- the steel ball reciprocates with the system in the closed cavity, and the collision between the steel ball - steel ball, steel ball - boundary And friction will consume a lot of system energy and reduce the vibration amplitude of the system, and the steel ball group shows strong damping characteristics as a whole.
- the energy dissipation caused by the contact of steel balls can be divided into three parts: normal direction, tangential direction 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 equilibrium faster, but the effect is not obvious.
- the test shows that the best effect is to choose the diameter of the steel ball between 2-10mm.
- the elastic unit is easy to install and has strong flexibility, meets the installation requirements under different conditions, and can form a vibration-absorbing structure with multiple degrees of freedom. Under the same space conditions, more discrete mass units can be set to increase the mass ratio, thereby effectively improving the vibration reduction effect of the vibration absorption device.
- the discrete mass unit, elastic unit, and damping unit can be independently designed according to the target vibration source to achieve the optimization of their respective characteristics, which is convenient for mass production, and the parameters are stable, the production process is simple, the cost is greatly reduced, and it is easy to popularize and apply.
- the vibration absorber is already a finished product when it leaves the factory.
- the effective working frequency band of the product can be set before leaving the factory. It does not need on-site debugging. It only needs to install elastic connectors for installation, which is safe and reliable.
- the dynamic vibration absorber of the present invention has simple structure, good vibration and noise reduction effect, stable performance, wider applicable frequency range, long service life, and high cost performance. It can be used in different occasions only by adjusting the whole structure shape and connection method of the dynamic vibration absorber, and its market application prospect is very broad.
- FIG. 1 is a schematic structural diagram of an embedded orbital dynamic vibration absorber disclosed in an embodiment of the present invention
- FIG. 2 is a schematic structural diagram of a cured elastic unit on the right side of the rail disclosed in an embodiment of the present invention
- FIG. 3 is a schematic structural diagram of a cured elastic unit on the left side of the rail disclosed in an embodiment of the present invention
- FIG. 4 is a schematic structural diagram of an elastic connector disclosed in an embodiment of the present invention.
- FIG. 5 is a schematic diagram 1 of the installation structure of the embedded track dynamic vibration absorber disclosed in the embodiment of the present invention.
- FIG. 6 is a second schematic diagram of the installation structure of the embedded track dynamic vibration absorber disclosed in the embodiment of the present invention.
- the present invention provides an embedded rail dynamic vibration absorber, as shown in FIG. 1 , comprising an elastic unit 1 , a damping unit 2 and a mass unit (steel ball 5 ) arranged on both sides of the rail waist of the steel rail 4 .
- the elastic unit 1 is fabricated.
- the side and bottom surfaces of the elastic unit 1 in contact with the rail waist of the rail 4 and the bottom flanks of the rail are the same as the surface shape of the rail 4, and the rest of the surface is flat.
- the wall thickness of the elastic unit 1 is 5-20mm, the material is silicone rubber, and it is empty before filling the steel ball 5 .
- the selection of Shore hardness and elastic modulus is related to the size of the steel ball 5, and the cooperation of the two determines the frequency and bandwidth of the vibration absorber.
- the elastic unit 1 is filled with discrete mass units---steel ball 5, the diameter of the steel ball 5 is 2-10mm, and the number and diameter of the steel ball 5 are determined according to ⁇ (mass ratio) and ⁇ (natural frequency ratio);
- the mass unit can also be some other granular substances.
- the liquid filling material When adding the filling material, the liquid filling material is fully filled into the gap between the steel balls by the vibration device before curing, and the point contact between the steel balls is ensured. . No matter whether it is cured by heating or curing at room temperature, the filler material has a shrinkage rate of about 2% to 3%, which can ensure the contact between the steel balls. Therefore, not only collision and friction can be ensured during forced vibration, but also the damping absorption with the filling material is increased. As shown in Figure 2 and Figure 3. When the material of the liquid rubber 7 and the elastic unit 1 are the same, they will be solidified as a whole, as shown in FIG. 5 and FIG. 6 , and when the material is different, as shown in FIG. 1 . In order to ensure that the structure does not deform during the above implementation process, it needs to be carried out in a mold, and the shape and structure of the mold should be consistent with the shape of the elastic unit 1 .
- the damping unit 2 itself has high viscosity and is attached to the top surface of the elastic unit 1 and the side surface that is not in contact with the rail.
- a high-damping rubber composite material hybridized with small organic molecules containing hydroxyl groups can be used.
- the damping material not only improves the effective damping temperature range, but also the small organic molecules can adjust the viscosity of the damping material, improve the wettability of the damping material to the substrate, improve the adhesive force, and make the rubber material have good self-adhesion, which gives The molding processing and on-site construction of composite materials bring great convenience.
- the damping unit 2 uses saturated rubber material as the base material, which has excellent anti-aging properties, water resistance, ethanol resistance and chemical resistance, chemical stability to acid and alkali, and good thermal stability.
- a thin steel plate 3 is applied outside the damping unit 2 to form the whole dynamic vibration absorber, and then fixed on the non-working surface along the vertical direction of the rail 4 or the transverse direction of the rail 4 through the elastic connecting piece 6.
- connection strengthening structures may also be provided on both sides of the thin steel plate 3 .
- the connection strengthening structure includes a surface convex-concave structure, a surface knurling structure or a surface roughening structure.
- Each group of dynamic vibration absorbers has a pair of elastic connections at both ends. Fix the piece 6, as shown in Figure 5 and Figure 6, and then remove the woodworking card tool after fixing.
- the elastic connector 6 is made of 65 manganese steel, and the production process is first annealing - making the desired shape - quenching - normalizing.
- the length of the dynamic vibration absorber is set according to the spacing of the sleepers, which is usually about half of the spacing of the sleepers.
- the control of vibration of different frequencies and bandwidths can be realized by optimizing the elastic modulus of the elastic unit 1 and the size and quantity of the auxiliary mass body-steel balls 5 .
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Abstract
本发明公开了一种嵌入式轨道动力吸振器，包括布置于钢轨的轨腰两侧的弹性单元、质量单元和阻尼单元，弹性单元顶部开口，一侧面与轨腰和钢轨的底部侧翼接触，内部填充有离散分布的多个质量单元，多个质量单元之间通过液态橡胶填充后固化，且固化后的上表面与弹性单元的两侧壁平齐，相邻的质量单元之间存在点接触，阻尼单元贴敷于弹性单元通过液态橡胶固化后的上表面，以及弹性单元与钢轨不接触的侧面。本发明所公开的动力吸振器采用离散的质量单元通过液态橡胶固化在弹性单元内部，保证了钢球之间的点接触，同时保证了频率比和质量比。本发明结构简单，减振降噪效果好，性能稳定，适用频域范围更广，同时降低钢轨波磨的产生，延长钢轨的使用寿命。
Description
本发明涉及一种动力吸振器，特别涉及一种嵌入式轨道动力吸振器。
随着经济的飞速发展和城市化进程的加快，城市轨道交通也进入大发展时期。轨道交通的快速发展缓解了城市交通压力、促进了城市的发展，但也带来了一些问题，特别是噪声问题。轨道列车运行时噪声源多种多样，主要有轮轨噪声，启动、制动噪声，压缩机进排气时产生的噪声，受电弓噪声，空调、通风设备噪声，牵引噪声，轨道列车喇叭、扬声器系统噪声等，其中影响较大的噪声源为牵引噪声、轮轨噪声和制动噪声，在城市轨道交通建设中，轨道列车的运行时速地下段一般不超过100km/h，高架线不超过120km/h，实测表明，此时轮轨噪声在轨道列车辐射噪声中占比最大。
国内外研究认为，轮轨噪声主要有滚动噪声、冲击噪声和尖啸声组成。采用车轮降噪阻尼吸振器，尖啸声基本能得到控制，采用超长无缝线路，基本上消灭了钢轨接头，使得轮轨撞击声也基本得到了控制，因而滚动声成为轮轨噪声中的主要噪声。通过分析得到噪声和振动在500-2500Hz频率范围内线性相关，且钢轨在此范围内是主要的辐射体，因此有效抑制钢轨振动，减小钢轨的振动加速度和频率，是降噪的关键。
为控制钢轨的振动及噪声，工程人员研发了多种类型的减振降噪产品，其中调谐质量吸振器较为常见，奥蒙德罗伊德等在1928年提出了动力吸振器的方法。其原理是在振动物体上附加质量弹簧共振系统，这种附加系统在共振时产生的反作用力可使振动物体的振动减小。当激发力以单频为主，或频率很低，不宜采用一般隔振器时，动力吸振器特别有用。如附加一系列的这种吸振器，还可以抵销不同频率的振动。例如专利申请号200480019707.1中公开的铁轨调谐减振器，此类产品可以实现一定的减振降噪效果。但是工程应用中发现，由于现有的此类技术方案中普遍利用橡胶等弹性材料制成弹性元件，然后在弹性元件中内置质量块，这种方式没有考虑固有频率比(α)对主系统振动的抑制影响作用。此外，该类装置仅由质量和橡胶类弹性材料组成，不像动力吸振器那样通过副振动系统的共振使振动增幅后，利用阻尼将振动能量吸收掉，因而制振效果会有所降低。而专利申请号201310287329.6中公开的一种轨道吸振器，包括与钢轨非工作表面制作成形状一致的连接框架，连接框架中包含至少一 个吸振腔，质量块和弹性元件均设置在连接框架内，再由连接框架和钢轨非工作表面之间需涂覆安装耦合层，而非质量—弹簧系统直接与钢轨耦合吸振，可能会导致设计吸振频率与实际工作频率不符。本人在专利申请号201921890225.3中公开的一种动力吸振器，采用辅助质量块、金属弹簧等弹性元件以及阻尼材料和扣件组成，具有弹性元件安装方便、灵活性强，满足不同条件下的安装要求，可形成自多由度的吸振结构等优点，但同样存在固有频率比考虑不足的问题。同时，这种被动式动力吸振器的使用局限性比较明显，仅对单一频率振动或频率很窄的振动响应抑制效果较好。
综上所述，在被动式动力吸振器的基础上，研制出在较宽的振动响应情况下都有较好的抑制效果的动力吸振器，同时能够得到较大的固有频率比，最大程度的提高对主振系统的抑制能力是本发明的目的。
发明内容
为解决上述技术问题，本发明提供了一种嵌入式轨道动力吸振器，以达到有效提高吸振效果、降低成本、安装方便的目的。
为达到上述目的，本发明的技术方案如下：
一种嵌入式轨道动力吸振器，包括布置于钢轨的轨腰两侧的弹性单元、质量单元和阻尼单元，所述弹性单元顶部开口，一侧面与轨腰和钢轨底部侧翼接触，内部填充有离散分布的多个质量单元，多个质量单元之间通过液态橡胶填充后固化，且固化后的上表面与弹性单元的两侧壁平齐，相邻的质量单元之间存在点接触，所述阻尼单元贴敷于弹性单元通过液态橡胶固化后的上表面，以及弹性单元与钢轨不接触的侧面。
上述方案中，所述阻尼单元外侧贴有钢板。
上述方案中，所述弹性单元的壁厚为5-20mm，材料为硅橡胶。
上述方案中，所述质量单元为钢球，钢球直径为2-10mm。
进一步的技术方案中，所述动力吸振器通过弹性连接件固定于钢轨的两侧翼板上。
更进一步的技术方案中，所述弹性连接件采用65锰钢制作。
本发明提供的嵌入式轨道动力吸振器是在经典单质块式动力吸振器和颗粒阻尼减振思想的基础上，提出一种新型的非线性阻尼动力吸振器—嵌入式离散质量单元动力吸振器。利用离散质量单元(钢球)的阻尼来扩展动力吸振器的频带，即离散的质量单元(钢球)不仅起到动力质量块的作用，而且自身的摩擦和碰撞耗能也能提供扩展动力吸振频率带宽的阻尼效 应，从而达到宽频带减振的效果。同时利用动力吸振器的弹性单元吸振放大各质量单元的运动，更好的发挥总体质量单元的减振能力。
本发明将弹性单元、离散质量单元(钢球)以及阻尼单元有机的结合在一起，可以充分发挥弹性橡胶(弹性单元)的弹性好的特点，填充在弹性单元中的离散质量单元通过碰撞和摩擦作用提供更优的耗能效果，选用材料具备物理性能受温湿度等环境影响小，减振性能更高效稳定，使用寿命长等优势。关键在于结构上各质量单元嵌入在弹性单元内与主振动系统耦合，从吸振角度来看，形成每个离散质量单元的弹性耦合吸振，这有利于在轨道主振系统中吸振器固有频率比α的提高；同时所有离散质量单元的总和又保证了吸振器质量比μ的要求。最终从能量吸收的角度来看，不仅有填充在离散质量单元缝隙的液态橡胶，离散质量单元自身的摩擦和碰撞耗能也能提供扩展动力吸振频率带宽的阻尼效应。
众所周知，在动力吸振器的设计上三个主要参数是：μ(质量比)、
(阻尼比)、α(固有频率比)，而且α对主振系统的影响最大。本发明的钢球的数量和直径根据μ(质量比)和α(主振系统与吸振器振动的固有频率比)确定，具体如下：
α对主系统振动的抑制影响作用程度大于
α对主系统振动的抑制影响作用程度大于μ；
并且有如下关系：
式中，
代表主系统振动的振幅，λ代表频率比；δ
st代表主振系统振动静位移。
因此，选取适当的μ，
α值，可以使
最小，即使主系统振动的振幅最小。
由此看来，本发明装置嵌入式离散质量单元动力吸振器有效的考虑到了动力吸振器的设计上三个主要参数，尤其是固有频率比的提高，极大程度的提高了吸振器对主振系统的抑制能力。
本发明在一体化结构上实现突破，可通过选择不同弹性模量的橡胶材料以及质量不同的小辅助的离散质量单元(不同质量的钢球)，形成不同频率的副振系统，增加了吸振器的带宽，可构成多重动力吸振器结构。
硅橡胶弹性结构(弹性单元)可以在不同方向传递振动能量到内部的钢球，钢球在封闭空腔内随系统作往复运动，钢球——钢球、钢球——边界之间的碰撞和摩擦会大量消耗系统能量并使系统降低振动幅值，钢球群体在整体上表现出很强的阻尼特性。钢球接触产生的能量耗散可以分为法向、切向和滚动三个部分。钢球直径变小可以在一定程度上提高能量耗散率并使系统更快趋于平衡，但效果并不明显。试验表明钢球的直径选择2-10mm之间效果最好。
弹性单元安装方便、灵活性强，满足不同条件下的安装要求，可形成自多由度的吸振结构。在相同空间条件下可以设置更多的离散质量单元，增加质量比，进而有效提高吸振装置的减振效果。
离散质量单元、弹性单元、阻尼单元可以按照目标振源独立设计，实现各自特性优化，便于大批量生产，而且参数稳定，生产工艺简单，很大程度的降低成本，便于推广应用。
根据应用方向吸振器出厂时就已是成品，可以在出厂前对产品的有效工作频段进行设定，无需现场调试，只需安装弹性连接件进行安装，安全可靠。
综上，本发明动力吸振器的结构简单，减振降噪效果好，性能稳定，适用频域范围更广，使用寿命长，性价比高，同时降低钢轨波磨的产生，延长钢轨的使用寿命。只需调动力吸振器整结构形状和连接方式，就可应用于不同场合，其市场应用前景十分广阔。
为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍。
图1为本发明实施例所公开的一种嵌入式轨道动力吸振器结构示意图；
图2为本发明实施例所公开的钢轨右侧的固化后的弹性单元结构示意图；
图3为本发明实施例所公开的钢轨左侧的固化后的弹性单元结构示意图；
图4为本发明实施例所公开的弹性连接件结构示意图；
图5为本发明实施例所公开的嵌入式轨道动力吸振器安装结构示意图一；
图6为本发明实施例所公开的嵌入式轨道动力吸振器安装结构示意图二。
图中，1、弹性单元；2、阻尼单元；3、钢板；4、钢轨；5、钢球；6、弹性连接件；7、液态橡胶。
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述。
本发明提供了一种嵌入式轨道动力吸振器，如图1所示，包括布置于钢轨4的轨腰两侧的弹性单元1、阻尼单元2和质量单元(钢球5)。
首先制作弹性单元1，弹性单元1与钢轨4的轨腰和钢轨底部侧翼接触的侧面和底面与钢轨4的表面形状相同，其余表面为平面，制作是通过模具热压硫化成型。弹性单元1的壁厚为5-20mm，材料为硅橡胶，在填充钢球5前是空的。邵氏硬度和弹性模量的选择与钢球5的大小有关，两者的配合与决定吸振器频率和带宽。
然后，在弹性单元1内填充离散的质量单元---钢球5、钢球5直径为2-10mm，钢球5的数量和直径根据μ(质量比)和α(固有频率比)确定；质量单元也可以为其他的一些颗粒状物质。然后在放入钢球5的弹性单元1的内部注满液态橡胶7(液态橡胶材质可与弹性单元1的材质相同也可以不同)，要使液态橡胶7充满所有钢球5之间的缝隙并使得弹性单元1的上端表面平整，最后将液态橡胶固化成为一体，加入填充材料时，在固化前通过振动装置使液态填充材料充分填入钢球间的缝隙，并保证钢球之间的点接触。固化时不论是采用加热固化还是采用常温固化，填充材料都有大约2％～3％的收缩率能够确保钢球之间的接触。因此，在受迫振动时不仅能够保证碰撞和摩擦，而且还增加了和填充材料的阻尼吸收。如图2和图3所示。当液态橡胶7与弹性单元1材质相同时，将固化为一体，如图5和图6所示，当材质不同时，如图1所示。为保证上述实施过程中结构不产生形变，需要在一个模具中进行，该模具的外形结构应与弹性单元1的外形一致。
阻尼单元2自身具备高粘粘性，贴敷于弹性单元1的顶面和与钢轨不接触的侧面，为了进一步提高系统阻尼，可采用含有羟基的有机小分子进行杂化的高阻尼橡胶复合材料，该阻尼材料不仅提高了有效阻尼温域，有机小分子还能够调节阻尼材料的粘度，改善阻尼材料对基材的润湿性，使粘接力提高，使橡胶材料具有良好的自粘性，这给复合材料的成型加工和现场施工带来很大便利。
阻尼单元2采用饱和橡胶材料作为基材，具有优异的抗老化性能和，耐水、耐乙醇和耐化学品等特性，对酸碱具有化学稳定，热稳定性好的特点。
为了有效的利用阻尼单元2再在阻尼单元2外敷贴一层薄钢板3，形成动力吸振器整体，再通过弹性连接件6固定在沿钢轨4垂向或钢轨4横向的非工作表面上。
为了增加动力吸振器与钢轨4的振动表面之间连接的可靠性，还可以在薄钢板3的两面设有连接加强结构。该连接加强结构包括表面凸凹结构、表面滚花结构或表面拉毛结构。
安装时，将动力吸振器放置在轨道底部的侧翼上，先用木工卡工具卡紧，采用如图4所示的弹性连接件6固定，每一组动力吸振器在两端各有一对弹性连接件6固定，如图5和图6所示，固定后再撤掉木工卡工具即可。弹性连接件6采用65锰钢制作，制作过程是先退火——制成所需形状——淬火——正火。
动力吸振器的长度是根据轨枕的间距设定的，通常为轨枕的间距的一半左右。实际应用中，可以通过优化弹性单元1的弹性模量以及辅助质量体-钢球5的大小以及数量，实现对不同频率和带宽振动的控制。
对所公开的实施例的上述说明，使本领域专业技术人员能够实现或使用本发明。对这些实施例的多种修改对本领域的专业技术人员来说将是显而易见的，本文中所定义的一般原理可以在不脱离本发明的精神或范围的情况下，在其它实施例中实现。因此，本发明将不会被限制于本文所示的这些实施例，而是要符合与本文所公开的原理和新颖特点相一致的最宽的范围。
Claims (6)
- 一种嵌入式轨道动力吸振器，其特征在于，包括布置于钢轨的轨腰两侧的弹性单元、质量单元和阻尼单元，所述弹性单元顶部开口，一侧面与轨腰和钢轨底部侧翼接触，内部填充有离散分布的多个质量单元，多个质量单元之间通过液态橡胶填充后固化，且固化后的上表面与弹性单元的两侧壁平齐，相邻的质量单元之间存在点接触，所述阻尼单元贴敷于弹性单元通过液态橡胶固化后的上表面，以及弹性单元与钢轨不接触的侧面。
- 根据权利要求1所述的一种嵌入式轨道动力吸振器，其特征在于，所述阻尼单元外侧贴有钢板。
- 根据权利要求1所述的一种嵌入式轨道动力吸振器，其特征在于，所述弹性单元的壁厚为5-20mm，材料为硅橡胶。
- 根据权利要求1所述的一种嵌入式轨道动力吸振器，其特征在于，所述质量单元为钢球，钢球直径为2-10mm。
- 根据权利要求1-4任一项所述的一种嵌入式轨道动力吸振器，其特征在于，所述动力吸振器通过弹性连接件固定于钢轨的两侧翼板上。
- 根据权利要求5所述的一种嵌入式轨道动力吸振器，其特征在于，所述弹性连接件采用65锰钢制作。
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