CN110285180B - Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator - Google Patents
Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator Download PDFInfo
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- CN110285180B CN110285180B CN201910628458.4A CN201910628458A CN110285180B CN 110285180 B CN110285180 B CN 110285180B CN 201910628458 A CN201910628458 A CN 201910628458A CN 110285180 B CN110285180 B CN 110285180B
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B19/00—Protection of permanent way against development of dust or against the effect of wind, sun, frost, or corrosion; Means to reduce development of noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
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- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
技术领域Technical Field
本发明涉及轨道减振降噪技术领域,具体而言,涉及一种高静低动刚度特性的隔振器及具有其的轨道系统。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.
背景技术Background technique
低频隔振是轨道交通隔振领域一大研究热点和难点。结构振动控制根据是否需要外部能源输入可分为被动控制、主动控制、半主动控制和混合控制,采用主动控制隔振和半主动控制隔振两种技术很好地隔离低频振动,但是其结构复杂,占用空间较大,制造成本高,均需要外界提供能量,且存在不稳定和电磁污染等问题。相比之下,传统的被动隔振结构简单、易于实现、工作可靠、不会额外消耗外界的能量,但是当其结构一旦确定,其固有频率就被确定,只有当激励频率大于隔振系统固有频率的特定倍数才能起到隔振效果。一般情况下被动隔振可较好地隔离中、高频振动,但隔离低频振动的能力较差。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.
根据隔振系统自身特性和描述振动的数学模型的不同,隔振系统又可分为线性隔振系统和非线性隔振系统。其中,线性隔振系统是指质量保持不变,但其弹性力和阻尼力与运动参数成线性关系的系统,其数学模型可以用线性常系数常微分方程表示。而不属于线性隔振系统的系统即为非线性隔振系统。由隔振理论可知,线性隔振系统的传递率与其刚度k和阻尼c有着密切的关系。当选择增加系统阻尼时,其阻尼比增大,则其共振频率对应的传递率最大值减小,但是其在高频段的传递率会增大;当选择减小系统刚度时,其固有频率减小,则隔振起始频率减小,隔振频率范围增大,但是其静态承载能力下降,静态变形量增大。因此对传统的线性隔振系统而言,无法同时获取较低的隔振起始频率和较高的静态承载能力,两者是相互对立矛盾的。这也是上述轨道交通减振措施在低频减振效果差的主要原因。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.
因此,现有的隔振器的隔振频率范围窄,设计一种能够有效隔离低频振动且同时控制轨道动态位移的隔振器,对于轨道交通或其他领域的低频隔振很有必要。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.
发明内容Summary of the invention
本发明的主要目的在于提供一种高静低动刚度特性的隔振器及具有其的轨道系统,在严格控制或降低轨道动态位移的前提下,降低既有隔振器及其轨道系统的固有频率,提高低频减振效果和隔振频率范围。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.
为了实现上述目的,根据本发明的一个方面,本发明提供了一种高静低动刚度特性的隔振器,包括:正刚度组件,正刚度组件包括座体和设置在座体的腔体内的第一弹性件;支撑部,支撑部与第一弹性件的上端抵接;浮动部,浮动部与支撑部配合连接;负刚度组件,负刚度组件包括相互配合的弹性部和承载部,弹性部与支撑部和/或浮动部连接,承载部与座体连接;浮动部在承受载荷并压缩第一弹性件的情况下,弹性部向承载部施加的作用力的方向相对第一弹性件的弹力的方向倾斜或垂直设置。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.
进一步地,弹性部包括第二弹性件和与第二弹性件连接的推动件,第二弹性件处于压缩状态,推动件与承载部抵接。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.
进一步地,承载部具有第一曲面,第二弹性件在伸缩的过程中,推动件能够与第一曲面的不同位置抵接。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.
进一步地,推动件具有第二曲面,第二曲面上的位置与第一曲面上的位置抵接。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.
进一步地,承载部包括连杆和承载件,连杆的下端与座体的底部连接,连杆的上端与承载件连接,推动件与承载件抵接。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.
进一步地,连杆穿设通过支撑部的至少一部分,支撑部上具有避让承载件的避让孔,承载件与连杆螺纹连接或焊接。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.
进一步地,弹性部与支撑部连接,弹性部设置在支撑部的第一腔体内。Further, the elastic part is connected to the supporting part, and the elastic part is arranged in the first cavity of the supporting part.
进一步地,支撑部包括:架体,承载部穿设通过架体;盖板,设置在架体的上部,盖板与架体之间具有第一腔体,第二弹性件与第一腔体的侧壁连接,浮动部与盖板连接。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.
进一步地,弹性部还包括:导向结构,导向结构水平设置在第一腔体内,第二弹性件设置在导向结构内。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.
进一步地,弹性部为多个,多个弹性部分布在承载部的周向。Furthermore, there are multiple elastic parts, and the multiple elastic parts are distributed in the circumference of the bearing part.
进一步地,浮动部包括筒体和设置在筒体的内壁上的支撑件,支撑件与支撑部的上部连接,筒体内在支撑件的上方具有第二腔体,弹性部设置在第二腔体内。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.
进一步地,弹性部与浮动部连接,浮动部还包括设置在筒体的内壁上的第一固定件,第二腔体位于支撑件和第一固定件之间,弹性部还包括导向结构,导向结构的上部与第一固定件连接,第二弹性件设置在导向结构内。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.
进一步地,浮动部还包括:第二固定件,第二固定件的下部与支撑部连接,导向结构的下部与第二固定件的上部连接。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.
进一步地,弹性部还包括:限位件,限位件设置在导向结构的端部,限位件用于对第二弹性件进行限位。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.
进一步地,支撑部与座体间隔设置,支撑部的下端面与座体的上端面对应设置,隔振器还包括密封件,密封件套设在支撑部和座体上,以封堵住支撑部与座体之间的间隙。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.
进一步地,浮动部包括筒体和设置在筒体的内壁上的环形的支撑件,支撑件上具有避让槽;支撑部能够相对浮动部转动以及沿筒体的轴向移动,支撑部包括架体和设置在架体上的盖板,通过支撑部与浮动部的相对移动,盖板能够穿设通过避让槽以及移动到与支撑件的下端面抵接的位置。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.
进一步地,隔振器还包括:阻尼液,设置在座体的腔体内;阻尼件,阻尼件的上端与支撑部连接,阻尼件的下端浸入阻尼液中。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.
根据本发明的另一方面,提供了一种轨道系统,包括高静低动刚度特性的隔振器,隔振器为上述提供的隔振器。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.
应用本发明的技术方案,在隔振器中设置正刚度组件、支撑部、浮动部和负刚度组件,浮动部用于承受载荷,负刚度组件的弹性部与支撑部或浮动部连接,承载部与座体连接,浮动部在承受载荷并压缩第一弹性件的情况下,第一弹性件收缩,弹性部向承载部施加的作用力的方向相对于第一弹性件的弹力的方向倾斜。这样,正刚度组件和负刚度组件配合产生的弹性力,与浮动部的位移呈非线性关系,这样该隔振器可同时获得较低的隔振起始频率和较高的静态承载能力,即具有较高的静态刚度和较低的动态刚度特性(简称高静低动),能够隔绝低频率振动,提高了隔振器的隔振频率范围。将该隔振器应用于轨道系统中,可提高轨道系统的隔振频率范围,减少低频率振动传递,减少对周围环境的影响。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.
附图说明BRIEF DESCRIPTION OF THE DRAWINGS
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解,本发明的示意性实施例及其说明用于解释本发明,并不构成对本发明的不当限定。在附图中: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:
图1示出了本发明的实施例一提供的隔振器的结构示意图;FIG1 shows a schematic structural diagram of a vibration isolator provided in Embodiment 1 of the present invention;
图2示出了图1中的隔振器在工作时弹性部对承载部的作用力示意图;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;
图3示出了图1中的隔振器中的弹性部的布置示意图;FIG3 shows a schematic diagram of the arrangement of the elastic part in the vibration isolator in FIG1 ;
图4示出了图1中的隔振器中的弹性部的另一布置示意图;FIG4 shows another schematic diagram of the arrangement of the elastic part in the vibration isolator in FIG1 ;
图5示出了图1中的隔振器中的弹性部的另一结构示意图;FIG5 shows another schematic structural diagram of the elastic part in the vibration isolator in FIG1 ;
图6示出了图1中的隔振器的俯视图;FIG6 shows a top view of the vibration isolator in FIG1 ;
图7示出了本发明的实施例二提供的隔振器的结构示意图。FIG. 7 shows a schematic structural diagram of a vibration isolator provided in the second embodiment of the present invention.
其中,上述附图包括以下附图标记:The above drawings include the following reference numerals:
10、正刚度组件;11、座体;12、第一弹性件;20、支撑部;21、架体;22、盖板;30、浮动部;31、筒体;32、支撑件;321、避让槽;33、第一固定件;34、第二固定件;40、弹性部;41、第二弹性件;42、推动件;421、第二曲面;43、导向结构;44、限位件;50、承载部;51、第一曲面;52、连杆;53、承载件;60、密封件;70、阻尼件。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.
具体实施方式Detailed ways
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。显然,所描述的实施例仅仅是本发明一部分实施例,而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的,决不作为对本发明及其应用或使用的任何限制。基于本发明中的实施例,本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例,都属于本发明保护的范围。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.
如图1至图6所示,本发明的实施例提供了一种高静低动刚度特性的隔振器,包括:正刚度组件10,正刚度组件10包括座体11和设置在座体11的腔体内的第一弹性件12;支撑部20,支撑部20与第一弹性件12的上端抵接;浮动部30,浮动部30与支撑部20配合连接;负刚度组件,负刚度组件包括相互配合的弹性部40和承载部50,弹性部40与支撑部20和/或浮动部30连接,承载部50与正刚度组件10的座体11连接;浮动部30在承受载荷并压缩第一弹性件12的情况下,弹性部40向承载部50施加的作用力的方向相对第一弹性件12的弹力的方向倾斜或垂直设置。具体地,弹性部40与承载部50的相互作用力的方向沿承载部50的曲面的法向方向的变化而变化。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.
应用本实施例的技术方案,在隔振器中设置正刚度组件10、支撑部20、浮动部30和负刚度组件,浮动部30用于承受载荷,负刚度组件的弹性部40与支撑部20或浮动部30连接,承载部50与正刚度组件10的座体11连接,浮动部30在承受载荷并压缩第一弹性件12的情况下,第一弹性件12收缩,弹性部40向承载部50施加的作用力的方向相对于第一弹性件12的弹力的方向倾斜。这样,正刚度组件10和负刚度组件配合产生的弹性力,与浮动部30的位移呈非线性关系,这样该隔振器可同时获得较低的隔振起始频率和较高的静态承载能力,即具有较高的静态刚度和较低的动态刚度特性(简称高静低动),能够隔绝低频率振动,提高了隔振器的隔振频率范围。将该隔振器应用于轨道系统中,可提高轨道系统的隔振频率范围,减少低频率振动传递,减少对周围环境的影响。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.
在本实施例中,弹性部40包括第二弹性件41和与第二弹性件41连接的推动件42,第二弹性件41处于压缩状态,推动件42与承载部50抵接。通过第二弹性件41与推动件42的配合与承载部50产生相互作用力。第二弹性件41向承载部50施加的作用力的方向相对第一弹性件12的弹力的方向倾斜或垂直设置。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.
如图2所示,当浮动部30承受载荷时,浮动部30和承载部50发生相对位移,承载部50的位移使第二弹性件41伸长,对承载部50施加作用力。通过上述设置,第一弹性件12对承载部50施加的作用力沿第一弹性件12的弹力的方向的分力变化与第二弹性件41的尺寸变化呈非线性关系,分力的变化与浮动部30的位移也呈非线性关系,从而使隔振器具有较高的静态刚度和较低的动态刚度特性,即具有高静低动的效果,与常规隔振器相比,能够隔绝低频率振动,提高了隔振器的隔振频率范围。该隔振器能够隔绝小于20Hz的低频振动。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.
具体地,在本实施例中,可以将第一弹性件12竖直设置,将第二弹性件41水平设置(未承载情况下),这样该隔振器能够较好地对竖直方向的载荷进行减振降噪,比较适用于轨道系统。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.
如图1或图5所示,承载部50具有第一曲面51,第二弹性件41在伸缩的过程中,推动件42能够与第一曲面51的不同位置抵接。通过设置第一曲面51,可根据需要改变第二弹性件41对承载部50施加的作用力的方向,以满足非线性需求,第一曲面51可以为凹型、凸型,圆面等形状。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.
在本实施例中,推动件42具有第二曲面421,第二曲面421上的位置与第一曲面51上的位置抵接。通过第二曲面421和第一曲面51的配合,可更好地实现非线性作用力需求,从而实现高静低动的效果。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.
在本实施例中,承载部50包括连杆52和承载件53,连杆52的下端与座体11的底部连接,连杆52的上端与承载件53连接,推动件42与承载件53抵接。通过上述设置,可使得承载部50与正刚度组件10连接,便于承载部50承受的负刚度组件的作用力传递给正刚度组件10,从而正刚度组件10和负刚度组件共同配合对载荷进行减振,同时减少振动对周围环境的传递,减少对周围环境的影响。具体地,第二弹性件41提供的力使推动件42与承载件53产生的相互作用力方向沿承载件53的法向方向。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.
需要说明的是,承载部50上的承载件53和承载件53上的第一曲面51都是可以根据实际需求设计成不同形状的,弹性部40中的推动件42的形状和滑动方式也可以进行多种不同的改变,例如增加轴承使滑动变成滚动,或者推动件42的前端也增加轴承,使推动件42与承载件53的第一曲面51接触滑动变为接触滚动等方式。无论其形状和方式如何变化,其原理都是采用本发明的方法原理,都在保护范围内。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.
具体地,连杆52穿设通过支撑部20的至少一部分,支撑部20上具有避让承载件53的避让孔,承载件53与连杆52螺纹连接或焊接。通过上述设置,使得隔振器结构紧凑、体积小,并且便于装配。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.
为了保证承载件53的稳定性,需要安装防松垫片和防松螺母,承载件53在连杆52上的位置可以调节,安装承载件53时,承载件53的下表面和推动件42的表面接触,并提供一定的压力,则第二弹性件41因为压力的存在而压缩,提供一定的刚度。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.
在本实施例中,弹性部40与支撑部20连接,弹性部40设置在支撑部20的第一腔体内。这样可使得隔振器结构紧凑,并且与原有的隔振器相比,整体结构变化少,可减少对相关部件的影响,便于制造和装配。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.
具体地,支撑部20包括:架体21,承载部50穿设通过架体21;盖板22,设置在架体21的上部,盖板22与架体21之间具有第一腔体,第二弹性件41与第一腔体的侧壁连接,浮动部30与盖板22连接。这样可使得隔振器结构紧凑,并且起到良好的减振降噪的效果。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.
在本实施例中,弹性部40还包括:导向结构43,导向结构43水平设置在第一腔体内,第二弹性件41设置在导向结构43内。通过导向结构43可对第二弹性件41的收缩方向进行引导,以更好地控制作用力的方向,并且便于弹性部40的装配。导向结构43可以设置为槽状结构或筒状结构。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.
如图3和图4所示,弹性部40可以设置为多个,多个弹性部40分布在承载部50的周向。这样可以提高负刚度组件对隔振器的整体影响,提高非线性特性的效果,提高隔振器的隔振频率范围。而且,可以使得承载部50的受力比较均匀。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.
在本实施例中,支撑部20与座体11间隔设置,支撑部20的下端面与座体11的上端面对应设置,隔振器还包括密封件60,密封件60套设在支撑部20和座体11上,以封堵住支撑部20与座体11之间的间隙。将支撑部20与座体11间隔设置,可以便于支撑部20以及浮动部30在承受载荷时发生位移,将支撑部20的下端面与座体11的上端面对应设置,当载荷过大时,支撑部20的下端面与座体11的上端面可以直接接触而起到限位作用,这样可以避免浮动部30的位移过大,以及由于第一弹性件12变形过大,产生塑性变形而损坏。为了保证有效性,本实施例的密封件60选用橡胶密封圈,并且通过喉箍分别固定在座体11和支撑部20上。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.
如图1和图6所示,浮动部30包括筒体31和设置在筒体31的内壁上的环形的支撑件32,支撑件32上具有避让槽321;支撑部20能够相对浮动部30转动以及沿筒体31的轴向移动,支撑部20包括架体21和设置在架体21上的盖板22,通过支撑部20与浮动部30的相对移动,盖板22能够穿设通过避让槽321以及移动到与支撑件32的下端面抵接的位置。采用上述设置,在装配隔振器时,转动支撑部20使盖板22上的凸出部分与避让槽321对应,然后向筒体31内部移动,即可将支撑部20穿入到支撑件32的下方,然后再次转动支撑部20,使得盖板22上的凸出部分与避让槽321错位,这样盖板22与支撑件32的下端面抵接,从而实现浮动部30与支撑部20的装配,即支撑部20对浮动部30进行支撑。在施工时,筒体31可预制在混凝土轨道板内部。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.
如图1所示,隔振器还包括:阻尼液,设置在座体11的腔体内;阻尼件70,阻尼件70的上端与支撑部20连接,阻尼件70的下端浸入阻尼液中。通过上述设置,支撑部20在承受载荷时,产生的振动可通过阻尼件70传导到阻尼液中,通过阻尼液的阻尼效果,可以对振动起到减缓作用,从而起到减振降噪的效果。具体地,阻尼件70包括杆状件和设置在杆状件下方的盘状件,杆状件的上端与支撑部20连接。为了提高连接强度以及传递效果,可以将杆状件设置为多个,多个杆状件围绕承载部50设置。阻尼液灌注在座体11中一定的高度,提供系统需要的阻尼系数。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.
如图7所示,在本发明的实施例二中,与上述实施例不同的是,浮动部30包括筒体31和设置在筒体31的内壁上的支撑件32,支撑件32与支撑部20的上部连接,筒体31内在支撑件32的上方具有第二腔体,弹性部40设置在第二腔体内。弹性部40可以与浮动部30中的结构连接,也可以与支撑部20中的结构连接。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.
具体地,在本实施例中,弹性部40与浮动部30连接,浮动部30还包括设置在筒体31的内壁上的第一固定件33,第二腔体位于支撑件32和第一固定件33之间,弹性部40还包括导向结构43,导向结构43的上部与第一固定件33连接,第二弹性件41设置在导向结构43内。通过导向结构43与第一固定件33的连接,可实现第二弹性件41的位置设定以及对第二弹性件41的导向。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.
在本实施例中,浮动部30还包括:第二固定件34,第二固定件34的下部与支撑部20连接,导向结构43的下部与第二固定件34的上部连接。通过上述设置,可实现隔振器中各部件的稳定、牢固的连接,从而提高隔振器的可靠性。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.
在本实施例中,弹性部40还包括:限位件44,限位件44设置在导向结构43的端部,限位件44用于对第二弹性件41进行限位。通过限位件44可对第二弹性件41进行限位,以使第二弹性件41进行限位保持压缩状态,并且避免第二弹性件41从导向结构43中脱出。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.
本发明的另一实施例提供了一种轨道系统,包括高静低动刚度特性的隔振器,隔振器为上述实施例提供的隔振器。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.
现有减振技术中,浮置板轨道结构被认为是减振效果最好的轨道减振形式。但是,现有的浮置板隔振器属于线性隔振系统,由于其结构局限性及材料极限性无法同时拥有较低的隔振起始频率和较高的静态承载能力,并且不能根据列车不同运行速度、轨道不平顺性等因素对其隔振性能进行实时调整,其隔振频率范围及隔振效果不尽人意。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.
应用本实施例的技术方案,在隔振器中设置正刚度组件10、支撑部20、浮动部30和负刚度组件,浮动部30用于承受载荷,负刚度组件的弹性部40与支撑部20或浮动部30连接,承载部50与正刚度组件10的座体11连接,浮动部30在承受载荷并压缩第一弹性件12的情况下,第一弹性件12收缩,弹性部40向承载部50施加的作用力的方向相对于第一弹性件12的弹力的方向倾斜。这样,正刚度组件10和负刚度组件配合产生的弹性力,与浮动部30的位移呈非线性关系,这样该隔振器可同时获得较低的隔振起始频率和较高的静态承载能力,即具有较高的静态刚度和较低的动态刚度特性(简称高静低动),能够隔绝低频率振动,提高了隔振器的隔振频率范围以及轨道系统的隔振频率范围,减少低频率振动传递,减少对周围环境的影响。应用该技术方案,在严格控制或降低轨道动态位移的前提下,降低了既有隔振器及其轨道系统的固有频率,提高了低频减振效果和隔振频率范围。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.
隔振器的筒体31预制在混凝土轨道板中,当列车经过时筒体31随轨道板向下运动,则支撑部20、导向结构43、第二弹性件41、推动件42同时向下运动,座体11放置在路基上,则连杆52、承载件53固定不动,正刚度的第一弹性件12受到压力压缩,提供刚度。此时因为负刚度的第二弹性件41原始处于压缩状态,随着推动件42同时的下降,第二弹性件41开始放松,对承载部50提供推力,推动件42前端沿着承载件53的表面向下滑动。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.
当列车经过后,第一弹性件12开始放松提供推力,则支撑部20、导向结构43、第二弹性件41、推动件42随筒体31同时向上运动,此时推动件42前端沿着承载件53的表面向上滑动,第二弹性件41开始压缩,提供刚度。整个系统因为承载件53和推动件42的配合而提供非线性的力。本实施例的原理图如图2所示,当列车经过时,负刚度组件向下运动,承载件53和推动件42的相对位置发生变化,负刚度组件提供的力的方向会因为接触面形状变化而变化。利用该隔振器的非线性动力学特性,可组成具有高静低动刚度特征的高性能轨道减振系统。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.
从以上的描述中,可以看出,本发明的技术方案实现了如下技术效果:From the above description, it can be seen that the technical solution of the present invention achieves the following technical effects:
1)实现浮置板的低频隔振,降低其低频传递率,从而优化地铁等轨道列车运行时对周围环境、人、建筑物以及精密仪器的影响;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)降低轨道系统中的浮置板在列车经过时的动态位移,控制轨道系统的变形,减少了轨道结构大变形引起的钢轨波磨等病害;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)整体结构具有高静、低动刚度特征,整体性好,易于现场安装。3) The overall structure has the characteristics of high static and low dynamic stiffness, good integrity and easy on-site installation.
以上所述仅为本发明的优选实施例而已,并不用于限制本发明,对于本领域的技术人员来说,本发明可以有各种更改和变化。凡在本发明的精神和原则之内,所作的任何修改、等同替换、改进等,均应包含在本发明的保护范围之内。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.
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