CN105672063B - A kind of design method of the fixed non-linear rubber shock absorber of frequency of floating plate track - Google Patents
A kind of design method of the fixed non-linear rubber shock absorber of frequency of floating plate track Download PDFInfo
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- CN105672063B CN105672063B CN201610152999.0A CN201610152999A CN105672063B CN 105672063 B CN105672063 B CN 105672063B CN 201610152999 A CN201610152999 A CN 201610152999A CN 105672063 B CN105672063 B CN 105672063B
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Classifications
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B1/00—Ballastway; Other means for supporting the sleepers or the track; Drainage of the ballastway
- E01B1/002—Ballastless track, e.g. concrete slab trackway, or with asphalt layers
-
- 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
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B2204/00—Characteristics of the track and its foundations
- E01B2204/12—Floating rails or sleepers
Abstract
A kind of design method of the fixed non-linear rubber shock absorber of frequency of floating plate track, ensure that floating plate railway roadbed has the anti-vibration performance same with loaded vehicle state and constant intrinsic frequency in complete vehicle curb condition, and loaded vehicle state trajectory vertical deviation is effectively suppressed, it is ensured that the security of system.Design method comprises the following steps：Draw vibration isolator stiffness curve and the vibration isolator curve of load；Conical rubber pile thickness and cone angle are determined, chooses the preliminary project of rubber metal pad nonlinear geometry structure type and elastomeric material；Establish the FEM model for determining frequency non-linear rigidity rubber metal pad parametrization；Set the optimization design index of intrinsic frequency error and intrinsic frequency stability as vibration isolator parameter designing；Mechanical property calculating is carried out using finite element method to FEM model, obtains the optimization design desired value corresponding to FEM model；Multiple-objection optimization iterative calculation is carried out, obtains optimal solution set, and vibration isolator optimal design parameters and optimizing index value are determined from optimal solution set.
Description
Technical field
The present invention relates to railroad track, more particularly to a kind of subway, light rail, inter-city passenger rail, high-speed railway etc. of being applied to floats
Put the design method for determining the non-linear rubber shock absorber of frequency of plate track.
Background technology
Floating plate track is a kind of effective ways for solving the problems, such as ambient vibration caused by track traffic.Floating plate track leads to
Cross to divide into track plates and put Elastic Isolator, by the vibration of track plates and base isolation, reach and reduce ring caused by track traffic
The purpose of border vibration.Floating plate track is substantially a mass-spring-damper vibrating isolation system.Floating plate mainly uses at present
Steel spring vibration isolator and common rubber shock absorber.The stiffness characteristics of both vibration isolators are all linear rigidities or close to linear
Rigidity.But the size of quality can be because train load be different in floating plate track-vehicle this quality spring vibration isolation system
Generation significant changes.This causes the floating plate track system based on the design of single-mode system intrinsic frequency method in different load-carryings
Intrinsic frequency under operating mode is widely different, causes empty wagons loaded vehicle status system performance inconsistent, and complete vehicle curb condition anti-vibration performance is poor, again
The problems such as car state trajectory vertical deviation is excessive.
Lot of domestic and international research institution has all carried out research and design to floating plate track rubber shock absorber, forms a variety of
Floating plate track rubber shock absorber patent.
Chinese patent ZL200410035441.1 discloses a kind of railway floating plate railway roadbed, and railway roadbed includes floating plate and bullet
Spring vibration isolator, floating plate flexibly support with spring vibration-isolator.Floated in addition to overcoming in patent ZL200410035441.1
Put railway roadbed construction, safeguard and maintenance on the shortcomings that, invented again a kind of easy to maintain floating ballast bed
(ZL200910013963.4), a kind of side floating track bed and its application (ZL200910019531.4), new precast panel are spelled
The patents such as dress formula floating ballast bed (ZL201210452046.8), lap jointing type floating ballast bed (ZL201420835219.9).
Chinese patent ZL200810034584.9 discloses a kind of floating plate vibration isolator for track traffic, vibration isolator bag
Formed containing undersetting, rubber damping circle and height-regulating device.Vibration isolator can better meet the requirement of bed height adjustment.
Chinese patent ZL201220294143.4 discloses a kind of board-like rubber damping vibration isolator for floating plate track.
The vibration isolator is sulfided into a tabular vibration isolator by rubber and upper and lower two blocks of steel plates.Filled in hollow out screwed hole in vibration isolator
Damping agent is to improve vibration isolator damping.
Chinese patent ZL201320385451.2 discloses a kind of rubber shock absorber for orbit traffic floating board, vibration isolation
As in bottom basin, the vibration isolation function of vertical direction can be achieved in one circular ring type rubber damper by device.
The rubber shock absorber scheme of above patent, basic vibration isolation and vibration suppression can be realized on vertical.But to difference
The train adaptability of load-carrying operating mode is poor, it is impossible to consistent anti-vibration performance is provided, because be limited to loaded vehicle by when excessive track
Vertical deviation, therefore can not further improve floating plate anti-vibration performance.It is vibration isolation complete vehicle curb condition to be all present in existing spring vibration-isolator
Can be poor, loaded vehicle state trajectory vertical deviation is excessive the defects of.
The content of the invention
The technical problems to be solved by the invention are to provide a kind of floating plate track with the fixed non-linear rubber shock absorber of frequency
Design method, it is ensured that floating plate railway roadbed has the anti-vibration performance same with loaded vehicle state and constant intrinsic frequency in complete vehicle curb condition
Rate, and loaded vehicle state trajectory vertical deviation is effectively suppressed, it is ensured that the security of system.
It is as follows that the present invention solves the technical scheme that above-mentioned technical problem is taken：
A kind of design method of the fixed non-linear rubber shock absorber of frequency of floating plate track of the present invention, the fixed non-linear rubber of frequency
Vibration isolator includes base, conical rubber pile, upper support seat, height adjusting cushion plate and lock screw, the top surface and conical rubber pile of base
Inner conical surface fit, the bottom surface of upper support seat and the male cone (strobilus masculinus) of conical rubber pile fit, and conical rubber pile includes coaxial
Inner conical steel disk, outer inner conical steel disk, and between inner conical steel disk, outer inner conical steel disk and connection fixed thereto extremely
Few one layer of cone rubber body, cone rubber body is by along inner conical steel disk, the cone rubber ring of the outer inner conical steel disk conical surface separately
Unit is formed, and each cone rubber ring element is multilayer with leading to the exhaust passage outside vibration isolator, cone rubber body, and interlayer is set
Middle taper steel disk is put, design method comprises the following steps：
(1) according to designed vibration isolator benchmark rigidity k0, the static vertical basis displacement x of floating plate0And stiffness function K
(x) vibration isolator stiffness curve and the vibration isolator curve of load, are drawn；
(2) maximum load is born according to track, the operation interval that takes vibration isolator and most is looked into the vibration isolator curve of load
Big work shift, determines conical rubber pile thickness and cone angle, chooses rubber metal pad nonlinear geometry structure type and elastomeric material
Preliminary project；
(3) FEM model for determining frequency non-linear rigidity rubber metal pad parametrization, wherein material are established according to preliminary project
Material model uses non-linear rubber cast, considers contact relation of the geometrically nonlinear structure during rubber deformation；
(4) the optimization design index of intrinsic frequency error and intrinsic frequency stability as vibration isolator parameter designing is set,
Intrinsic frequency error is error of the vibration isolator in working range between intrinsic frequency average and design load；Intrinsic frequency stability
For the fluctuating range of vibration isolator intrinsic frequency in working range；
(5) according to the optimization design index, mechanical property meter is carried out using finite element method to the FEM model
Calculate, obtain the optimization design desired value corresponding to the FEM model；
(6) according to the optimization design desired value obtained by the optimization design index and calculating, carry out multiple-objection optimization and change
In generation, calculates, and obtains optimal solution set, and vibration isolator optimal design parameters and optimizing index value are determined from optimal solution set；
(7) terminate to design if vibration isolator optimal design parameters and optimizing index value meet design requirement, if can not
Meet design requirement, then adjust vibration isolator topological structure, repeat step (3)~(6).
The invention has the advantages that provide a kind of design method for determining frequency rubber shock absorber non-linear rigidity curve and
Its implementation, complete vehicle curb condition anti-vibration performance caused by overcoming common spring vibration isolator linear rigidity is poor, loaded vehicle state rail
The defects of road vertical deviation is excessive.It may insure that floating plate track system all has constant intrinsic frequency under the conditions of any car weight
Rate, stable anti-vibration performance.And loaded vehicle state trajectory vertical deviation is effectively suppressed, it is ensured that the security of system.Resonating
FrequencyTimes frequencies above section damping capacity reaches 20~30dB, can meet Special zone anti-vibration performance requirement；Due to
Rubber has larger viscous damping, therefore near resonant frequency, it still has preferable vibration suppression performance, better than common steel spring
Floating plate track.The rubber shock absorber is replaceable, easy-maintaining, both can be applied to prefabricated floating plate track, it can also be used to existing
Pour formula floating plate track.
Brief description of the drawings
This specification includes following five width accompanying drawing：
Fig. 1 is structural representation of the floating plate track with the fixed non-linear rubber shock absorber of frequency；
Fig. 2 is structural representation of the floating plate track with conical rubber pile in the fixed non-linear rubber shock absorber of frequency；
Fig. 3 is structural representation of the floating plate track with conical rubber pile in the fixed non-linear rubber shock absorber of frequency；
It is involved in the design method that Fig. 4 is floating plate track with the fixed non-linear rubber shock absorber of frequency that to determine frequency non-linear just
Write music line chart；
Fig. 5 is that a kind of floating plate track of the present invention is determined with involved in the design method for determining the non-linear rubber shock absorber of frequency
Frequency non-linear load curve map；
Mark and its implication in figure：Base 1, conical rubber pile 2, upper support seat 3, height adjusting cushion plate 4, lock screw 5, outside
Taper steel disk 31, inner conical steel disk 32, middle taper steel disk 33, cone rubber ring element 34, exhaust passage 35, conical rubber pile
Upper inner diameter p, conical rubber pile cone angle gamma, cone rubber body thickness in monolayer h, cone rubber czermak space S1、S2、S3。
Embodiment
Below in conjunction with the accompanying drawings and specific embodiment the present invention is further described.
Reference picture 1, Fig. 2 and Fig. 3, the floating plate track fixed non-linear rubber shock absorber of frequency, including base 1, cone rubber
Heap 2, upper support seat 3, height adjusting cushion plate 4 and lock screw 5, the inner conical surface of the top surface and conical rubber pile 2 of base 1 fit, on
The bottom surface of support base 3 and the male cone (strobilus masculinus) of conical rubber pile 2 fit.The conical rubber pile 2 includes coaxial male-tapered steel disk
31st, inner conical steel disk 32, and between male-tapered steel disk 31, inner conical steel disk 32 and connection fixed thereto at least one layer
Cone rubber body, cone rubber body is by along male-tapered steel disk 31, the cone rubber ring element of the conical surface of inner conical steel disk 32 separately
34 are formed, and each cone rubber ring element 34, which has, to lead to and the exhaust passage 35 outside vibration isolator.By being set in cone rubber body
The gap put forms the line style of the non-linear rigidity curve of rubber structure, is controlled by cone rubber body thickness and rubber compounding
Rubber metal pad integral rigidity, the ratio of rubber metal pad lateral stiffness and vertical stiffness is controlled by the cone angle of conical rubber pile, it is ensured that floating
Put plate railway roadbed has the anti-vibration performance same with loaded vehicle state and constant intrinsic frequency, and loaded vehicle state trajectory in complete vehicle curb condition
Vertical deviation is effectively suppressed, it is ensured that the security of system.
Reference picture 3, the male-tapered steel disk 31, the cone rubber body between inner conical steel disk 32 can be one layer or more
Layer.When cone rubber body is multilayer, interlayer sets middle taper steel disk 33.Reference picture 3, when vibration isolator is pressurized, each taper
Rubber ring element 34 can expand to both sides and progressively eat up mutual gap, and adjacent two cone rubbers ring element 34 connects
Limit value rubber swelling is touched, so that vibration isolator rigidity increases.By setting being partitioned into according to certain of gap width and gap
Functional form changes, it is possible to controls the change curve of rigidity.
A kind of floating plate track of present invention design method of the fixed non-linear rubber shock absorber of frequency, comprises the following steps：
(1) according to designed vibration isolator benchmark rigidity k0, the static vertical basis displacement x of floating plate0And stiffness function K
(x) vibration isolator stiffness curve and the vibration isolator curve of load, are drawn；
(2) maximum load is born according to track, the operation interval that takes vibration isolator and most is looked into the vibration isolator curve of load
Big work shift, determines conical rubber pile thickness and cone angle, chooses rubber metal pad nonlinear geometry structure type and elastomeric material
Preliminary project；
(3) FEM model for determining frequency non-linear rigidity rubber metal pad parametrization, wherein material are established according to preliminary project
Material model uses non-linear rubber cast, considers contact relation of the geometrically nonlinear structure during rubber deformation；
(4) the optimization design target of intrinsic frequency error and intrinsic frequency stability as vibration isolator parameter designing is set,
Including：Intrinsic frequency error, the error in working range between intrinsic frequency average and design load；Intrinsic frequency stability,
The fluctuating range of intrinsic frequency in working range；
(5) according to the optimization design target, mechanical property meter is carried out using finite element method to the FEM model
Calculate, obtain the optimization design desired value corresponding to the FEM model；
(6) according to the optimization design desired value obtained by the optimization design target and calculating, carry out multiple-objection optimization and change
In generation, calculates, and obtains optimal solution set, and vibration isolator optimal design parameters and optimizing index value are determined from optimal solution set；
(7) terminate to design if vibration isolator optimal design parameters and optimizing index value meet design requirement, if can not
Meet design requirement, then adjust vibration isolator topological structure, repeat step (3)~(6).
In the step (1), vibration isolator stiffness curve and the vibration isolator curve of load determine as the following formula：
In formula, k0For vibration isolator benchmark rigidity, d is that vibration isolator arranges spacing, and ω is system frequency, x0For floating plate
Static vertical basis displacement, x are vibration isolator displacement, and α is the adjusted value of vibration isolator stiffness curve.
Benchmark rigidity and basis displacement determine：Required according to floating plate track system isolation performance and track stability, really
Determine the static vertical basis displacement x of floating plate under train floating plate track system frequency ω and track plates Gravitative Loads0.Profit
With floating plate track per linear meter(lin.m.) weight msAnd vibration isolator arrangement spacing d, determine vibration isolator benchmark rigidity k0：
k0=4 π2ω2ms
Determine the determination of frequency non-linear rigidity curve：Utilize obtained vibration isolator benchmark rigidity k0With the static vertical benchmark of floating plate
Displacement x0, according to the following formula determine vibration isolator stiffness curve adjusted value α,
Nonlinear curve proposed by the invention realizes that the principle for determining frequency is as follows：
According to the calculating formula of mass-spring system intrinsic frequency：
Understand, need to ensure the rigidity k and quality m of mass-spring system if system vibrational frequency to be ensured is constant
Ratio is constant.Therefore spring rate should be with the nonlinear curve of vibration isolator change in displacement, be designated as k (x),
The π of k (x)=42ω2m
And the camber of spring caused by quality m gravity can be obtained by following formula,
In summary two formulas obtain
The solution of above equation is,
But the solution, which needs x domains, can just be met when being (- ∞, ∞), but work of the quality m gravity to spring in practice
With always facing one direction, i.e., always having x >=0, to ensure that non trivial solution is effective, appeal formula is modified and can obtained
Stiffness curve given by above formula can ensure to work as x >=x0When, system frequency ω keeps constant.In view of floating
Plate is discrete support, and vibration isolator arrangement spacing is the stiffness curve K (x) that d then can obtain vibration isolator.
Embodiment：
Required to determine that floating plate track system frequency ω is 9Hz according to vibration isolation, according to Structural Design Requirement track plates
Per linear meter(lin.m.), deadweight is 3000kg, the static vertical basis displacement x of floating plate0For 0.3mm.Vibration isolator arrangement spacing d is 1.8m.
First, floating plate track vibration isolator benchmark rigidity k is determined according to formula (2)0：
k0=4 π2ω2M=4 π2×82× 3000=7.57 × 106N/m
Then, obtained vibration isolator benchmark rigidity k is walked using A0With the static vertical basis displacement x of floating plate0, according to the following formula
The adjusted value α of vibration isolator stiffness curve is determined,
Above-mentioned value substitution following formula can be obtained to stiffness curve such as Fig. 4, the curve of load such as Fig. 5 of vibration isolator.
Based on gained determine frequency non-linear rigidity curve map, determine frequency non-linear load curve map carry out non-linear rigidity determine frequency rubber
Glue vibration isolator elastic element structure designs.
Conical rubber pile 2 is the core component for realizing designed non-linear rigidity, and Fig. 3 is to determine frequency non-linear rigidity rubber
The structure example of heap.Cone rubber uses Multi-layer design, and cone rubber ring element 34 is sandwiched in male-tapered steel disk 31, inner conical steel disk
Between 32 and middle taper steel disk 33.And steel disk and rubber bound are integrated.Cone rubber czermak space is set in cone rubber
S1、S2、S3..., cone rubber thickness in monolayer h, minimum diameter ds, cone angle gamma.Wherein cone rubber thickness in monolayer h, minimum diameter
ds, cone angle gamma is the control parameter of cone rubber vertical stiffness and lateral stiffness ratio.By adjusting rubber compounding and taper rubber
Cone rubber czermak space S is set in glue1、S2、S3... quantity and the size in each gap adjust rubber non-linear stiffness curve
Line style.
Vibration isolator parameter designing process is as follows：
(1) according to vibration isolator benchmark rigidity k0, and vertical stiffness and lateral stiffness ratio requires that synthesis primarily determines that rubber
Glue vibration isolator cone rubber thickness in monolayer h, minimum diameter ds, the initial value { h of cone angle gamma0, d0, γ0, and take and determine vibration isolator
Gap setting number n, and corresponding gap { S1, S2, S3…Sn}；
(2) parametric modeling is carried out to vibration isolator, vibration isolator modeling program P1 is worked out, by parameter set { h to be optimized0, d0,
γ0, S1, S2, S3…SnIt is used as optimized variable.Establish the parameter finite element model of vibration isolator cone rubber.This example is by repairing
The shape and its stiffness characteristics of cone rubber can be changed by changing the value of Optimal Parameters collection；
(3) intrinsic frequency error e is setfWith optimization aims of the intrinsic frequency stability r as vibration isolator parameter designing, 1.
Intrinsic frequency error, i.e., the error in working range between system frequency ω averages and design load；2. intrinsic frequency is steady
It is qualitative, i.e., the system frequency ω fluctuating range in working range；Design object calculation procedure P2 is worked out, program P2's is defeated
Enter for target stiffness curve and vibration isolator stiffness curve.
(4) least square method is used, weights multiple-objection optimization program using Matlab software programmings, program calls journey first
Sequence P1 establishes vibration isolator model, generation model script.Then FEM model script is read in by driven by program finite element software,
And load history is set, displacement-force curve of the vibration isolator under specified load course is calculated, and derivation obtains its stiffness curve.
Then caller P2 obtains the optimization aim of this calculating, using least square method to design parameter { h0, d0, γ0, S1,
S2, S3…SnOptimize acquisition optimal solution set.
(5) optimization aim intrinsic frequency error e is checkedfWith intrinsic frequency stability r.If gained optimization design target
Optimal value meet that design requirement then terminates to design, if design requirement can not be met, adjust vibration isolator number of gaps n, and
Repeat step (2)-(4).
A kind of floating plate track of the present invention setting with the non-linear rubber shock absorber of fixed frequency described above that simply explain through diagrams
The principle of meter method, it is not intended to the present invention being confined in shown and described concrete structure and the scope of application, therefore every institute
Corresponding modification and the equivalent being utilized are possible to, belongs to the apllied the scope of the claims of the present invention.
Claims (2)
1. a kind of floating plate track design method of the fixed non-linear rubber shock absorber of frequency, the fixed non-linear rubber shock absorber of frequency include
Base (1), conical rubber pile (2), upper support seat (3), height adjusting cushion plate (4) and lock screw (5), the top surface and cone of base (1)
The inner conical surface of shape rubber metal pad (2) fits, and the bottom surface of upper support seat (3) and the male cone (strobilus masculinus) of conical rubber pile (2) fit, taper
Rubber metal pad (2) includes coaxial male-tapered steel disk (31), inner conical steel disk (32), and positioned at male-tapered steel disk (31), inner cone
Between shape steel disk (32) and connection fixed thereto at least one layer of cone rubber body, cone rubber body is by along male-tapered steel disk
(31), the cone rubber ring element (34) of inner conical steel disk (32) conical surface separately is formed, each cone rubber ring element (34) tool
There is the exhaust passage (35) led to outside vibration isolator, cone rubber body is multilayer, and interlayer sets middle taper steel disk (33), design
Method comprises the following steps：
(1) according to designed vibration isolator benchmark rigidity k0, the static vertical basis displacement x of floating plate0And stiffness function K (x), paint
Vibration isolator stiffness curve and the vibration isolator curve of load processed；
(2) maximum load is born according to track, the operation interval for taking vibration isolator and maximum work is looked into the vibration isolator curve of load
Make displacement, determine conical rubber pile thickness and cone angle, choose the preliminary of rubber metal pad nonlinear geometry structure type and elastomeric material
Design；
(3) FEM model for determining frequency non-linear rigidity rubber metal pad parametrization, wherein material mould are established according to preliminary project
Type uses non-linear rubber cast, considers contact relation of the geometrically nonlinear structure during rubber deformation；
(4) the optimization design target of intrinsic frequency error and intrinsic frequency stability as vibration isolator parameter designing is set, including：
Intrinsic frequency error, the error in working range between intrinsic frequency average and design load；Intrinsic frequency stability, working
In the range of intrinsic frequency fluctuating range；
(5) according to the optimization design target, mechanical property calculating is carried out using finite element method to the FEM model, obtained
To the optimization design desired value corresponding to the FEM model；
(6) according to the optimization design desired value obtained by the optimization design target and calculating, multiple-objection optimization iteration meter is carried out
Calculate, obtain optimal solution set, and vibration isolator optimal design parameters and optimizing index value are determined from optimal solution set；
(7) terminate to design if vibration isolator optimal design parameters and optimizing index value meet design requirement, if can not meet
Design requirement, then adjust vibration isolator topological structure, repeat step (3)~(6).
2. the design method of the fixed non-linear rubber shock absorber of frequency of a kind of floating plate track as claimed in claim 1, it is characterized in that：
In the step (1), vibration isolator stiffness curve and the vibration isolator curve of load determine as the following formula：
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In formula, k0For vibration isolator benchmark rigidity, d is that vibration isolator arranges spacing, and ω is system frequency, x0It is static for floating plate
Vertical basis displacement, x are vibration isolator displacement, and α is the adjusted value of vibration isolator stiffness curve.
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| CN109583139B (en) * | 2018-12-29 | 2022-09-23 | 武昌船舶重工集团有限公司 | Method for determining fixing form of base plate of vibration isolator |
| CN110055834B (en) * | 2019-05-30 | 2020-07-24 | 西南交通大学 | Dynamic stiffness design method |
| CN110644292B (en) * | 2019-10-10 | 2021-05-11 | 同济大学 | Spring vibration isolator jacking method for floating slab track |
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| JPS6480601A (en) * | 1987-09-21 | 1989-03-27 | Nippon Senro Gijutsu Kk | Vibrationproof track structure |
| CN1236144C (en) * | 2004-12-13 | 2006-01-11 | 中国船舶重工集团公司第七一一研究所 | Railway traffic floating slab vibration isolator with high damping shock absorption module |
| CN203768745U (en) * | 2014-04-15 | 2014-08-13 | 衡水中铁建工程橡胶有限责任公司 | Easily-replaced rubber vibration isolator for rail traffic floating slab |
| CN104805740B (en) * | 2015-03-03 | 2016-12-07 | 中国船舶重工集团公司第七一一研究所 | Rubber shock absorber for orbit traffic floating board railway roadbed vibrating isolation system |
| CN104762853A (en) * | 2015-04-29 | 2015-07-08 | 中铁二院工程集团有限责任公司 | Rubber vibration isolator for floating slab track |
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