CN206815108U - A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly - Google Patents
A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly Download PDFInfo
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- CN206815108U CN206815108U CN201720202823.1U CN201720202823U CN206815108U CN 206815108 U CN206815108 U CN 206815108U CN 201720202823 U CN201720202823 U CN 201720202823U CN 206815108 U CN206815108 U CN 206815108U
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Abstract
It the utility model is related to a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly, the vibration damping combination body (1) includes more than two multistage resonant elements (2), the multistage resonant element (2) includes two or more rigidity mass ratio or the tuned mass body (3) and resonance flexible member (4) no less than two mode, and described multistage resonant element (2) direction along ng a path is arranged by more than two combinations；Described multistage resonant element (2) is fixed on road bed board (5) by constraining elastic anchor log (6)；The equivalent stiffness of described constraint elastic anchor log (6) is less than the minimum resonance rigidity of multistage resonant element (2).Compared with prior art, the utility model multi-mode resonance frequencies include the inherent feature frequency of multistage driving frequency and track structure under the conditions of car load under vehicle operating condition, so as to solve the problems, such as the actual vibration of the very scabrous complicated multiband of single vibration reducing measure traditional in track vibration damping denoising and its noise radiation, ballast bed structure low-frequency vibration particularly caused by track vibrating isolation system.
Description
Technical field
The utility model belongs to railway technology field, and in particular to a kind of dismountable multistage resonant track railway roadbed power subtracts
Shake assembly.
Background technology
Prefabricated road bed board has been widely used among the various line constructions of China's track traffic.By domestic each research
The improvement of mechanism and manufacture craft are improved, and have produced multiple deformations at present.But its basic structure still has for solid slab and middle part
Hollow two kinds of structure types of framework road bed board, the bottom that both sides set up rail is continuous solid.
Combined frame road bed board described in Chinese patent ZL201110102334.6, in order to facilitate road bed board dismounting and
The replacing of bottom vibration isolator, jack machinism is added in middle part is hollow.During use along track direction of advance on railway roadbed basis just
Gutter can be set in central part.But because the middle part hollow design of framework road bed board reduces the mass of vibration of road bed board, if
Add the thickness of road bed board under conditions of same mass of vibration or width is that bridge increase is wanted in the design space of ballast bed structure, it is right
The rail system of the confined space possibly can not be applied.
Detachable track travel cover plate and elastic packing described in Chinese patent ZL201410185629.8, avoid debris
Fall into ditch and facilitate maintenance personal to be walked in track middle row.But the patented technology is simple unified cover plate and close
Envelope, quality etc. are adapted to different frequency requirements without change.
The floating plate rail structure of passive type power vibration damping described in Chinese patent ZL201310524476.08, introduce
Power vibration damping principle absorbs the theoretical mould of the vibration at structural natural frequencies (5-15Hz) place of track floating plate track road bed board
Type.But for the peak value vibration problem of usual rail system mainly in more than 20Hz, peak value vibration problem is due to more vehicle
Track runs driving frequency, and supporting resonant frequency of track elasticity fastener etc. under the conditions of car load, this patent does not solve
The principal vibration problem of bed and corresponding structural design scheme.
Track is special because the impact by carrier vehicle and the rough suitable excitation of running surface of wheeltrack can produce strong vibration
Vibration not near the characteristic frequency of rail system or its is often strong.
The scope of these characteristic frequencies is very wide, including 1) stock rail operation driving frequency：Such as track discontinuously supports
By frequency (to speed 50km/h to 400km/h, about from 20Hz to 200Hz) and axletree interval by frequency (to speed
50km/h to 400km/h, about from 5Hz to 50Hz)；2) each rank resonant frequency of rail system：Such as the branch of track elasticity fastener
Hold frequency (typically from 20Hz to 100Hz), floating plate railway roadbed isolation frequency (typically in 5Hz to 30Hz scopes).
The vibration of the structure of rail system particularly road bed board or plate of walking not only produces noise radiation, and it vibrates meeting
Pass through railway roadbed base diffusion to adjacent building.Due to track structure and the different operating modes of vehicle are run, are made traditional single
Vibration reducing measure be difficult solve the problems, such as complexity multiband actual vibration and its noise radiation.
The content of the invention
The purpose of this utility model be exactly in order to overcome above-mentioned prior art to exist the defects of and providing one kind can effectively solve
Certainly traditional single effectively actual vibration of the very scabrous complicated multiband of vibration reducing measure and its made an uproar in track vibration damping denoising
Dismountable multistage resonant track railway roadbed power vibration damping assembly of Acoustic Radiation Problems.
The purpose of this utility model can be achieved through the following technical solutions：A kind of dismountable multistage resonant track road
Bed power vibration damping assembly, it is characterised in that the vibration damping combination body (1) includes more than two multistage resonant elements (2), and this is more
Rank resonant element (2) includes two or more rigidity mass ratio or the tuned mass body (3) and resonance elasticity no less than two mode
Element (4), described multistage resonant element (2) direction along ng a path are arranged by more than two combinations；Described multistage resonance list
First (2) are fixed on road bed board (5) by constraining elastic anchor log (6)；The equivalent stiffness of described constraint elastic anchor log (6)
Less than the minimum resonance rigidity of multistage resonant element (2).
The resonant frequency range of described vibration damping combination body (1) is made up of more than two multistage resonant elements (2), vibration damping
The frequency band range that assembly (1) is formed is the segmentation frequency band of a broadband or multiple certain bandwidth.
The resonant frequency range of described vibration damping combination body (1) covers main train and passes through driving frequency and main rail
Channel structure characteristic frequency；
Described train passes through frequency f by driving frequency comprising wheel shaft corresponding with train wheelbase aea, or with rail branch
Hold spacing l and frequency f is supported by rail accordinglyes：
fea=v/a Eq (1a)
fes=v/l Eq (1b)
Here v is speed；feaIt is the driving frequency that wheelbase passes through；fesIt is the excitation frequency that train supports spacing by rail
Rate；
Described track structure characteristic frequency is included in rail supporting P2 intrinsic frequencies f under the conditions of car loadp2Or railway roadbed
Isolation frequency fi, rail discontinuously support p-p frequency f, wherein
Rail supporting P2 intrinsic frequencies fp2Or railway roadbed isolation frequency fiIt can be calculated by following formula：
fp2=(kep2/mep2)0.5/(2π) Eq(2a)
fi=(kei/mei)0.5/(2π) Eq(2b)
Wherein, kep2It is the equivalent support stiffness of track mode, mep2It is corresponding mode equivalent mass；keiIt is track vibration isolation system
System mode equivalent stiffness, meiIt is corresponding track vibrating isolation system mode equivalent mass；
Rail discontinuously supports p-p frequencies f and calculated by following formula：
Wherein, E is the elasticity modulus of materials of rail, and I is rail section the moment of inertia, mrIt is the equivalent matter of rail unit length
Amount, l are that rail fastening supports spacing, rgIt is the rail radius of gyration, ν is the Poisson's ratio of rail material, and κ is rail (for 0.34)
Cross-sectional shear constant.
The design resonant frequency of described multistage resonant element (2) passes through driving frequency and track knot with the train respectively
Structure characteristic frequency is same or like, according to the design resonance frequency selective resonance mass body (3) and resonance flexible member (4)：First
Resonant frequency range is calculated, suitable mass body and flexible member are then selected according to the frequency range, vibration damping combination body (1)
Resonant frequency range passes through driving frequency and one or more track knot including at least one or more train
Structure characteristic frequency.
Multistage resonant element (2) direction along ng a path combination arrangement, it can be flexible according to actual conditions in the position of road bed board
Design：
Described multistage resonant element (2) direction along ng a path combination is arranged in the road bed board among railway roadbed in road bed board (5)
Above cavity (51), and/or road bed board (5).
Described multistage resonant element (2) direction along ng a path combination is arranged in the road bed board side of railway roadbed both sides road bed board (5)
Above face (53), or the road bed board end (54) of road bed board (5), or on road bed board side groove (55).
The length or train of of length no more than road bed board of described multistage resonant element (2) direction along ng a path combination arrangement
The two of wheel-base bogie accompany, and the length range of vibration damping combination body (1) is in 0.3-6.0m.
Described resonance flexible member (4) is arranged between tuned mass body (3) and road bed board (5), forms multistage resonance,
Multistage resonance realizes two by the elastic stiffness resonance flexible member (4) for possessing two or more direction by tuned mass body (3)
The resonance mode in above direction, the resonance mode in two or more direction include three translation mode and three torsion modes or its not
With the combination of mode.
Described tuned mass body (3) is in step-like, is fastened on road bed board cavity (51), resonance flexible member (4) is set
Put in the bottom surface and side of tuned mass body (3)；
Or described tuned mass body (3) is in rectangular-shape, resonance flexible member (4) is identical with its shape, positioned at it
Bottom surface；
Or described tuned mass body (3) is L-shape, resonance flexible member (4) is identical with its shape, positioned at its bottom surface
And side.
The built-in fitting (56) of installation constraint elastic anchor log (6) is disposed with described road bed board (5)；
Described constraint elastic anchor log (6) is by constraint fastener (61), constraint pressing plate (62) and constraint cushion (63)
Composition；Described constraint fastener (61) is connected through constraint pressing plate (62) and constraint cushion (63) with built-in fitting (56)
Constrain tuned mass body (3).
For the ease of installation and removal, described tuned mass body (3) is provided with boom hoisting (31).
The material of described tuned mass body (3) is metal or concrete or composite；
Described resonance flexible member (4) is elastomer or geotextiles or synthetic resin or mortar made of rubber.
Space between two sleeper beams of the corresponding ladder-type sleepers of vibration damping combination body (1) is set.
Compared with prior art, the utility model passes through detachable multistage resonant track vibration damping combination body of the present utility model
(1) application, the wide-band excitation frequency under track service condition in certain vehicle speed range and multiple rails can be greatly reduced
Multi-peak level of vibration under road system features frequency, using direction along ng a path design arrangement multiple multistage resonant elements not only
Solve driving frequency and the vibration of ballast bed system resonant frequency multimodal, the frequency of these wide scopes includes the discontinuous supporting of track and led to
Overfrequency, the supporting resonance P2 frequencies of track elasticity fastener, track discontinuously support p-p frequencies etc., while also solved generally
Vibration isolation ballast bed system is for example at floating plate railway roadbed isolation frequency the problem of the increase of road bed board level of vibration, so as to reduce railway roadbed knot
Low-frequency noise radiation caused by structure vibration, low-frequency vibration energy is more effectively absorbed so as to control low-frequency vibration particularly 1-80Hz
The transmission of the ground vibration of frequency range and the vibration of adjacent buildings.Dismountable multistage resonant track railway roadbed of the present utility model moves
The implementation of power vibration damping combination body is simple and easy, is easy to repair and change again, can be effectively reduced excitation frequency range or road bed board resonance
Level of vibration reach more than 10dB, the utility model is applied in underground line, can make the vibration of circuit overhead surface or building
Level reduces 5-10dB or more, and it is very scabrous multiple effectively to solve single effectively vibration reducing measure traditional in track vibration damping denoising
The actual vibration and its noise radiation problem of miscellaneous multiband.
Brief description of the drawings
Fig. 1 is the structure top view of the utility model embodiment 1；
Fig. 2 is Fig. 1 A-A sectional views；
The structural representation of road bed board in Fig. 3 embodiments 1；
Fig. 4 is constraint elastic anchor log schematic diagram
Fig. 5 is the structure top view of the utility model embodiment 2；
Fig. 6 is Fig. 5 B-B sectional views；
Fig. 7 is Fig. 5 C-C sectional views；
Fig. 8 is the structure top view of the utility model embodiment 3；
Fig. 9 is Fig. 8 D-D sectional views；
Figure 10 is the structure top view of the other embodiments of the utility model；
Figure 11 a are Figure 10 E-E sectional views；
Figure 11 b are Figure 11 a F portions enlarged drawings；
Figure 11 c are Figure 11 a G portions enlarged drawings；
Figure 11 d are Figure 11 a G portions another kind schematic enlarged-scale views；
Figure 12 a are Figure 10 F-F sectional views；
Figure 12 b are Figure 12 a H portions enlarged drawings；
Figure 12 c are Figure 12 a H portions another kind schematic enlarged-scale views；
Figure 13 a are Figure 10 G-G sectional views；
Figure 13 b are Figure 13 a K portions enlarged drawings；
Figure 14 a are Figure 10 H-H sectional views；
Figure 14 b are Figure 14 a L portions enlarged drawings；
Figure 14 c are Figure 14 a L portions another kind schematic enlarged-scale views；
Figure 15 is the arrangement schematic diagram of the multistage resonant element of vibration damping combination body；
Figure 16 is driving frequency schematic diagram.
All accompanying drawings are that schematic diagram is not drawn to scale；
In figure：1st, vibration damping combination body；2nd, multistage resonant element；3rd, tuned mass body；4th, resonance flexible member；5th, railway roadbed
Plate；6th, elastic anchor log is constrained；7th, car body；8th, rail；9th, bogie spacing；10th, wheelbase；11st, rail supporting spacing；21st, it is more
Rank resonant element I-1；22nd, multistage resonant element II-1；23rd, multistage resonant element I-2；31st, boom hoisting；33rd, multistage resonance
The vertical resonance directions of unit；34th, multistage resonant element transverse resonance direction；35th, multistage resonant element torsional resonances direction；51、
Road bed board cavity；53rd, road bed board side；54th, road bed board end；55th, road bed board side groove；56th, built-in fitting；61st, constraint fastening
Part；62nd, pressing plate is constrained；63rd, cushion is constrained；71st, bogie；72nd, wheel；81st, sleeper.
Embodiment
The utility model is described in detail with specific embodiment below in conjunction with the accompanying drawings.
Embodiment 1- subway applications：
The present embodiment is to be directed to subway circulation condition：Vehicle speed range 40-100km/h, fastener spacing 0.55-0.65m, fastener
Rigidity 5-50kN/mm, axletree is away from minimum 2-3m.
As described in Figure 16, road bed board 5 is provided with sleeper 81, sets rail 8 on sleeper 81, Subway Body 7 operates in rail
On 8,71 times setting wheels 72 of bogie of car body 7, two wheels, 72 wheelbases 10 of same bogie 71 are a, adjacent bogie
Spacing 9 is b, and rail supporting spacing 11 is l.
Figure 16 gives the rough schematic of each frequency listed by formula 1-3
The driving frequency f that wheelbase passes throughea=v/a Eq (1a)
Train supports the driving frequency f of spacing by railes=v/l Eq (1b)
Bogie passes through frequency feb=v/b
Here v is speed, and a is train wheelbase, and l is rail supporting spacing, and b is spacing between bogie.
Rail supporting P2 intrinsic frequencies fp2=(kep2/mep2)0.5/(2π) Eq(2a)
Railway roadbed isolation frequency fi=(kei/mei)0.5/(2π) Eq(2b)
Here kep2It is the equivalent support stiffness of track mode, mep2It is corresponding mode equivalent mass；keiIt is track vibration isolation
System mode equivalent stiffness, meiIt is corresponding track vibrating isolation system mode equivalent mass；
Rail discontinuously supports p-p frequencies
Frequency range below can be calculated by above-mentioned formula：
Train passes through rail brace driving frequency fesScope：17-50Hz；
Rail supporting intrinsic frequency fP2Frequency range：22-60Hz；
Rail is in laterally discontinuous supporting p-p frequency f scopes：400-600Hz；
The actual design resonant frequency thus considered is divided to two sections of designs, and its frequency range is respectively I sections：15-70Hz, and II
Section：400-600Hz.
The two sections of resonant frequency range designs of this example：
First paragraph I sections carry out resonance design using 3 rank centre frequencies, include 2 multistage resonant elements, the 1st multistage
Resonant element I-121 is two rank resonant elements, the design resonance center frequeHs of two rank resonant elements be respectively 16Hz and
31.5Hz, corresponding modal stiffness modal mass ratio are respectively：1.0E4 and 3.9E4；2nd multistage resonant element I-2 23
Also it is two rank resonant elements, the design resonance center frequeH of two rank resonant elements distinguishes 31.5Hz and 63Hz, corresponding mode
Rigidity modal mass ratio is respectively：3.9E4 and 1.57E5.The mode of two rank resonant elements is humorous by same tuned mass body and two
The flexible member that shakes is formed, the resonance flexible members of two different modalities rigidity be separately positioned on tuned mass body vertical direction and
Laterally, the vertical resonance directions 33 of multistage resonant element as shown in Figure 2 and multistage resonant element transverse resonance direction 34.
Second segment II sections carry out resonance design using 2 rank centre frequencies, only include 1 multistage resonant element II-1 22,
Multistage resonant element is three rank resonant elements, and the design resonance center frequeHs of three rank resonant elements is respectively 400Hz, 500Hz and
630Hz, corresponding modal stiffness modal mass ratio are respectively：6.3E6,9.9E6 and 1.56E7.The mould of three rank resonant elements
State is made up of same tuned mass body and vertical direction, the equivalent tank flexible member in three directions of transverse direction and torsion, such as Fig. 2 institutes
The vertical resonance directions 33 of multistage resonant element, multistage resonant element transverse resonance direction 34 and the multistage resonant element shown reverses humorous
Shake direction 35.
Here modal stiffness modal mass ratio is determined by formula below：
ke/me=(2 π fr)2
Here ke is modal stiffness, and me is modal mass, and fr is design resonance center frequeH.
The weight of each tuned mass body in 20-300kg scopes, the equivalent stiffness design of corresponding resonance flexible member by
Following formula calculates：
ke=(2 π fr)2me
1 of 2 multistage resonant element I-1 21 of first paragraph I sections and multistage resonant element I-2 23 and second segment II sections
Multistage resonant element II-1 22 forms 1,3 multistage resonance lists of track travel vibration damping combination body by 3 multistage resonant elements
The layout direction along ng a path of member presses (I-1)-(II-1)-(I-2) assembled arrangement, as shown in Figure 15, track travel vibration damping combination body
1 length is 550-650mm, and 3 multistage resonant element (I-1)-(II-1)-(I-2) designs are divided into two kinds of series, Yi Zhongshi
It is adapted to flat road bed board, as shown in Figure 6：The bottom level land of tuned mass body 3, divides into tabular resonance flexible member 4, and pass through
Constraint elastic anchor log 6 is fixed on road bed board 5.A kind of is the setting that corresponding road bed board center has road bed board cavity 51, such as
Shown in Fig. 2, tuned mass body 3 is in step-like, is fastened on road bed board cavity 51, resonance flexible member 4 is arranged on tuned mass
The bottom surface and side of body 3, and be fixed on by constraining elastic anchor log 6 on road bed board 5.
As depicted in figs. 1 and 2, each resonant element includes tuned mass body 3 and resonance flexible member 4 as shown in Figure 2.
There is the setting of road bed board cavity 51 for road bed board center, the resonant element in cover plate combination is by described constraint elasticity anchor
Firmware 6 is constrained at the cavity 51 of railway roadbed.
On 1 each tuned mass body 3 of track travel vibration damping combination body and resonance flexible member 4 and road bed board described in this example
The kissing of road bed board cavity 51 is matched somebody with somebody, and described resonance flexible member 4 is located at the side of the direction along ng a path of resonant element tuned mass body 3
Face and bottom.The resilient support of vibration damping combination body 1 is by resonance flexible member 4 and constrains elastic anchor log 6 (Fig. 4), while vibration damping
Gap is left between the bottom surface of assembly 1 and the bottom surface of road bed board 5.
Have on the tuned mass body 3 of the resonant element 2 of vibration damping combination body 1 to facilitate the boom hoisting of detachable cover plate
31；Described boom hoisting 31 is suspension ring or pre-buried sling sleeve pipe or pre-buried sling reinforcing bar.
Described constraint elastic anchor log 6 is as shown in figure 4, constrain elastic anchor log 6 by constraint fastener 61, constraint pressing plate
62 form with constraint cushion 63；Described constraint fastener through constraint pressing plate and constraint cushion with it is pre-buried on road bed board
Part 56 is connected to constrain tuned mass body 3.
The intercity iron applications of embodiment 2-
Intercity iron service condition is as follows：Vehicle speed range 100-200km/h, fastener spacing 0.55-0.65m, fastener rigidity 10-
50kN/mm, axletree is away from minimum 2-3m.It is possible thereby to calculate frequency range below：
Train passes through driving frequency：40-100Hz；
Rail supports intrinsic frequency P2 frequency ranges：30-60Hz；
The actual design resonant frequency range thus considered is 30-100Hz.
This example carries out resonance design using 6 rank centre frequencies, and the track travel that installation includes 3 two resonant elements subtracts
Shaken assembly 1, and each two ranks resonant frequency is realized by vertical direction and transverse resonance mode respectively, and as shown in Figure 2 is multistage humorous
The design resonance center of the vertical resonance directions 33 of the unit that shakes and 34,3, multistage resonant element transverse resonance direction resonant element frequency
Rate is respectively 31.5Hz and 63Hz；40Hz and 80Hz；And 50Hz and 100Hz, the former is vertically oriented mode, and the latter is laterally
Mode.When the determination of quality rigidity and design method are same as Example 1 for modal stiffness modal mass, and corresponding mode is firm
Spending modal mass ratio is respectively：3.92E4 and 1.57E5；6.3E4 and 2.52E5；9.86E4 and 3.94E5.
The track travel vibration damping combination body 1 for including 3 resonant elements of this example can be as shown in Fig. 1 and Fig. 2, right
Road bed board cavity 51 possessed by road bed board center is answered to set, the resonant element in cover plate combination is by described constraint elasticity anchoring
Part 6 (Fig. 4) is constrained at the road bed board cavity 51 of railway roadbed.
Including the track travel vibration damping combination body 1 of 3 resonant elements can also be placed in as shown in Fig. 5, Fig. 6 and Fig. 7
Above road bed board 5.Elastic anchor log 6 is constrained by resonant element tuned mass body 3 and associated resonance flexible member 4 about
Beam is in railway roadbed plate surface.The position and quantity for constraining elastic anchor log 6 arrange that Fig. 5 is only depending on concrete condition and design requirement
Signal.Fig. 5 section B-B Fig. 6 and C-C sectional view 7 gives the position signal of two kinds of constraint elastic anchor logs 6.
Embodiment 3：High ferro application
High ferro service condition is as follows：
Vehicle speed range 250-350km/h, fastener spacing 0.55-0.65m, fastener rigidity 10-50kN/mm, axletree is away from minimum
2-3m, it is possible thereby to calculate frequency range below：
Train passes through driving frequency：100-160Hz；Rail supports intrinsic frequency P2 frequency ranges：30-60Hz
The actual design resonant frequency range thus considered is 30-160Hz
This example carries out resonance design using 4 rank centre frequencies, and installation includes the track travel of 2 two rank resonant elements
Vibration damping combination body 1, the design resonance center frequeH of each resonant element is respectively 31.5Hz and 125Hz；And 63Hz and 160Hz,
Two rank resonance center frequeHs are respectively by the vertical and horizontal realization of resonant element, the vertical resonance of multistage resonant element as shown in Figure 2
Modal stiffness modal mass point corresponding to two rank resonant elements of direction 33 and 34,2, multistage resonant element transverse resonance direction
It is not：3.92E4 and 6.17E5；And 1.57E5 and 1.01E6.
The track travel vibration damping combination body 1 for including 2 resonant elements of this example can be by examples detailed above 1 and example 2
Mounting means be arranged on road bed board.Also the diverse location of road bed board can be placed in depending on concrete engineering condition by Fig. 8-Figure 14.
Fig. 8 and Fig. 9 gives described resonant element tuned mass body 3 and associated resonance flexible member 4 disposes
The schematic diagram in road bed board cavity 51 above road bed board 5, the bottom of resonant element tuned mass body 3 and road bed board cavity 51
Face will leave space.Resonant element tuned mass body 3 and associated resonance flexible member 4 road bed board the way of restraint with
Example 1 is similar.
Embodiment 4：
It is identical to example 3 with embodiment 1, but track travel vibration damping combination body 1 is arranged on the outside of road bed board.
Figure 10 and Figure 11-14 gives described resonant element tuned mass body 3 and associated resonance flexible member 4
Other several arrangements on road bed board 5.Described resonant element tuned mass body 3 and associated resonance bullet
Property element 4 can dispose along the lateral surface 53 of road bed board 5, road bed board side end 54 or road bed board side groove 55.
Described each resonant element includes resonant element tuned mass body 3 and associated resonance flexible member 4,
Its installation position and the position of described constraint elastic anchor log 6 and quantity on road bed board 5 can be according to concrete engineering application
It is required that optimize design.
Above-mentioned example is also applied for ladder-type sleepers and the ballast bed structure of other forms.
The material of the tuned mass body 3 of described multistage resonance cover plate is metal or concrete or composite.
The resonance flexible member 4 of described multistage resonance cover plate is elastomer or geotextiles or synthesis tree made of rubber
Fat or mortar.
It is described above simply to briefly explain some principles and structure of the present utility model, not only have described structure and table
Existing form, it is all using simple modification of the present utility model and equivalent, belong to the scope of the claims that the utility model is protected.
Claims (10)
1. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly, it is characterised in that the vibration damping combination body (1) wraps
More than two multistage resonant elements (2) are included, the multistage resonant element (2) includes two or more rigidity mass ratio or no less than two
The tuned mass body (3) and resonance flexible member (4) of individual mode, described multistage resonant element (2) direction along ng a path press two
Combination arrangement above；Described multistage resonant element (2) is fixed on road bed board (5) by constraining elastic anchor log (6)；Institute
The equivalent stiffness for the constraint elastic anchor log (6) stated is less than the minimum resonance rigidity of multistage resonant element (2).
2. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In the resonant frequency range of described vibration damping combination body (1) is made up of more than two multistage resonant elements (2), vibration damping combination
The frequency band range that body (1) is formed is the segmentation frequency band of a broadband or multiple certain bandwidth.
3. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In the combination of described multistage resonant element (2) direction along ng a path is arranged in the road bed board cavity among railway roadbed in road bed board (5)
(51), and/or above road bed board (5).
4. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In described multistage resonant element (2) direction along ng a path combines the road bed board side for being arranged in railway roadbed both sides road bed board (5)
(53), or above the road bed board end (54) of road bed board (5), or on road bed board side groove (55).
5. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In the length or train of of length no more than road bed board of described multistage resonant element (2) direction along ng a path combination arrangement turn to
The two of frame wheelbase accompany, and the length range of vibration damping combination body (1) is in 0.3-6.0m.
6. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In described resonance flexible member (4) is arranged between tuned mass body (3) and road bed board (5), forms multistage resonance, multistage
Resonance realizes two or more by the elastic stiffness resonance flexible member (4) for possessing two or more direction by tuned mass body (3)
The resonance mode in direction, the resonance mode in two or more direction include three translation mode and three torsion modes or its different mould
The combination of state.
7. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 3, its feature exist
In described tuned mass body (3) is in step-like, is fastened on road bed board cavity (51), resonance flexible member (4) is arranged on humorous
Shake the bottom surface and side of mass body (3)；
Or described tuned mass body (3) is in rectangular-shape, resonance flexible member (4) is identical with its shape, positioned at its bottom
Face；
Or described tuned mass body (3) is L-shape, resonance flexible member (4) is identical with its shape, positioned at its bottom surface and side
Face.
8. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In, be disposed with described road bed board (5) installation constraint elastic anchor log (6) built-in fitting (56)；
Described constraint elastic anchor log (6) is made up of constraint fastener (61), constraint pressing plate (62) and constraint cushion (63)；
Described constraint fastener (61) is connected humorous to constrain through constraint pressing plate (62) and constraint cushion (63) with built-in fitting (56)
Shake mass body (3).
9. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In described tuned mass body (3) is provided with boom hoisting (31).
10. a kind of dismountable multistage resonant track railway roadbed power vibration damping assembly according to claim 1, its feature exist
In the material of described tuned mass body (3) is metal or concrete or composite；
Described resonance flexible member (4) is elastomer or geotextiles or synthetic resin or mortar made of rubber.
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| CN201720202823.1U CN206815108U (en) | 2017-03-03 | 2017-03-03 | A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly |
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| CN201720202823.1U CN206815108U (en) | 2017-03-03 | 2017-03-03 | A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106894299A (en) * | 2017-03-03 | 2017-06-27 | 上海工程技术大学 | A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly |
| CN109594434A (en) * | 2018-11-22 | 2019-04-09 | 同济大学 | A kind of nacre structure rail damper |
| CN114606807A (en) * | 2022-04-18 | 2022-06-10 | 武汉铁路职业技术学院 | Vibration isolation structure for reducing railway vibration |
-
2017
- 2017-03-03 CN CN201720202823.1U patent/CN206815108U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106894299A (en) * | 2017-03-03 | 2017-06-27 | 上海工程技术大学 | A kind of dismountable multistage resonant track railway roadbed power vibration damping assembly |
| WO2018157665A1 (en) * | 2017-03-03 | 2018-09-07 | 上海工程技术大学 | Detachable multi-order resonance track roadbed dynamic vibration absorption assembly |
| CN109594434A (en) * | 2018-11-22 | 2019-04-09 | 同济大学 | A kind of nacre structure rail damper |
| CN114606807A (en) * | 2022-04-18 | 2022-06-10 | 武汉铁路职业技术学院 | Vibration isolation structure for reducing railway vibration |
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