WO2022100553A1 - Dispositif d'amortissement de vibrations de chemin de fer à masses d'oscillation réfléchissantes - Google Patents

Dispositif d'amortissement de vibrations de chemin de fer à masses d'oscillation réfléchissantes Download PDF

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Publication number
WO2022100553A1
WO2022100553A1 PCT/CN2021/129372 CN2021129372W WO2022100553A1 WO 2022100553 A1 WO2022100553 A1 WO 2022100553A1 CN 2021129372 W CN2021129372 W CN 2021129372W WO 2022100553 A1 WO2022100553 A1 WO 2022100553A1
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WO
WIPO (PCT)
Prior art keywords
rail
vibration damping
damping device
mounting member
oscillation
Prior art date
Application number
PCT/CN2021/129372
Other languages
English (en)
Inventor
Wai Lun Ho
Tsz Fung Dominic TSE
Original Assignee
Wai Tat Innovation Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wai Tat Innovation Limited filed Critical Wai Tat Innovation Limited
Publication of WO2022100553A1 publication Critical patent/WO2022100553A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B19/00—Protection of permanent way against development of dust or against the effect of wind, sun, frost, or corrosion; Means to reduce development of noise
    • E01B19/003—Means for reducing the development or propagation of noise

Definitions

  • This invention relates to railway installations, and in particular to rail damper structures for reduction of rail vibration and noise generated from the railway.
  • Rail damper is generally designed to have a large area in contact with rail surface through resilient interfacing material hoping to maximize vibration dissipation at the interface and transmit the remaining vibration energy into the rail damping for further dissipation.
  • the resilient interfacing material should be relatively thick and soft.
  • rail vibration is partially isolated from the rail damper, such that a significant portion of rail vibration energy is neither dissipated at the interface nor transmitted to rail damper, i.e., reflected back into the rail.
  • the performance of rail damper is discounted significantly.
  • Pin-pin resonance is found to be a general characteristic of noisy rails.
  • Tuned Mass Dampers are commonly used in rail dampers to provide a reaction damping force that is amplified to several times its weight at the pin-pin resonance frequency, but at the expense of a narrower frequency damping bandwidth. Higher mounting force is required for the amplified reaction damping force.
  • Rail damper mounting clips of existing designs (even with adhesives) fail to provide sufficient mounting force to overcome the TMD amplified damping force.
  • the clips currently used in the industry only provide mounting forces around 100kg per damper and may be up to 300kg per damper with specific designs for extreme cases. With such mounting force under strong rail vibration, existing rail dampers would be temporarily disengaged from the rail by a fraction of micrometers. The mounting force is insufficient to overcome the acceleration force at the peak of TMD oscillation cycles, and rail damper performance is therefore discounted.
  • rail vibration along vertical and lateral directions is the main concern, while vibration in the longitudinal direction along the rail is not important.
  • the vertical and lateral rail vibrations are oscillation movements along a plane aligned perpendicular to the rail.
  • normally rails have different vertical and lateral pin-pin resonant frequencies.
  • Vertical rail vibrations are typically higher than lateral rail vibrations.
  • the TMD in rail dampers are commonly designed to suppress only the vertical pin-pin resonance in order to minimize the number of TMD and total mass in the rail damper.
  • a single TMD can suppress both vertical and lateral pin-pin resonances in different frequencies without additional masses.
  • a rail damper is preferred to have a small area in contact with the rail surface, such that most of the rail surface is easily viewable for routine rail maintenance inspections.
  • the present invention provides in one aspect a vibration damping device for reducing noise and vibrations of a rail, where the rail has a top, a web and a foot.
  • the device contains a first oscillation mass, a second oscillation mass, a mounting member for fixing the first and second oscillation masses to said rail; and resilient materials disposed between the first oscillation mass and the mounting member, and between the second oscillation mass and the mounting member.
  • the first and second oscillation masses are symmetrically installed to two sides of the mounting member, the two sides being substantially opposite to each other.
  • the mounting member has a substantially plate shape, and is adapted to be fastened to the rail in such a way that the mounting member is positioned substantially perpendicular to the rail.
  • the vibration damping device further contains an under-rail bolt that is adapted to secure the mounting member to the rail.
  • the two sides of the mounting member are parallel to each other such that the first and second oscillation masses are configured parallel to each other.
  • a distance between the two sides of the mounting member varies along a vertical direction when the vibration damping device is installed to the rail.
  • a distance between the two sides of the mounting member varies along a lateral direction of the rail when the vibration damping device is installed to the rail.
  • At least one of the first oscillation mass and the second oscillation mass has a flat disc shape.
  • the resilient material disposed between the first oscillation mass and the mounting member, or between the second oscillation mass and the mounting member has different stiffnesses at different portions of the resilient material, so that both rotational vibration and translational vibrations are caused to the resilient material.
  • the resilient material has a region of higher stiffness offset from a center of the resilient material, and a region of lower stiffness covering the center.
  • the resilient material has multiple said regions of lower stiffness at the top and bottom ends of the resilient material.
  • the mounting member contains two mounting plates each of which providing one said side of the mounting member; the first and second oscillation masses each installed to a respective one of the two mounting plates.
  • a distance between the two mounting plates varies along a vertical direction when the vibration damping device is installed to the rail.
  • the two mounting plates each have a first portion that abuts each other; as well as a second portion that are separated from each other, so that the two mounting plates form a "Y" shape when observed from a lateral direction of the rail when the vibration damping device is installed to the rail.
  • a rail damper system including a plurality of vibration damping devices as mentioned above which are installed to a railway.
  • the plurality of vibration damping devices is positioned along a longitudinal direction of a rail, and/or positioned symmetrically on rail of the railway.
  • Tuned Mass Dampers are used in rail vibration damping devices for reduction of rail vibration and noise emission from the railway system.
  • a device has a small and rigid contact area on the rail surface and can provide strong mounting with an under-rail bolt underneath the rail.
  • the rail vibration damping device provides amplified damping force strong enough to slow down rail corrugation growth, and to reduce civil structure vibration and its associated ground-borne/structure-borne noise.
  • the oscillation mass movements are designed to have amplified reactions to the vertical and lateral rail vibration, mostly by the translational oscillation and relatively small rotational oscillation.
  • the movement of the two oscillation masses is designed to be in the same direction during the oscillation cycles. If there is rotational oscillation, the resilient material undergoes localized compression and tension for rotation, in addition to shearing for translational oscillation.
  • Fig. 1a is a perspective view of a vibration damping device installed to a rail according to a first embodiment of the invention.
  • Fig. 1b is a front view of a mounting member of the vibration damping device in Fig. 1a.
  • Fig. 1c shows the dissembled status of the vibration damping device in Fig. 1a.
  • Fig. 2 is a cross-sectional view of two vibration damping devices installed to a rail according to another embodiment of the invention.
  • Fig. 3 is a side view showing a vibration damping device with two oscillation masses forming an angle with each other in the vertical direction, according to a further embodiment of the invention.
  • Fig. 4 is a top view showing a vibration damping device with two oscillation masses forming an angle with each other in the lateral direction, according to a further embodiment of the invention.
  • Fig. 5 is a perspective view of a vibration damping device installed to a rail according to another embodiment of the invention.
  • Figs. 6-8 show respectively variations of the vibration damping device in which portions of the resilient materials have different stiffnesses, according to further embodiments of the invention.
  • Figs. 9a-9b show respectively a perspective view and a side view of a vibration damping device according to a further embodiment of the invention.
  • Figs. 10a-10b show respectively a perspective view and a side view of the mounting member of a vibration damping device according to a further embodiment of the invention.
  • Figs. 1a-1c show a vibration damping device 20 according to a first embodiment of the invention which is suitable for attaching to a rail 28 .
  • the rail 28 has a typical flat-bottom profile that is standard to most modern railway systems in the world.
  • the rail 28 has a foot 28c , a web 28b , and a head 28a . In the embodiment of Figs. 1a-1c, it is the foot 28c and the web 28b of the rail 28 onto which the vibration damping device 20 is mounted.
  • the vibration damping device 20 is installed to the outer side of the rail 28 , i.e., the side adjacent to an end of the sleeper (not shown).
  • the vibration damping device 20 includes a mounting member 26 , two oscillation masses 22 , and two resilient members 24 . Each resilient member 24 is made from a resilient material and is configured at the interface between the mounting member 26 and one oscillation mass 22 .
  • the mounting member 26 has a substantially plate shape, and as shown in Fig. 1a the mounting member 26 is installed to be perpendicular to the length of the rail 28 . As shown in Fig. 1b, the mounting member 26 contains a rail foot contact portion 26a , and a rail web contact portion 26b , where a smooth, curved edge 26c connects the rail foot contact portion 26a and the rail web contact portion 26b .
  • the rail foot contact portion 26a is a stiff mounting clip which is dragged into a wedge-shaped rail foot tip by a horizontal pulling (or pushing) force from an under-rail bolt 32 underneath the rail. There are two opposite sides 26e (see Fig.
  • each of which is suitable for an oscillation mass to be installed via the resilient member 24 , as shown in Fig. 1a.
  • the mounting member 26 is symmetrical in shape on its two sides 26e which are separated from each other along its thickness direction.
  • the two sides 26e of the mounting member 26 are parallel to each other such that the two oscillation masses 22 are also configured parallel to each other.
  • Each side 26e defines a dissipating surface 26f , and thus each resilient member 24 (i.e., the resilient material) is sandwiched between a dissipating surface 26f and a corresponding oscillation mass 22 .
  • each resilient member 24 i.e., the resilient material
  • the paired dissipating surfaces 26f , resilient members 24 and oscillation masses 22 are mirror-symmetric about a virtual mirror plane 34 which is perpendicular to the rail 28 and which divides the mounting member 26 into two equal halves.
  • a lateral axis 36 and a vertical axis 38 can be defined, where the lateral axis 36 and the vertical axis 38 are perpendicular to each other.
  • the vertical axis 38 divides the rail 28 equally into two parts along the lateral direction
  • the lateral axis 36 divides each oscillation mass 22 equally into two parts along the vertical direction.
  • Each one of the pair of the dissipating surfaces 26f , the resilient members 24 and the oscillation masses 22 constitute a TMD 44 . Therefore, in the vibration damping device 20 shown in Figs. 1a and 1c there are two TMDs 44 .
  • the vibration damping device 20 When the vibration damping device 20 is installed to the rail 28 as shown in Fig. 1, the rail foot 28c is received in the tapering recess formed between the curved edge 26c and the rail foot contact portion 26a . In the meantime, the curved edge 26c is partially urged against the rail web 28b , in particular near the upper end of the curved edge 26c . As such, there are multiple contact points formed between the vibration damping device 20 and the rail 28 , and because of the pulling (or pushing) force from the under-rail bolt 32 the vibration damping device 20 is tightly secured to the rail 28 with a good transmission of vibrations from the rail 28 to the vibration damping device 20 , and further to the oscillation masses 22 in the vibration damping device 20 .
  • each oscillation mass 22 has a flat disc shape.
  • Movements of the oscillation masses 22 are designed to have amplified reactions to the vertical and lateral rail vibration, mostly by the translational oscillation and relatively small rotational oscillation.
  • the movements of the two oscillation masses 22 are designed to be in the same direction during the oscillation cycles. If there is rotational oscillation, the resilient members 24 undergoes localized compression and tension for rotation in addition to shearing for translational oscillation.
  • Fig. 2 in which another embodiment of the invention is shown.
  • two identical vibration damping devices 120 are symmetrically installed on two lateral sides of the rail 128 , and each vibration damping device 120 contains two TMDs like the embodiment shown in Figs. 1a and 1c.
  • each vibration damping device 120 contains two TMDs like the embodiment shown in Figs. 1a and 1c.
  • the assembly shown in Fig. 2 there are in total four TMDs.
  • For each one of the vibration damping devices 120 its installation is similar to that shown in Figs. 1a-1c.
  • the two vibration damping devices 120 are coupled by a single under-rail bolt 132 so that the two vibration damping devices 120 are firmly coupled to the rail 128 to allow effective vibration transmission.
  • a compression bolt 130 secures the oscillation masses 122 to respective dissipating surfaces 126f of the sides 126e of the mounting member 126 .
  • a mirror plane 134 , a lateral axis 136 and a vertical axis 138 can be defined for the two vibration damping devices 120 .
  • Fig. 3 shows a vibration damping device 220 according to a third embodiment of the invention, where the two sides 226e of the mounting member 226 form an angle with each other.
  • a distance between the two sides 226e of the mounting member 226 varies along a vertical direction (as defined by a vertical axis 238 ), as the distance is smaller near the head 228a of the rail 228 , and larger near the foot 228c of the rail 228 .
  • the distance mentioned here refers to the dimension of the mounting member 226 along a direction parallel to the longitudinal axis 246 of the rail 228 .
  • the vibration damping device 220 similar to previous embodiments is secured to the rail 228 by an under-rail bolt 232 at a rail foot contact portion 226a .
  • a mirror plane 234 and a lateral axis 236 can be defined for the vibration damping device 220 .
  • the two oscillation masses 222 in Fig. 3 as they are being secured to the mounting member 226 by a compression bolt 230 experience translational movements containing slight movements along the longitudinal axis 246 in addition to the major vertical translational movements along a plane parallel to the mirror plane 234 , in reaction to vertical rail vibrations.
  • Such longitudinal movements of the two oscillation masses 222 are designed to be in opposite directions during the oscillation cycles.
  • the vertical translational oscillations of the TMDs 244 consist of both shearing and compression actions onto the resilient members 240 while the lateral translational oscillations of the TMDs 244 consist mostly of a shearing action.
  • the effective stiffness along the vertical direction is larger than that along the lateral direction. Consequently, the vertical TMD frequency can be controlled higher than the lateral TMD frequency by varying the inclination angle. It should be noted that generally compression stiffness is significantly larger than shear stiffness for various resilience materials.
  • Fig. 4 shows two vibration damping devices 320 according to a fourth embodiment of the invention, where the two sides 326e of the mounting member 326 of each vibration damping device 320 form an angle with each other.
  • a distance between the two sides 326e of the mounting member 326 varies along a lateral direction (as defined by a lateral axis 336 ), as the distance is smaller near the end of the mounting member 326 that is away from the web (not shown) of the rail 328 .
  • the distance mentioned here refers to the dimension of the mounting member 326 along a direction parallel to the longitudinal axis 346 of the rail 328 .
  • a mirror plane 334 and a vertical axis 338 can be defined for each of the vibration damping devices 320 .
  • each vibration damping device 320 in Fig. 3 experiences translational movements containing slight movements along the longitudinal axis 346 in addition to the major lateral translational movements along a plane parallel to the mirror plane 334 , in reaction to lateral rail vibrations.
  • Such longitudinal movements of the two oscillation masses 322 are designed to be in opposite directions during the oscillation cycles.
  • the lateral translational oscillations of the TMDs 344 consist of both shearing and compression actions onto the resilient members 324 while the vertical translational oscillations of the TMDs 344 consist mostly of a shearing action.
  • the effective stiffness along the lateral direction is larger than that along the vertical direction. Consequently, the effective TMD frequency along the lateral direction can be controlled higher than the vertical TMD frequency by varying the inclination angle.
  • a vibration damping devices 420 containing two TMDs 444 according to a fifth embodiment of the invention is shown.
  • the vibration damping device 420 notably contains two separate mounting plates 450 that are separated from each other substantially.
  • the thickness of each mounting plate 450 can be the same or smaller than a mounting member as a single piece.
  • the distance between the two separate mounting plates 450 varies along a vertical direction (as defined by a vertical axis 438 ), as the distance is smaller near the head 428a of the rail 428 , and larger near the foot 428c of the rail 428 .
  • the distance mentioned here refers to the dimension along a direction parallel to the longitudinal axis 446 of the rail 428 .
  • the vibration damping device 420 similar to previous embodiments is secured to the rail 428 by an under-rail bolt 432 at a rail foot contact portion 426a .
  • the under-rail bolt 432 is wider and has a rectangle cross-section for it to couple to both mounting plates 450 .
  • a mirror plane 434 and a lateral axis 436 can be defined for the vibration damping devices 420 .
  • a compressive force is provided to push the two separated mounting plates 450 towards the mirror plane 434 by a compression bolt 448 passing through the two separated mounting plates 450 . Because of the vertically inclined mounting plates 450 , and resilient members 424 attached thereto, the two oscillation masses 422 also form an angle with each other.
  • This arrangement with the separated mounting plates 450 allows a relative movement between the two separated mounting plates 450 during the installation of the vibration damping device 450 onto the rail 428 .
  • the relative movement can provide tolerance adjustments during the damper installation process and provide a better-balanced mounting force on uneven mounting surfaces.
  • thinner separated mounting plates facilitate the manufacturing process by using laser cutting or wire cutting to open up more options for lowering the manufacturing cost.
  • Fig. 6 shows a vibration damping device 520 containing two TMDs 544 according to a sixth embodiment of the invention.
  • the vibration damping device 520 notably contains two resilient members 524 that each has varying stiffness at the sides of the resilient members 524 .
  • Such a configuration allows providing different TMD frequencies respectively in the vertical and lateral directions even if the dissipating surfaces 526f are not inclined to each other, i.e., when they are kept parallel to each other like the case in Figs. 1a-1c.
  • Fig. 6 shows a vibration damping device 520 containing two TMDs 544 according to a sixth embodiment of the invention.
  • the vibration damping device 520 notably contains two resilient members 524 that each has varying stiffness at the sides of the resilient members 524 .
  • Such a configuration allows providing different TMD frequencies respectively in the vertical and lateral directions even if the dissipating surfaces 526f are not inclined to each other, i.e., when they are kept parallel to each
  • each resilient member 524 adopt different stiffness.
  • a mirror plane 534 can be defined for the vibration damping device 520 .
  • Fig. 7 shows a vibration damping device 620 containing two TMDs 644 according to a seventh embodiment of the invention.
  • the vibration damping device 620 notably contains two resilient members 624 that each has varying stiffness at the sides of the resilient members 624 .
  • Such a configuration allows providing different TMD frequencies respectively in the vertical and lateral directions even if the dissipating surfaces 626f are not inclined to each other, i.e., when they are kept parallel to each other like the case in Figs. 1a-1c.
  • Fig. 7 shows a vibration damping device 620 containing two TMDs 644 according to a seventh embodiment of the invention.
  • the vibration damping device 620 notably contains two resilient members 624 that each has varying stiffness at the sides of the resilient members 624 .
  • Such a configuration allows providing different TMD frequencies respectively in the vertical and lateral directions even if the dissipating surfaces 626f are not inclined to each other, i.e., when they are kept parallel to each
  • each resilient member 624 adopt different stiffness.
  • the central portion 652 represented by shadow lines and cover a central hole 624a of the resilient member 624 ) has a higher stiffness than two side portions 654 .
  • a mirror plane 634 can be defined for the vibration damping device 620 .
  • Fig. 8 shows a vibration damping device 720 containing two TMDs 744 according to an eighth embodiment of the invention.
  • the vibration damping device 720 notably contains two resilient members 724 that each has varying stiffness at the sides of the resilient members 724 .
  • Such a configuration allows providing different TMD frequencies respectively in the vertical and lateral directions even if the dissipating surfaces 726f are not inclined to each other, i.e., when they are kept parallel to each other like the case in Figs. 1a-1c.
  • the localized spot 752 has a round shape and is offset from a central hole 724a through which a compression bolt 730 secures two oscillation masses 722 to the mounting member 726 .
  • a compression bolt 730 secures two oscillation masses 722 to the mounting member 726 .
  • the configuration of the localized spot 752 configuration allows rotational oscillation along shearing surfaces of each resilient member 724 , and such rotation is a left-and-right oscillation around a rotational axis 756 that is parallel to the length direction of the rail (not shown).Like the embodiment in Fig. 1a, a mirror plane 734 can be defined for the vibration damping device 720 .
  • An alternative vibration damping device 820 has a mounting member 826 that consists of two mounting plates 850 similar to the configuration in Fig. 5. However, as compared to the embodiment in Fig. 5, the vibration damping device 820 additionally contains two spacing rods 860 placed between opposite inner surfaces 850a of the mounting plates 850 , as well as two spacing slots 858 formed on the dissipating surfaces 826f on the outer sides 826e of the mounting plates 850 .
  • the two spacing rods 860 have different diameters while both extending along a lateral direction of the rail (not shown), and the different diameters make respective spacing slot 858 fit into the varying distances between the opposite inner surfaces 850a .
  • the spacing slots 858 each has a rectangular shape, and they are spaced at different distances to the central hole 824a at the dissipating surfaces 826f .
  • the locations of the spacing slots 858 align with those of the spacing rods 860 in the vertical direction as each spacing rod 860 is partially received in its two corresponding spacing slots 858 .
  • the inclination angle of the two mounting plates 850 relative to the vertical direction could be controlled by respective diameters of the two spacing rods 860 , thus providing control over the effective stiffness of the resilient members 824 along the vertical and lateral directions.
  • each mounting plate 850 is formed with a rail foot contact portion 826a similar to that in previous embodiments.
  • Figs. 10a-10b shows a vibration damping device 920 according to a tenth embodiment of the invention.
  • the vibration damping device 920 has a mounting member 926 that consists of two mounting plates 950 .
  • the mounting plates 950 are not in flat, plate shapes. Rather, each mounting plate 950 contains a base portion 950a , a leg portion 950c , and a transition portion 950b connecting the base portion 950a and the leg portion 950c .
  • the base portion 950a and the leg portion 950c are parallel to each other but are offset from each other in the thickness direction of the base portion 950a .
  • the mounting plate 950 has a folded design.
  • the two mounting plates 950 are assembled by using for example adhesives between the base portions 950a .Therefore, for the two mounting plates 950 , while their base portion 950a abut each other, their leg portions 950c are separate from each other.
  • the two mounting plates 950 form a “Y” shape when observed from a lateral direction of the rail when the vibration damping device is installed 920 to the rail.
  • the mounting member is a plate-like piece.
  • the mounting member may take any form, and/or installed to a rail in any manner, while still being encompassed by the invention.
  • the oscillation mass may take any form or dimension.
  • the spirit of the invention lies in the symmetrical arrangement of TMDs on two sides of a mounting member, and the internal structure and/or shape of each TMD including the oscillation mass, the resilient member and the dissipating surface can be varied by skilled persons in the art as needed.
  • the rail that the vibration damping device is suitable to use with a rail that has a flat-bottom profile, which is common in most modern railways.
  • a rail that has a flat-bottom profile which is common in most modern railways.
  • other types of rails may also be suitable to be used by the vibration damping device according to the invention which may have different cross-sectional shapes.
  • the two separate mounting plates are inclined to each other.
  • the mounting plates can also be made parallel to each other (e.g., the configuration of the base portions in Figs. 10a and 10b).

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un dispositif d'amortissement de vibrations qui est conçu pour réduire le bruit et les vibrations d'un rail, le rail ayant une partie supérieure, une bande et un pied. Le dispositif comprend une première masse d'oscillation, une seconde masse d'oscillation, un élément de montage pour fixer les première et seconde masses d'oscillation au rail, et des matériaux élastiques disposés entre la première masse d'oscillation et l'élément de montage, et entre la seconde masse d'oscillation et l'élément de montage. Les première et seconde masses d'oscillation sont installées symétriquement sur deux côtés de l'élément de montage, les deux côtés étant sensiblement opposés l'un à l'autre. Outre la réduction de la vibration du rail et de l'émission de bruit, la présente invention fournit une force d'amortissement amplifiée suffisamment résistante pour ralentir la croissance des ondulations de rail, et pour réduire les vibrations de structure civile et son bruit de structure/plancher associé.
PCT/CN2021/129372 2020-11-10 2021-11-08 Dispositif d'amortissement de vibrations de chemin de fer à masses d'oscillation réfléchissantes WO2022100553A1 (fr)

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US202063111640P 2020-11-10 2020-11-10
US63/111,640 2020-11-10

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WO2022100553A1 true WO2022100553A1 (fr) 2022-05-19

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0761879A1 (fr) * 1995-09-06 1997-03-12 Hutchinson Absorbeur de bruit pour rails d'une voie ferrée
EP1876295A2 (fr) * 2006-07-03 2008-01-09 Corus UK LTD. Amortisseurs de rails
CN101849068A (zh) * 2007-11-07 2010-09-29 何伟麟 可调谐震动吸收装置
CN102713066A (zh) * 2009-12-14 2012-10-03 威信声学顾问有限公司 铁轨震动吸收器和紧固机构
CN203346739U (zh) * 2013-07-10 2013-12-18 铁道第三勘察设计院集团有限公司 轨道吸振器
CN107254814A (zh) * 2017-03-14 2017-10-17 上海工程技术大学 一种多阶剪切型钢轨动力阻尼吸振器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0761879A1 (fr) * 1995-09-06 1997-03-12 Hutchinson Absorbeur de bruit pour rails d'une voie ferrée
EP1876295A2 (fr) * 2006-07-03 2008-01-09 Corus UK LTD. Amortisseurs de rails
CN101849068A (zh) * 2007-11-07 2010-09-29 何伟麟 可调谐震动吸收装置
CN102713066A (zh) * 2009-12-14 2012-10-03 威信声学顾问有限公司 铁轨震动吸收器和紧固机构
CN203346739U (zh) * 2013-07-10 2013-12-18 铁道第三勘察设计院集团有限公司 轨道吸振器
CN107254814A (zh) * 2017-03-14 2017-10-17 上海工程技术大学 一种多阶剪切型钢轨动力阻尼吸振器

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