WO2023065115A1 - Dispositif d'amortissement de vibrations de chemin de fer à matériaux élastiques cylindriques - Google Patents

Dispositif d'amortissement de vibrations de chemin de fer à matériaux élastiques cylindriques Download PDF

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Publication number
WO2023065115A1
WO2023065115A1 PCT/CN2021/124710 CN2021124710W WO2023065115A1 WO 2023065115 A1 WO2023065115 A1 WO 2023065115A1 CN 2021124710 W CN2021124710 W CN 2021124710W WO 2023065115 A1 WO2023065115 A1 WO 2023065115A1
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WO
WIPO (PCT)
Prior art keywords
rail
mounting member
vibration damping
resilient
damping device
Prior art date
Application number
PCT/CN2021/124710
Other languages
English (en)
Inventor
Wai Lun Ho
Original Assignee
Jabez 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 Jabez Innovation Limited filed Critical Jabez Innovation Limited
Priority to PCT/CN2021/124710 priority Critical patent/WO2023065115A1/fr
Publication of WO2023065115A1 publication Critical patent/WO2023065115A1/fr

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

Definitions

  • 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 dampers have been widely used to reduce railway noises in newly developed railway lines and as an improved noise reduction measure in operating railways.
  • Rail dampers are generally designed to cover a large surface area on rail foot and rail web at both sides of the rail by a thin layer of resilient interface material.
  • Tuned mass damper (TMD) is commonly used among all kinds of rail dampers to enhance the vibration damping effect.
  • TMD Tuned Mass Damper
  • TMD oscillation movements are mainly translational oscillations along planes parallel to a plate-shaped mounting member, to which the TMD oscillator (s) are mounted. Rotational oscillation about the axis at the centerline of the resilient contact area may also occur simultaneously with the translational oscillations depending on the width of contact area. The narrower the contact area, the greater the rotational movement. Both translational and rotational oscillations are useful to generate TMD against rail vibrations.
  • noisy railways are normally relating to vibration resonance of the rail system.
  • Vertical and lateral rail vibrations normally resonate at different frequencies. In general vertical rail resonance frequency is higher than its lateral resonance frequency due to its higher vertical stiffness.
  • Some conventional rail dampers using TMD contain shearing resilient layers that are disposed perpendicular to the rail, where the rail damper TMD can respond to both vertical and lateral rail vibrations using the same oscillation mass.
  • the TMD frequency in vertical and lateral rail vibrations is not independently tunable.
  • the resilient layer may gradually slip off from the mounting plate in case of extremely strong rail vibration.
  • the present invention in one aspect, is a vibration damping device for reducing noise and vibrations of a rail.
  • the device includes a first oscillation mass, a mounting member for fixing the first oscillation mass to the rail; and a resilient member disposed between the first oscillation mass and the mounting member.
  • At least part of the resilient member has a substantially cylindrical shape defining a central axis that is parallel to a virtual interface plane between the mounting member and the resilient member.
  • the mounting member has a substantially plate shape which is adapted to be fastened to the rail in such a way that the mounting member is positioned substantially perpendicular to the rail.
  • the mounting member has a first side for the first oscillation mass to be fixed thereto; the first side and the interface plane being substantially perpendicular to the rail.
  • a recess is formed so as to fit the at least part of the resilient member.
  • the vibration damping device further includes a plurality of resilient members which are formed in one or more of the following configurations: one resilient member being in a straight-line shape along its length direction; one resilient member forming a ring shape around a center of the mounting member or the oscillation mass; and more than one resilient members, each being in a ring shape and separated from each other along the interface plane.
  • the plurality of resilient members each is in the straight-line shape, and the plurality of resilient members are configured to be parallel with each other along the interface plane.
  • the plurality of resilient members each extend across the entire height of the mounting member or the first oscillation mass when the vibration damping device is installed to the rail.
  • the plurality of resilient members each is in the ring shape, and are concentrically arranged around the center of the mounting member or the oscillation mass.
  • the mounting member has a second side opposite to the first side.
  • the device further contains a second oscillation mass fixed to the second side of the mounting member.
  • a vibration damping device for reducing noise and vibrations of a rail having a rail foot and a rail web.
  • the device includes a first oscillation mass, a mounting member for fixing the first oscillation mass to said rail; and a resilient member disposed between the first oscillation mass and the mounting member.
  • the resilient member has a first stiffness along a first direction, and a second stiffness along a second direction. The first stiffness or the second stiffness is determined by one or more of the following factors: a magnitude of a compression force applied to the resilient member by the mounting member or the first oscillation mass; and a surface profile of the resilient member at an interface between the resilient member and the mounting member or first oscillation mass.
  • a change in the magnitude of the compression force results in a change of a contract area between the resilient member, and the mounting member or first oscillation mass.
  • a rail damper system includes a plurality of vibration damping devices as mentioned above, and 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.
  • the cylindrical resilient members provided between the oscillation mass and the mounting member exhibit different stiffness along axial and lateral directions of the cylindrical shape.
  • the effective stiffness can also be controlled by contact surface profiles, for example particular shapes that results in different contact areas between the resilient member and the oscillation mass or the mounting member.
  • the contact area can be controlled by adjusting the compression force between the resilient member and the oscillation mass or the mounting member when the vibration damping device is installed to a rail.
  • the effective stiffness of the oscillation mass at corresponding directions can be also independently controlled.
  • TMD oscillation mass this means that the TMD frequencies for vertical and lateral rail vibrations are adjusted independently.
  • Fig. 1 is a perspective view of a vibration damping device for railway according to a first embodiment of the invention.
  • Fig. 2 shows the perspective view of the vibration damping device of Fig. 1 when it is installed to a rail.
  • Fig. 3a shows the shapes of two resilient members in the vibration damping device of Fig. 1 when less compression force is applied.
  • Fig. 3b shows the shapes of two resilient members in the vibration damping device of Fig. 1 when more compression force is applied.
  • Fig. 4 shows an oscillation mass for use in a vibration damping device according to another embodiment of the invention.
  • Fig. 5 shows an oscillation mass for use in a vibration damping device according to a further embodiment of the invention.
  • Fig. 6a shows a front view of a vibration damping device installed to a rail according to a further embodiment of the invention.
  • Fig. 6b is the side view of the vibration damping device in Fig. 6a.
  • Fig. 6c is the perspective view of the vibration damping device in Fig. 6a.
  • Figs. 1-2 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 1-2, 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, an oscillation mass 22, and a plurality of resilient members 24 configured at the interface between the mounting member 26 and the oscillation mass 22.
  • the mounting member 26 has a substantially plate shape, and as shown in Fig. 2 the mounting member 26 is installed to be perpendicular to the length of the rail 28. As shown in Fig. 1, 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. There are two opposite sides 26e of the mounting member 26 each of which is suitable for an oscillation mass to be installed to, however in Figs. 1-2 only one oscillation mass 22 is shown that is attached to one of the two sides 26e of the mounting member 26. The mounting member 26 is symmetrical on its two sides 26e which are separated from each other along its thickness direction. On each side 26e there are formed a plurality of curved recesses 36 which are parallel to each other along a horizontal, lateral direction, and all of the curved recesses 36 extend across substantially the entire the height of the curved recesses 36.
  • the plurality of resilient members 24 are shown to be located between a side 26e of the mounting member 26 and the oscillation mass 22. Because each resilient member 24 is received in a corresponding curved recess 36, and that the curved recesses 36 are parallel to each other, the plurality of resilient members 24 are also configured to be parallel to each other along a virtual interface plane 27 (see Fig. 2) and also perpendicular to the web 28b of the rail 28. In Fig. 2 the interface plane 27 extends between the head 28a and foot 28c of the rail 28, and the interface plane 27 is parallel to the mounting member 26.
  • each resilient member 24 has a substantially circular cross section, and thus each resilient member 24 is in a substantially cylindrical shape that extends along the vertical direction as in Figs. 1-2.
  • the central axis 29 of each of the resilient member 24 is therefore parallel to the interface plane 27.
  • Each resilient member 24 is partially received in a recess 22a formed on a side of the oscillation mass 22 that opposites to the mounting member 26, and the recess 22a can have the same or different shape as the curved recesses 36 on the mounting member 26.
  • FIG. 3a includes recesses 22a in substantially rectangular shape, and for the sake of simplicity, the curved recesses 36 on the side 26e of the mounting member 26 are not shown in Figs. 3a and 3b.
  • the contact surface profile as shown in Figs. 1-3b can also prevent the resilient members 24 from sliding off the oscillation mass 22 or the mounting member 26.
  • the cross-sectional shape of the resilient members 24 will change, and look like rectangles with rounded corners as shown in Fig. 3b.
  • the resilient members 24 when subjected to a larger compression force will have increased contact area with both the oscillation mass 22 and the mounting member 26, as the resilient members substantially occupies the entire inner space enclosed by the recess 22a of the oscillation mass 22.
  • the compression force applied to the resilient members 24 is configured when the user assembles different components of the vibration damping device 20 to form a complete device.
  • the compression force applied to the resilient members 24 is exerted by fasteners such as bolts where the fasteners (not shown) are used to mount the oscillation mass 22 to the mounting member 26.
  • the vibration damping device 20 has two different bolts, one for mounting the vibration damping device 20 onto the rail 28 and the other one for providing the compression force. The user then tightens or loosens the second bolt to apply a required compression force onto the resilient members 24.
  • the compression force as mentioned above makes the resilient members 24 change shape, and the larger the compression force is, the larger the contact area is between the resilient members 24, and both the oscillation mass 22 and the mounting member 26.
  • the contact area determines the dynamic stiffness of the resilient materials of the resilient members 24.
  • the TMD frequency depends on the dynamic stiffness of the resilient material. Stiffer resilient material provides higher TMD frequency according to the following equation:
  • the effective stiffness K can be controlled by 1) material bulk stiffness; 2) the area of contact surface, 3) the shape of the resilient material, 4) the contact surface profiles, in addition to 5) the compression force.
  • the compression force directly makes the area of the contact surface to change, and in turn the effective stiffness, one should realize that the resilient member 24 may be designed in a different shape, and thus has have different contact surface profile.
  • the default (e.g. minimal) compression force may also be tuned when installing the vibration damping device 20 to the rail 28 and in particular by varying the compression force exerted on the fastener.
  • parameters 1) -5) can all be individually pre-configured during the manufacturing of the vibration damping device 20 and/or installation of the same.
  • the final dynamic stiffness of the resilient members 24 will be decided by the pre-configured parameters 1) -4) which are all affected by varying the compression force exerted on the fastener.
  • the plurality of resilient members 24 are distributed along the lateral direction of the rail 28 along the interface plane 27, and they all extend substantially along the entire height of the oscillation mass 22. In this way, the TMD frequency for the vertical rail vibration is higher than that of the lateral rail vibration.
  • the difference in TMD frequencies of the vertical and lateral rail vibrations is achieved by the cylindrical shape of the resilient members 24, because a cylindrical resilient member has different stiffness along its axial and lateral directions.
  • the TMD frequency for the vertical rail vibration achieved by the resilient member 24 is higher than that of the lateral rail vibration.
  • the tunable the TMD frequencies for vertical and lateral rail vibrations can also be adjusted independently.
  • traditional sheet-like resilient layer between the oscillation mass and mounting member does not allow independent tuning of the TMD frequency along different directions.
  • the resilient member can be arranged in ring-shape to provide homogeneous stiffness along the interface plane parallel to the mounting member.
  • Fig. 4 shows an oscillation mass 122 with such a configuration according to another embodiment of the invention, although the resilient members and the mounting member are not shown.
  • the oscillation mass 122 on its side facing the mounting member has two concentrically arranged ring-shape grooves 130, each of which is adapted to receive a resilient member (not shown) .
  • the two ring-shape grooves 130 extend radially to the edges of the oscillation mass 122, and their centers falls at the geometric center 134 of oscillation mass 122 in the virtual interface plane (not shown) .
  • the resilient member partially received in a ring-shape groove 130 therefore also has a ring-shape, and has a curvature everywhere along the circumferential direction. However, it can be said that at an angular portion of the ring-shape (in particular if the portion spans a small-enough angle) the portion has a substantially cylindrical shape.
  • each of the smaller ring-shaped grooves 132 is also adapted to receive corresponding resilient member (not shown) that similar to the ones for the ring-shape groove 130 has portions in substantially the cylindrical shape.
  • the smaller ring-shaped grooves 132 are therefore off- centered from the geometric center 134 of oscillation mass 122.
  • Resilient members received in the larger ring-shape grooves 130 provide homogeneous stiffness along the interface plane in both the lateral direction and the vertical direction, and so are the resilient members received in the smaller ring-shape grooves 132.
  • Fig. 5 shows the oscillation mass 222 according to another embodiment of the invention. Compared to the one in Fig. 4, one can see that the oscillation mass 222 does not have the large, ring-shaped grooves centered at the geometric center of oscillation mass 222. Instead, the oscillation mass 222 contains both straight-line-shaped grooves 236 like those in Figs. 1-2, as well as small ring-shaped grooves 232 like those in Fig. 4. As the resilient members (not shown in Fig. 5) in both the straight-line-shaped grooves and the ring-shaped grooves 232. provide different geometry profiles along the vertical and lateral directions, the effective stiffness in the vertical direction and the lateral direction are different.
  • Figs. 6a-6c show another embodiment of the invention in which a vibration damping device 320 is installed to one side of the rail 328, but in the vibration damping device 320 there are two oscillation masses 322 installed to both sides of the mounting member 326.
  • the oscillation masses 322 are identical to each other, and the configuration of resilient members 324 between the oscillation masses 322 and the mounting member 326 is generally the same as that in Figs. 1-2.
  • the paired oscillating masses 322 sandwich the mounting plate 326 from both sides to balance the damping forces of the mounting plate 326 and minimize any potential rotational movement of the mounting plate 326.
  • 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 shape, orientation and position of the resilient material between the mounting member and the oscillation mass, and how the resilient material is held by the mounting member and the oscillation mass.
  • 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.
  • one to two oscillators are installed on each vibration damping device.
  • any number of oscillators may be installed on a vibration damping device depending on the type and number of mounting devices.

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

Abstract

La présente invention concerne un dispositif d'amortissement de vibrations destiné à réduire le bruit et les vibrations d'un rail. Le dispositif comprend une première masse d'oscillation, un élément de montage pour fixer la première masse d'oscillation au rail ; et un élément élastique disposé entre la première masse d'oscillation et l'élément de montage. Au moins une partie de l'élément élastique a une forme sensiblement cylindrique définissant un axe central qui est parallèle à un plan d'interface virtuel entre l'élément de montage et l'élément élastique. Le matériau élastique cylindrique a une rigidité différente le long des directions axiale et latérale. La rigidité effective peut également être commandée par des profils de surface de contact. Ceci permet d'accorder les fréquences TMD pour les vibrations de rail verticales et latérales indépendamment.
PCT/CN2021/124710 2021-10-19 2021-10-19 Dispositif d'amortissement de vibrations de chemin de fer à matériaux élastiques cylindriques WO2023065115A1 (fr)

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PCT/CN2021/124710 WO2023065115A1 (fr) 2021-10-19 2021-10-19 Dispositif d'amortissement de vibrations de chemin de fer à matériaux élastiques cylindriques

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PCT/CN2021/124710 WO2023065115A1 (fr) 2021-10-19 2021-10-19 Dispositif d'amortissement de vibrations de chemin de fer à matériaux élastiques cylindriques

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117005251A (zh) * 2023-08-04 2023-11-07 华东交通大学 一种轨道吸振隔声装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0872593A1 (fr) * 1997-04-18 1998-10-21 Gmundner Fertigteile Gesellschaft m.b.H. & Co. KG. Couverture pour passage à niveau de voies ferrées
EP1988213A1 (fr) * 2007-05-02 2008-11-05 edilon)(sedra B.V. Élément support de rail préfabriqué
CN101413232A (zh) * 2008-11-11 2009-04-22 中国船舶重工股份有限公司洛阳分公司 一种楔式安装的浮轨减振降噪扣件设计方法及装置
CN104894928A (zh) * 2015-06-12 2015-09-09 洛阳双瑞橡塑科技有限公司 一种轨道交通用钢轨吸振装置
CN107938439A (zh) * 2017-12-20 2018-04-20 中铁二院工程集团有限责任公司 带吸振器阻尼钢轨
CN110747701A (zh) * 2019-10-12 2020-02-04 隆昌瑞博轨道科技有限公司 一种钢轨用阻尼护套系统
CN112796177A (zh) * 2021-01-29 2021-05-14 中国铁道科学研究院集团有限公司城市轨道交通中心 一种装配式各向同频钢轨阻尼吸振器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0872593A1 (fr) * 1997-04-18 1998-10-21 Gmundner Fertigteile Gesellschaft m.b.H. & Co. KG. Couverture pour passage à niveau de voies ferrées
EP1988213A1 (fr) * 2007-05-02 2008-11-05 edilon)(sedra B.V. Élément support de rail préfabriqué
CN101413232A (zh) * 2008-11-11 2009-04-22 中国船舶重工股份有限公司洛阳分公司 一种楔式安装的浮轨减振降噪扣件设计方法及装置
CN104894928A (zh) * 2015-06-12 2015-09-09 洛阳双瑞橡塑科技有限公司 一种轨道交通用钢轨吸振装置
CN107938439A (zh) * 2017-12-20 2018-04-20 中铁二院工程集团有限责任公司 带吸振器阻尼钢轨
CN110747701A (zh) * 2019-10-12 2020-02-04 隆昌瑞博轨道科技有限公司 一种钢轨用阻尼护套系统
CN112796177A (zh) * 2021-01-29 2021-05-14 中国铁道科学研究院集团有限公司城市轨道交通中心 一种装配式各向同频钢轨阻尼吸振器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117005251A (zh) * 2023-08-04 2023-11-07 华东交通大学 一种轨道吸振隔声装置
CN117005251B (zh) * 2023-08-04 2024-02-23 华东交通大学 一种轨道吸振隔声装置

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