[go: up one dir, main page]

EP0873928A1 - Seitliches Auflager für ein Eisenbahn-Drehgestell - Google Patents

Seitliches Auflager für ein Eisenbahn-Drehgestell Download PDF

Info

Publication number
EP0873928A1
EP0873928A1 EP98302271A EP98302271A EP0873928A1 EP 0873928 A1 EP0873928 A1 EP 0873928A1 EP 98302271 A EP98302271 A EP 98302271A EP 98302271 A EP98302271 A EP 98302271A EP 0873928 A1 EP0873928 A1 EP 0873928A1
Authority
EP
European Patent Office
Prior art keywords
rigid
elastomeric
side bearing
bearing
respect
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP98302271A
Other languages
English (en)
French (fr)
Inventor
John G. Faryniak
James S. Kennedy
Aubra D. Mckisic
James F. Wright
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hansen Inc
Original Assignee
Hansen Inc
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 Hansen Inc filed Critical Hansen Inc
Publication of EP0873928A1 publication Critical patent/EP0873928A1/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/14—Side bearings
    • B61F5/142—Side bearings made of rubber elements, graphite or the like

Definitions

  • railway truck side bearings are those which employ elastomeric elements to provide some or all of the load bearing capacity afforded by the bearing as well as hunting response restraint.
  • elastomeric elements include those disclosed in U.S. patents 4,715,290, 3,707,927, 3,670,661, 4,434,720, 3,045,998, 3,895,206, 4,355,583, 4,030,424 and 5,386,783.
  • U.S. patent 3,957,318 is another example of a side bearing utilizing elastomeric bearing elements.
  • a constant contact side bearing is characterized as a constant contact side bearing, because the bearing assembly becomes engaged in load bearing engagement between the railway truck and the car body during the setup process when the car body is mounted on the truck.
  • a constant contact side bearing remains in load bearing engagement, and preferably uniform load bearing engagement, between the truck and the car body throughout the entire range of car body motion relative to the truck. This includes, most notably, the entire range of car body roll motion.
  • the present invention contemplates a novel and improved constant contact side bearing having improved vertical travel characteristics whereby improved bearing load response in the normal bearing operating range is achieved.
  • the bearing of this invention preferably employs compliant bearing assemblies of elastomeric elements bonded to rigid substrates.
  • the bearing assemblies are configured in a novel way to provide an extended vertical travel or movement characteristic through reliance primarily on shear deformation of the elastomeric bearing elements as the vertical height of the bearing varies in response to changes in the vertical spacing between the truck and the car body at the bearing location.
  • the increased vertical travel available with this side bearing allows for greater setup height tolerance or variation and a controlled spring rate in the operating range.
  • the force deflection characteristic of the novel bearing can be customized by varying any of a variety of geometric, structural or dimensional specifications. These may include the deformation characteristics of the elastomeric elements, their section thicknesses, the number of elastomer sections employed, the shape or geometry of unbonded elastomeric surfaces, employment of multiple elastomeric materials of differing deformation characteristics, and so forth.
  • the invention also contemplates use of elastomeric bearing elements such as above characterized in conjunction with appropriate solid stops to limit the maximum elastomer deformation which can occur in operation of the bearing.
  • the novel side bearing includes modular assemblies of elastomeric elements bonded to rigid substrates such as steel in configurations to provide a relatively lower stiffness or spring rate in response to vertical deformation of the elastomeric elements in shear, while providing a relatively greater stiffness or spring rate in the longitudinal direction as a response to compressive deformation of the elastomeric elements.
  • the longer vertical travel for the bearing thus is achieved without compromising longitudinal stiffness which is desirable for assisting in control of hunting.
  • novel side bearing can include employment of tapered or other shapes for unbonded elastomer surfaces, and variation in the shape of the substrates to which elastomeric elements are bonded.
  • a further object of the invention is to provide a railway vehicle side bearing with extended vertical travel achieved through use of elastomeric bearing assemblies.
  • Another object of the invention is to provide a constant contact side bearing with a force-deflection characteristic achieved primarily through deformation of elastomeric elements in vertical shear.
  • a railway truck side bearing according to one embodiment of the instant invention and comprising a rigid, unitary bearing housing 12 having a base portion 14 with mounting flanges 16, and an upstanding, generally cylindrical perimeteral wall portion 18.
  • Flanges 16 include through openings 20 to receive suitable fasteners such as rivets or nut and bolt assemblies (not shown) for securing the side bearing 10 to a railway truck bolster (not shown) or comparable structure.
  • a bearing assembly 22 is received within the confines of perimeteral wall 18, the assembly 22 being comprised of plural, concentric elastomeric rings 24 and 26 having confronting cylindrical surfaces 28 and 30 thereof suitably bonded to a rigid, cylindrical substrate 32 of steel, for example.
  • the inner cylindrical wall 34 of elastomeric element 26 is similarly bonded to a rigid cylindrical substrate 36, and the radially outermost cylindrical wall 38 of elastomeric element 24 is similarly bonded to the cylindrical inner surface 40 of bearing carrier wall portion 18.
  • the plural elastomeric elements 24 and 26, as well as the cylindrical substrate elements 32 and 36, are arranged in mutually concentric relationship about axis X-X with respect to wall 18. Further, the radially inner elastomeric element 26 is positioned to extend vertically above the radially outer elastomeric element 24, and similarly substrate element 36 is positioned to extend vertically above substrate element 32. Additionally, both of the substrate elements 32 and 36 extend above the uppermost extent of either elastomeric element 24 or 26.
  • a vertical clearance 42 (Fig. 1) is provided between all elements of bearing assembly 22 and the upper surface 44 of base 14 to permit a range of vertical motion for elements of bearing assembly 22 upon application of downwardly directed loads L thereto.
  • the bonding of the elastomeric elements to the metal substrates allows a side bearing with lower stiffness or spring rate in a vertical direction, while providing much greater stiffness in the horizontal direction.
  • much larger strains in the elastomeric material can be sustained with less permanent set or damage to the material.
  • the shape of the force-deflection curve for a side bearing such as disclosed in Figs. 1 and 2 may be readily tailored to a specific application.
  • the overall force-deflection characteristic for the side bearing of Fig. 1 and 2 embodiments can be customized by such variations as the elastomeric material selected, the geometry of the elastomeric elements, the number of elastomeric elements used, and the shape of both the bonded and unbonded elastomer surfaces.
  • preloading the side bearing in various ways. For example, preloading the elastomer in shear, tension, compression or torsion can assist in generating the initial stiffness of the bearing so that the shear loading which the elastomer undergoes during setup will not have to generate as high a force response in order to provide adequate performance. It is to be appreciated that torsion is merely a special case of shear loading.
  • the loading conventionally referred to as shear is developed by applying equal and opposite forces in planes parallel to the bonded interfaces between the substrates and the elastomeric element, whereas torsion is developed by applying equal and opposite torques to the substrate elements in planes parallel to the bonded faces.
  • Fig. 9 illustrates a force-deflection characteristic for a non-preloaded bearing with the values at the origin 0 of zero force and zero deflection being the starting point for bearing installation and setup.
  • the initial point for the force-deflection curve of a preloaded bearing would be shifted upward along the vertical (force) axis.
  • Additional possible variations to influence bearing performance may include the following, by way of example.
  • more elastomeric rings of smaller radial cross section would be expected to provide a stiffer bearing than fewer rings of larger radial cross section.
  • the radial section of the rings may be reduced and/or its vertical dimension increased as radius increases.
  • the vertical clearance of the individual rigid substrate elements from the base or from the cap member may be individually varied to customize the bottoming behavior of the bearing assembly. This can permit equalization of the strain energy stored in each elastomeric element.
  • the bearing may exhibit different stiffness characteristics in the lateral and longitudinal directions.
  • Fig. 3 Still further variations and additional structural features of the invention are illustrated by Fig. 3 in a side bearing generally indicated at 46 and having an elongated bearing carrier 48 similar to a conventional side bearing housing or carrier.
  • An assembly of plural elastomeric bearing elements 50 bonded to intervening rigid substrate elements 52 provide load bearing capacity which affords a range of vertical movement under loading L, with bearing response principally occurring as shear deformation S of the elastomeric elements 50.
  • bearing 46 is similar to the bearing described above with reference to Figs 1 and 2; however, because it can utilize a conventional bearing carrier 48, the bearing assembly of Fig. 3 can be retrofitted to existing side bearing hardware on freight car trucks.
  • the bearing assembly Since the option of retrofitting the Fig. 3 bearing assembly requires that they fit within the confines of a conventional bearing carrier 48, the bearing assembly must be configured accordingly.
  • the elastomeric elements 50 are located only at opposed longitudinal ends of the bearing assembly.
  • One or more of the substrate elements 52 may include side portions 53 extending longitudinally of the bearing assembly, but having no elastomeric material bonded thereto.
  • the side portions 53 on opposed lateral sides of the bearing assembly therefore lie closely adjacent one another and move vertically with respect to one another in response to loading L, but the bearing response afforded by shearing S of the elastomeric elements 50 is confined to the longitudinal end portions of the bearing assembly where the elastomeric elements 50 are located.
  • a solid stop arrangement such as a roller 54 and a cap member 56.
  • cap member 56 is carried atop the bonded elastomer and rigid substrate bearing assemblies to impart vertical loading thereto from a car body (not shown).
  • the maximum vertical deflection of the Fig. 3 side bearing is limited to that deflection where a depending stop portion 58 of cap member 56 engages roller 54.
  • either the roller or a corresponding solid bearing element, and/or cap member 56 may be incorporated in the Fig. 1 and 2 embodiment.
  • FIGs. 4 and 5 One presently preferred embodiment of the invention is shown in Figs. 4 and 5 as a bearing assembly 60 carried by a conventional side bearing cage or housing 62 and including a longitudinally spaced pair of bonded elastomeric bearing assemblies 64, and an intervening rigid bearing element such as roller 66.
  • Each of assemblies 64 includes outer and inner rigid substrate elements 68 and 70, respectively, each being preferably of a generally rectangular form as shown in Fig. 5, but having rounded or radiused corners as shown at 72 and 74, for example.
  • An intervening elastomeric element 76 is bonded to the confronting surfaces 78 and 80 of substrate elements 68 and 70, respectively.
  • FIG. 4 one of the options mentioned hereinabove for customizing bearing response is illustrated in Fig. 4 by the selected shaping or forming of free (i.e. unbonded) surfaces of elastomeric element 76, for example as indicated at 82 and 84.
  • Each of substrate elements 70 includes an opening 86 which receives a downwardly projecting interlock portion 88 of a rigid cap 90.
  • the cap 90 spans the longitudinally spaced bearing assemblies 64 and includes an intervening depending portion 92 which is engageable with roller 66. This provides a solid stop to limit vertically downward travel of cap 90 under loadings L, thus also limiting deformation of elastomeric elements 76 in shear.
  • Figs. 6 and 7 show another presently preferred embodiment of the invention wherein an assembly of bearing elements 93 is carried by a conventional side bearing housing or carrier 94.
  • Assembly 93 comprises a bonded elastomer and metal substrate bearing assembly 96 that is similar in many salient respects to that described with reference to Figs. 4 and 5.
  • bearing assembly 96 may be of a generally rectangular section form, rather than generally square as in the Fig. 4 and 5 embodiment.
  • the cap or wear member 90 of the Fig. 4 and 5 embodiment is substituted in the Fig. 6 and 7 embodiment by an integral wear member portion 98 of the bearing assembly 96.
  • the assembly 96 resides in bearing carrier 94 longitudinally adjacent to a saddle member 100 having an upwardly projecting abutment 102 which confines bearing assembly 96 between itself and the opposed end 104 of housing 94. Between abutment 102 and the opposite end 106 of housing 94 there is confined a roller element 108, which may roll freely within a range of longitudinal movement between carrier end 106 and abutment 102.
  • Fig. 8 shows yet another embodiment of the invention in generally schematic form as a bearing assembly 110 comprising a base portion 112 having either a plurality of elastomeric elements, or a unitary ring-shaped elastomeric element 114 as shown.
  • a substrate element 116 includes a peripheral side portion 118 and a top portion 120.
  • a radially inwardly facing wall portion 122 of the peripheral side portion 118 confronts the radially outwardly facing wall 124 of base element 112, and elastomeric element 114 is bonded to these surfaces.
  • the confronting wall portions 122 and 124 are angled outward from the vertical by an angle A such that loading L produces shear deformations that are not parallel to the confining walls 122 and 124.
  • the result is a degree of elastomeric compression in addition to the shear deformation under loading L.
  • the limit on angle A for practical purposes has not been determined, although it will be clear that as angle A increases the deformation of the elastomeric elements 114 in response to loading L is increasingly greater compression and decreasing shear deformation. Since the novel bearing as described operates primarily in reliance on the response from shear deformation of the elastomeric elements, the magnitude of angle A is to be limited accordingly so that the bearing response is indeed primarily shear response.
  • Bearings according to the present invention may be configured in accordance with any described embodiment, and others not described.
  • any embodiment of the invention may be modified in accordance with any of the alternative structures or modifications mentioned herein, as well as others which would have the function of altering in some preferred way the force-deflection response of the bearing upon deformation of the elastomeric materials in shear under vertical loading.
  • a force-deflection curve for a hypothetical side bearing of the present invention is illustrated in Fig. 9 as curve C representing the vertical bearing deflection D under force F.
  • Origin 0 represents the free or unloaded state of the bearing extending to its full free height. (As noted hereinabove, for a preloaded bearing, the initial point 0 of curve C would be shifted upwardly along the vertical axis.)
  • the bearing response is observed as a deflection D over an initial range of loading I representing bearing installation and setup.
  • the range of deflection R represents the variation which occurs due to normal error or variation in setup of the bearing.
  • the functional characteristics of the bearing are such that, in this region the slope of curve C flattens significantly. Consequently, the variation V in force F over the entire setup range R of the bearing is relatively small. This provides for greater uniformity of the bearing setup.
  • setup range R The significance of flattening of the force-deflection characteristic in setup range R may be appreciated by extrapolating that portion of the curve C backward toward 0 deflection as indicated by extrapolation E.
  • the deformation behavior of the elastomeric bearing assemblies in the setup range R corresponds to a hypothetical linear force-deflection characteristic which has undergone a very large deflection D before reaching the setup force range V.
  • Elastomeric materials for the invention may be chosen from a range of materials having suitable properties that they can be subjected to the necessary deflections with minimal permanent set or hysteresis, while generating the required load responses as described hereinabove within the side bearing space limitations.
  • metallic substrates may be selected from a variety of materials based on load bearing capacity and the wear to which the material may be subjected.
  • the bonding techniques for producing the elastomer and metal substrate bearing assemblies may be standard bonding methods or heretofore unknown bonding techniques.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)
EP98302271A 1997-03-28 1998-03-25 Seitliches Auflager für ein Eisenbahn-Drehgestell Withdrawn EP0873928A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US4173997P 1997-03-28 1997-03-28
US41739P 1997-03-28

Publications (1)

Publication Number Publication Date
EP0873928A1 true EP0873928A1 (de) 1998-10-28

Family

ID=21918071

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98302271A Withdrawn EP0873928A1 (de) 1997-03-28 1998-03-25 Seitliches Auflager für ein Eisenbahn-Drehgestell

Country Status (4)

Country Link
EP (1) EP0873928A1 (de)
AU (1) AU707086B2 (de)
CA (1) CA2233056A1 (de)
ZA (1) ZA982515B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001054958A1 (en) * 2000-01-31 2001-08-02 Lord Corporation Resilient member for railway vehicle side bearings and method of manufacture thereof
CN101607561B (zh) * 2009-07-16 2010-09-15 中国北车集团沈阳机车车辆有限责任公司 组合式双作用弹性旁承
JP2014201083A (ja) * 2013-04-01 2014-10-27 日本車輌製造株式会社 鉄道車両用軸箱支持装置
CN114670592A (zh) * 2022-03-25 2022-06-28 江苏徐工工程机械研究院有限公司 一种重载的公铁两用车转向架旁承机构及转向架

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3045998A (en) 1958-08-05 1962-07-24 Metalastik Ltd Side bearers for railway vehicles
DE1455152A1 (de) * 1962-06-06 1969-02-06 Metalastik Ltd Schienenfahrzeug
DE1605132A1 (de) * 1951-01-28 1970-07-23 Wegmann & Co Federung fuer Schienenfahrzeuge mit Drehgestell
US3670661A (en) 1970-03-02 1972-06-20 Mcmullen Ass John J Resilient roll controlling railway car side bearings
US3707927A (en) 1970-09-28 1973-01-02 Standard Car Truck Co Resilient truck side bearings
US3895206A (en) 1973-02-20 1975-07-15 Hitachi Ltd Railway vehicle suspension
US3957318A (en) 1974-05-16 1976-05-18 A. Stuck, Company Elastomeric railway truck side bearing
US4030424A (en) 1975-04-29 1977-06-21 Acf Industries, Incorporated Rigid railway car truck
US4355583A (en) 1980-11-12 1982-10-26 The Budd Company Side bearing for a railway car
US4434720A (en) 1982-02-18 1984-03-06 Amsted Industries Incorporated Multi-rate side bearing for a railway truck
US4715290A (en) 1986-05-19 1987-12-29 Amsted Industries Incorporated Hunting control side bearing
US5386783A (en) 1990-02-01 1995-02-07 Hansen Inc. Railway truck side bearing

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3915520A (en) * 1974-05-14 1975-10-28 Evans Prod Co Elastomeric railway car side bearing
SU1792384A3 (ru) * 1989-08-07 1993-01-30 Лугahckий Teплoboзoctpoиteльhый Зaboд Бokobaя oпopa peльcoboгo tpahcпopthoгo cpeдctba

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1605132A1 (de) * 1951-01-28 1970-07-23 Wegmann & Co Federung fuer Schienenfahrzeuge mit Drehgestell
US3045998A (en) 1958-08-05 1962-07-24 Metalastik Ltd Side bearers for railway vehicles
DE1455152A1 (de) * 1962-06-06 1969-02-06 Metalastik Ltd Schienenfahrzeug
US3670661A (en) 1970-03-02 1972-06-20 Mcmullen Ass John J Resilient roll controlling railway car side bearings
US3707927A (en) 1970-09-28 1973-01-02 Standard Car Truck Co Resilient truck side bearings
US3895206A (en) 1973-02-20 1975-07-15 Hitachi Ltd Railway vehicle suspension
US3957318A (en) 1974-05-16 1976-05-18 A. Stuck, Company Elastomeric railway truck side bearing
US4030424A (en) 1975-04-29 1977-06-21 Acf Industries, Incorporated Rigid railway car truck
US4355583A (en) 1980-11-12 1982-10-26 The Budd Company Side bearing for a railway car
US4434720A (en) 1982-02-18 1984-03-06 Amsted Industries Incorporated Multi-rate side bearing for a railway truck
US4715290A (en) 1986-05-19 1987-12-29 Amsted Industries Incorporated Hunting control side bearing
US5386783A (en) 1990-02-01 1995-02-07 Hansen Inc. Railway truck side bearing

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001054958A1 (en) * 2000-01-31 2001-08-02 Lord Corporation Resilient member for railway vehicle side bearings and method of manufacture thereof
US6357732B1 (en) 2000-01-31 2002-03-19 Lord Corporation Resilient member for railway vehicle side bearings
CN101607561B (zh) * 2009-07-16 2010-09-15 中国北车集团沈阳机车车辆有限责任公司 组合式双作用弹性旁承
JP2014201083A (ja) * 2013-04-01 2014-10-27 日本車輌製造株式会社 鉄道車両用軸箱支持装置
CN114670592A (zh) * 2022-03-25 2022-06-28 江苏徐工工程机械研究院有限公司 一种重载的公铁两用车转向架旁承机构及转向架
CN114670592B (zh) * 2022-03-25 2023-05-05 江苏徐工工程机械研究院有限公司 一种重载的公铁两用车转向架旁承机构及转向架

Also Published As

Publication number Publication date
ZA982515B (en) 1998-09-30
CA2233056A1 (en) 1998-09-28
AU5967698A (en) 1998-10-01
AU707086B2 (en) 1999-07-01

Similar Documents

Publication Publication Date Title
US4915031A (en) Railway truck damping assembly
CN102700560B (zh) 用于安装在火车车厢转向架侧架导框中的轴承座及其转向架
CA1250327A (en) Spring
US3957318A (en) Elastomeric railway truck side bearing
US4986192A (en) Railway truck bolster friction assembly
EP2170634B1 (de) Einfederungsanschlaganordnung und gasfederanordnung damit
US4090750A (en) Resilient railway truck side bearing
US20160152106A1 (en) Vehicle suspension and leaf spring therefore
CA2616750A1 (en) Constant contact side bearing for railroad freight cars
US4109934A (en) Self-contained frictionally damped resilient suspension system
EP0834408A1 (de) Isolatorsystem für Aufhängung
US5046431A (en) Railway truck
US4150627A (en) Self-contained frictionally damped resilient suspension system for railcars
US20170305225A1 (en) Variable rate auxiliary leaf engagement
US7641182B2 (en) Rigid jounce bumper and gas spring assembly including same
AU707086B2 (en) Railway truck side bearing
RU2348556C1 (ru) Амортизирующее устройство для железнодорожного вагона
JP2005518975A (ja) 円錐ゴム軸受
US3932005A (en) Elastomeric railway car with side bearing
JP2008049878A (ja) アクスルの取付構造
US20030106456A1 (en) Railway truck side bearing
CA1202988A (en) Wheel suspension with eccentric shear disc
EP3098472B1 (de) Stopper für aufhängungssystem
US6148734A (en) Elastomeric bearing with softening spring rate
US6357732B1 (en) Resilient member for railway vehicle side bearings

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

AKX Designation fees paid
18W Application withdrawn

Withdrawal date: 19990611