EP0512089A1 - Vehicule sur rails. - Google Patents

Vehicule sur rails.

Info

Publication number
EP0512089A1
EP0512089A1 EP91920077A EP91920077A EP0512089A1 EP 0512089 A1 EP0512089 A1 EP 0512089A1 EP 91920077 A EP91920077 A EP 91920077A EP 91920077 A EP91920077 A EP 91920077A EP 0512089 A1 EP0512089 A1 EP 0512089A1
Authority
EP
European Patent Office
Prior art keywords
spring
rail vehicle
roll
vehicle according
roll angle
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.)
Granted
Application number
EP91920077A
Other languages
German (de)
English (en)
Other versions
EP0512089B1 (fr
Inventor
Hans Peter Lang
Alfred Uttner
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.)
Alstom Transportation Germany GmbH
Original Assignee
MAN GHH Schienenverkehrstechnik GmbH
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 MAN GHH Schienenverkehrstechnik GmbH filed Critical MAN GHH Schienenverkehrstechnik GmbH
Publication of EP0512089A1 publication Critical patent/EP0512089A1/fr
Application granted granted Critical
Publication of EP0512089B1 publication Critical patent/EP0512089B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • B61F5/148—Side bearings between bolsterless bogies and underframes
    • 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
    • B61F5/04—Bolster supports or mountings
    • B61F5/06—Bolster supports or mountings incorporating metal springs
    • 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
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies
    • B61F5/24—Means for damping or minimising the canting, skewing, pitching, or plunging movements of the underframes

Definitions

  • the invention relates to a rail vehicle according to the preamble of patent claim 1.
  • a high level of driving comfort requires extensive decoupling of the undercarriage and car body so that the undercarriage can follow the track position elastically and as freely as possible when driving in a straight line.
  • This in turn requires a soft roll damping of the car body, for example by means of two air springs arranged laterally between the car body and the undercarriage, which in addition to the roll damping also take over the vertical support of the car body on the undercarriage.
  • Controllable air suspensions for soft secondary cushioning of the car body which, by corresponding air pressure control of the individual air springs, should also limit the car body inclination in addition to a height level regulation.
  • air spring systems however, only static or quasi-static changes in position between chassis and car body can be compensated for, but due to the design-related inertia of the air pressure control, the dynamic roll movements cannot be effectively stabilized, so that, for example, the car body overshoots rapidly when entering a curve, apart from the fact that a roll angle-dependent air pressure control results in an undesirably high consumption of compressed air.
  • Passively acting roll stabilizers in the form of torsion spring bars are also known in connection with regulated secondary air spring systems.
  • the air springs are interconnected in terms of vibrations, so they are not regulated depending on the roll angle and are only intended to compensate for changes in height level due to different loads, while the roll stabilizers alone take over the limitation of the car body inclination.
  • Their spring characteristic is determined by the maximum permissible roll angle during fast bend travel and therefore causes a tight coupling of chassis and body, even when driving in a straight line, with the result that driving comfort and the vertical wheel force dynamics are negatively affected.
  • Add to that adjustable suspension or bogie air suspension require the installation of emergency springs which, in the event of a failure of the air supply, take over the car body - which is now much harder due to the construction.
  • the disadvantages described cannot be effective Fix, because on the one hand the roll restoring torque is distributed extremely unevenly on both bogies during fast bend travel and essentially has to be compensated for by wheel force differences of only one bogie, which results in a large quasi-static wheel relief on the wheels inside the bow, and on the other hand the roll stabilizer increases the Car body coupled with the bogie so strongly with regard to higher-frequency, dynamic roll movements when driving in a straight line that the driving comfort is thereby impaired, with the additional structural disadvantage that the car body has two different equipment ete bogies are required.
  • the object of the invention is to design a rail vehicle of the type claimed so that the cushioning between the body and the chassis reliably limits the body tilt to a predetermined roll angle range without impairing the safety against derailment and driving comfort in
  • the combination of a relatively soft secondary spring arrangement for example in the form of a multi-point air spring support regulated depending on the roll angle, with an additional spring which is essentially ineffective in the lower part of the permissible roll movement and only then intervenes, but then generates a steeply increasing restoring torque, ensuring that The dynamic roll movements of the car body when driving in a straight line and the roll angle deflections of the undercarriage when driving on twisted tracks and when driving slowly on a ramp are almost completely absorbed by the spring arrangement, while the additional spring does not respond, so that even when using a relatively stiff primary suspension, the one for high level of driving comfort required, vibration-related decoupling of the chassis and car body is achieved without impairing the dynamics of the wheel force, and yet in particular with fast bends or rams the permitted roll angle limit value due to the then automatically effective restoring torque of the additional spring regardless of the response speed of an air spring control reliably and without a wheel relief critical for derailment uncertainty.
  • the characteristic curve of the additional spring expediently runs essentially on the restoring torque zero line in the mentioned working range of small roll angle deflections.
  • the additional spring in a further advantageous embodiment of the invention according to claim 3, it is designed as a torsion bar effective between the running gear and the car body with a limited rotational play, in such a way that the ends of the torsion bars arranged at a relative inclination of car body and undercarriage twisted actuating lever according to claim 4 are expediently connected to the torsion bar via a claw-driver coupling with rotational play.
  • centering springs are advantageously provided for centering the claw driver coupling on the rotational play center position, which, however, is in comparison to that between the car body and Chassis effective spring arrangement have negligible spring hardness.
  • the levers are expediently limited in each case with little friction at the associated end of the torsion bar pivoted, preferably according to claim 7 by a maintenance-free plain bearing.
  • the roll angle range in which the torsion bar is disengaged generally extends only over a fraction of the maximum permitted roll angle deflections, but is highly dependent on the external boundary conditions of the respective installation case and can therefore be adjusted in a particularly preferred manner.
  • Another important aspect of the invention results in connection with a regulated air spring arrangement with associated No suspension, which takes over the body support and roll stabilization in the event of a failure of the air supply with a design-related often higher spring hardness.
  • a passive emergency suspension and an additional roll stabilizer in terms of
  • Figure 1 is a side view of a bogie rail vehicle in the area of one of the vehicle ends.
  • FIG. 2 shows a partially sectioned illustration of the air, auxiliary and emergency springs of the rail vehicle according to FIG. 1;
  • FIG. 3 shows an additional spring designed as a torsion bar in a perspective representation
  • FIG. 4 shows a partially sectioned view of a claw-driving clutch with rotational play between an actuating lever and the torsion bar according to FIG. 3;
  • FIG. 5 shows the partially sectioned top view of the claw driver coupling according to FIG. 4.
  • Fig. 6 is a diagram showing the individual spring characteristics.
  • two identical bogies 4 (only one of which is shown) arranged in the region of the ends of the car body are provided as the chassis for supporting the car body 2, each of which has an H-shaped, rigidly connected to one another
  • Longitudinal and cross members 6, 8 contain existing bogie frame 10, on which the two rigid wheel sets 12, 14 of the bogie 4 each via wheel set bearing housing 16 and a primary suspension 18 elastic in all three coordinate directions with an in
  • the effective secondary suspension between car body 2 and bogie 4 consists of a pressure-controlled Air spring assembly 20 in the form of laterally on the bogie frame 10 between the underside of the car body and the bogie ssensträgem 6 arranged air springs 22.1 and 22.2 relatively low spring hardness, which support the car body 2 on the bogie frame 10 and are regulated so that they the floor level regardless of the load keep the body 2 at a constant height and with a relative inclination of body 2 and bogie frame 10 counteracting the rolling movement
  • the spring travel x of the air springs 22 with respect to the zero inclination position of the car body is predetermined by the maximum permissible roll angle at which the car body 2 is inclined to the right or left up to the boundary profile shown in dashed lines in FIG. 2.
  • the air springs 22 are designed so that they the turning movements of the bogie 4 e.g. around a pivot bearing (not shown) lying in the center of the frame.
  • the spring arrangement 20 is assigned an emergency suspension 24, which consists of passively acting, each integrated in the air springs 22 e.g. emergency springs 24.1 and 24.2 formed as sleeve rubber elements, on which the body 2 at a
  • the emergency springs 2 .1 and 24.2 have a significantly smaller spring travel y and a much higher spring hardness than the air springs 22. Accordingly, the roll movements occurring when the emergency springs 24 are traveling are also significantly less than the permissible roll angle deflections corresponding to the spring travel x of the air suspension 20 .
  • a passive additional spring 26 is installed between the body 2 and the bogie frame 10, which only responds to roll movements, but not to changes in the height of the body 2, and its special feature is a non-linear spring characteristic curve that runs in this way that the additional spring 26 is essentially ineffective in the driving dynamically optimal range of small roll angle movements and only in the upper part of the permissible roll angle deflections produces a restoring torque which counteracts the roll tendency of the body 2, but then increases steeply.
  • the additional spring 26 consists of a torsion spring rod 28, which is rotatably supported about its longitudinal axis on the underside of the car body by means of bearing blocks 30 transversely to the direction of travel.
  • actuating lever 32 At each end of the torsion bar 28 there is an actuating lever 32, the free lever end of which is connected in an articulated manner to the bogie longitudinal member 6 via a control rod 34 and a pivot pin 36.
  • Torsion bar end provided. 4 and 5 show in detail, the coupling 38 contains a serration 40 non-rotatably connected to the end of the torsion bar bearing sleeve 42 and one in an end recess of the bearing sleeve 42nd backlash-free and form-fitting engagement, double-armed driver 44, which are fastened interchangeably at the head end of the torsion bar 28 by screw connections 46 and a holding plate 48.
  • the center hub 50 of the actuating lever 32 is axially immovable on the bearing sleeve 42, but can be rotated smoothly via a slide bearing 52.
  • the lever hub 50 is provided on the end face with coupling claws 54 which have a backlash corresponding to the desired rotational play with respect to the driver 44.
  • the size of the rotational play determines - apart from the low restoring force of the rubber springs 58 - restoring torque-free working area of the additional spring 26 and can either be predetermined or as a result are designed to be adjustable so that the effective length of each pressure plunger 56 between the front, spherical contact surface and the rear 60 is adjustable according to FIG. 4.
  • the air suspension 20 has a spring curve a which is relatively weakly inclined in the entire permissible roll angle range Z between + ⁇ z and - ⁇ z , that is to say a smooth coupling between the body 2 and the bogie frame 10 with regard to the roll movements
  • the non-linear spring curve b of the torsion Additional spring 26 in the lower part S small roll angle deflections between + ⁇ s and - ⁇ g corresponding to the rotational play of the claw driver coupling 38 almost without restoring torque, in the upper part larger roll angle movements between ⁇ g and ⁇ z, however, rising steeply, such that the additional spring 26 at
  • the area of engagement of the additional spring 26 between S and Z is reached in the case of rapid arc and ramp travel on air suspension.
  • the roll angle ⁇ is effectively limited to the maximum permissible value ⁇ z by the common restoring effect of air suspension 20 and much harder additional spring 26, the response time of the air spring control irrelevant and the air consumption being minimal.
  • the emergency springs 24 are used in accordance with the spring characteristic curve c 1 and limit the roll angle movements of the car body 2 to a region N which lies within the essentially restoring-torque-free partial region S of the additional spring characteristic curve b, so that the torsion spring rod 28 rides when driving Emergency springs provide no additional restoring torque R and therefore the safety against derailment is not impaired.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Springs (AREA)
  • Amplifiers (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Control Of Stepping Motors (AREA)
  • Control Of Vehicles With Linear Motors And Vehicles That Are Magnetically Levitated (AREA)
  • Platform Screen Doors And Railroad Systems (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
  • Length Measuring Devices By Optical Means (AREA)

Abstract

Un véhicule sur rails comprend une suspension secondaire (20) agencée entre le mécanisme de roulement (4) et la caisse de wagon (2) qui génère, en cas d'inclinaison relative entre ces deux unités un moment de rappel qui augmente continuellement jusqu'à ce que l'angle maximal admissible de roulis soit atteint. Afin d'obtenir une limitation fiable de l'angle de roulis sans effets néfastes sur la protection contre le déraillement ni sur le confort des passagers dans les lignes droites, par une construction simple et à l'épreuve de défaillances, la suspension est relativement souple; en outre, un ressort supplémentaire (26) passif ayant une marge de rotation limitée (embrayage à jeu de rotation 38) est relié en parallèle à la suspension, fonctionne pratiquement sans moment de rappel dans une plage partielle d'angles de roulis réduite, mais génère un moment de rappel plusieurs fois supérieur à celui de la suspension et qui augmente rapidement dans une plage d'angles de roulis admissibles, lorsque l'angle de roulis subit de plus grandes déviations, avec une inclinaison maximale admissible de la caisse de wagon.
EP91920077A 1990-11-27 1991-11-22 Vehicule sur rails Expired - Lifetime EP0512089B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4037672A DE4037672A1 (de) 1990-11-27 1990-11-27 Schienenfahrzeug
DE4037672 1990-11-27
PCT/DE1991/000918 WO1992009469A1 (fr) 1990-11-27 1991-11-22 Vehicule sur rails

Publications (2)

Publication Number Publication Date
EP0512089A1 true EP0512089A1 (fr) 1992-11-11
EP0512089B1 EP0512089B1 (fr) 1995-03-08

Family

ID=6418989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91920077A Expired - Lifetime EP0512089B1 (fr) 1990-11-27 1991-11-22 Vehicule sur rails

Country Status (8)

Country Link
US (1) US5311821A (fr)
EP (1) EP0512089B1 (fr)
AT (1) ATE119481T1 (fr)
DE (2) DE4037672A1 (fr)
DK (1) DK0512089T3 (fr)
ES (1) ES2069315T3 (fr)
GR (1) GR3015617T3 (fr)
WO (1) WO1992009469A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE4037672A1 (de) * 1990-11-27 1992-06-04 Man Ghh Schienenverkehr Schienenfahrzeug
DE4410970C1 (de) * 1994-03-29 1995-07-20 Talbot Waggonfab Wankstütze für Schienenfahrzeuge mit einer Querneigeeinrichtung
FR2831126B1 (fr) * 2001-10-23 2004-05-28 Alstom Procede de controle securitaire de la pendulation d'un vehicule ferroviaire
FR2896751B1 (fr) * 2006-01-30 2008-04-18 Alstom Transport Sa Essieu pour vehicule ferroviaire a plancher bas, bogie et vehicule ferroviaire correspondant.
DE102006012110A1 (de) * 2006-02-23 2007-08-30 Benteler Automobiltechnik Gmbh Fahrwerksanordnung
AT504186A3 (de) * 2006-09-13 2010-11-15 Siemens Ag Oesterreich Einrichtung zur veränderung der wanksteifigkeit
ES2638874T3 (es) * 2009-03-06 2017-10-24 Construcciones Y Auxiliar De Ferrocarriles, S.A. Sistema de control de basculación de vehículos ferroviarios
GB2475325A (en) 2009-11-16 2011-05-18 Bombardier Transp Gmbh Torsion bar assembly and method, particularly for rail vehicle anti-roll bar
US8079310B2 (en) * 2009-11-25 2011-12-20 LTK Consulting Services, Inc. Vertical position compensating device for a vehicle
DE102011052275B4 (de) * 2010-08-26 2026-01-29 Ovalo Gmbh Aktiver Wankstabilisator
DE102011085029A1 (de) * 2011-10-21 2013-04-25 Luhn & Pulvermacher - Dittmann & Neuhaus GmbH Stabilisator in Faserkunststoffverbund und Verfahren zu dessen Herstellung
DE102013225471A1 (de) * 2013-12-10 2015-06-11 Siemens Aktiengesellschaft Schienenfahrzeug mit hinsichtlich ihres Drucks gesteuerter Luftfeder
JP6564292B2 (ja) * 2015-10-07 2019-08-21 川崎重工業株式会社 車体傾斜装置を備えた鉄道車両および列車編成
AT519187A1 (de) * 2016-09-29 2018-04-15 Siemens Ag Oesterreich Luftfedersteueranordnung für ein Schienenfahrzeug
EP3617030B1 (fr) * 2017-04-25 2021-09-08 Hitachi, Ltd. Véhicule ferroviaire
CN109532913B (zh) * 2019-01-02 2020-09-22 中车株洲电力机车有限公司 一种一系悬挂装置及转向架
DE102019108532A1 (de) * 2019-04-02 2020-10-08 Schaeffler Technologies AG & Co. KG Radsatzlagergehäuse für ein Schienenfahrzeug und Verfahren zur Herstellung eines Radsatzlagergehäuses
CN111016950B (zh) * 2019-12-31 2024-12-03 中车长江车辆有限公司 适用于高速铁路货车的无摇枕构架式转向架

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Title
See references of WO9209469A1 *

Also Published As

Publication number Publication date
US5311821A (en) 1994-05-17
DE4037672A1 (de) 1992-06-04
EP0512089B1 (fr) 1995-03-08
DE4037672C2 (fr) 1993-05-19
ATE119481T1 (de) 1995-03-15
WO1992009469A1 (fr) 1992-06-11
DK0512089T3 (da) 1995-05-22
DE59104894D1 (de) 1995-04-13
GR3015617T3 (en) 1995-06-30
ES2069315T3 (es) 1995-05-01

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