EP0944513B1 - Drehgestell-fahrwerk für ein schienenfahrzeug - Google Patents

Drehgestell-fahrwerk für ein schienenfahrzeug Download PDF

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Publication number
EP0944513B1
EP0944513B1 EP97946701A EP97946701A EP0944513B1 EP 0944513 B1 EP0944513 B1 EP 0944513B1 EP 97946701 A EP97946701 A EP 97946701A EP 97946701 A EP97946701 A EP 97946701A EP 0944513 B1 EP0944513 B1 EP 0944513B1
Authority
EP
European Patent Office
Prior art keywords
running gear
pendulum
frame
pendulum carrier
transverse
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.)
Expired - Lifetime
Application number
EP97946701A
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German (de)
English (en)
French (fr)
Other versions
EP0944513A1 (de
Inventor
Martin Teichmann
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.)
Siemens AG Oesterreich
Original Assignee
Siemens SGP Verkehrstechnik 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 Siemens SGP Verkehrstechnik GmbH filed Critical Siemens SGP Verkehrstechnik GmbH
Publication of EP0944513A1 publication Critical patent/EP0944513A1/de
Application granted granted Critical
Publication of EP0944513B1 publication Critical patent/EP0944513B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies

Definitions

  • the invention relates to a bogie chassis for a rail vehicle, in particular for a high-speed train with a two-axle drive, which has a Primary suspension is attached to a frame, on which a Secondary suspension is arranged a pendulum carrier aligned transversely to the vehicle longitudinal direction is, which has a four-joint pendulum bearing around a running in the vehicle longitudinal direction
  • Axis is pivotally connected to a transverse crossbar, in which four-joint self-aligning bearing two pendulums symmetrical to the longitudinal median plane of the chassis and from seen in front or rear - are arranged trapezoidal, the lateral distance of the Articulation points of the pendulums on the pendulum carrier are less than the lateral distance between them the articulation points of the pendulum on the traverse to which the vehicle body of the vehicle is located can be put on immediately, with an active between the pendulum support and the traverse Tilt position device with at least one actuating unit, e.g. B
  • a chassis of the type mentioned above is, for example, in DE-C-2 145 738 in two different Design variants described.
  • the secondary suspension for the pendulum support is usually formed by air springs that sit on the frame of the chassis and support the pendulum support in the area of its lateral ends.
  • the traverse is over one mechanical joint arrangement pivotable about a horizontal pivot axis with the Pendulum carrier connected in such a way that the pivot axis in the area above the crossbar in the car body, e.g. B. is at passenger height. This allows the tilting mechanism to be operated with little Be exerted. If the swivel axis is above or below the center of gravity is arranged, the tilt mechanism is also by the action of a Restoring force brought into its initial state.
  • a secondary spring tilt mechanism for a bogie of a rail vehicle which enables a low overall height is described, inter alia, in EP 736 437 and EP 736 438 shown and described.
  • This tilting mechanism includes a secondary spring Pendulum bracket, on which the car body is directly linked via a four-bar linkage, with hydraulic cylinder / piston units at the top of the pendulum support at both ends attack that on the associated side walls of the car body in are supported a distance above the pendulum support.
  • a major disadvantage of this Construction lies in the fact that by integrating the tilting mechanism in the car body construction less passenger space and therefore less space for seats is available. Furthermore, with such a construction, both the chassis and the car body is manufactured and assembled at a manufacturing site.
  • the car body must be dimensioned accordingly to absorb the forces that occur are, so that the production costs of such a car body are increased. Because the force application points comparatively high for the tilting mechanism and therefore in one less distance from the center of gravity of the car, must be inclined to the car body higher forces are undesirably overcome.
  • the chassis according to DE 2 001 282 A has a comparatively complicated suspension before, which not only has pendulums, but also angle levers and a steering gear.
  • Two external actuators are provided in front of and behind the frame.
  • This object is achieved according to the invention in a bogie undercarriage of the type mentioned at the beginning solved in that the traverse as a frame with two transverse to the vehicle longitudinal direction aligned, arranged in front of or behind the pendulum crossmember and that these cross-member cross members in the vehicle longitudinal direction on the pendulum support are supported and slidably arranged transversely to the longitudinal direction of the vehicle.
  • the frame-shaped design of the cross beam for the car body can be the pendulum carrier and the traverse nested and arranged at substantially the same height are, so that the overall height of the chassis can be significantly reduced without the Car body must be changed. Due to the frame-shaped design of the crossbar around the pendulum support, the traverse can be sufficiently stable in a small space Longitudinal direction are produced, which also achieves a small overall length of the chassis can be.
  • An advantageous implementation of the chassis according to the invention is in practice possible that depending on the support and guidance of the crossbeam on the pendulum support two friction plates arranged symmetrically to the longitudinal center plane of the undercarriage and on each Truss cross members are provided opposite friction surfaces.
  • This Friction plates / friction surface arrangement allows sufficient longitudinal driving and is in Realizable in terms of the most compact possible construction with little space consumption.
  • a particularly advantageous embodiment of the pendulum results if each pendulum consists of one
  • a plurality of spring steel sheets is made, which are laminated together and are articulated to the pendulum support or the crossmember by means of a common bolt each. Since spring steel sheets have a high tensile strength in their longitudinal direction, the Pendulums are built extremely narrow, which further increases the compactness of the chassis improved. Furthermore, the pendulums are transverse to the direction of pull, i.e. in the longitudinal direction of the vehicle elastic and thus advantageously allow a certain elasticity to compensate of tolerances between the pendulum support and the crossbeam.
  • the pins for the pendulums can be attached to the pendulum carrier by means of a sliding or roller bearing or the traverse.
  • the pendulum bearing four has pendulums arranged in pairs, two pendulums each in the longitudinal direction of the chassis are arranged one behind the other.
  • the tilting device a has only cylinder / piston unit, which is arranged below the pendulum support, wherein one end of the cylinder / piston unit at a distance from the longitudinal median plane with the Pendulum bracket and the other end on the opposite side of the chassis at a distance is connected to the traverse from the longitudinal median plane.
  • the compactness of the arrangement is further improved by the fact that the crossbar one has two crossbeams connecting the central central section below the pendulum beam, which for absorbing longitudinal forces via a lemniscate guide with the frame of the Undercarriage is connected in such a way that the traverse can be rotated about a vertical axis and is deflectable essentially transversely to the direction of travel.
  • the crossbeam thus forms a stable one Construction that encloses the pendulum carrier up to its top.
  • the pendulum support is designed to accommodate those occurring between the chassis and the body Lateral forces in a manner known per se via an active transverse suspension and damping with the Frame of the chassis connected, one in front and one behind the pendulum support Cross spring and damping element is provided and the spring and damping elements in Attack the area of the longitudinal median plane on the pendulum support.
  • an opening is provided in the central section of the traverse, through which a connecting piece of the pendulum beam below the crossmember is led forward or backward. This allows the transverse suspension outside of The crossbar and pendulum support are nested on the frame of the chassis become.
  • the pendulum support can also in the region of its lateral ends with a known per se Roll stabilization should be provided, which one on each side of the frame below the Pendulum carrier arranged around a horizontal transverse axis hinged to the frame in Vehicle longitudinal direction and substantially horizontally aligned roll stabilizer lever has, each via an upward push-push rod with the associated end of the pendulum carrier is connected, the opposite to each other transversely to the direction of travel Arranged stabilizer lever connected to each other resiliently by means of a torsion bar are.
  • Embodiment of the chassis of the stabilizer lever of the roll stabilization according to the invention via a damping device, which is at a distance from the articulation axis of the stabilizer lever attacks this, supported on the frame.
  • the roll stabilization is formed by four stabilizer levers and pull-push rods, where two stabilizer levers and pull-push rods in the direction of travel and one behind the other are arranged symmetrically to the longitudinal center of the chassis.
  • the pendulum support lies in the area of its lateral ends in a manner known per se above an air spring forming the secondary suspension on the frame, the interior of the hollow pendulum carrier in an advantageous manner as an additional volume of the air springs in the Secondary suspension is integrated.
  • each axle of the undercarriage has an electric drive it has proven to be advantageous if this drive on the pendulum support facing side of the wheel axle is arranged, as a result of this having a compact design low moment of inertia can be achieved.
  • this drive on the pendulum support facing side of the wheel axle is arranged, as a result of this having a compact design low moment of inertia can be achieved.
  • An advantageous embodiment of the frame is possible in that the interior of the hollow frame at least in sections connected to the air springs and in the volume the air springs is integrated, as a result of this measure a compact implementation of the secondary suspension is made possible with a low overall height.
  • FIGS. 1 to 3 in which a bogie chassis 1 of the type according to the invention is shown.
  • the chassis 1 has an H-shaped frame 2 on, which is formed by two side members 3, 4 and two two cross members 5, 6 each are welded together.
  • At the front and rear ends of the frame 2 is each a wheel set consisting of two wheels 7, 8, 9, 10 arranged opposite one another is provided, which are rigidly connected to each other by means of an axis 11, 12.
  • the one Primary spring stage with the frame 2 connected wheels 7, 8, 9, 10 are each on a rocker 13, 14 rotatably mounted, which is pivotable about a transverse axis S1, S2 on the longitudinal beams 3, 4th the frame 2 is articulated.
  • the primary suspension is pressurized by two Coil springs 15, 16, 17, 18 each rocker 13, 14 formed, the vertically arranged Springs 15, 16, 17, 18 with their lower end on the associated rocker 13, 14 and with their upper end are supported against the associated side members 3, 4 of the frame 2.
  • the spring constants are dependent on their distance from the rocker axis S1, S2 designed so that when the primary suspension deflects as far as possible on the Swing axis S1, S2 no vertical forces occur.
  • the swing arm bearings of the wheels Using two primary springs each has the advantage that the primary spring stage is compact can be and the chassis therefore has a lower overall height. Furthermore, through the smaller diameter spring 16, 18 created additional space for the arrangement a wheel disc brake can be used.
  • the embodiment shown in the figures relates to a two-axle chassis, at which each axis is driven.
  • each axis there is one on each of the axes 11, 12 axle-mounted gear 19, 20, e.g. a gear transmission, which has a Clutch, e.g. via a curved tooth coupling, each with a transverse drive motor 21, 22 is connected.
  • the drive motors 21, 22 are on the associated cross member 5 and 6, respectively attached to the frame 2, the relative movements between the frame-fixed motor and the primary suspension gearbox are taken up by the clutch.
  • Drives this Art are known to those skilled in the art of bogie chassis and are therefore not described in detail here. Essential for realizing one if possible compact chassis, especially for high-speed applications Arrangement of all essential mechanical components of the drives each on the Longitudinal center side of axles 11, 12.
  • the wheels 7, 8, 9, 10 of the chassis 1 are each with a brake unit 23, 24, 25, 26 so-called wheel disc brake.
  • the brake units 23, 24, 25, 26 are fixed to the frame attached to the cross beams 5, 6 of the frame 2 and each have a brake caliper, the Attack brake shoes on the side surfaces of the wheels 7, 8, 9, 10 concerned, which too both sides are provided with a brake disc.
  • Braking devices of this type are the Those skilled in the art are also already known and are therefore not explained in more detail here.
  • One air spring 28, 29 is arranged for the secondary suspension of the chassis 1.
  • a transverse pendulum support 30 placed on the by means of a pendulum arrangement around a substantially horizontal longitudinal axis is pivotally or inclinably connected to an equally transverse traverse 31 which a (not shown) car body of the rail vehicle can be placed and is attachable.
  • the secondary suspension by means of air springs 28, 29 has the advantage that the regulation of the spring travel is essentially not load-dependent and therefore low Stiffness can be achieved. For realizing the greatest possible driving comfort a large volume of air directly connected to the air springs is absolutely necessary.
  • the interior of the hollow frame 2 and Interior of the equally hollow pendulum support 30 at least in sections in the volume of Air springs 28, 29 integrated, so that a particularly compact design of the secondary suspension can be achieved with a low overall height.
  • the pendulum support 30 is in the embodiment shown with an active cross suspension and provided with roll stabilization.
  • the one arranged in front of and behind the pendulum support 30 in the direction of travel Cross suspension is by a transversely arranged active spring element 32, 33 and a cross arranged damper element 34, 35 formed, the spring element 23, 33 laterally next to the associated damper element 34, 35 is arranged and the side by side Elements 32, 34 and 33, 35 with their opposite ends on the frame 2 of the Chassis 1 and with their mutually facing ends in the region of the longitudinal median plane a connecting part 36, 37 of the pendulum support 30 are supported. That in the direction of travel the pendulum support 30 arranged cross spring element 32 is made of symmetry and Stability reasons on the diagonally opposite chassis side like that behind arranged transverse spring element 33 is provided.
  • the roll stabilization of the pendulum support 30 has two transverse to the chassis 1 and Arranged symmetrically to the longitudinal center of the torsion bars 38, 39, with their Ends are rotatably mounted on the longitudinal beams 3, 4 of the frame 2 and rigid with one in each roll stabilizer lever 40 oriented essentially horizontally and in the direction of the pendulum support, 41 are connected, wherein the stabilizer levers 40, 41 by means of upward push-push rods 42, 43 are pivotally connected to the outer ends of the pendulum support 30.
  • the elements of roll stabilization are both in relation to the chassis center also arranged symmetrically with respect to the longitudinal center plane of the chassis 1.
  • the cross member 31 for the car body is frame-shaped formed and has two cross member arranged symmetrically to the middle of the chassis 46, 47, the invention on both sides of the pendulum support 30 and parallel to this are arranged, and two each connecting the outer ends of the crossmember 46, 47 Longitudinal struts 48, 49.
  • the pendulum support 30 is thus frame-shaped by the cross member 31 enclosed, so that advantageously a space-saving, namely both short and low construction of the chassis 1 is possible.
  • the cross member 31 furthermore each have a section 50, 51 projecting downward from the cross member 46, 47 the sections 50, 51 are tapered and over at their lower ends a substantially horizontal connecting plate 52 are interconnected. So is the pendulum support 30 - except for its top - by the cross member 31 essentially on all sides enclosed. Due to the special construction of the traverse 31 described above, this can can be built to be sufficiently resistant to bending and torsion in a small space.
  • a downwardly projecting pin 53 arranged is guided and held on the undercarriage by means of a so-called lemniscate guide.
  • the known lemniscate guide of the pin 53 (not shown in the figures) two longitudinally aligned trailing arms on either side of the Longitudinal center of the chassis arranged diagonally opposite and with their Longitudinal ends remote from the chassis are hinged to the chassis frame.
  • the the Ends of the trailing arms facing the longitudinal center of the chassis are articulated via a wishbone connected to each other, which has a central bore for receiving the pin 53.
  • the pin 53 is a Rubber element held in the hole in the wishbone.
  • the lemniscate tour enables a direct transfer of the longitudinal forces from the chassis frame to the Traverse. Nevertheless, turning out is a vertical movement up and down and sideways Swinging out of the traverse or the car body with respect to the frame possible.
  • the aforementioned pivotable mounting of the cross member 31 on the pendulum support 30 takes place in the chassis 1 of the type according to the invention by means of a four-bar linkage, which is realized by pendulums 54, 55, 56, 57, two pendulums 54, 56 and 55, 57 in Longitudinal direction are arranged one behind the other and the opposite arranged pendulums 54, 55 and 56, 57 symmetrical to the longitudinal median plane trapezoidal are arranged.
  • the pendulums 54, 55, 56, 57 are at their upper ends by means of a bolt on the pendulum support 30 and at its lower ends by means of a bolt on each Connection plate 52 of the cross member 31 articulated.
  • the advantage of this construction lies among others in that the spring plates 62a, 62b, 62c, 62d are high in their longitudinal direction (vertical) Have tensile strength, but high across their longitudinal direction (in the direction of travel) Have elasticity, so that a precisely defined inclination of the crossbar with respect to the Pendulum carrier can take place, but in the longitudinal direction a certain elasticity to compensate of movements within existing games or tolerances.
  • the two ends of the pendulum 55 are articulated by means of one each Bolt 65, 66, which fits in the associated bore 58, 59 in a slide bearing is stored.
  • the friction plate 67 is received in a holding piece 75, which in the Bore 58 used for the self-aligning bearing and is fixed therein.
  • the sliding surface 71 on the other hand, a conical section of the friction plate 67 faces section 50 of the cross member 31 projecting below.
  • the instantaneous pivot axis when the cross member 31 is inclined with respect to the pendulum support 30 usually in the area above the center of gravity.
  • the swivel axis lies in the longitudinal median plane of the carriage, whereas the swivel axis is opposite away from the longitudinal median plane of the carriage when the traverse is inclined. Because of that Center of gravity distant position of the current swivel axis in the inclined state of the However, a specific restoring moment is generated by the crossbeam, which the carriage or the Traverse automatically moves back to its starting position, or move this back supported so that a passive inclination reset of the car body is possible is.
  • controllable actuator 76 which in the embodiment shown as a Piston / cylinder unit is realized, which is transverse to the direction of travel and essentially lying below the pendulum support 30 and above the connecting plate 52 of the cross member 31 is arranged.
  • the actuator 76 is at a distance from the Longitudinal center plane of the chassis via a bearing 77 of the connecting plate 52 on the Traverse 31 articulated, whereas it has the other end at the opposite Chassis side at a distance from the longitudinal center plane via a bearing 78 on the Pendulum support 30 is articulated.
  • the articulation of the actuating unit 76 at the bearing points 77, 78 takes place by means of a pin 79, 80 each. Due to the particularly deep arrangement of the Actuator 76 are the force introduction points in a comparatively large Distance from the center of gravity, so that the inclination position at a low Use of force is possible. This has a particularly advantageous effect on the dimensioning and the Of the entire tilting mechanism (actuator, bearings, bolts, etc.). Furthermore, the entire tilting mechanism according to the invention is via the secondary spring stage (Air springs 28, 29) supported on the chassis frame, so that the mechanics of the Chassis essentially does not have to absorb or transmit vibrations or shocks. This has an advantageous effect on the service life and operational reliability of the Tilt mechanism off. At this point it should be noted that in the context of the present Invention any actuator can be used, provided the installation and function According to the above description, what is possible is essential for the present invention, that the sufficiency can be found with a single actuator.
  • the cross member 31 is together with the pendulum support 30 with respect to the chassis frame 2 by a substantially vertical Axis can be turned out.
  • a reset of this turning movement is by the Transverse stiffness of the air springs 28, 29 realized.
  • the shown Embodiment provided a damping of this turning movement to Intercept rolling movements of the bogie.
  • Truss longitudinal struts 48, 49 each with a downwardly projecting bracket 81, 82, the articulated with one end of a horizontal damper element oriented in the direction of travel 83, 84 is connected.
  • the other end of the damper element 83, 84 is rigid in each case Anti-roll damper bracket 85, 86 on the associated side member 3, 4 of the frame 2 attached.
  • connecting part 36, 37 is provided with an opening 88, 89 of the conical sections 50, 51 of the cross member 31 passed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Body Structure For Vehicles (AREA)
  • Vehicle Interior And Exterior Ornaments, Soundproofing, And Insulation (AREA)
  • Packaging Of Machine Parts And Wound Products (AREA)
  • Sealing Devices (AREA)
  • Springs (AREA)
  • Gear Transmission (AREA)
  • Seats For Vehicles (AREA)
  • Vibration Prevention Devices (AREA)
  • Motorcycle And Bicycle Frame (AREA)
  • Platform Screen Doors And Railroad Systems (AREA)
  • Character Spaces And Line Spaces In Printers (AREA)
EP97946701A 1996-12-19 1997-12-03 Drehgestell-fahrwerk für ein schienenfahrzeug Expired - Lifetime EP0944513B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT222996 1996-12-19
AT0222996A AT405166B (de) 1996-12-19 1996-12-19 Drehgestell-fahrwerk für ein schienenfahrzeug
PCT/AT1997/000269 WO1998026970A1 (de) 1996-12-19 1997-12-03 Drehgestell-fahrwerk für ein schienenfahrzeug

Publications (2)

Publication Number Publication Date
EP0944513A1 EP0944513A1 (de) 1999-09-29
EP0944513B1 true EP0944513B1 (de) 2000-07-26

Family

ID=3530433

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97946701A Expired - Lifetime EP0944513B1 (de) 1996-12-19 1997-12-03 Drehgestell-fahrwerk für ein schienenfahrzeug

Country Status (20)

Country Link
US (1) US6247413B1 (hu)
EP (1) EP0944513B1 (hu)
JP (1) JP4254971B2 (hu)
KR (1) KR100492853B1 (hu)
CN (1) CN1098185C (hu)
AT (2) AT405166B (hu)
AU (1) AU722532B2 (hu)
CA (1) CA2274118C (hu)
CZ (1) CZ297368B6 (hu)
DE (1) DE59702092D1 (hu)
ES (1) ES2151747T3 (hu)
HK (1) HK1023970A1 (hu)
HR (1) HRP970695B1 (hu)
HU (1) HU221927B1 (hu)
NO (1) NO306899B1 (hu)
PL (1) PL184653B1 (hu)
RU (1) RU2203818C2 (hu)
SK (1) SK285921B6 (hu)
TW (1) TW480227B (hu)
WO (1) WO1998026970A1 (hu)

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DE102011014273B4 (de) * 2011-03-17 2014-04-03 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Bremseinrichtung eines Schienenfahrzeugs mit in Neutralposition federbelasteter Bremszangeneinheit
DE102012207194A1 (de) * 2012-04-30 2013-10-31 Siemens Aktiengesellschaft Bremseinheit für ein Fahrzeug und Fahrzeug mit einer derartigen Bremseinheit
CN103569149A (zh) * 2012-06-28 2014-02-12 庞巴迪运输有限公司 用于一种带有空气弹簧装置的轨道车辆的运行机构
UA120782U (uk) * 2013-02-28 2017-11-27 Оффене Акціенгезельшафт Руссіше Айзенбанен Бігунковий візок для рейкових транспортних засобів
EP2883775A1 (de) * 2013-12-13 2015-06-17 Siemens Aktiengesellschaft Drehgestell mit auf den Lagerungen gelagertem Radsatzantrieb
AT517179A3 (de) * 2015-04-30 2018-03-15 Siemens Ag Oesterreich Vorrichtung zur Befestigung von Bremseinrichtungen an einem Fahrwerksrahmen eines Schienenfahrzeuges
RU2613922C2 (ru) * 2016-05-04 2017-03-22 Владимир Викторович Бодров Трехтележечное транспортное средство и средняя тележка конструкции в.в. бодрова
CN106004913B (zh) * 2016-06-21 2019-03-19 中车唐山机车车辆有限公司 转向架
WO2019185119A1 (de) * 2018-03-27 2019-10-03 Siemens Ag Österreich Fahrwerk für ein schienenfahrzeug
CN110254461B (zh) * 2019-07-02 2024-04-05 株洲时代新材料科技股份有限公司 抗侧滚扭杆上的刚度可调的横向弹性止档及刚度调节方法
RU201083U1 (ru) * 2020-08-10 2020-11-26 Акционерное общество "Научно-исследовательский и конструкторско-технологический институт подвижного состава" (АО "ВНИКТИ") Люлечное подвешивание тележки грузового вагона

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DE19543747B4 (de) * 1994-11-24 2018-11-29 Josef Nusser Vorrichtung zur Neigungsregulierung des Wagenkastens bei Schienenfahrzeugen
IT1280855B1 (it) 1995-04-07 1998-02-11 Fiat Ferroviaria Spa "sistema di comando della rotazione della cassa in un veicolo ferroviario ad assetto variabile"
IT1280854B1 (it) 1995-04-07 1998-02-11 Fiat Ferroviaria Spa "veicolo ferroviario con cassa ad assetto variabile"
IT1281352B1 (it) * 1995-09-22 1998-02-18 Fiat Ferroviaria Spa Veicolo ferroviario con cassa ad assetto variabile
FR2756241B1 (fr) * 1996-11-25 2003-11-14 Gec Alsthom Transport Sa Dispositif de pendulation a bielles et bogie a pendulation a bielles

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HUP0001085A3 (en) 2002-01-28
SK79499A3 (en) 2000-01-18
HK1023970A1 (en) 2000-09-29
CZ210699A3 (cs) 2000-04-12
RU2203818C2 (ru) 2003-05-10
NO306899B1 (no) 2000-01-10
PL184653B1 (pl) 2002-11-29
ATE194947T1 (de) 2000-08-15
KR100492853B1 (ko) 2005-06-02
CZ297368B6 (cs) 2006-11-15
JP2001506202A (ja) 2001-05-15
CN1098185C (zh) 2003-01-08
DE59702092D1 (de) 2000-08-31
HU221927B1 (hu) 2003-02-28
US6247413B1 (en) 2001-06-19
NO992439D0 (no) 1999-05-20
ES2151747T3 (es) 2001-01-01
CA2274118C (en) 2007-01-30
AT405166B (de) 1999-06-25
AU5184698A (en) 1998-07-15
HRP970695A2 (en) 1998-06-30
AU722532B2 (en) 2000-08-03
PL334340A1 (en) 2000-02-28
TW480227B (en) 2002-03-21
HRP970695B1 (en) 2001-02-28
ATA222996A (de) 1998-10-15
HUP0001085A2 (hu) 2000-08-28
SK285921B6 (sk) 2007-11-02
CA2274118A1 (en) 1998-06-25
KR20000057630A (ko) 2000-09-25
WO1998026970A1 (de) 1998-06-25
EP0944513A1 (de) 1999-09-29
JP4254971B2 (ja) 2009-04-15
CN1240397A (zh) 2000-01-05
NO992439L (no) 1999-08-12

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