EP0401618A1 - Bogie for rapid railway vehicles - Google Patents

Bogie for rapid railway vehicles Download PDF

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Publication number
EP0401618A1
EP0401618A1 EP90109959A EP90109959A EP0401618A1 EP 0401618 A1 EP0401618 A1 EP 0401618A1 EP 90109959 A EP90109959 A EP 90109959A EP 90109959 A EP90109959 A EP 90109959A EP 0401618 A1 EP0401618 A1 EP 0401618A1
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EP
European Patent Office
Prior art keywords
bogie
spring leaf
damper
bogie frame
axle bearing
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
EP90109959A
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German (de)
French (fr)
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EP0401618B1 (en
Inventor
Guido Dipl.-Ing. Bieker
Gerhard Kampmann
Alfred Dipl.-Ing. Lohmann
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.)
ABB Henschel Waggon Union GmbH
Original Assignee
Waggon Union GmbH
ABB Henschel Waggon Union GmbH
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Publication of EP0401618A1 publication Critical patent/EP0401618A1/en
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    • 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
    • B61F5/26—Mounting or securing axle-boxes in vehicle or bogie underframes
    • B61F5/30—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes
    • B61F5/32—Guides, e.g. plates, for axle-boxes
    • B61F5/325—The guiding device including swinging arms or the like to ensure the parallelism of the axles
    • 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
    • B61F5/26—Mounting or securing axle-boxes in vehicle or bogie underframes
    • B61F5/30—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes
    • B61F5/305—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes incorporating rubber springs

Definitions

  • the invention relates to a bogie for high-speed rail vehicles, in which the wheel sets are connected and guided on the bogie frame by means of double spring leaf links acting on the axle bearings, elastic intermediate bearings are provided between double spring leaf links and axle bearings or bogie frame, and a vertical primary spring between each axle bearing and the bogie frame is arranged.
  • Bogies of the type mentioned above are known for example from DE-PS 17 55 072.
  • the long girders of the bogie frame are supported by springs on the axle bearing housings of the wheel sets, each of which is arranged in two mutually parallel, spring leaf links, the ends of the spring leaf links facing away from the axle bearing housings being firmly connected with a fixed bracket as part of the bogie frame without play and friction .
  • each axle bearing housing there is a sprue eye that extends horizontally in the longitudinal direction between the free ends of the handlebar blades with a vertical bore that symmetrically widens upwards and downwards and a bushing made of elastic material located therein and concentric with the bushing from above and below with a clamping ring externally conical jacket can be used, the small end faces facing each other and on the upper and lower outer larger end faces the free ends of the handlebar blades can be pressed on by means of an expansion screw, the clamping rings and the free handlebar blade ends being able to be joined together to form a unit which is supported by the bushing relative to the axle bearing housing .
  • This arrangement improves the running properties of a rail vehicle at high speeds due to the flexible mounting of the spring leaf link mounting on the axle bearing housing, because a certain automatic radial adjustment of the wheel sets can be achieved.
  • the arrangement of the rubber intermediate bearings means that the resonance range of the bogie can be relocated to a speed range that experience has shown that it can be driven through in a short time when moving off, that is, not the travel area speed of the rail vehicle corresponds.
  • the resonance range can be adjusted precisely in that the clamping rings are moved closer or closer to one another in the axial direction, with the bushing made of elastic material being deformed to a greater or lesser extent.
  • This known wheel set guidance represents a compromise between stable, relatively quiet wheel set running in the straight line and a run that is as wear-resistant and low-power as possible in the curve, since a longitudinally rigid wheel set guide with high running stability in the straight line results in only a slight radial adjustment of the wheel sets in the curve, whereas with a longitudinally soft one
  • the stability of the wheelset and thus the maximum speed is very much reduced in order to achieve a substantially improved radial setting of the wheelsets and low tracking forces in the curve.
  • the most rigid longitudinal linkage of the wheel sets is chosen. This in turn leads to poorer radial adjustment of the wheel sets in the bend and thus to higher tracking forces and greater wear on the flange. If, on the other hand, the radial setting of the wheel sets is to be improved, a reduction in the stable, smooth straight running of the wheel sets in the straight line and thus a lower maximum speed are accepted.
  • the object of the present invention was to eliminate the above-described opposite running behavior in the straight line and in the rail curve by suitable, simple constructive measures in a bogie of the type mentioned above, and with a stable, smooth straight line running in the straight line at maximum speeds, a radial adjustment of the wheel sets in the rail curve to achieve low tracking forces.
  • Anti-roll damper can be designed as a double-acting hydraulic damper.
  • the roll damper is designed as a friction damper. When using a hydraulic damper as a roll damper, it is attached at one end to the axle bearing and at the other end to the bogie frame.
  • a friction damper is used as a roll damper, according to one exemplary embodiment, this is designed to act between the spring leaf links on the bearing of the double spring leaf link, which is provided with the elastic intermediate bearing.
  • the friction damper is attached to the double spring leaf link on the one hand and to the axle bearing or to the bogie frame on the other.
  • the friction damper consists of at least two adjustable leaf springs which bear against one another on their longitudinal ends against friction surfaces of the axle bearing housing and / or the bogie frame arranged in the longitudinal direction of the bogie.
  • the wheelsets 1 of the bogie are connected and guided on the bogie frame 4 via their axle bearings 2 and on these double spring leaf links 3 arranged horizontally.
  • the two spring leaf links of each double spring leaf link 3 are adjustable on the bogie frame 4 via toothed plates 5 and rigidly attached.
  • the spring leaf links of each double spring leaf link 3 are also fixed to the axle bearing 2 via toothed plates 6 but with the interposition of elastic intermediate layers 7.
  • the rubber intermediate layers 7 can be precisely preloaded by means of an expansion screw 8, which fastens the two spring leaf links to the axle bearing housing.
  • the horizontal longitudinal stiffness of the rubber intermediate layer 7 can in turn be precisely adjusted by an appropriately selected prestressing of the expansion screw 8.
  • a hydraulic damper 9 is arranged between the two spring leaf links of the double spring leaf link 3 and is articulated at one end to the bogie frame 4 and at the other end to the axle bearing 2.
  • the hydraulic damper which is double-acting, thus acts in the horizontal longitudinal direction between the bogie frame and the axle bearing housing.
  • the wheel set is likewise connected and guided horizontally on the bogie frame 4 via the axle bearing housing 2 and double spring leaf link 3.
  • the double spring leaf link 3 is fastened to the bogie frame 4 and to the axle bearing 2 as in the exemplary embodiment of the invention described in FIGS. 2 and 3.
  • elastic intermediate bearings 7 are also arranged between the tooth plates 6 and the axle bearing housing 2.
  • disc springs 10 are provided between the tooth plates 6 and a horizontal flange 2a of the axle bearing housing 2 and press the friction rings 11 on both sides against friction linings 12 of the flange 2a of the axle bearing housing 2.
  • the plate springs 10 and thus the contact pressure of the friction surface 11 on the friction lining 12 can be adjusted via the expansion screw 8. Toothed plates 6 and expansion screw 8 are guided with play in a bore 13 in the flange 2a of the axle bearing housing 2, so that the required swiveling out of the wheel set with the axle bearing 2 is possible with the wheel set being set radially in the arc.
  • the wheel set 1 is again fastened and guided horizontally on the bogie frame 4 via the axle bearing housing 2 and double spring leaf link 3.
  • two curved spring leaves 15 are arranged, which abut laterally at their longitudinal ends against friction surfaces 16 of the axle bearing housing 2 and friction surfaces 17 of the bogie frame 4 arranged in the longitudinal direction of the bogie.
  • the friction surfaces 16 and 17 are expediently provided with a friction lining.
  • the two spring leaves 15 are braced against one another by means of an adjusting screw 18 such that a defined contact pressure is exerted on the friction surfaces 16 and 17.
  • Lateral guide webs 19 of the axle bearing housing 2 and guide webs 20 of the bogie frame guide the spring leaves 15.

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Abstract

The invention relates to a bogie for high-speed railway vehicles in which the wheel sets (1) are guided on the bogie frame (4) by means of double spring leaf guides (3). <??>The objective of the present invention consists in achieving in the bogie a stable, quiet, straight line passage in a straight line at maximum speed and a radial adjustment of the wheel sets (1) in a track curve with low track guiding forces. <??>This object is achieved in that a hunting damper (9 and 10 - 12 and 15 - 17, respectively) which damps the horizontal longitudinal movements between axle bearing (2) and bogie frame (4) is arranged between the spring leaf guides (3) of each double spring leaf guide. <IMAGE>

Description

Die Erfindung betrifft ein Drehgestell für schnellfahrende Schienenfahr­zeuge, bei dem die Radsätze mittels an den Achslagern angreifenden Dop­pel-Federblattlenkern am Drehgestellrahmen angebunden und geführt sind, zwischen Doppel-Federblattlenker und Achslager oder Drehgestellrahmen elastische Zwischenlager vorgesehen sind und zwischen jedem Achslager und dem Drehgestellrahmen eine vertikale Primärfeder angeordnet ist.The invention relates to a bogie for high-speed rail vehicles, in which the wheel sets are connected and guided on the bogie frame by means of double spring leaf links acting on the axle bearings, elastic intermediate bearings are provided between double spring leaf links and axle bearings or bogie frame, and a vertical primary spring between each axle bearing and the bogie frame is arranged.

Drehgestelle der vorstehend genannten Art sind beispielsweise aus der DE-PS 17 55 072 bekannt. Hierbei sind die Langträger des Drehgestellrah­mens über Federn auf die mittels je zwei in verschiedenen Ebenen überein­ander angeordneten, zueinander parallelen Federblattlenker geführten Achslagergehäuse der Radsätze abgestützt, wobei die den Achslagergehäusen abgewandten Enden der Federblattlenker mit einem Festbock als Teil des Drehgestellrahmens spiel- und reibungsfrei fest verbunden sind. An jedem Achslagergehäuse ist hierbei ein in Längsrichtung waagerecht zwischen die freien Enden der Lenkerblätter reichendes Angußauge mit senkrechten, sich symmetrisch nach oben und unten erweiternden Bohrung und einer in dieser befindlichen Buchse aus elastischem Material angebracht und konzentrisch zu der Buchse von oben und unten Klemmringe mit einem außen kegeligen Mantel einsetzbar, deren kleine Stirnflächen einander zugewandt und an deren obere und untere äußere größere Stirnflächen mittels einer Dehn­schraube die freien Enden der Lenkerblätter andrückbar sind, wobei die Klemmringe und die freien Lenkerblätterenden zu einer sich über die Buchse gegenüber dem Achslagergehäuse abstützenden Einheit zusammenfügbar sind. Durch diese Anordnung werden die Laufeigenschaften eines Schienenfahrzeugs bei hohen Geschwindigkeiten durch die nachgiebige Halterung der Feder­blattlenker-Befestigung am Achslagergehäuse verbessert, weil eine gewisse selbsttätige Radialeinstellung der Radsätze erreichbar ist. Durch die Anordnung der Gummizwischenlager ist der Resonanzbereich des Drehgestells in einen Geschwindigkeitsbereich verlegbar, der erfahrungsgemäß in kurzer Zeit beim Anfahren durchfahrbar ist, das heißt, der nicht der Reisege­ schwindigkeit des Schienenfahrzeugs entspricht. Der Resonanzbereich ist dadurch exakt einstellbar, daß die Klemmringe in axialer Richtung einander angenähert oder voneinander entfernt festgestellt werden, wobei eine mehr oder weniger starke Verformung der aus elastischem Material bestehenden Buchse stattfindet.Bogies of the type mentioned above are known for example from DE-PS 17 55 072. Here, the long girders of the bogie frame are supported by springs on the axle bearing housings of the wheel sets, each of which is arranged in two mutually parallel, spring leaf links, the ends of the spring leaf links facing away from the axle bearing housings being firmly connected with a fixed bracket as part of the bogie frame without play and friction . On each axle bearing housing there is a sprue eye that extends horizontally in the longitudinal direction between the free ends of the handlebar blades with a vertical bore that symmetrically widens upwards and downwards and a bushing made of elastic material located therein and concentric with the bushing from above and below with a clamping ring externally conical jacket can be used, the small end faces facing each other and on the upper and lower outer larger end faces the free ends of the handlebar blades can be pressed on by means of an expansion screw, the clamping rings and the free handlebar blade ends being able to be joined together to form a unit which is supported by the bushing relative to the axle bearing housing . This arrangement improves the running properties of a rail vehicle at high speeds due to the flexible mounting of the spring leaf link mounting on the axle bearing housing, because a certain automatic radial adjustment of the wheel sets can be achieved. The arrangement of the rubber intermediate bearings means that the resonance range of the bogie can be relocated to a speed range that experience has shown that it can be driven through in a short time when moving off, that is, not the travel area speed of the rail vehicle corresponds. The resonance range can be adjusted precisely in that the clamping rings are moved closer or closer to one another in the axial direction, with the bushing made of elastic material being deformed to a greater or lesser extent.

Diese vorbekannte Radsatzführung stellt einen Kompromiß aus stabilem, relativ ruhigem Radsatzlauf in der Geraden und einem möglichst verschleiß­und kräftearmem Lauf im Bogen dar, da eine längsstarre Radsatzführung bei hoher Laufstabilität in der Geraden nur eine geringe radiale Einstellung der Radsätze im Bogen ergibt, wogegen bei einer längsweichen Radsatzfüh­rung die Laufstabilität und damit die Höchstgeschwindigkeit sehr stark herabgesetzt wird zur Erzielung einer wesentlich verbesserten radialen Einstellung der Radsätze und niedrigen Spurführungskräften im Bogen. Es wird also zur Erzielung einer hohen Geschwindigkeit in der Geraden eine möglichst starre Längsanlenkung der Radsätze gewählt. Dieses wiederum führt zu einer schlechteren Radialeinstellung der Radsatze im Bogen und damit zu höheren Spurführungskräften und größerem Spurkranzverschleiß. Soll dagegen die Radialeinstellung der Radsätze verbessert werden, wird eine Verminderung des stabilen, ruhigen Geradeauslaufs der Radsätze in der Geraden und damit eine niedrigere Höchstgeschwindigkeit in Kauf genommen.This known wheel set guidance represents a compromise between stable, relatively quiet wheel set running in the straight line and a run that is as wear-resistant and low-power as possible in the curve, since a longitudinally rigid wheel set guide with high running stability in the straight line results in only a slight radial adjustment of the wheel sets in the curve, whereas with a longitudinally soft one The stability of the wheelset and thus the maximum speed is very much reduced in order to achieve a substantially improved radial setting of the wheelsets and low tracking forces in the curve. In order to achieve a high speed in the straight line, the most rigid longitudinal linkage of the wheel sets is chosen. This in turn leads to poorer radial adjustment of the wheel sets in the bend and thus to higher tracking forces and greater wear on the flange. If, on the other hand, the radial setting of the wheel sets is to be improved, a reduction in the stable, smooth straight running of the wheel sets in the straight line and thus a lower maximum speed are accepted.

Die Aufgabe vorliegender Erfindung bestand darin, bei einem Drehgestell der eingangs genannten Art das vorstehend geschilderte gegensätzliche Laufverhalten in der Geraden und im Schienenbogen durch geeignete, ein­fache konstruktive Maßnahmen aufzuheben und bei einem stabilen ruhigen Geradeauslauf in der Geraden bei Höchstgeschwindigkeiten eine Radialein­stellung der Radsätze im Schienenbogen bei niedrigen Spurführungskräften zu erreichen.The object of the present invention was to eliminate the above-described opposite running behavior in the straight line and in the rail curve by suitable, simple constructive measures in a bogie of the type mentioned above, and with a stable, smooth straight line running in the straight line at maximum speeds, a radial adjustment of the wheel sets in the rail curve to achieve low tracking forces.

Gemäß der Erfindung wird diese Aufgabe bei einem Drehgestell der eingangs genannten Art dadurch gelöst, daß zwischen den Federblattlenkern jeden Doppel-Federblattlenkers ein die horizontalen Längsbewegungen zwischen Achslager und Drehgestellrahmen dampfender Schlingerdämpfer angeordnet ist. Hierbei kann gemäß einem Ausführungsbeispiel der Erfindung der Schlingerdämpfer als doppelt wirkender Hydrodämpfer ausgebildet sein. Gemäß anderen Ausführungsbeispielen der Erfindung ist der Schlingerdämpfer als Reibdämpfer ausgebildet. Bei Verwendung eines Hydrodämpfers als Schlingerdämpfer ist dieser mit seinem einen Ende am Achslager und mit seinem anderen Ende am Drehgestellrahmen befestigt. Bei Verwendung eines Reibdämpfers als Schlingerdämpfer ist dieser gemäß einem Ausführungsbei­spiel zwischen den Federblattlenkern auf das Lager des Doppel-Federblatt­lenkers wirkend ausgebildet, das mit dem elastischen Zwischenlager ver­sehen ist. Hierbei ist der Reibdämpfer einerseits an den Doppel-Feder­blattlenker und andererseits am Achslager oder am Drehgestellrahmen befestigt.According to the invention, this object is achieved in a bogie of the type mentioned in that a horizontal longitudinal movements between the axle bearing and bogie frame damping anti-roll damper is arranged between the spring leaf links of each double spring leaf link. Here, according to an embodiment of the invention Anti-roll damper can be designed as a double-acting hydraulic damper. According to other exemplary embodiments of the invention, the roll damper is designed as a friction damper. When using a hydraulic damper as a roll damper, it is attached at one end to the axle bearing and at the other end to the bogie frame. If a friction damper is used as a roll damper, according to one exemplary embodiment, this is designed to act between the spring leaf links on the bearing of the double spring leaf link, which is provided with the elastic intermediate bearing. The friction damper is attached to the double spring leaf link on the one hand and to the axle bearing or to the bogie frame on the other.

Bei einem dritten Ausführungsbeispiel besteht der Reibdämpfer aus minde­stens zwei einstellbar gegeneinander verspannten Blattfedern, die an ihren Längsenden beidseitig gegen in Drehgestellängsrichtung angeordnete Reib­flächen des Achslagergehäuses und/oder des Drehgestellrahmens anliegen.In a third exemplary embodiment, the friction damper consists of at least two adjustable leaf springs which bear against one another on their longitudinal ends against friction surfaces of the axle bearing housing and / or the bogie frame arranged in the longitudinal direction of the bogie.

Durch eine weiche Ausbildung des elastischen Zwischenlagers kann eine fast ideale radiale Einstellung der Radsätze bis zu den im Personenfernverkehr kleinsten Bogenradien von 250 m bei einer guten Gleichverteilung der Radsatzführungskräfte am vor- und nachlaufenden Radsatz erreicht werden. Ebenfalls können mit der erfindungsgemäßen Ausbildung des Drehgestells jetzt höhere Geschwindigkeiten in größeren Bögen gefahren werden, da genügend Reserven für die Aufnahme von dynamischen Führungskräften infolge Gleislagefehlern vorhanden sind. Der Spurkranzverschleiß wird deutlich verringert. Durch die Anordnung der Schlingerdämpfer bleiben die für einen stabilen, ruhigen Radsatzlauf in der Geraden erforderlichen Radsatzfüh­rungskräfte erhalten.Thanks to a soft design of the elastic intermediate bearing, an almost ideal radial adjustment of the wheel sets down to the smallest radius of curvature of 250 m in long-distance passenger transport can be achieved with a good uniform distribution of the wheel set executives on the leading and trailing wheel set. Likewise, with the design of the bogie according to the invention, higher speeds can now be driven in larger arches, since there are sufficient reserves for the accommodation of dynamic managers as a result of track position errors. Wheel flange wear is significantly reduced. The arrangement of the anti-roll damper means that the wheelset guidance forces required for stable, quiet wheel set running in the straight line are retained.

Einzelheiten der Erfindung werden anhand von Ausführungsbeispielen in der Zeichnung erläutert.Details of the invention are explained using exemplary embodiments in the drawing.

Es zeigen

  • Fig. 1 die Seitenansicht eines Drehgestells für schnellfahrende Schie­nenfahrzeuge gemäß der Erfindung in Seitenansicht,
  • Fig. 2 eine vergrößerte Darstellung der Radsatzführung des Drehgestells nach Fig. 1 in Draufsicht, zum Teil im Schnitt, gemäß einem ersten Ausführungsbeispiel der Erfindung,
  • Fig. 3 den Schnitt nach Linie III-III der Fig. 2,
  • Fig. 4 die Draufsicht wie Fig. 2, gemäß einem zweiten Ausführungsbei­spiel der Erfindung,
  • Fig. 5 den Schnitt nach Linie V-V der Fig. 4.
  • Fig. 6 einen vertikalen Längsschnitt durch die Radsatzführung des Drehgestells nach Fig. 1, gemäß einem dritten Ausführungsbei­spiel der Erfindung,
  • Fig. 7 die Draufsicht auf die Radsatzführung nach Fig. 6, zum Teil im Schnitt.
Show it
  • 1 is a side view of a bogie for high-speed rail vehicles according to the invention,
  • Fig. 2 is an enlarged view of the wheelset guide of the bogie 1 in plan view, partly in section, according to a first embodiment of the invention,
  • 3 shows the section along line III-III of FIG. 2,
  • 4 shows the top view like FIG. 2, according to a second exemplary embodiment of the invention,
  • 5 shows the section along line VV of FIG. 4th
  • 6 shows a vertical longitudinal section through the wheelset guide of the bogie according to FIG. 1, according to a third embodiment of the invention
  • Fig. 7 is a plan view of the wheel set guide according to Fig. 6, partly in section.

Die Radsätze 1 des Drehgestells sind über ihre Achslager 2 und an diesen horizontal angeordnete Doppel-Federblattlenker 3 am Drehgestellrahmen 4 angebunden und geführt. Die beiden Federblattlenker jeden Doppel-Feder­blattlenkers 3 sind dabei am Drehgestellrahmen 4 über Zahnplatten 5 einstellbar und starr befestigt. Am Achslager 2 sind die Federblattlenker jeden Doppel-Federblattlenkers 3 ebenfalls über Zahnplatten 6 jedoch unter Zwischenschaltung von elastischen Zwischenlagen 7 einstellbar befestigt. Mittels einer Dehnschraube 8, die die beiden Federblattlenker am Achsla­gergehäuse befestigt, sind die Gummizwischenlagen 7 exakt vorspannbar. Durch eine entsprechend gewählte Vorspannung der Dehnschraube 8 ist wiederum die horizontale Längssteifigkeit der Gummizwischenlage 7 genau einstellbar. Zwischen den beiden Federblattlenkern des Doppel-Federblatt­lenkers 3 ist ein Hydrodämpfer 9 angeordnet, der mit seinem einen Ende am Drehgestellrahmen 4 und mit seinem anderen Ende am Achslager 2 gelenkig befestigt ist. Der Hydrodämpfer, der doppelwirkend ausgebildet ist, wirkt somit in horizontaler Längsrichtung zwischen Drehgestellrahmen und Achs­lagergehäuse.The wheelsets 1 of the bogie are connected and guided on the bogie frame 4 via their axle bearings 2 and on these double spring leaf links 3 arranged horizontally. The two spring leaf links of each double spring leaf link 3 are adjustable on the bogie frame 4 via toothed plates 5 and rigidly attached. The spring leaf links of each double spring leaf link 3 are also fixed to the axle bearing 2 via toothed plates 6 but with the interposition of elastic intermediate layers 7. The rubber intermediate layers 7 can be precisely preloaded by means of an expansion screw 8, which fastens the two spring leaf links to the axle bearing housing. The horizontal longitudinal stiffness of the rubber intermediate layer 7 can in turn be precisely adjusted by an appropriately selected prestressing of the expansion screw 8. A hydraulic damper 9 is arranged between the two spring leaf links of the double spring leaf link 3 and is articulated at one end to the bogie frame 4 and at the other end to the axle bearing 2. The hydraulic damper, which is double-acting, thus acts in the horizontal longitudinal direction between the bogie frame and the axle bearing housing.

Bei dem in den Figuren 4 und 5 dargestellten Ausführungsbeispiel der Erfindung ist der Radsatz ebenfalls über das Achslagergehäuse 2 und Doppel-Federblattlenker 3 am Drehgestellrahmen 4 horizontal angebunden und geführt. Der Doppel-Federblattlenker 3 ist dabei wie bei dem in den Figuren 2 und 3 beschriebenen Ausführungsbeispiel der Erfindung am Dreh­gestellrahmen 4 und am Achslager 2 befestigt. Zwischen den Zahnplatten 6 und dem Achslagergehäuse 2 sind ebenfalls elastische Zwischenlager 7 angeordnet. Zwischen den Zahnplatten 6 und einem horizontalen Flansch 2a des Achslagergehäuses 2 sind bei diesem Ausführungsbeispiel der Erfindung Tellerfedern 10 vorgesehen, die Reibringe 11 beidseitig gegen Reibbeläge 12 des Flansches 2a des Achslagergehäuses 2 anpressen. Über die Dehn­schraube 8 sind die Tellerfedern 10 und damit die Anpreßkraft der Reib­fläche 11 auf dem Reibbelag 12 einstellbar. Zahnplatten 6 und Dehnschraube 8 sind mit Spiel in einer Bohrung 13 des Flansches 2a des Achslagergehäu­ses 2 geführt, so daß die erforderliche Ausschwenkung des Radsatzes mit dem Achslager 2 bei Radialeinstellung des Radsatzes im Bogenlauf möglich ist.In the exemplary embodiment of the invention illustrated in FIGS. 4 and 5, the wheel set is likewise connected and guided horizontally on the bogie frame 4 via the axle bearing housing 2 and double spring leaf link 3. The double spring leaf link 3 is fastened to the bogie frame 4 and to the axle bearing 2 as in the exemplary embodiment of the invention described in FIGS. 2 and 3. Between the tooth plates 6 and the axle bearing housing 2, elastic intermediate bearings 7 are also arranged. In this exemplary embodiment of the invention, disc springs 10 are provided between the tooth plates 6 and a horizontal flange 2a of the axle bearing housing 2 and press the friction rings 11 on both sides against friction linings 12 of the flange 2a of the axle bearing housing 2. The plate springs 10 and thus the contact pressure of the friction surface 11 on the friction lining 12 can be adjusted via the expansion screw 8. Toothed plates 6 and expansion screw 8 are guided with play in a bore 13 in the flange 2a of the axle bearing housing 2, so that the required swiveling out of the wheel set with the axle bearing 2 is possible with the wheel set being set radially in the arc.

Bei dem in den Figuren 6 und 7 dargestellten Ausführungsbeispiel der Erfindung ist der Radsatz 1 wieder über das Achslagergehäuse 2 und Dop­pel-Federblattlenker 3 am Drehgestellrahmen 4 horizontal befestigt und geführt. Zwischen den beiden Federblattlenkern des Doppel-Federblattlen­kers 3 sind zwei gewölbte Federblätter 15 angeordnet, die an ihren Längs­enden seitlich gegen in Drehgestellängsrichtung angeordnete Reibflächen 16 des Achslagergehäuses 2 und Reibflachen 17 des Drehgestellrahmens 4 anliegen. Die Reibflächen 16 und 17 sind zweckmäßig mit einem Reibbelag versehen. In ihrer Längsmitte werden die beiden Federblätter 15 mittels einer Stellschraube 18 so gegeneinander verspannt, daß ein definierter Anpreßdruck auf die Reibflächen 16 und 17 entsteht. Seitliche Führungs­stege 19 des Achslagergehäuses 2 und Führungsstege 20 des Drehgestellrah­mens führen die Federblätter 15.In the embodiment of the invention illustrated in FIGS. 6 and 7, the wheel set 1 is again fastened and guided horizontally on the bogie frame 4 via the axle bearing housing 2 and double spring leaf link 3. Between the two spring leaf links of the double spring leaf link 3, two curved spring leaves 15 are arranged, which abut laterally at their longitudinal ends against friction surfaces 16 of the axle bearing housing 2 and friction surfaces 17 of the bogie frame 4 arranged in the longitudinal direction of the bogie. The friction surfaces 16 and 17 are expediently provided with a friction lining. In the longitudinal center thereof, the two spring leaves 15 are braced against one another by means of an adjusting screw 18 such that a defined contact pressure is exerted on the friction surfaces 16 and 17. Lateral guide webs 19 of the axle bearing housing 2 and guide webs 20 of the bogie frame guide the spring leaves 15.

Claims (7)

1. Drehgestell für schnellfahrende Schienenfahrzeuge, bei dem die Radsätze mittels an den Achslagern angreifenden Doppel-Federblattlenkern am Drehgestellrahmen angebunden und geführt sind, zwischen Doppel-Feder­blattlenker und Achslager oder Drehgestellrahmen Gummizwischenlager vorgesehen sind und zwischen jedem Achslager und dem Drehgestellrahmen eine vertikale Primärfeder angeordnet ist, dadurch gekennzeichnet, daß zwischen den Federblattlenkern (3) jeden Doppel-Federblattlenkers ein die horizontalen Längsbewegungen zwischen Achslager (2) und Drehgestellrahmen (4) dämpfender Schlingerdämpfer (9 bzw. 10 - 12 bzw. 15 - 17) angeordnet ist.1.Bogie for high-speed rail vehicles, in which the wheel sets are connected and guided to the bogie frame by means of double spring leaf links which engage the axle bearings, rubber intermediate bearings are provided between double spring leaf links and axle bearings or bogie frame and a vertical primary spring is arranged between each axle bearing and the bogie frame, characterized in that between the spring leaf links (3) of each double spring leaf link is a horizontal longitudinal movement between the axle bearing (2) and the bogie frame (4) damping anti-roll damper (9 or 10-12 or 15-17). 2. Drehgestell nach Anspruch 1, dadurch gekennzeichnet, daß der Schlingerdämpfer als doppelt wirkender Hydrodämpfer (9) ausgebildet ist.2. Bogie according to claim 1, characterized in that the roll damper is designed as a double-acting hydraulic damper (9). 3. Drehgestell nach Anspruch 1, dadurch gekennzeichnet, daß der Schlingerdämpfer als Reibdämpfer (10 - 12 bzw. 15 - 17) ausgebildet ist.3. Bogie according to claim 1, characterized in that the roll damper is designed as a friction damper (10 - 12 or 15 - 17). 4. Drehgestell nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß der Hydrodämpfer (9) mit seinem einen Ende am Achslager (2) und mit seinem anderen Ende am Drehgestellrahmen (4) befestigt ist.4. Bogie according to claims 1 and 2, characterized in that the hydraulic damper (9) is attached at one end to the axle bearing (2) and with its other end to the bogie frame (4). 5. Drehgestell nach den Ansprüchen 1 und 3, dadurch gekennzeichnet, daß der Reibdämpfer (10 - 12) zwischen den Federblattlenkern (3) auf das Lager des Doppel-Federblattlenkers wirkend angeordnet ist, das mit dem elastischen Zwischenlager (7) versehen ist.5. Bogie according to claims 1 and 3, characterized in that the friction damper (10 - 12) between the spring leaf links (3) is arranged acting on the bearing of the double spring leaf link, which is provided with the elastic intermediate bearing (7). 6. Drehgestell nach den Ansprüchen 1, 3 und 5, dadurch gekennzeich­net, daß der Reibdämpfer (10 - 12) einerseits an dem Doppel-Federblattlen­ker (3) und andererseits am Achslager (2) oder am Drehgestellrahmen befestigt ist.6. Bogie according to claims 1, 3 and 5, characterized in that the friction damper (10 - 12) on the one hand on the double spring leaf link (3) and on the other hand on the axle bearing (2) or on the bogie frame is attached. 7. Drehgestell nach den Ansprüchen 1 und 3, dadurch gekennzeichnet, daß der Reibdämpfer aus mindestens zwei einstellbar gegeneinander verspann­ten Blattfedern (15) besteht, die an ihren Längsenden beidseitig gegen in Drehgestellängsrichtung angeordnete Reibflächen (16) des Achslagergehäuses (2) und/oder Reibflächen (17) des Drehgestellrahmens (4) anliegen.7. Bogie according to claims 1 and 3, characterized in that the friction damper consists of at least two adjustable leaf springs (15) which are arranged on both sides at their longitudinal ends against in the bogie longitudinal direction friction surfaces (16) of the axle bearing housing (2) and / or friction surfaces (17) of the bogie frame (4).
EP90109959A 1989-06-05 1990-05-25 Bogie for rapid railway vehicles Expired - Lifetime EP0401618B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3918300A DE3918300A1 (en) 1989-06-05 1989-06-05 BOG FOR FAST-SPEED RAIL VEHICLES
DE3918300 1989-06-05

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EP0401618A1 true EP0401618A1 (en) 1990-12-12
EP0401618B1 EP0401618B1 (en) 1994-07-13

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US (1) US5090333A (en)
EP (1) EP0401618B1 (en)
JP (1) JPH0328067A (en)
AT (1) ATE108383T1 (en)
CA (1) CA2018197A1 (en)
CS (1) CS272490A2 (en)
DE (2) DE3918300A1 (en)
DK (1) DK0401618T3 (en)
ES (1) ES2058672T3 (en)
FI (1) FI902789A0 (en)
HR (1) HRP930620A2 (en)
HU (1) HU205309B (en)
IN (1) IN171296B (en)
NO (1) NO902445L (en)
PL (1) PL163572B1 (en)
PT (1) PT94274A (en)
RO (1) RO108228B1 (en)
TR (1) TR24412A (en)
YU (1) YU47915B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0600172A1 (en) * 1992-11-28 1994-06-08 Siemens Schienenfahrzeugtechnik GmbH Running gear for railway vehicles
CN104477199A (en) * 2014-12-15 2015-04-01 南车二七车辆有限公司 Wagon bogie tumbler fast clamping band

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4306848C2 (en) * 1993-03-01 1996-10-31 Inst Schienenfahrzeuge High speed freight bogie
CN1129181A (en) * 1994-12-28 1996-08-21 标准汽车公司 Roller bearing adapter stabilizer bar
US5918547A (en) * 1994-12-28 1999-07-06 Standard Car Truck Company Roller bearing adapter stabilizer bar
DE19824937A1 (en) * 1998-06-04 1999-12-09 Alstom Lhb Gmbh Non-positive and positive connection between two components, in particular connection between two components of different materials
GB2430421A (en) * 2005-09-22 2007-03-28 Bombardier Transp Gmbh Rail vehicle bogie
KR100898610B1 (en) * 2007-06-26 2009-05-21 주식회사 부민엔지니어링 Hydraulic skid bogie system installed driving and breaking system
KR100936822B1 (en) 2007-12-06 2010-01-14 한국철도기술연구원 The steering bogie with variable damper for railway vehicle
KR100921549B1 (en) 2007-12-06 2009-10-12 한국철도기술연구원 The self steering bogie for railway vehicle
US10011287B2 (en) * 2015-02-05 2018-07-03 Crrc Qingdao Sifang Co., Ltd. Bogie for high-speed railway vehicle

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2326729A1 (en) * 1973-05-25 1974-12-12 Maschf Augsburg Nuernberg Ag WHEEL SET GUIDE FOR A DRIVE, IN PARTICULAR A BOGIE OF A RAIL VEHICLE
FR2344432A1 (en) * 1976-03-20 1977-10-14 Waggon Union Gmbh BOGIE FOR FAST RAIL VEHICLES
US4561360A (en) * 1984-06-06 1985-12-31 Amsted Industries Incorporated Single axle suspension system for railroad vehicle

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1881139A (en) * 1929-12-17 1932-10-04 Seidel Arnold Sprung bogie for railway and tramway cars
DE1255698B (en) * 1959-03-04 1967-12-07 Goerlitz Waggonbau Veb Axle control arm for bogies of rail vehicles
DE1605137B2 (en) * 1967-07-07 1977-06-30 Wegmann & Co, 3500 Kassel WHEEL SET GUIDES FOR BOGIES OF HIGH-SPEED RAIL VEHICLES
DE1755072C3 (en) * 1968-03-27 1979-01-04 Waggon Union Gmbh, 1000 Berlin Und 5900 Siegen Bogie for fast moving rail vehicles
GB1261896A (en) * 1968-09-17 1972-01-26 British Railways Board Improvements in or relating to railway vehicles
US4067261A (en) * 1972-11-10 1978-01-10 South African Inventions Development Corporation Damping railway vehicle suspension
DE2320323C3 (en) * 1973-04-21 1979-01-18 Maschinenfabrik Augsburg-Nuernberg Ag, 8500 Nuernberg Wheelset guide, in particular for a rail vehicle, for express traffic
JPS5369313A (en) * 1976-12-01 1978-06-20 Hitachi Ltd Device for supporting axle box of railway train
US4589346A (en) * 1983-09-26 1986-05-20 Pullman Standard, Inc. Axle stop arrangement for single axle wheel truck for a skeleton type railway car

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2326729A1 (en) * 1973-05-25 1974-12-12 Maschf Augsburg Nuernberg Ag WHEEL SET GUIDE FOR A DRIVE, IN PARTICULAR A BOGIE OF A RAIL VEHICLE
FR2344432A1 (en) * 1976-03-20 1977-10-14 Waggon Union Gmbh BOGIE FOR FAST RAIL VEHICLES
US4561360A (en) * 1984-06-06 1985-12-31 Amsted Industries Incorporated Single axle suspension system for railroad vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0600172A1 (en) * 1992-11-28 1994-06-08 Siemens Schienenfahrzeugtechnik GmbH Running gear for railway vehicles
CN104477199A (en) * 2014-12-15 2015-04-01 南车二七车辆有限公司 Wagon bogie tumbler fast clamping band

Also Published As

Publication number Publication date
FI902789A0 (en) 1990-06-05
NO902445D0 (en) 1990-06-01
JPH0328067A (en) 1991-02-06
US5090333A (en) 1992-02-25
CS272490A2 (en) 1991-11-12
PT94274A (en) 1991-12-31
YU103390A (en) 1995-03-27
PL285478A1 (en) 1991-01-14
RO108228B1 (en) 1994-03-31
ES2058672T3 (en) 1994-11-01
PL163572B1 (en) 1994-04-29
HU903294D0 (en) 1990-10-28
NO902445L (en) 1990-12-06
YU47915B (en) 1996-05-20
DK0401618T3 (en) 1994-11-21
DE3918300A1 (en) 1990-12-06
HU205309B (en) 1992-04-28
ATE108383T1 (en) 1994-07-15
HUT56778A (en) 1991-10-28
CA2018197A1 (en) 1990-12-05
DE59006405D1 (en) 1994-08-18
EP0401618B1 (en) 1994-07-13
IN171296B (en) 1992-09-05
TR24412A (en) 1991-11-01
HRP930620A2 (en) 1995-10-31

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