EP0601677B1 - Twin axle drive - Google Patents

Twin axle drive Download PDF

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Publication number
EP0601677B1
EP0601677B1 EP93250330A EP93250330A EP0601677B1 EP 0601677 B1 EP0601677 B1 EP 0601677B1 EP 93250330 A EP93250330 A EP 93250330A EP 93250330 A EP93250330 A EP 93250330A EP 0601677 B1 EP0601677 B1 EP 0601677B1
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EP
European Patent Office
Prior art keywords
twin
axle
centre
gear according
running gear
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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
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EP93250330A
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German (de)
French (fr)
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EP0601677A1 (en
Inventor
Franz Moeschler
Wolfgang Trommler
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Institut fur Schienenfahrzeuge GmbH
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Institut fur Schienenfahrzeuge GmbH
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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
    • B61F3/00—Types of bogies
    • B61F3/02—Types of bogies with more than one axle
    • B61F3/08—Types of bogies with more than one axle without driven axles or wheels
    • B61F3/10—Types of bogies with more than one axle without driven axles or wheels with three or more 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
    • B61F3/00—Types of bogies
    • B61F3/02—Types of bogies with more than one axle
    • B61F3/08—Types of bogies with more than one axle without driven axles or wheels
    • 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
    • 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

Definitions

  • the invention relates to a double-axle drive or possibly the connection of two double-axle drives to a drive group, preferably for low-floor wagons with a continuous floor height and small wheels, as defined in the first part of claim 1; such a drive is known from DE-U-91 15 467.
  • DE-AS 3839994 describes a cheaper solution.
  • the side leaf springs of the double-axle drive are located on side brackets that are connected to the side walls.
  • a short flow of force is achieved and overall height and mass are saved.
  • the disadvantage of this solution is that, due to the available space, the spring hooks cannot be made with the necessary length and therefore a large turning resistance and a large restoring force occur when traveling through bends, which are at the limit of derailment security. This is reinforced by the fact that double-axle drives on the same track curve result in a larger turning angle than a free steering axle.
  • the object of the invention is to provide a double-axle drive or possibly the connection of two such double-axle drives, which save height and mass in the short flow of force of the vertical load, when driving in a narrow track curve the necessary turning angle with a permissible turning resistance and lateral play more optimally than a suspension hook guarantee.
  • the object is achieved in the novel double-axle drive of claim 1 in that the leaf spring is hinged at its ends on the cheek stems laterally, for example, next to the side cheeks.
  • a supporting pendulum is supported on the spring collar of the leaf spring, which can roll in the longitudinal direction of the vehicle with the required resistance without restoring force and can thereby generate the necessary turning-out inhibition.
  • the restoring force and transverse restraint required for the transverse play can be generated by the design of the spherical rolling segment of the supporting pendulum as a result of different radii.
  • connection of two double-axis drives to a four-axis drive group requires not only the connection elements described below, but also individual modifications of the single double-axis drive.
  • the longitudinal and transverse articulation of the drive group is carried out by a flexion lever 27.
  • This is rotatably and transversely slidably mounted on a pivot pin 28 flattened on both sides with the interposition of a slot bushing 29.
  • the desired transverse displacement of the flexion lever 27 is limited in the plane of the transverse axis of the flattened pivot 28 by elastic cross stops which are fastened to the console 25 of the low-floor car 1.
  • the two double-axle drives are connected longitudinally and transversely by means of triangular links 30 at the top thereof via a gimbal bearing 23 to the flexion lever 27 and articulated at the base thereof via two expandable bearings 31 which are fastened to the outer carriage stems 4.
  • the vertical power transmission takes place from the low-floor car 1 on both sides via a balancing lever 32 mounted in the middle, which carries the flat abutments 20 at its ends. These are based on the support pendulum 14.
  • the rolling segments 16 and the flat abutments 20 have to be made correspondingly large in accordance with the larger drive deflections, which result from a larger pivot distance and a larger end axis distance of the drive group.
  • a cross coupling of both drives is available. This consists of a coupling rod 33 which is articulated by means of elastic cardanic joints 34, which are each articulated approximately at the level of the leaf springs 10 on an opposite spring bracket 9 of the drive frame.

Abstract

Twin axle drive or connection of two twin axle drives which save on overall height and mass in the short powerflux of the perpendicular loading and ensure, when travelling in a tight bend in the track, the necessary rotation angle with an acceptable rotation resistance and ensure transverse play better than a link suspension. According to the invention, the object is achieved in that the leaf springs (10) are coupled at their ends to the wagon stays to the side of the lateral members (3). A support pendulum (14) is supported on the spring collar (11) of the leaf springs (10) and rolls with the necessary resistance in the longitudinal direction of the vehicle without restoring force and thus brings about the necessary restriction on rotation. In the transverse direction, the restoring force and transverse restriction required for transverse play is produced by the design of the crowned rolling segment of the support pendulum (14). In the connection of two twin axle units, steering is effected by a Beugniot lever. Both axle units are connected to a transverse coupling. The invention is preferably suitable for use with low-level wagons (1) with a continuous floor height and small wheels. <IMAGE>

Description

Die Erfindung betrifft ein Doppelachslaufwerk bzw. möglicherweise die Verbindung von zwei Doppelachslaufwerken zu einer Laufwerksgruppe, vorzugsweise für Niederflurwagen mit durchgehender Flurhöhe und kleinen Rädern, wie im ersten Teil des Anspruchs 1 definiert ist; ein solche Laufwerk is aus der DE-U-91 15 467 bekannt.The invention relates to a double-axle drive or possibly the connection of two double-axle drives to a drive group, preferably for low-floor wagons with a continuous floor height and small wheels, as defined in the first part of claim 1; such a drive is known from DE-U-91 15 467.

Es sind 2-achsige Laufwerke mit kleinen Rädern bekannt, die über eine mittige Drehpfanne, die auf einem Querträger befestigt ist, die beiden seitlich längsliegenden Blattfedern belasten. Diese Blattfedern sind mittels Schaken an den Seitenwangen aufgehängt. Die DE-OS 1530146 beschreibt ein solches Laufwerk. Nachteilig ist bei dieser Bauweise der Kraftfluß der senkrechten Belastung. Von den neben dem Niederflurboden befindlichen Langträgern muß die Last im Fahrzeug zur Mitte über das Laufwerk geleite werden und von hier über eine Drehpfanne im Laufwerk wieder auf die seitlich angeordneten Federn. Dieses erfordert sowohl Bauhöhe als auch Masse.There are 2-axis drives with small wheels known, the load on the two laterally longitudinal leaf springs via a central rotary pan, which is attached to a cross member. These leaf springs are hung on the side cheeks by means of hooks. DE-OS 1530146 describes such a drive. The disadvantage of this design is the force flow of the vertical load. From the long girders next to the low-floor floor, the load in the vehicle must be directed to the center of the drive and from here via a rotating pan in the drive to the springs on the side. This requires both height and mass.

Eine günstigere Lösung beschreibt die DE-AS 3839994. Hier befinden sich die seitlichen Blattfedern des Doppelachslaufwerkes auf seitlichen Konsolen, die an den Seitenwangen angeschlossen sind. Dadurch werden ein kurzer Kraftfluß erzielt und Bauhöhe sowohl als auch Masse eingespart. Nachteilig ist bei dieser Lösung, daß infolge des zur Verfügung stehenden Bauraumes die Federschaken nicht mit der nötigen Länge ausgeführt werden können und sich daher bei Bogenfahrten ein großer Ausdrehwiderstand und eine große Rückstellkraft einstellen, die an der Grenze der Entgleisungssicherheit liegen. Dies wird durch den Umstand verstärkt, daß Doppelachslaufwerke im gleichen Gleisbogen einen größeren Ausdrehwinkel ergeben als eine frei Lenkachse.DE-AS 3839994 describes a cheaper solution. Here, the side leaf springs of the double-axle drive are located on side brackets that are connected to the side walls. As a result, a short flow of force is achieved and overall height and mass are saved. The disadvantage of this solution is that, due to the available space, the spring hooks cannot be made with the necessary length and therefore a large turning resistance and a large restoring force occur when traveling through bends, which are at the limit of derailment security. This is reinforced by the fact that double-axle drives on the same track curve result in a larger turning angle than a free steering axle.

Aufgabe der Erfindung ist es, ein Doppelachslaufwerk bzw. möglicherweise die Verbindung von zwei solchen Doppelachslaufwerken zu schaffen, die im kurzen Kraftfluß der senkrechten Belastung Bauhöhe und Masse einsparen, bei Fahrt im engen Gleisbogen den notwendigen Ausdrehwinkel bei einem zulässigen Ausdrehwiderstand und Querspiel optimaler als eine Schakenaufhängung gewährleisten. Die Aufgabe wird erfindungsgemäß bei dem neuartigen Doppelachslaufwerk des Anspruchs 1 dadurch gelöst, daß die Blattfeder an ihren Enden an den Wangenstielen seitlich z.B. neben den Seitenwangen angelenkt werden. Auf dem Federbund der Blattfeder stützt sich ein Stützpendel ab, das in Fahrzeuglängsrichtung mit dem erforderlichen Widerstand ohne Rückstellkraft abrollen kann und hierdurch die notwendige Ausdreh-Hemmung erzeugen kann. In Querrichtung können die beim Querspiel erforderliche Rückstellkraft und Querhemmung durch die Gestaltung des balligen Abrollsegmentes des Stützpendels infolge unterschiedlicher Radien erzeugt.The object of the invention is to provide a double-axle drive or possibly the connection of two such double-axle drives, which save height and mass in the short flow of force of the vertical load, when driving in a narrow track curve the necessary turning angle with a permissible turning resistance and lateral play more optimally than a suspension hook guarantee. The object is achieved in the novel double-axle drive of claim 1 in that the leaf spring is hinged at its ends on the cheek stems laterally, for example, next to the side cheeks. A supporting pendulum is supported on the spring collar of the leaf spring, which can roll in the longitudinal direction of the vehicle with the required resistance without restoring force and can thereby generate the necessary turning-out inhibition. In the transverse direction, the restoring force and transverse restraint required for the transverse play can be generated by the design of the spherical rolling segment of the supporting pendulum as a result of different radii.

Bei der Verbindung von zwei derartigen Doppelachslaufwerken zu einer Laufwerkgruppe erfolgt die Längs- und Queranlenkung durch einen Beugniothebel am Fahrzeug. Die senkrechten Kräfte werden auf jeder Seite durch Ausgleichshebel auf die hintereinanderliegenden Widerlager der Stützpendel gleichmäßig verteilt. Zur Gewährleistung der Radialeinstellung beider verbundener Doppelachslaufwerke bei Bogenfahrt und eines ruhigen Fahrzeuglaufes ist eine Querkupplung beider benachbarter Laufwerksrahmen vorhanden.When two such double-axle drives are connected to form a drive group, the longitudinal and transverse articulation is carried out using a flexion lever on the vehicle. The vertical forces are evenly distributed on each side by means of compensating levers on the abutments of the supporting pendulums lying one behind the other. To ensure the radial setting of both connected double-axle drives when traveling through bends and a smooth vehicle run, a cross coupling of both adjacent drive frames is available.

Die Ausführungsbeispiele der Erfindung sind an Hand von Zeichnungen erläutert.The embodiments of the invention are explained with reference to drawings.

Es zeigen:

Fig.1
Die Seitenansicht eines Doppelachslaufwerkes unter einemteilweise dargestellten Niederflurwagen.
Fig.2
Die Draufsicht auf ein Doppelachslaufwerk
Fig.3
Den Schnitt nach Linie I - I der Fig.2 in vergrößerter Darstellung
Fig.4
Einen Schnitt nach Linie II - II der Fig.2 in vergrößerter Darstellung
Fig.5
Eine weitere Ausführung eines Teils des Schnittes nach Linie II - II der Fig.2 in vergrößerter Darstellung
Fig 6
Einen Schnitt nach Linie III - III der Fig.2
Fig.7
Die Seitenansicht einer Verbindung von zwei Doppelachslaufwerken
Fig.8
Die Draufsicht einer Verbindung von zwei Doppelachslaufwerken mit zwei Ausbrüchen "A" zur Darstellung der Anlenkung der Koppelstange
Fig.9
Einen Schnitt nach Linie IV - IV der Fig.8
Die in den Zeichnungen dargestellten Ausführungsbeispiele des Doppelachslaufwerkes und seiner zugehörigen Verbindungselemente sind unter einem Niederflurwagen 1, der nur zu einem kleinen Stück dargestellt ist, angeordnet. Der verwindbare Laufwerksrahmen 2 besteht aus zwei T-förmigen Teilen, die wiederum aus der Seitenwange 3 und dem damit fest verbundenen Wangenstiel 4 bestehen; jeweils ein kardanisches Lager 5 verbindet die beiden T-förmigen Teile und ermöglicht die Verwindbarkeit. In den Seitenwangen 3 sind die Achslager 6 mittel elastischer Polster 7 eingespannt, welche die Radsätze 8, die mit kleinen Rädern versehen sind, tragen. An allen vier Enden der Wangenstiele 4 befinden sich Federkonsolen 9, an denen die Blattfedern 10 angelenkt sind. Die Blattfedern 10 tragen auf ihrem Federbund 11 eine Haube 12 mit kugelförmigen Kopf. Nach erfolgter Umrißberichtigung der Laufflächen der Radsätze 8 läßt sich zum Ausgleichen des Höhenverlustes zwischen Federbund 11 und Haube 12 eine Beilage 13 einfügen. Die Haube 12 und das Stützpendel 14 besitzen einen gemeinsamen Kugelradius 15 auf dem letzteres schwenk- und kippbar gelagert ist. Das Stützpendel 14 hat oben ein Abrollsegment 16, dessen Rollradius 17 mit dem Kugelradius 15 einen gemeinsamen Mittelpunkt besitzt. Hierdurch entsteht ein rückstellfreies Ausdrehen bei Einfahrt in einen Gleisbogen. Die durch Reibung auf der Kugelfläche erzeugte Drehhemmung ist abhängig von der darauf ruhenden Last, wobei durch Variation beider Radien (Kugelradius 15 und Rollradius 17) ist die Drehhemmung weitgehend veränderlich. Zur Erzeugung einer rückstellbehafteten, pendelartigen Querbewegung besitzt das Abrollsegment 16 mit dem Rollradius 17 eine ballige Kontur mit dem Kippradius 18. Dieser Kippradius 18 ist größer als der Rollradius 17. Das Verhältnis beider Radien bestimmt die Rückstellkraft. Die infolge lastabhängiger Reibung der kugelförmigen Auflagefläche entstehende Querhemmung ist im Verhältnis der Radien geringer. Zur Erzielung einer exakten Mittellage lassen sich die Mittelpunkte der Kippradien 18 um einen geringen Abstend 19 voneinander trennen, so daß oben eine ebene Rollspannbreite mit dem Rollradius 17 entsteht, an dem sich der Kippradius 18 anschließt. Durch diese Maßnahme entsteht eine Quercharakteristik, die, bevor eine Bewegung eintritt, einen Kraftanstieg bewirkt, der bei entsprechender Breite des Abstandes 19 über dem Betrag der Querhemmung liegt. Das Abrollsegment 16 stützt über ein ebenes Widerlager 20 mit einem umlaufenden Rand den Niederflurwagen 1 auf beiden Seiten ab. In Längsrichtung wird das Doppelachslaufwerk über einen Drehzapfen 21, der in der Mitte des Laufwerkes unter dem Niederfluhrwagen 1 befestigt ist, einer Lenkerstange 22, die an beiden Enden kardanische Lager 23 trägt, an den Wagenstiel 4 angelenkt.Show it:
Fig. 1
The side view of a double-axle drive under a low-floor car partially shown.
Fig. 2
The top view of a dual-axis drive
Fig. 3
The section along line I - I of Figure 2 in an enlarged view
Fig. 4
A section along line II - II of Figure 2 in an enlarged view
Fig. 5
Another version of part of the section along line II - II of Figure 2 in an enlarged view
Fig. 6
A section along line III - III of Fig.2
Fig. 7
The side view of a connection of two double-axis drives
Fig. 8
The top view of a connection of two double-axle drives with two cutouts "A" to illustrate the articulation of the coupling rod
Fig. 9
A section along line IV - IV of Fig.8
The exemplary embodiments of the double-axle drive and its associated connecting elements shown in the drawings are arranged under a low-floor car 1, which is only shown in small pieces. The twistable drive frame 2 consists of two T-shaped parts, which in turn consist of the side cheek 3 and the cheek stick 4 firmly connected thereto; each a gimbal 5 connects the two T-shaped parts and enables torsion. In the side cheeks 3, the axle bearings 6 are clamped by means of elastic pads 7 which hold the wheel sets 8 with small Wheels are provided, wear. At all four ends of the cheek stems 4 there are spring brackets 9 to which the leaf springs 10 are articulated. The leaf springs 10 carry on their spring collar 11 a hood 12 with a spherical head. After the contour of the treads of the wheel sets 8 has been corrected, an insert 13 can be inserted to compensate for the loss of height between the spring collar 11 and the hood 12. The hood 12 and the support pendulum 14 have a common spherical radius 15 on which the latter is pivotally and tiltably mounted. The support pendulum 14 has a rolling segment 16 at the top, the rolling radius 17 of which has a common center point with the ball radius 15. This creates a reset-free turning when entering a track curve. The rotational inhibition generated by friction on the spherical surface is dependent on the load resting thereon, the rotational inhibition being largely variable by varying both radii (spherical radius 15 and rolling radius 17). To generate a resilient, pendulum-like transverse movement, the rolling segment 16 with the rolling radius 17 has a spherical contour with the tipping radius 18. This tipping radius 18 is larger than the rolling radius 17. The ratio of the two radii determines the restoring force. The transverse inhibition resulting from the load-dependent friction of the spherical bearing surface is lower in the ratio of the radii. In order to achieve an exact central position, the center points of the tilt radii 18 can be separated from one another by a small distance 19, so that a flat roll span width is created with the roll radius 17, to which the tilt radius 18 adjoins. This measure creates a transverse characteristic which, before a movement occurs, causes an increase in force which, given the corresponding width of the distance 19, is greater than the amount of transverse inhibition. The rolling segment 16 supports the low-floor car 1 on both sides via a flat abutment 20 with a peripheral edge. In the longitudinal direction, the double-axle drive is articulated to the car arm 4 via a pivot pin 21, which is fastened in the middle of the drive under the low-loader truck 1, a handlebar 22, which carries cardanic bearings 23 at both ends.

In Querrichtung wird der seitliche Ausschlag des Doppelachslaufwerkes durch elastische Queranschläge 24, die an Konsolen 25 des Niederflurwagen 1 befestigt sind und sich im gewünschten Abstand von Anschlagkonsolen 26 des Laufwerkes befinden, begrenzt.In the transverse direction, the lateral deflection of the double-axle drive is limited by elastic cross stops 24, which are fastened to brackets 25 of the low-floor car 1 and are located at the desired distance from the stop brackets 26 of the drive.

Die Verbindung von zwei Doppelachslaufwerken zu einer vierachsigen Laufwerksgruppe erfordert neben nachfolgend beschriebenen Verbindungselementen auch einzelne Modifikationen des Einzel-Doppelachslaufwerkes. So erfolgt die Längs- und Queranlenkung der Laufwerksgruppe durch einen Beugniothebel 27. Dieser ist dreh- und querverschiebbar auf einen beidseitig abgeflachten Drehzapfen 28 unter Zwischenschaltung einer Schlitzbuchse 29 gelagert. Die gewünschte Querverschiebung des Beugniothebels 27 wird in der Ebene der Querachse des abgeflachten Drehzapfen 28 durch elastische Queranschläge, die an Konsole 25 des Niederflurwagens 1 befestigt sind, begrenzt. Die beiden Doppelachslaufwerke sind längs und quer mittels Dreiecklenker 30 an deren Spitze über ein kardanisches Lager 23 mit dem Beugniothebel 27 verbunden und an deren Basis über zwei dehbare Lager 31, die an den äußeren Wagenstielen 4 befestigt sind, angelenkt. Die senkrechte Kraftübertragung erfolgt vom Niederflurwagen 1 auf beiden Seiten über einen in der Mitte gelagerten Ausgleichshebel 32, der an seinen Enden die ebenen Widerlager 20 trägt. Diese stützen sich auf die Stützpendel 14.The connection of two double-axis drives to a four-axis drive group requires not only the connection elements described below, but also individual modifications of the single double-axis drive. Thus, the longitudinal and transverse articulation of the drive group is carried out by a flexion lever 27. This is rotatably and transversely slidably mounted on a pivot pin 28 flattened on both sides with the interposition of a slot bushing 29. The desired transverse displacement of the flexion lever 27 is limited in the plane of the transverse axis of the flattened pivot 28 by elastic cross stops which are fastened to the console 25 of the low-floor car 1. The two double-axle drives are connected longitudinally and transversely by means of triangular links 30 at the top thereof via a gimbal bearing 23 to the flexion lever 27 and articulated at the base thereof via two expandable bearings 31 which are fastened to the outer carriage stems 4. The vertical power transmission takes place from the low-floor car 1 on both sides via a balancing lever 32 mounted in the middle, which carries the flat abutments 20 at its ends. These are based on the support pendulum 14.

Die Abrollsegmente 16 und die ebenen Widerlager 20 müssen entsprechend der größeren Laufwerksausschläge, die aus einem größern Drehzapfenabstand und einem größeren Endachsabstand der Laufwerksgruppe resultieren, ensprechend großflächiger ausgeführt werden. Zur Erzielung eines ruhigen Fahrzeuglaufes und einer radialen Einstellung der Doppelachslaufwerke einer Laufwerksgruppe ist eine Querkupplung beider Laufwerke vorhanden. Diese besteht aus einer Koppelstange 33, die mittels elastisch-kardanischer Gelenke 34, welche ungefähr in Höhe der Blattfedern 10 jeweils an einer gegenüberliegenden Federkonsole 9 des Laufwerksrahmen angelenkt sind.The rolling segments 16 and the flat abutments 20 have to be made correspondingly large in accordance with the larger drive deflections, which result from a larger pivot distance and a larger end axis distance of the drive group. To achieve a smooth vehicle run and a radial adjustment of the double-axle drives of a drive group, a cross coupling of both drives is available. This consists of a coupling rod 33 which is articulated by means of elastic cardanic joints 34, which are each articulated approximately at the level of the leaf springs 10 on an opposite spring bracket 9 of the drive frame.

Claims (10)

  1. Twin-axle running gear having a twistable running-gear frame, two wheel sets of small wheel diameter and axle bearings mounted on universal joints in the side pieces by means of an elastic pad, the twistable running-gear frame (2) comprising two T-shaped parts which are formed from a side piece (3) and a side-piece strut (4) which is firmly connected thereto and are connected to one another by a universal-joint bearing (5) at the end of a side piece (3) with another side-piece strut (4'), characterized in that spring brackets (9) are located at the four ends of the two side-piece struts (4;4'), to which spring brackets the two leaf springs (10) are linked, which each bear, in their centre on the spring collar (11), a supporting pendulum (14) on which the pallet truck (1) is supported via a planar abutment (20).
  2. Twin-axle running gear according to Claim 1, characterized in that a hood (12) with a spherical head is seated on each spring collar (11) of the leaf spring (10), on which head the supporting pendulum (14) is mounted, and in that shims (13) can be inserted, if required, between the spring collar (11) and the hood (12).
  3. Twin-axle running gear according to Claims 1 and 2, characterized in that the supporting pendulums (14) with their spherical rolling-off segments (16) have a rolling radius (17) whose centre-point coincides with the centre-point of the radius (15) of the sphere of the hood (12) and has a tilting radius (18) which brings about the spherical shape, which tilting radius is greater than the rolling radius (17), and the rolling-off segments (16) support planar abutments (20).
  4. Twin-axle running gear according to Claims 1 to 3, characterized in that the rolling-off segment (16) has, in the centre, a planar region with the spacing (19), adjoining which on both sides are tilting radii (18) producing the spherical shape, the two centre-points of the tilting radii (18) being located with the spacing (19) between them.
  5. Twin-axle running gear according to Claims 1 to 4, characterized in that a pivot (21) is attached below the pallet truck (1) above the centre of the running-gear frame (2), which pivot bears a universal-joint bearing (23) which is connected to the connecting rod (22) which, in turn, is linked via a universal-joint bearing (23) to a side-piece strut (4).
  6. Twin-axle running gear according to Claims 1 to 5, characterized in that the transverse stops (24) are of elastic design and are arranged between the stop brackets (26) of the side piece (3) and the brackets (25) below the pallet truck (1).
  7. Twin-axle running gear according to Claims 1 to 4, characterized in that the horizontal connection of two running-gear frames (2,2') is effected by means of a Beugniot lever (27) which is linked to the bottom of the pallet truck (1) so as to be rotatable and transversely displaceable via a pivot (28) which is flattened on both sides and has a slotted bush (29) in the centre of both running-gear frames (2, 2'), and the connection between the Beugniot lever (27) and the outer side-piece struts (4,4') is effected via triangular connecting rods (30), the latter being linked at their base by two rotatable bearings (31) and at their tip by a universal-joint bearing (23).
  8. Twin-axle running gear according to Claims 1 to 4 and 7, characterized in that elastic transverse stops (24) are arranged on both sides in the centre of the Beugniot lever (27), which are connected to the pallet truck (1) at the bottom by brackets (25).
  9. Twin-axle running gear according to Claims 1 to 4 and 8, characterized in that the two planar abutments (20), located one behind the other on each side, of the supporting pendulums (14) are arranged at both ends of the compensating lever (32), and the latter is linked movably below the pallet truck (1).
  10. Twin-axle running gear according to Claims 1 to 4 and 7 to 9, characterized in that the two running-gear frames (2; 2') are connected to one another via elastic, universal joints (34) by a coupling rod (33) located transversely to the direction of travel at the height of the leaf springs (10).
EP93250330A 1992-12-08 1993-11-30 Twin axle drive Expired - Lifetime EP0601677B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4241300A DE4241300C2 (en) 1992-12-08 1992-12-08 Double-axle drive for low-floor wagons
DE4241300 1992-12-08

Publications (2)

Publication Number Publication Date
EP0601677A1 EP0601677A1 (en) 1994-06-15
EP0601677B1 true EP0601677B1 (en) 1996-06-19

Family

ID=6474692

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93250330A Expired - Lifetime EP0601677B1 (en) 1992-12-08 1993-11-30 Twin axle drive

Country Status (10)

Country Link
EP (1) EP0601677B1 (en)
AT (1) ATE139499T1 (en)
CZ (1) CZ282029B6 (en)
DE (2) DE4244851C2 (en)
DK (1) DK0601677T3 (en)
ES (1) ES2089707T3 (en)
FI (1) FI935483A (en)
NO (2) NO180479C (en)
PL (2) PL173044B1 (en)
SK (1) SK137893A3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112298253A (en) * 2019-08-02 2021-02-02 中车唐山机车车辆有限公司 Side beam of bogie

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19731867C1 (en) 1997-07-24 1998-10-29 Abb Daimler Benz Transp Bogie for railway vehicle
RU2544259C2 (en) 2009-07-16 2015-03-20 Сименс Аг Эстеррайх Undercarriage frame for rail vehicles
WO2012137257A1 (en) * 2011-04-07 2012-10-11 川崎重工業株式会社 Railway bogie
EP2733041B1 (en) 2011-07-14 2019-09-11 Kawasaki Jukogyo Kabushiki Kaisha Railway vehicle truck
CN112298251B (en) * 2019-08-02 2022-07-26 中车唐山机车车辆有限公司 Steering frame
RU202640U1 (en) * 2020-11-02 2021-03-01 Акционерное общество "Научно-исследовательский и конструкторско-технологический институт подвижного состава" (АО "ВНИКТИ") DEVICE FOR SUSPENSING THE TRACTION ENGINE TO THE LOCOMOTIVE TROLLEY FRAME

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Publication number Priority date Publication date Assignee Title
CH269693A (en) * 1948-03-25 1950-07-15 Werz Jacob Two-axle bogie for rail vehicles.
FR1062754A (en) * 1952-09-06 1954-04-27 Sncf Bogie without chassis, high flexibility
DE1530146C3 (en) * 1965-07-03 1973-11-08 Rheinstahl Ag Transporttechnik, 3500 Kassel Two-axle bogie for rail vehicles with small wheel diameters
DE2850878C2 (en) * 1978-11-24 1983-09-15 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Weighing beam-less bogie with air suspension for rail vehicles
DE3827706A1 (en) * 1987-09-22 1989-04-06 Simmering Graz Pauker Ag Four-axle bogey for rail vehicles
DE3839994A1 (en) * 1988-11-26 1990-05-31 Waggon Union Gmbh UNDERCARRIAGE FOR RAIL VEHICLES
DE9115467U1 (en) * 1991-11-25 1992-06-04 Lokomotivbau-Elektrotechnische Werke Hennigsdorf Gmbh, O-1422 Hennigsdorf, De

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112298253A (en) * 2019-08-02 2021-02-02 中车唐山机车车辆有限公司 Side beam of bogie

Also Published As

Publication number Publication date
NO180479B (en) 1997-01-20
DE4241300A1 (en) 1994-06-09
NO934451D0 (en) 1993-12-07
DE4244851C2 (en) 1996-09-12
FI935483A0 (en) 1993-12-08
ATE139499T1 (en) 1996-07-15
PL301365A1 (en) 1994-06-13
PL173034B1 (en) 1998-01-30
ES2089707T3 (en) 1996-10-01
NO180479C (en) 1997-04-30
SK137893A3 (en) 1994-08-10
DE4241300C2 (en) 1995-11-09
NO934451L (en) 1994-06-09
EP0601677A1 (en) 1994-06-15
FI935483A (en) 1994-06-09
CZ263793A3 (en) 1994-06-15
CZ282029B6 (en) 1997-04-16
DK0601677T3 (en) 1996-07-29
PL173044B1 (en) 1998-01-30

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