EP0054134A1 - Double axle drive for rail vehicles - Google Patents

Double axle drive for rail vehicles Download PDF

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Publication number
EP0054134A1
EP0054134A1 EP81108686A EP81108686A EP0054134A1 EP 0054134 A1 EP0054134 A1 EP 0054134A1 EP 81108686 A EP81108686 A EP 81108686A EP 81108686 A EP81108686 A EP 81108686A EP 0054134 A1 EP0054134 A1 EP 0054134A1
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EP
European Patent Office
Prior art keywords
pinion
electric motor
shaft
double
gear stage
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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.)
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EP81108686A
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German (de)
French (fr)
Inventor
Ernst Piepenbreier
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ThyssenKrupp Technologies AG
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Thyssen Industrie AG
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Publication of EP0054134A1 publication Critical patent/EP0054134A1/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
    • B61F3/00—Types of bogies
    • B61F3/02—Types of bogies with more than one axle
    • B61F3/04—Types of bogies with more than one axle with driven axles or wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61C—LOCOMOTIVES; MOTOR RAILCARS
    • B61C9/00—Locomotives or motor railcars characterised by the type of transmission system used; Transmission systems specially adapted for locomotives or motor railcars
    • B61C9/38—Transmission systems in or for locomotives or motor railcars with electric motor propulsion
    • B61C9/48—Transmission systems in or for locomotives or motor railcars with electric motor propulsion with motors supported on vehicle frames and driving axles, e.g. axle or nose suspension
    • B61C9/50—Transmission systems in or for locomotives or motor railcars with electric motor propulsion with motors supported on vehicle frames and driving axles, e.g. axle or nose suspension in bogies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61C—LOCOMOTIVES; MOTOR RAILCARS
    • B61C9/00—Locomotives or motor railcars characterised by the type of transmission system used; Transmission systems specially adapted for locomotives or motor railcars
    • B61C9/38—Transmission systems in or for locomotives or motor railcars with electric motor propulsion
    • B61C9/52—Transmission systems in or for locomotives or motor railcars with electric motor propulsion with transmission shafts at an angle to the driving axles

Definitions

  • the invention relates to a double-axle drive for rail vehicles with wheelsets mounted in a bogie or frame and an electric motor located between them in the direction of travel, which has an angular gear on its end faces with a bevel gear stage for driving the wheel sets and its armature shaft on the drive shafts of the angular gear mutually rotatably supported radially and is connected to them by a torque transmitting clutch only.
  • the invention has for its object to provide a double-axle drive of the type mentioned in such a way that it enables the installation of high engine performance and improves cornering properties without the weight of the bogie increasing to the extent known from the prior art. From this point of view, the possibility should be created in particular of being able to provide a brake for the impellers and of eliminating lubrication problems.
  • the invention consists in that the bevel gear is of two stages and one of the stages consists of a spur gear and a large gear.
  • An advantage of the invention is that the proven mounting of the armature shaft of the electric motor on the drive shafts of the angular gear can also be extended to high-speed electric motors thanks to the high translation capacity of the angular gear, without lubrication problems in the armature shaft bearing or weight problems when installing high power or that The problem arises that the armature shaft should be supported on the drive shafts via a torque-transmitting centering.
  • the torque is guided around the centering (bearing) with the aid of the couplings.
  • the motor can be arranged low in relation to the overall center of gravity or the center distance of the impellers when the spur gear stage drive stage is significantly shortened, which has a positive effect when the bogie turns when cornering.
  • the fact that there is now an intermediate shaft in the angular gear there is the possibility of leading this shaft out of the gear housing and arranging a disc brake on it, in contrast to the usual solutions in which the brake disc is provided on the shaft of the impellers. Since the torque on the intermediate shaft is considerably smaller, the dimensions of the brake are also smaller and their weight is lighter.
  • the favorable cornering properties of the double-axle drive can be achieved in particular if the spur-toothed large wheel in the output stage and with its center around its pinion - facing away from the electric motor - is arranged in an obliquely downward angle range of approximately 200 °, one leg of which is inclined pointing at an angle of about 45 ° to the horizontal.
  • the large wheel is expediently arranged in the region of its pinion facing away from the electric motor.
  • the motor can be low in terms of focus, but can also be set relatively high if, for example, high ground clearance is desired.
  • the spur-toothed large wheel can advantageously also be arranged in the area of its pinion facing the electric motor. This makes extremely short center distances in the bogie possible, the achievable dimensions being significantly less than the center distances of single-stage drives, especially if the pinion of the bevel gear stage meshes with the bevel gear in its area facing away from the electric motor and ends there with its shaft in a bearing.
  • a double-axle drive consists of two wheel sets 1, each having a two-stage bevel gear 3 drivingly mounted on the axle shaft 2 of the wheel sets and an electric motor 4 which is arranged with its armature shaft 5 in the direction of travel and carries the bevel gear 3 on its end faces.
  • Each of the bevel gear 3 has a bevel gear stage with a pinion 6, which sits at the end of the drive shaft 7 or also bevel pinion shaft of the gear and meshes with a bevel gear 8.
  • the shaft 9 of the bevel gear 8 forms an intermediate shaft and has a spur-toothed pinion 10 which meshes with a large gear 11 and together with this forms the output stage.
  • the armature shaft 5 is centered on stepped ends of the bevel pinion shafts 7 and is freely rotatable in itself.
  • the torque is guided around the centering and bearing points by a torsionally flexible and flexible coupling 12.
  • the armature of the electric motor 4 is in this respect only indirectly supported in the motor-transmission block, specifically via the bevel pinion mounted there directly and statically determined waves 7.
  • the angular gear 3 are mirror-inverted with respect to the electric motor 4 such that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 in the side view (FIG. 1) diverge downward. This arrangement ensures a high ground clearance of the bogie.
  • the intermediate shaft 9 is guided out of the housing 13 of the angular gear 3 on both sides. It carries at its ends a brake disc 14 on which brake devices 15 act, e.g. a brake caliper 16 with a brake cylinder 17. The two latter are connected to the housing 13, so that no relative movement occurs between the brake disc 14 and the braking devices 15.
  • Figures 2 to 4 and 6 are similar to Figures 1 and 5 and contain parts that are largely identical to the parts discussed so far. These identical parts are therefore no longer described in detail but numbered unchanged, in each case on the right half of the figure, since the left half of the drive is a mirror image.
  • bevel gears 3a are designed in mirror image with respect to the electric motor 4 in such a way that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 diverge upwards in the side view.
  • the axle shaft 2 is arranged in an angular range around the center point of the intermediate shaft 9, one leg 18 of which is inclined upwards at approximately 45 ° to the horizontal and extends downward therefrom. This arrangement favors the lowering of the electric motor 4 and ensures a low center of gravity.
  • the bevel gears 3b and 3c in FIGS. 3 and 4 are mirror-inverted with respect to the electric motor 4 so that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 converge downwards in the side view.
  • the axle shaft 2 is arranged around the center of the intermediate shaft 9 in a downward-facing angular range, which extends from the perpendicular to the electric motor 4 approximately up to 65 °.
  • These orders grant have a particularly short center distance.
  • FIG. 4 where the pinion 6 on the bevel pinion shaft 7a meshes with the bevel gear 8 in the area of the bevel gear 8 used by the electric motor 4.
  • a bearing 19 is provided for the end of the bevel pinion shaft 7a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

The electric motor (4) of this double axle drive is arranged between the driven wheel sets (1) of a bogie in the travelling direction and equipped on its end sides with one angular gear (3) in each case which has a bevel gear stage (6, 8). The armature shaft (5) of the electric motor (4) is mounted in the drive shafts (7) of the angular gears (3) in a freely rotatable and radial manner but connected thereto by a coupling (12) in each case which is only intended for torque transmission. In order to be able to use motors with a high speed of rotation and therefore with small dimensions, a spur gear stage (10, 11) is connected downstream of the bevel gear stage (6, 8) in the angular gears (3), the output shaft of the said spur gear stage is the axle shaft (2) of the wheel sets (1). Thus, during construction, the position of the wheel sets (1) can be freely selected around the pinion (10) of the spur gear stage (10, 11). The floor clearance and the axial spacing of the bogie then changes in dependence thereon. The shaft (9) of the pinion (10) is led out of the gearing housing (13) and provided on the outside with a brake disc on which a brake device suspended directly on the housing (13) engages. <IMAGE>

Description

Die Erfindung bezieht sich auf einen Doppelachsantrieb für Schienenfahrzeuge mit in einem Drehgestell oder Rahmen gelagerten Radsätzen und einem zwischen diesen in Fahrtrichtung liegenden Elektromotor, der an seinen Stirnseiten je ein Winkelgetriebe mit einer Kegelradstufe zum Antreiben der Radsätze trägt und dessen Ankerwelle auf den Antriebswellen der Winkelgetriebe an sich gegenseitig drehbar radial gelagert und mit diesen durch je eine nur Drehmomente übertragende Kupplung verbunden ist.The invention relates to a double-axle drive for rail vehicles with wheelsets mounted in a bogie or frame and an electric motor located between them in the direction of travel, which has an angular gear on its end faces with a bevel gear stage for driving the wheel sets and its armature shaft on the drive shafts of the angular gear mutually rotatably supported radially and is connected to them by a torque transmitting clutch only.

Ein derartiger Antrieb, dessen Winkelgetriebe in einem einzigen Kegelradpaar besteht, ist durch die deutsche Offenlegungsschrift 25 48 058 bekannt. Er kann Antriebstypen, die eine Gewichtsverringerung durch schnellaufende und daher kleinere Motoren zum Ziel gesetzt haben, allerdings nicht gerecht werden, weil das einstufige Getriebe zur genügenden Drehzahlreduktion in der Regel nicht ausreicht.Such a drive, whose angular gear consists of a single pair of bevel gears, is known from German Offenlegungsschrift 25 48 058. However, it cannot do justice to drive types that aim to reduce weight through high-speed and therefore smaller motors, because the single-stage gearbox is usually not sufficient to reduce the speed sufficiently.

Es ist ferner durch die deutsche Offenlegungsschrift 26 16 310 bekannt, das Drehmoment der Ankerwelle auf die Ritzelwelle nicht durch eine Kupplung, sondern durch ein dazwischengeschaltetes Planetengetriebe mit feststehendem Planetenträger zu übertragen. Bei dieser Anordnung kehrt sich die Drehrichtung des äußeren Zentralrades gegenüber der Drehrichtung des inneren Zentralrades um. Da das mit der Ankerwelle fest verbundene innere Zentralrad sich auf der Kegelritzelwelle mindestens in radialer Richtung abstützt, entsteht eine Relativdrehzahl, die sich aus Motordrehzahl plus Kegelritzeldrehzahl zusammensetzt. Damit sind Drehzahlgrößen erreicht, die schmiertechnisch für die Lagerung der Ankerwelle in der Ritzelwelle kaum zu bewältigen sind.It is also known from German Offenlegungsschrift 26 16 310 to transmit the torque of the armature shaft to the pinion shaft not through a clutch, but through an interposed planetary gear with a fixed planet carrier. With this arrangement, the direction of rotation of the outer central wheel is reversed with respect to the direction of rotation of the inner central wheel. Because that is firmly connected to the armature shaft inner central wheel is supported on the bevel pinion shaft at least in the radial direction, a relative speed arises, which is composed of the engine speed plus the bevel pinion speed. This achieves speed values that are difficult to manage in terms of lubrication for the mounting of the armature shaft in the pinion shaft.

Der Erfindung liegt die Aufgabe zugrunde, einen Doppelachsantrieb der eingangs genannten Art so auszubilden, daß er den Einbau hoher Motorleistungen und verbessert Kurvenlaufeigenschaften ermöglicht, ohne daß dabei das Gewicht des Drehgestells in dem durch den Stand der Technik bekannten Maße steigt. Unter diesem Aspekt soll insbesondere die Möglichkeit geschaffen werden, eine Bremse für die Laufräder vorsehen zu können und schmiertechnische Probleme zu beseitigen.The invention has for its object to provide a double-axle drive of the type mentioned in such a way that it enables the installation of high engine performance and improves cornering properties without the weight of the bogie increasing to the extent known from the prior art. From this point of view, the possibility should be created in particular of being able to provide a brake for the impellers and of eliminating lubrication problems.

Die Erfindung besteht darin, daß das Winkelgetriebe zweistufig ausgebildet ist und eine der Stufen in stirnverzahntem Ritzel und Großrad besteht.The invention consists in that the bevel gear is of two stages and one of the stages consists of a spur gear and a large gear.

Es ist zwar bei einem Winkelgetriebe für Schienenfahrzeug-Antriebe durch die deutsche Offenlegungsschrift 29 10 392 bekannt, das übersetzungsverhältnis des Getriebes neben der Kegelradstufe noch durch eine hinzugeschaltete Stirnradstufe zu bewirken. Bei diesem Antrieb ergeben sich aber nicht die Probleme, die durch die Erfindung gelöst werden sollen.In the case of an angular gear for rail vehicle drives, it is known from German Offenlegungsschrift 29 10 392 to effect the transmission ratio of the gear in addition to the bevel gear stage by means of an additional spur gear stage. However, this drive does not give rise to the problems which the invention is intended to solve.

Ein Vorteil der Erfindung besteht darin, daß die bewährte Lagerung der Ankerwelle des Elektromotors auf den Antriebswellen der Winkelgetriebe auch auf schnellaufende Elektromotoren Dank des hohen übersetzungsvermögens der Winkelgetriebe ausgeweitet werden kann, ohne daß dabei schmiertechnische Probleme bei der Ankerwellenlagerung oder Gewichtsprobleme beim Einbau hoher Leistungen oder das Problem auftauchen, daß sich die Ankerwelle auf den Antriebswellen über eine Drehmomente übertragende Zentrierung abstützen sollte. Bei der Erfindung wird das Drehmoment mit Hilfe der Kupplungen um die Zentrierung (Lagerung) herumgeführt. Dadurch, daß die eine Getriebestufe eine Stirnradstufe ist, kann der Motor günstig in bezug auf den Gesamtschwerpunkt tief angeordnet werden oder auch der Achsabstand der Laufräder, wenn die Stirnradstufe die triebsstufe ist, erheblich verkürzt werden, was sich günstig auswirkt, wenn das Drehgestell bei Kurvenfahrt ausdreht. Dadurch, daß in dem Winkelgetriebe nunmehr eine Zwischenwelle vorhanden ist, besteht die Möglichkeit, diese Welle aus dem Getriebegehäuse herauszuführen und auf ihr eine Scheibenbremse anzuordnen, und zwar im Gegensatz zu den üblichen Lösungen, bei denen die Bremsscheibe auf der Welle der Laufräder vorgesehen ist. Da auf der Zwischenwelle das Drehmoment erheblich kleiner ist, sind die Abmessungen der Bremse ebenfalls kleiner und ihr Gewicht leichter.An advantage of the invention is that the proven mounting of the armature shaft of the electric motor on the drive shafts of the angular gear can also be extended to high-speed electric motors thanks to the high translation capacity of the angular gear, without lubrication problems in the armature shaft bearing or weight problems when installing high power or that The problem arises that the armature shaft should be supported on the drive shafts via a torque-transmitting centering. In the invention, the torque is guided around the centering (bearing) with the aid of the couplings. The fact that the one gear stage is a spur gear stage, the motor can be arranged low in relation to the overall center of gravity or the center distance of the impellers when the spur gear stage drive stage is significantly shortened, which has a positive effect when the bogie turns when cornering. The fact that there is now an intermediate shaft in the angular gear, there is the possibility of leading this shaft out of the gear housing and arranging a disc brake on it, in contrast to the usual solutions in which the brake disc is provided on the shaft of the impellers. Since the torque on the intermediate shaft is considerably smaller, the dimensions of the brake are also smaller and their weight is lighter.

Die günstigen Kurvenlaufeigenschaften des Doppelachsantriebs sind insbesondere zu erreichen, wenn vorteilhaft das stirnverzahnte Großrad in der Abtriebsstufe und mit seinem Mittelpunkt um sein Ritzel herum - vom Elektromotor abgewandt - in einem schräg nach unten weisenden Winkelbereich von etwa 200° angeordnet ist, dessen einer Schenkel schräg nach oben weisend etwa unter 45° gegen die Horizontale geneigt ist.The favorable cornering properties of the double-axle drive can be achieved in particular if the spur-toothed large wheel in the output stage and with its center around its pinion - facing away from the electric motor - is arranged in an obliquely downward angle range of approximately 200 °, one leg of which is inclined pointing at an angle of about 45 ° to the horizontal.

Zweckmäßig ist das Großrad in dem vom Elektromotor abgewandten Bereich seines Ritzels angeordnet. Hierdurch kann der Motor schwerpunktgünstig tief liegen, aber auch verhältnismäßig hoch angesetzt werden, wenn z.B. hohe Bodenfreiheit gewünscht wird.The large wheel is expediently arranged in the region of its pinion facing away from the electric motor. As a result, the motor can be low in terms of focus, but can also be set relatively high if, for example, high ground clearance is desired.

Das stirnverzahnte Großrad kann vorteilhaft auch in dem dem Elektromotor zugewandten Bereich seines Ritzels angeordnet sein. Hierdurch werden extrem kurze Achsabstände im Drehgestell möglich, wobei die erreichbaren Maße wesentlich unter den Achsabständen einstufiger Antriebe liegen, insbesondere wenn zweckmäßig das Ritzel der Kegelradstufe mit dem Kegelrad in dessen vom Elektromotor abgewandtem Bereich kämmt und dort mit seiner Welle in einem Lager endet.The spur-toothed large wheel can advantageously also be arranged in the area of its pinion facing the electric motor. This makes extremely short center distances in the bogie possible, the achievable dimensions being significantly less than the center distances of single-stage drives, especially if the pinion of the bevel gear stage meshes with the bevel gear in its area facing away from the electric motor and ends there with its shaft in a bearing.

Für die Anordnung einer Scheibenbremse hat es sich schließlich als besonders vorteilhaft ergeben, mit der Welle des stirnverzahnten Ritzels das Gehäuse des Winkelgetriebes senkrecht zur Fahrtrichtung durchsetzen zu lassen und die Welle außen mit einer Bremsscheibe zu versehen, an der eine direkt am Gehäuse aufgehängte Bremseinrichtung angreift.For the arrangement of a disc brake, it finally turned out to be particularly advantageous to have the shaft of the spur gear pinion push through the housing of the angular gear perpendicular to the direction of travel and to provide the outside of the shaft with a brake disc on which a braking device suspended directly on the housing acts.

Im folgenden wird die Erfindung anhand von in den Zeichnungen schematisch dargestellten Ausführungsbeispielen näher erläutert. Es zeigen:

  • Fig. 1 einen Doppelachsantrieb mit einem hochliegenden Elektromotor,
  • Fig. 2 einen Doppelachsantrieb mit einem tiefliegenden Elektromotor,
  • Fig. 3 einen Doppelachsantrieb mit einem besonders kurzen Achsabstand,
  • Fig. 4 einen Doppelachsantrieb mit einem noch weiter verkürzten Achsabstand,
  • Fig. 5 die Draufsicht eines Doppelachsantriebs im Schnitt, der in der linken Figurenhälfte durch die Mitte des Antriebsmotors gemäß Fig. 1 und in der rechten Figurenhälfte durch dieselbe gemäß Fig. 2 verläuft und
  • Fig. 6 die Draufsicht eines Doppelachsantriebs im Schnitt, der in der linken Figurenhälfte durch die Mitte des Antriebsmotors gemäß Fig. 3 und in der rechten Figurenhälfte durch dieselbe gemäß Fig. 4 verläuft.
The invention is explained in more detail below on the basis of exemplary embodiments schematically illustrated in the drawings. Show it:
  • 1 shows a double-axis drive with a high-lying electric motor,
  • 2 a double-axis drive with a low-lying electric motor,
  • 3 shows a double-axis drive with a particularly short center distance,
  • 4 shows a double-axle drive with an even shorter center distance,
  • Fig. 5 is a plan view in section of a double-axis drive which in the left half of the figure runs through the center of the drive motor according to FIG. 1 and in the right half of the figure through the same according to FIG. 2 and
  • Fig. 6 is a plan view in section of a double-axis drive, which in the left half of the figure runs through the center of the drive motor according to FIG. 3 and in the right half of the figure through the same according to FIG. 4.

Ein Doppelachsantrieb besteht aus zwei Radsätzen 1, je einem auf der Achswelle 2 der Radsätze treibend montierten zweistufigen Winkelgetriebe 3 und einem Elektromotor 4, der mit seiner Ankerwelle 5 in der Fahrtrichtung angeordnet ist und an seinen Stirnseiten die Winkelgetriebe 3 trägt.A double-axle drive consists of two wheel sets 1, each having a two-stage bevel gear 3 drivingly mounted on the axle shaft 2 of the wheel sets and an electric motor 4 which is arranged with its armature shaft 5 in the direction of travel and carries the bevel gear 3 on its end faces.

Jedes der Winkelgetriebe 3 weist eine Kegelradstufe mit einem Ritzel 6 auf, das am Ende der Antriebswelle 7 oder auch Kegelritzelwelle des Getriebes sitzt und mit einem Kegelrad 8 kämmt. Die Welle 9 des Kegelrades 8 bildet eine Zwischenwelle und weist ein stirnverzahntes Ritzel 10 auf, das mit einem Großrad 11 kämmt und mit diesem zusammen die Abtriebsstufe bildet.Each of the bevel gear 3 has a bevel gear stage with a pinion 6, which sits at the end of the drive shaft 7 or also bevel pinion shaft of the gear and meshes with a bevel gear 8. The shaft 9 of the bevel gear 8 forms an intermediate shaft and has a spur-toothed pinion 10 which meshes with a large gear 11 and together with this forms the output stage.

Die Ankerwelle 5 ist auf abgesetzten Enden der Kegelritzelwellen 7 zentriert und an sich frei drehbar gelagert. Das Drehmoment wird dabei durch je eine dreh- und biegeelastische Kupplung 12 um die Zentrierungs-und Lagerungsstellen herumgeführt. Der Anker des Elektromotors 4 ist insofern nur mittelbar in dem Motor-Getriebe-Block gelagert, und zwar über die dort unmittelbar und statisch bestimmt gelagerten Kegelritzelwellen 7. Die Winkelgetriebe 3 sind in bezug auf den Elektromotor 4 spiegelbildlich derart ausgebildet, daß ihre die Mittelpunkte der Zwischenwelle 9 und der Achswelle 2 in der Seitenansicht (Fig. 1) verbindenden Linien nach unten divergieren. Diese Anordnung gewährleistet eine hohe Bodenfreiheit des Drehgestells.The armature shaft 5 is centered on stepped ends of the bevel pinion shafts 7 and is freely rotatable in itself. The torque is guided around the centering and bearing points by a torsionally flexible and flexible coupling 12. The armature of the electric motor 4 is in this respect only indirectly supported in the motor-transmission block, specifically via the bevel pinion mounted there directly and statically determined waves 7. The angular gear 3 are mirror-inverted with respect to the electric motor 4 such that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 in the side view (FIG. 1) diverge downward. This arrangement ensures a high ground clearance of the bogie.

Wie die Fig. 5 zeigt, ist die Zwischenwelle 9 beidseitig aus dem Gehäuse 13 des Winkelgetriebes 3 herausgeführt. Sie trägt an ihren Enden je eine Bremsscheibe 14, an der Bremseinrichtungen 15 angreifen, z.B. eine Bremszange 16 mit einem Bremszylinder 17. Die zwei letzteren sind mit dem Gehäuse 13 verbunden, so daß zwischen der Bremsscheibe 14 und den Bremseinrichtungen 15 keine Relativbewegung entsteht.As shown in FIG. 5, the intermediate shaft 9 is guided out of the housing 13 of the angular gear 3 on both sides. It carries at its ends a brake disc 14 on which brake devices 15 act, e.g. a brake caliper 16 with a brake cylinder 17. The two latter are connected to the housing 13, so that no relative movement occurs between the brake disc 14 and the braking devices 15.

Die Figuren 2 bis 4 bzw. 6 sind der Figur 1 bzw. 5 ähnlich und enthalten Teile, die mit den bisher behandelten Teilen größtenteils identisch sind. Diese identischen Teile sind daher im einzelnen nicht mehr beschrieben aber unverändert beziffert, und zwar jeweils auf der rechten Figurenhälfte, da die linke Antriebshälfte spiegelbildlich ist.Figures 2 to 4 and 6 are similar to Figures 1 and 5 and contain parts that are largely identical to the parts discussed so far. These identical parts are therefore no longer described in detail but numbered unchanged, in each case on the right half of the figure, since the left half of the drive is a mirror image.

Hervorzuheben ist, daß die Winkelgetriebe 3a in bezug auf den Elektromotor 4 spiegelbildlich derart ausgebildet sind, daß ihre die Mittelpunkte der Zwischenwelle 9 und der Achswelle 2 in der Seitenansicht verbindenden Linien nach oben divergieren. Dabei ist die Achswelle 2 in einem Winkelbereich um den Mittelpunkt der Zwischenwelle 9 angeordnet, dessen einer Schenkel 18 schräg nach oben weisend etwa unter 45° gegen die Horizontale geneigt ist und der sich hiervon nach unten erstreckt. Diese Anordnung begünstigt das Heruntersenken des Elektromotors 4 und gewährleistet einen tiefliegenden Gesamtschwerpunkt.It should be emphasized that the bevel gears 3a are designed in mirror image with respect to the electric motor 4 in such a way that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 diverge upwards in the side view. The axle shaft 2 is arranged in an angular range around the center point of the intermediate shaft 9, one leg 18 of which is inclined upwards at approximately 45 ° to the horizontal and extends downward therefrom. This arrangement favors the lowering of the electric motor 4 and ensures a low center of gravity.

Die Winkelgetriebe 3b und 3c in den Figuren 3 und 4 sind in bezug auf den Elektromotor 4 spiegelbildlich so ausgebildet, daß ihre die Mittelpunkte der Zwischenwelle 9 und der Achswelle 2 in der Seitenansicht verbindenden Linien nach unten konvergieren. Dabei ist die Achswelle 2 um den Mittelpunkt der Zwischenwelle 9 herum jeweils in einer nach unten weisenden Winkelbereich angeordnet, der sich von der Lotrechten etwa bis zu 65° zum Elektromotor 4 hin erstreckt. Diese Anordnungen gewährleisten einen besonders kurzen Achsabstand. Dies ist deutlich in Fig. 4 zu sehen, wo das Ritzel 6 auf der Kegelritzelwelle 7a in dem vom Elektromotor 4 angewandten Bereich des Kegelrades 8 mit diesem kämmt. Jenseits des Ritzels 6 ist ein Lager 19 für das Ende der Kegelritzelwelle 7a vorgesehen. Die letztere und die Achswelle 2 kreuzen sich hier räum-lich, was in der rechten Häfte der Fig. 6 noch deutlicher zu sehen ist. Dort ist die Zwischenwelle 9a nur einseitig aus dem Winkelgetriebe 3c herausgeführt. Für diesen Radsatz 1 ist daher nur eine einzige Bremsscheibe 14 mit den zugehörigen Bremseinrichtungen 15 vorgesehen.The bevel gears 3b and 3c in FIGS. 3 and 4 are mirror-inverted with respect to the electric motor 4 so that their lines connecting the centers of the intermediate shaft 9 and the axle shaft 2 converge downwards in the side view. Here, the axle shaft 2 is arranged around the center of the intermediate shaft 9 in a downward-facing angular range, which extends from the perpendicular to the electric motor 4 approximately up to 65 °. These orders grant have a particularly short center distance. This can be clearly seen in FIG. 4, where the pinion 6 on the bevel pinion shaft 7a meshes with the bevel gear 8 in the area of the bevel gear 8 used by the electric motor 4. Beyond the pinion 6, a bearing 19 is provided for the end of the bevel pinion shaft 7a. The latter and the axle shaft 2 intersect spatially here, which can be seen even more clearly in the right half of FIG. 6. There, the intermediate shaft 9a is guided out of the angular gear 3c only on one side. Therefore, only a single brake disc 14 with the associated braking devices 15 is provided for this wheel set 1.

Claims (6)

1. Doppelachsantrieb für Schienenfahrzeuge mit in einem Drehgestell oder Rahmen gelagerten Radsätzen und einem zwischen diesen in Fahrtrichtung liegenden Elektromotor, der an seinen Stirnseiten je ein Winkelgetriebe mit einer Kegelradstufe zum Antreiben der Radsätze trägt und dessen Ankerwelle auf den Antriebswellen der Winkelgetriebe an sich gegenseitig drehbar radial gelagert und mit diesen durch je eine nur Drehmomente übertragende Kupplung verbunden ist, dadurch gekennzeichnet, daß das Winkelgetriebe (3) zweistufig ausgebildet ist und eine der Stufen in stirnverzahntem Ritzel (10) und Großrad (11) besteht.1.Double-axle drive for rail vehicles with wheel sets mounted in a bogie or frame and an electric motor located between them in the direction of travel, each of which has an angular gear with a bevel gear stage on its front sides for driving the wheel sets and its armature shaft on the drive shafts of the angular gear rotates mutually radially mounted and connected to them by a torque-transmitting coupling only, characterized in that the angular gear (3) is designed in two stages and one of the stages consists of a spur-toothed pinion (10) and a large wheel (11). 2. Doppelachsantrieb nach Anspruch 1, dadurch gekennzeichnet, daß das Großrad (11) in der Abtriebsstufe und mit seinem Mittelpunkt um sein Ritzel (10) herum - vom Elektromotor (4) abgewandt - in einem schräg nach unten weisenden Winkelbereich von etwa 200° angeordnet ist, dessen einer Schenkel (18) nach oben weisend etwa unter 45° gegen die Horizontale geneigt ist.2. Double-axis drive according to claim 1, characterized in that the large wheel (11) in the output stage and with its center around its pinion (10) around - from the electric motor (4) - arranged in an obliquely downward angle range of about 200 ° is, one leg (18) is inclined upward at about 45 ° to the horizontal. 3. Doppelachsantrieb nach Anspruch 2, dadurch gekennzeichnet, daß das Großrad (11) in dem vom Elektromotor (4) abgewandten Bereich seines Ritzels (10) angeordnet ist.3. Double-axis drive according to claim 2, characterized in that the large wheel (11) is arranged in the region of its pinion (10) facing away from the electric motor (4). 4. Doppelachsantrieb nach Anspruch 2, dadurch gekennzeichnet, daß das Großrad (11) in dem dem Elektromotor (4) zugewandten Bereich seines Ritzels (10) angeordnet ist.4. Double-axis drive according to claim 2, characterized in that the large wheel (11) is arranged in the region of its pinion (10) facing the electric motor (4). 5. Doppelachsantrieb nach Anspruch 4, dadurch gekennzeichnet, daß das Ritzel (6) der Kegelradstufe mit dem Kegelrad (8) in dessen vom Elektromotor (4) angewandtem Bereich kämmt und dort mit seiner Welle (7a) in einem Lager (19) endet.5. Double-axis drive according to claim 4, characterized in that the pinion (6) of the bevel gear stage meshes with the bevel gear (8) in the area applied by the electric motor (4) and ends there with its shaft (7a) in a bearing (19). 6. Doppelachsantrieb nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Welle (9) des stirnverzahnten Ritzels (10) das Gehäuse (13) des Winkelgetriebes (3) senkrecht zur Fahrtrichtung durchsetzt und außen eine Bremsscheibe (14) trägt, an der eine direkt am Gehäuse aufgehängte Bremseinrichtung (15) angreift.6. Double-axis drive according to one of the preceding claims, characterized in that the shaft (9) of the spur gear (10) the housing (13) of the angular gear (3) passes perpendicular to the direction of travel and carries a brake disc (14) on the outside, which is engaged by a brake device (15) suspended directly on the housing.
EP81108686A 1980-12-17 1981-10-22 Double axle drive for rail vehicles Withdrawn EP0054134A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3047413 1980-12-17
DE19803047413 DE3047413A1 (en) 1980-12-17 1980-12-17 DOUBLE AXLE DRIVE FOR RAIL VEHICLES

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Publication Number Publication Date
EP0054134A1 true EP0054134A1 (en) 1982-06-23

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EP81108686A Withdrawn EP0054134A1 (en) 1980-12-17 1981-10-22 Double axle drive for rail vehicles

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EP (1) EP0054134A1 (en)
JP (1) JPS57164857A (en)
BR (1) BR8107642A (en)
CA (1) CA1197726A (en)
DE (1) DE3047413A1 (en)

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Publication number Priority date Publication date Assignee Title
EP3020611A1 (en) * 2014-11-14 2016-05-18 Siemens Aktiengesellschaft Railway drive with braking device
CZ307130B6 (en) * 2008-11-06 2018-01-31 Ĺ KODA TRANSPORTATION a.s. A brake device for a driving unit of a low-floor tram chassis
CN108602518A (en) * 2016-01-26 2018-09-28 西门子股份公司 Two axle drive device

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Publication number Priority date Publication date Assignee Title
DE3704454A1 (en) * 1987-02-13 1988-08-25 Voith Gmbh J M Axle transmission

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FR684497A (en) * 1929-02-07 1930-06-26 Soc D Const Et D Entretien De Transmission control system for rail vehicles and other applications
DE2325787A1 (en) * 1973-05-22 1974-12-19 Hurth Masch Zahnrad Carl DRIVE DEVICE FOR THE DRIVE AXLES OF RAIL VEHICLES
DE2548058A1 (en) * 1975-10-27 1977-04-28 Thyssen Industrie DOUBLE AXLE DRIVE FOR RAIL VEHICLES
DE2616310A1 (en) * 1976-04-12 1977-10-20 Siemens Ag DRIVE FOR AN ELECTRIC RAIL DRIVE
DE2910392A1 (en) * 1979-03-16 1980-09-25 Thyssen Industrie Railway vehicle or tram bogie mounting - has mitre gears inside individually driven wheels on rocker arms

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CH126207A (en) * 1927-07-01 1928-08-01 Hans Blattner Clip fastener for loose sheets.
DE1127934B (en) * 1957-12-30 1962-04-19 Arn Jung Lokomotivfabrik G M B Drive arrangement for vehicles, in particular rail vehicles
DE1815003A1 (en) * 1968-12-17 1970-12-10 Atlas Mak Maschb Gmbh Two-axle motor bogie for rail vehicles

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Publication number Priority date Publication date Assignee Title
CH126707A (en) * 1929-01-22 1928-09-01 Oerlikon Maschf Vehicle drive with double gear reduction.
FR684497A (en) * 1929-02-07 1930-06-26 Soc D Const Et D Entretien De Transmission control system for rail vehicles and other applications
DE2325787A1 (en) * 1973-05-22 1974-12-19 Hurth Masch Zahnrad Carl DRIVE DEVICE FOR THE DRIVE AXLES OF RAIL VEHICLES
DE2548058A1 (en) * 1975-10-27 1977-04-28 Thyssen Industrie DOUBLE AXLE DRIVE FOR RAIL VEHICLES
DE2616310A1 (en) * 1976-04-12 1977-10-20 Siemens Ag DRIVE FOR AN ELECTRIC RAIL DRIVE
DE2910392A1 (en) * 1979-03-16 1980-09-25 Thyssen Industrie Railway vehicle or tram bogie mounting - has mitre gears inside individually driven wheels on rocker arms

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ307130B6 (en) * 2008-11-06 2018-01-31 Ĺ KODA TRANSPORTATION a.s. A brake device for a driving unit of a low-floor tram chassis
EP3020611A1 (en) * 2014-11-14 2016-05-18 Siemens Aktiengesellschaft Railway drive with braking device
WO2016075002A1 (en) * 2014-11-14 2016-05-19 Siemens Aktiengesellschaft Rail vehicle drive with a brake device
RU2662109C1 (en) * 2014-11-14 2018-07-23 Сименс Акциенгезелльшафт Drive unit of the railway rolling stock, with brake system
US10780902B2 (en) 2014-11-14 2020-09-22 Siemens Mobility GmbH Rail vehicle drive with a brake device
CN108602518A (en) * 2016-01-26 2018-09-28 西门子股份公司 Two axle drive device
US11046337B2 (en) 2016-01-26 2021-06-29 Siemens Mobility GmbH Double axle drive

Also Published As

Publication number Publication date
JPS57164857A (en) 1982-10-09
CA1197726A (en) 1985-12-10
DE3047413A1 (en) 1982-07-01
BR8107642A (en) 1982-08-24

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