EP0553802B1 - Driving device for a gate or the like - Google Patents

Driving device for a gate or the like Download PDF

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Publication number
EP0553802B1
EP0553802B1 EP93101242A EP93101242A EP0553802B1 EP 0553802 B1 EP0553802 B1 EP 0553802B1 EP 93101242 A EP93101242 A EP 93101242A EP 93101242 A EP93101242 A EP 93101242A EP 0553802 B1 EP0553802 B1 EP 0553802B1
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EP
European Patent Office
Prior art keywords
gear
crank
shaft
driving device
spring
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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
Application number
EP93101242A
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German (de)
French (fr)
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EP0553802A2 (en
EP0553802A3 (en
Inventor
Bernhard Dr.-Ing. Bouché
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.)
Rhein-Getriebe GmbH
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Rhein-Getriebe GmbH
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Application filed by Rhein-Getriebe GmbH filed Critical Rhein-Getriebe GmbH
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Publication of EP0553802A3 publication Critical patent/EP0553802A3/en
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01F—ADDITIONAL WORK, SUCH AS EQUIPPING ROADS OR THE CONSTRUCTION OF PLATFORMS, HELICOPTER LANDING STAGES, SIGNS, SNOW FENCES, OR THE LIKE
    • E01F13/00—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions
    • E01F13/04—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions movable to allow or prevent passage
    • E01F13/06—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions movable to allow or prevent passage by swinging into open position about a vertical or horizontal axis parallel to the road direction, i.e. swinging gates

Definitions

  • the invention relates to a drive device for a between two end positions by a predetermined pivot angle of preferably substantially 90 ° pivotable barrier boom or the like with an electric drive motor carried by a carrier, which rotates a tree shaft back and forth via a gear transmission and crank mechanism, and with am Supporting compensating spring for the barrier.
  • Such a drive device is known from DE-OS 37 15 936, in which a drive motor is mounted in a housing which at the same time carries bearings for mounting a tree shaft for a barrier tree or the like, the drive motor via a gear mechanism and a crank mechanism with the tree shaft is coupled to pivot the latter back and forth by 90 °, and additional compensating springs are provided between the carrier and a lever engaging the tree shaft, which is part of the crank mechanism, for relieving the torque of the drive gear motor.
  • the tree wave or its storage and the compensation springs form a unit here.
  • the drive geared motor has to be designed relatively strong despite the compensating springs, since the crank gear provides a non-uniform transmission ratio and therefore the torque relief by the compensating springs does not work optimally.
  • the required travel requires a relatively long spring crank arm, which affects a compact design.
  • the object of this invention is to provide a drive device according to the preamble of claim 1, in which the torque load and the electrical energy consumption of the drive gear motor are significantly reduced and smaller crank arms are required for the compensating springs.
  • the compensating spring acts via a crank on a gear shaft of a gear connected downstream of the drive motor, which gear shaft rotates back and forth by double the pivoting angle of the barrier boom.
  • Fig. 1 shows schematically in section a drive device for a barrier.
  • FIG. 2 shows a top view of the drive device from FIG. 1.
  • Fig. 3 shows the course of the transmission torque (ordinate) for the drive device of Fig. 1 and 2 plotted against the angle of rotation of the transmission shaft.
  • the drive device shown comprises a carrier 1, which can preferably be designed as a separate part fastened to a barrier housing 2 and carries an electric drive motor 3.
  • the drive motor 3 is coupled to a crank mechanism via a gear 4, for example a worm gear.
  • the crank mechanism comprises a double crank 6 fastened on the transmission shaft 5 of the transmission 4, which is fastened via a link 7 articulated thereon with a barrier boom 9 or the like which is attached to the tree shaft 8 for an essentially 90 ° pivotable between a closed horizontal and an open vertical position Lever 10 is articulated.
  • the tree shaft 8 is mounted on the carrier 1 via, for example, two bearing blocks 11, the Lever 10 in the area between the two bearing blocks 11 engages.
  • the gear shaft 5 is connected to the double crank 6, which on the one hand - as already described - causes the movement of the tree shaft 8 and the barrier boom 9, on the other hand contains a rotatably mounted shaft 12 which is designed at its free end as a spring cup. This accommodates a compensating spring 13 designed as a compression spring, which is supported on the counter-holder 14, which is screwed to the carrier 1.
  • the drive motor 3 rotates the transmission output shaft 5 by twice the swivel angle of the barrier boom 9, i.e. in the illustrated embodiment by 180 °, so that the spring cup 12 with the compensating spring 13 is pivoted by this angle between the illustrated end position (barrier boom 9 open) and an end position (barrier boom 9 closed).
  • the crank mechanism is designed in such a way that it causes the barrier boom 9 to pivot by 90 ° when the transmission shaft 5 is rotated through 180 °.
  • the bore for the spring cup shaft 12 is located opposite the pin for the crank mechanism, consisting of the parts double crank 6, intermediate member 7 and lever 10 by the angle ⁇ 40 ° with a horizontally arranged compensating spring 13 and with a vertically mounted compensating spring rotated by 130 °.
  • the total torque in the 0 ° position is just positive.
  • the total torque is somewhat larger negative, which causes a preload against the closed position, i.e. the opening of the barrier boom 9, i.e. the beginning of its pivoting into its vertical position is supported.
  • the size of the moments at 0 ° and 180 ° can be influenced by appropriate choice of the angle ⁇ . In the dead positions, there are only small torques from the crank mechanism and also from the compensating spring 13.
  • a relatively weak drive motor 3 can be used, at the same time no large crank arm is required for the compensating spring 13.
  • the unit formed by the carrier 1, which comprises the drive motor 3, the gear 4, the compensating spring arrangement and the crank mechanism, can be designed separately replaceable.
  • the gear 4 can contain a releasable slip clutch, which enables an emergency opening of the barrier boom 9.
  • the emergency opening when the slip clutch is released is supported by the compensating spring 13 due to the resulting negative torque in the 180 ° position of the transmission 4 corresponding to the 90 ° horizontal position of the barrier boom 9.
  • An emergency opening with a hand crank can be done with the free drive shaft journal when the slip clutch is closed 15 can be made.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Transmission Devices (AREA)

Description

Die Erfindung betrifft eine Antriebsvorrichtung für einen Zwischen Zwei Endpositionen um einen vorbestimmten Schwenkwinkel von vorzugsweise im wesentlichen 90° verschwenkbaren Schrankenbaum oder dergleichen mit einem von einem Träger getragenen, elektrischen Antriebsmotor, der über ein Zahnradgetriebe und Kurbeltrieb eine Baumwelle hin- und herdreht, sowie mit am Träger angreifender Ausgleichsfeder für die Schranke.The invention relates to a drive device for a between two end positions by a predetermined pivot angle of preferably substantially 90 ° pivotable barrier boom or the like with an electric drive motor carried by a carrier, which rotates a tree shaft back and forth via a gear transmission and crank mechanism, and with am Supporting compensating spring for the barrier.

Eine derartige Antriebsvorrichtung ist aus der DE-OS 37 15 936 bekannt, bei der ein Antriebsmotor in einem Gehäuse montiert ist, das gleichzeitig Lager zur Lagerung einer Baumwelle für einen Schrankenbaum oder dergleichen trägt, wobei der Antriebsmotor über ein Zahnradgetriebe und ein Kurbelgetriebe mit der Baumwelle gekoppelt ist, um letztere um 90° hin- und herzuschwenken, und zusätzlich Ausgleichsfedern zwischen dem Träger und einem an der Baumwelle angreifenden Hebel, der Teil des Kurbelgetriebes ist, zur Drehmomententlastung des Antriebsgetriebemotors vorgesehen sind. Die Baumwelle bzw. deren Lagerung und die Ausgleichsfedern bilden hier eine Einheit. Außerdem ist der Antriebsgetriebemotor trotz der Ausgleichsfedern relativ stark auszulegen, da das Kurbelgetriebe eine ungleichförmige Übersetzung liefert und daher die Drehmomententlastung durch die Ausgleichsfedern nicht optimal wirkt. Außerdem bedingt der erforderliche Federweg einen relativ langen Federkurbelarm, der eine kompakte Bauweise beeinträchtigt.Such a drive device is known from DE-OS 37 15 936, in which a drive motor is mounted in a housing which at the same time carries bearings for mounting a tree shaft for a barrier tree or the like, the drive motor via a gear mechanism and a crank mechanism with the tree shaft is coupled to pivot the latter back and forth by 90 °, and additional compensating springs are provided between the carrier and a lever engaging the tree shaft, which is part of the crank mechanism, for relieving the torque of the drive gear motor. The tree wave or its storage and the compensation springs form a unit here. In addition, the drive geared motor has to be designed relatively strong despite the compensating springs, since the crank gear provides a non-uniform transmission ratio and therefore the torque relief by the compensating springs does not work optimally. In addition, the required travel requires a relatively long spring crank arm, which affects a compact design.

Aufgabe dieser Erfindung ist es, eine Antriebsvorrichtung nach dem Oberbegriff des Anspruchs 1 zu schaffen, bei der die Drehmomentbelastung und der elektrische Energieverbrauch des Antriebsgetriebemotors wesentlich verringert sind und kleinere Kurbelarme für die Ausgleichsfedern benötigt werden.The object of this invention is to provide a drive device according to the preamble of claim 1, in which the torque load and the electrical energy consumption of the drive gear motor are significantly reduced and smaller crank arms are required for the compensating springs.

Diese Aufgabe wird dadurch gelöst, daß die Ausgleichsfeder über eine Kurbel an einer jeweils um den doppelten Schwenkwinkel des Schrankenbaums hin- und herdrehenden Getriebewelle eines dem Antriebsmotor nachgeschalteten Getriebes angreift.This object is achieved in that the compensating spring acts via a crank on a gear shaft of a gear connected downstream of the drive motor, which gear shaft rotates back and forth by double the pivoting angle of the barrier boom.

Weitere Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung zu entnehmen.Further embodiments of the invention can be found in the following description.

Die Erfindung wird nachstehend anhand des in den beigefügten Abbildungen dargestellten Ausführungsbeispiels näher erläutert.The invention is explained below with reference to the embodiment shown in the accompanying figures.

Fig. 1 zeigt schematisiert im Schnitt eine Antriebsvorrichtung für eine Schranke.Fig. 1 shows schematically in section a drive device for a barrier.

Fig. 2 zeigt eine Draufsicht auf die Antriebsvorrichtung von Fig. 1.FIG. 2 shows a top view of the drive device from FIG. 1.

Fig. 3 zeigt den Verlauf des Getriebedrehmoments (Ordinate) für die Antriebsvorrichtung von Fig. 1 und 2 aufgetragen gegenüber dem Drehwinkel der Getriebewelle.Fig. 3 shows the course of the transmission torque (ordinate) for the drive device of Fig. 1 and 2 plotted against the angle of rotation of the transmission shaft.

Die dargestellte Antriebsvorrichtung umfaßt einen Träger 1, der bevorzugt als separates, an einem Schrankengehäuse 2 befestigtes Teil ausgebildet sein kann und einen elektrischen Antriebsmotor 3 trägt. Der Antriebsmotor 3 ist über ein Getriebe 4, etwa ein Schneckengetriebe, mit einem Kurbeltrieb gekoppelt. Der Kurbeltrieb umfaßt eine auf der Getriebewelle 5 des Getriebes 4 befestigte Doppelkurbel 6, die über ein daran angelenktes Zwischenglied 7 mit einem an der Baumwelle 8 für einen zwischen einer geschlossenen horizontalen und einer geöffneten vertikalen Stellung um im wesentlichen 90° verschwenkbaren Schrankenbaum 9 oder dergleichen befestigten Hebel 10 gelenkig gekoppelt ist. Die Baumwelle 8 ist über beispielsweise zwei Lagerböcke 11 am Träger 1 gelagert, wobei der Hebel 10 im Bereich zwischen den beiden Lagerböcken 11 greift.The drive device shown comprises a carrier 1, which can preferably be designed as a separate part fastened to a barrier housing 2 and carries an electric drive motor 3. The drive motor 3 is coupled to a crank mechanism via a gear 4, for example a worm gear. The crank mechanism comprises a double crank 6 fastened on the transmission shaft 5 of the transmission 4, which is fastened via a link 7 articulated thereon with a barrier boom 9 or the like which is attached to the tree shaft 8 for an essentially 90 ° pivotable between a closed horizontal and an open vertical position Lever 10 is articulated. The tree shaft 8 is mounted on the carrier 1 via, for example, two bearing blocks 11, the Lever 10 in the area between the two bearing blocks 11 engages.

Die Getriebewelle 5 ist mit der Doppelkurbel 6 verbunden, die einerseits - wie bereits beschrieben - die Bewegung der Baumwelle 8 und des Schrankenbaumes 9 bewirkt, andererseits eine drehbar gelagerte Welle 12 enthält, die an ihrem freien Ende als Federtopf ausgebildet ist. Dieser nimmt eine als Druckfeder ausgebildete Ausgleichsfeder 13 auf, die sich auf dem Gegenhalter 14, der mit dem Träger 1 verschraubt ist, abstützt.The gear shaft 5 is connected to the double crank 6, which on the one hand - as already described - causes the movement of the tree shaft 8 and the barrier boom 9, on the other hand contains a rotatably mounted shaft 12 which is designed at its free end as a spring cup. This accommodates a compensating spring 13 designed as a compression spring, which is supported on the counter-holder 14, which is screwed to the carrier 1.

Der Antriebsmotor 3 dreht die Getriebeabtriebswelle 5 um den doppelten Schwenkwinkel des Schrankenbaumes 9, d.h. im dargestellten Ausführungsbeispiel um 180° , so daß der Federtopf 12 mit der Ausgleichsfeder 13 um diesen Winkel zwischen der dargestellten Endposition (Schrankenbaum 9 offen) und einer Endposition (Schrankenbaum 9 geschlossen) verschwenkt wird. Der Kurbeltrieb ist hierbei derart ausgelegt, daß er bei einer 180°-Drehung der Getriebewelle 5 eine Schwenkung des Schrankenbaumes 9 um 90° bewirkt.The drive motor 3 rotates the transmission output shaft 5 by twice the swivel angle of the barrier boom 9, i.e. in the illustrated embodiment by 180 °, so that the spring cup 12 with the compensating spring 13 is pivoted by this angle between the illustrated end position (barrier boom 9 open) and an end position (barrier boom 9 closed). The crank mechanism is designed in such a way that it causes the barrier boom 9 to pivot by 90 ° when the transmission shaft 5 is rotated through 180 °.

Die Bohrung für die Federtopfwelle 12 befindet sich gegenüber dem Zapfen für den Kurbeltrieb, bestehend aus den Teilen Doppelkurbel 6, Zwischenglied 7 und Hebel 10 um den Winkel β≈40° bei waagerecht angeordneter Ausgleichsfeder 13, bei senkrecht gelagerter Ausgleichsfeder um 130° verdreht.The bore for the spring cup shaft 12 is located opposite the pin for the crank mechanism, consisting of the parts double crank 6, intermediate member 7 and lever 10 by the angle β≈40 ° with a horizontally arranged compensating spring 13 and with a vertically mounted compensating spring rotated by 130 °.

Hierdurch ergibt sich eine wesentliche Kompensation der Getriebedrehmomente entsprechend Fig. 3 im gesamten Bereich von 0° bis 180°, vgl. die durchgezogene, das Gesamtdrehmoment wiedergegebende Kurve A, die sich aus der Federkomponente B (strichpunktiert) und dem Moment des Kurbeltriebes C (gestrichelt) zusammensetzt, wobei sich das Moment des Kurbeltriebes aus der Eigengewichtskraft des Schrankenbaumes 9 und aus der (sinusförmigen) Beschleunigung der Massenträgheit des Schrankenbaumes 9 bewirkte Moment zusammensetzt.This results in a substantial compensation of the transmission torques according to FIG. 3 in the entire range from 0 ° to 180 °, cf. the solid curve A, which represents the total torque, which is composed of the spring component B (dash-dotted) and the moment of the crank mechanism C (dashed), the moment of the crank mechanism the moment caused by the dead weight of the barrier boom 9 and the (sinusoidal) acceleration of the inertia of the barrier boom 9.

Ersichtlich ist das Gesamtdrehmoment in der 0°-Stellung gerade eben positiv. In der 180°-Stellung ist das Gesamtdrehmoment etwas größer negativ, wodurch eine Vorspannung gegen die Schließstellung bewirkt, d.h. das Öffnen des Schrankenbaumes 9, d.h. der Beginn seines Schwenkens in seine vertikale Lage, wird ünterstützt. Die Größe der Momente bei 0° und 180° ist durch entsprechende Wahl des Winkels β beeinflußbar. In den Totlagen existieren nur kleine Drehmomente aus dem Kurbeltrieb und ebenso von der Ausgleichsfeder 13.Obviously, the total torque in the 0 ° position is just positive. In the 180 ° position, the total torque is somewhat larger negative, which causes a preload against the closed position, i.e. the opening of the barrier boom 9, i.e. the beginning of its pivoting into its vertical position is supported. The size of the moments at 0 ° and 180 ° can be influenced by appropriate choice of the angle β. In the dead positions, there are only small torques from the crank mechanism and also from the compensating spring 13.

Dementsprechend kommt man mit einem relativ schwach bemessenen Antriebsmotor 3 aus, wobei gleichzeitig kein großer Kurbelarm für die Ausgleichsfeder 13 benötigt wird. Die vom Träger 1 gebildete Einheit, die den Antriebsmotor 3, das Getriebe 4, die Ausgleichsfederanordnung und den Kurbeltrieb umfaßt, kann seperat auswechselbar gestaltet werden.Accordingly, a relatively weak drive motor 3 can be used, at the same time no large crank arm is required for the compensating spring 13. The unit formed by the carrier 1, which comprises the drive motor 3, the gear 4, the compensating spring arrangement and the crank mechanism, can be designed separately replaceable.

Das Getriebe 4 kann eine lösbare Rutschkupplung enthalten, die eine Notöffnung des Schrankenbaumes 9 ermöglicht. Die Notöffnung bei gelöster Rutschkupplung wird unterstützt durch die Ausgleichsfeder 13 aufgrund des hierdurch ausgeübten negativen Drehmomentes in der 180°-Position des Getriebes 4 entsprechend der 90°-Horizontalposition des Schrankenbaumes 9. Eine Notöffnung mit einer Handkurbel kann bei geschlossener Rutschkupplung mit Hilfe des freien Antriebswellenzapfens 15 vorgenommen werden.The gear 4 can contain a releasable slip clutch, which enables an emergency opening of the barrier boom 9. The emergency opening when the slip clutch is released is supported by the compensating spring 13 due to the resulting negative torque in the 180 ° position of the transmission 4 corresponding to the 90 ° horizontal position of the barrier boom 9. An emergency opening with a hand crank can be done with the free drive shaft journal when the slip clutch is closed 15 can be made.

Claims (10)

  1. Driving device for a gate bar (9) or the like pivotable between to final positions via a predetermined pivot angle of preferably about 90°, comprising an electrical drive motor (3) supported by a support (1) and rotating to and fro a gate shaft (8) via a toothed wheel gear (4) and a crank gear (6, 7, 10), and an equalizer spring (13) for the gate connected with the support (1), characterized in that the equalizer spring (13) via a crank (6) of the crank gear (6, 7, 10) is acting on a gear shaft (5) of a gear (4) following the drive motor (3), the gear shaft (5) being rotatable each time to and fro by the double of the pivot angle of the gate bar (9).
  2. Driving device according to claim 1, characterized in that the equalizer spring (13) is acting as a pressure spring.
  3. Driving device according to claim 1 or 2, characterized in that the equalizer spring (13) is coupled with the crank (6) via a shaft (12) provided with a spring cup and received by a bore of the crank (6).
  4. Driving device according to claim 3, characterized in that, when the equalizer spring (13) is in a horizontal position, the bore in the crank (6) for receiving the spring cup shaft (12) is rotatably positioned with respect to the connecting line between the axes of the gear shaft (5) and a joint at the crank (6) for connecting of this with a following part of the crank gear (6, 7, 10) via an angle (β) of about 40° around the axis of th gear shaft (5) such that in the final closure position of the gate bar (9) for the gear (4) a resulting small torque against the closure position is resulting.
  5. Driving device according to claim 4, characterized in that, when the equalizer spring (13) is in a horizontal position, the bore for the spring cup shaft (12) is rotatably positioned via an angle of about 40° around the axis of the gear shaft (5).
  6. Driving device according to anyone of the claims 3 to 5, characterized in that the bore in the crank (6) for the spring cup shaft (12) is rotatably positioned with respect to the connecting line between the axes of the gear shaft (5) and a joint at the crank (6) for connecting of this with a following part of the crank gear (6, 7, 10) via an angle (β) around the axis of th gear shaft (5) such that within the final opening position the equalizer spring (13) exerts a small torque directed into the closure position onto the gate bar (9) via corresponding bias.
  7. Driving device according to anyone of the claims 1 to 6, characterized in that the gear (4) is a worm gear.
  8. Driving device according to anyone of the claims 1 to 6, characterized in that the gear (4) contains a releasable slipper clutch.
  9. Driving device according to anyone of the claims 1 to 6, characterized in that the gear (4) contains a free drive shaft journal (15) for an emergency actuation under use of a crank handle.
  10. Driving device according to anyone of the claims 1 to 6, characterized in that the support (1) together with the drive motor (3), the gear (4), the crank gear (6, 7, 10) and the equalizer spring (13) is formed an a replaceable unit.
EP93101242A 1992-01-30 1993-01-28 Driving device for a gate or the like Expired - Lifetime EP0553802B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4202584 1992-01-30
DE4202584A DE4202584A1 (en) 1992-01-30 1992-01-30 DRIVE DEVICE FOR A CABINET OR THE LIKE

Publications (3)

Publication Number Publication Date
EP0553802A2 EP0553802A2 (en) 1993-08-04
EP0553802A3 EP0553802A3 (en) 1993-09-15
EP0553802B1 true EP0553802B1 (en) 1995-08-09

Family

ID=6450578

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93101242A Expired - Lifetime EP0553802B1 (en) 1992-01-30 1993-01-28 Driving device for a gate or the like

Country Status (2)

Country Link
EP (1) EP0553802B1 (en)
DE (2) DE4202584A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012148A1 (en) 2010-03-20 2011-09-22 Rhein-Getriebe Gmbh Drive device for barrier boom, has electric drive that is supported by carrier, where balancing spring is engaged at carrier and is engaged over chain link of crank gear at drive shaft of gearbox

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4435601A1 (en) * 1994-10-05 1996-04-11 Malkmus Doernemann Carola Electromechanical drive mechanism for railway level crossing boom
AT402311B (en) * 1995-03-20 1997-04-25 Skidata Gmbh SHUT-OFF DEVICE
DE202010003545U1 (en) 2010-03-13 2010-07-22 Magnetic Autocontrol Gmbh driving device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1991565U (en) * 1968-04-26 1968-08-14 Parkautomatic Hans Farmont CABINETS.
DE8516062U1 (en) * 1985-06-01 1985-07-18 Rhein-Getriebe Gmbh, 4005 Meerbusch Barrier drive
DE8706868U1 (en) * 1987-05-13 1987-07-09 Magnetic-Elektromotoren GmbH, 7867 Maulburg Drive device for barrier or similar
DE9000478U1 (en) * 1990-01-17 1990-03-01 K. & A. Knödler GmbH, 7302 Ostfildern Drive device for a barrier

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012148A1 (en) 2010-03-20 2011-09-22 Rhein-Getriebe Gmbh Drive device for barrier boom, has electric drive that is supported by carrier, where balancing spring is engaged at carrier and is engaged over chain link of crank gear at drive shaft of gearbox

Also Published As

Publication number Publication date
DE59300432D1 (en) 1995-09-14
EP0553802A2 (en) 1993-08-04
DE4202584A1 (en) 1993-08-05
EP0553802A3 (en) 1993-09-15

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