EP2172380B1 - Electric overhead conveyor - Google Patents

Electric overhead conveyor Download PDF

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Publication number
EP2172380B1
EP2172380B1 EP09011859.7A EP09011859A EP2172380B1 EP 2172380 B1 EP2172380 B1 EP 2172380B1 EP 09011859 A EP09011859 A EP 09011859A EP 2172380 B1 EP2172380 B1 EP 2172380B1
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EP
European Patent Office
Prior art keywords
support rail
drive roller
transported
support
coupling member
Prior art date
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Application number
EP09011859.7A
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German (de)
French (fr)
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EP2172380A1 (en
Inventor
Herbert Schulze
Alexander Schurba
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Eisenmann SE
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Eisenmann SE
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Publication of EP2172380A1 publication Critical patent/EP2172380A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61C—LOCOMOTIVES; MOTOR RAILCARS
    • B61C13/00—Locomotives or motor railcars characterised by their application to special systems or purposes
    • B61C13/04—Locomotives or motor railcars characterised by their application to special systems or purposes for elevated railways with rigid rails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61B—RAILWAY SYSTEMS; EQUIPMENT THEREFOR NOT OTHERWISE PROVIDED FOR
    • B61B3/00—Elevated railway systems with suspended vehicles
    • B61B3/02—Elevated railway systems with suspended vehicles with self-propelled vehicles

Definitions

  • the contact pressure of the drive roller is increased against the tread of the support rail when the carrier car is loaded with respect to a previously transported load heavier cargo. Conversely, the contact pressure is reduced when the wagon is loaded with respect to a previously transported load lighter cargo.
  • this comprises a supporting console carrying the drive roller, which in turn is pivotably mounted about a pivot axis on the chassis of the carrier and can be coupled to the object to be transported.
  • the drive roller is mounted in a simple manner so that their distance, and thus the distance between their axis of rotation, relative to the mounting rail can be changed.
  • the pressing device comprises a pivoting element, which is pivotally mounted on the chassis about a horizontal pivot axis and connectable at a free portion with the object to be transported, wherein the pivoting element cooperates with a coupling device through which a pivoting movement of the pivoting element the support bracket is transmitted, so that the support bracket pivoted in the direction of the support rail.
  • the coupling device comprises at least one coupling member which is connected to the support bracket. At this coupling member may abut the pivot member and so transmit its movement to the coupling device.
  • the pivoting element is preferably a rocker element which is mounted between a first and a second rocker section and is connectable to the first free rocker section with the object to be transported, wherein a force is exerted on the coupling element by the second free rocker section of the rocker element, when the rocker element pivots. Due to the weight of the article connected to the rocker element, the rocker element is pivoted and transmits a force to the coupling device and thus in terms of the contact pressure on the drive roller, of the Weight of the object depends.
  • the pivoting element is preferably a lever element, which is pivotably mounted on the chassis at a first end, wherein the pivot axis of the pivoting element is perpendicular to the mounting rail, and at its opposite, downwardly facing end is connectable to the object to be transported, wherein a force is exerted on the coupling member by the lever member when the lever member pivots.
  • a lever element it is possible that, in particular in a gradient or downward travel, the contact pressure of the drive roller against the mounting rail is not only increased depending on the weight of the object to be transported by the distance of the axis of rotation of the drive roller is reduced to the mounting rail.
  • the contact pressure of the drive roller against the support rail is increased in this case also depending on the inclination angle of the slope or the slope of the support rail.
  • the contact pressure can be increased both pitch and downhill, since the lever member so cooperates in each pivoting with a coupling member.
  • FIG. 1 Referenced.
  • a section of a monorail system 2 is shown, which a support rail 4, from the in FIG. 1 a horizontal section 6 is shown, and a movable on the support rail 4 carriage 8 includes.
  • the transport direction, in which material to be conveyed is transported by means of the overhead monorail 2, is in FIG. 1 indicated by an arrow 10.
  • the support rail 4 is designed in a conventional manner as I-profile. It is suspended in a manner known per se on a ceiling construction or a steel structure and extends above the level of the room floor. Further, the support rail 4 has two opposing upper vertical guide surfaces 16, 18, a arranged below the upper guide surface 16 lower vertical guide surface 20 and one of these opposite vertical drive surface 22 (see. FIG. 3 ).
  • the guide tread 18 extends in the FIGS. 1 . 4 and 5 behind the guide tread 16 and the drawing plane.
  • sliding lines which serve the power supply of the carrier car 8 and the signal transmission to this.
  • Such sliding lines correspond to the prior art.
  • the axes of rotation of the support rollers 26, 28 run in a horizontal plane perpendicular to the support rail 4.
  • the chassis 24 also supports on both sides of the support rail 4 in a known manner four lateral upper guide rollers 30 which are perpendicular to the upper tread 12 of the support rail 4 extending, in FIG. 1 can rotate according to vertical axes and each of which two roll laterally at the opposite upper vertical guide surfaces 16 and 18.
  • the chassis 24 also supports two lateral lower guide rollers 32, which can rotate about axes that are parallel to the axes of the upper guide rollers 30.
  • the lower guide rollers 32 run on the lower guide surface 20 from.
  • a third lateral lower guide roller 34 is rotatably mounted on the chassis 24 corresponding to an axis which extends parallel to the axes of the upper guide rollers 30.
  • the third lower guide roller 34 rolls on the drive running surface 22 and is disposed opposite to the lower guide roller 32, which is viewed in the transport direction 10 is mounted front of the chassis 24.
  • a drive roller 36 which is rotatable about an axis of rotation 38 which runs parallel to the axes of rotation of the guide rollers 30, 32 and 34, rolls on the drive running surface 22 of the support rail 4.
  • the axis of rotation 38 of the drive roller 36 is mounted on a motor console 40, which in turn carries an electric motor 42 which drives the drive roller 36.
  • the electric motor 42 is energized and controlled via the above-mentioned sliding lines.
  • rollers which receive the load to be transported i. the carrying rollers 26 and 28, and the rollers or the single roller over which the carrying carriage 8 is driven, i. here the drive roller 36, functionally separated from each other.
  • the engine console 40 is pivotable about a pivot axis 44 connected to the chassis 24 of the carrier carriage 8, which parallel to the axis of rotation 38 of the drive roller 36, in FIG. 1 thus vertically, runs.
  • the motor console 40 and the electric motor 42 and the drive roller 36 relative to the chassis 24 of the support carriage 8 and the support rail 4 are pivotable.
  • a coupling member 46 is pivotally mounted about a pivot axis 48 which extends parallel to the pivot axis 44 of the engine console 40.
  • the coupling member 46 extends below the two lower guide rollers 32 in the lateral direction of the support rail 4 away.
  • the pivot axis 48 of the coupling member 46 is disposed on the drive running surface 22 opposite side of the support rail 4.
  • this On the drive roller 36 facing side of the pivot axis 48 of the coupling member 46, this carries a cam 50 which engages in a recess 52 of the motor console 40.
  • the chassis 24 supports a rocker member 54, which is pivotable about a horizontal and perpendicular to the transport direction 10 rocker axis 56.
  • a transport hanger 60 is articulated via a not specifically provided with a reference numeral horizontal and perpendicular to the support rail 4 extending pivot axis, in which to be conveyed objects can be introduced.
  • the longitudinal axes of this pivot axis and the rocker axis 56 lie in a common horizontal plane when the carriage 8 is in a horizontal portion of the support rail 4, as in FIG. 1 is shown.
  • the first rocker section 58 opposite second rocker section 62 is formed as a two-legged 90 ° angle, with its free leg 64 is parallel to the first rocker section 58, but this is offset from the bottom.
  • the free leg 64 of the second rocker member 62 carries on the end face of its free end a plunger 66, via which the rocker member 54 rests against the coupling member 46.
  • the rocker member 54, the coupling member 46 and the pivotable motor console 40 together form a pressing device 68, with which the contact pressure of the drive roller 36 against the drive surface 22 of the support rail 4 can be adjusted depending on the load carried by the wagon 8 by the distance between the axis of rotation 38 of the drive roller 36 and the drive surface 22 of the support rail 4 is changed.
  • FIG. 4 is a downwardly inclined in the transport direction 10 section 72 and in FIG. 5 a in the transport direction 10 upwardly inclined portion 74 of the support rail 4 shown.
  • the rocker member 54 is shown significantly more pivoted to illustrate its pivotal movement, as is the case in practice.
  • FIGS. 6 to 8 is shown as a second embodiment, a monorail system 102.
  • a monorail system 102 There carry components that correspond to those of the monorail system 2, the same reference numerals plus 100th
  • the monorail 102 differs from the monorail 2 in the formation of the pressing device 168.
  • a lever rod 172 is provided there. This is at its one end of the bearing via a lever axis 174, which coincides in their orientation and position relative to the chassis 124 of the support carriage 108 with the rocker axis 56, mounted on the chassis 124.
  • a plunger 166 is mounted, which rests against the coupling member 146, as is the case with the plunger 66 and the coupling member 46 of the pressing device 68.
  • the lever rod 172 On the opposite side of the first side arm 176 The lever rod 172 has a second side arm 178 which runs coaxially with the first side arm 176 and carries on the end face of its free end a second plunger 180, which points in the transport direction 110.
  • the second plunger 180 abuts against a second coupling member 182, which extends parallel to the first coupling member 146 and is rigidly connected to the engine console 140 of the chassis 124.
  • lever rod 172 is connected via a tow bar 184 articulated to a tow truck 186, which rolls in a manner known per se on the ground.
  • the pressing device 168 is formed by the lever rod 172, the first and the second coupling member 146 and 182 and the pivotable motor console 140. By the pressing device 168, the contact pressure of the drive roller 136 against the Antriebsmoor materials1 22 of the support rail 104 is adjusted depending on the load carried by the tractor 184 load.
  • the contact pressure of the drive roller 136 is increased by the pressing device 168 against the support rail 104 when the carriage 108 is accelerated or decelerated.
  • the lever rod 172 due to the inertia of the hinged to these tow truck 186 about its lever axis 174 that the plunger 166 moves in the direction of the coupling member 146.
  • the lever rod 172 is pivoted due to the addition of the slope on the lever rod 172 weight force of the towing vehicle 186, as in an acceleration of the Dolly 108 is the case.
  • the drive roller 136 is pressed more strongly against the support rail 104, wherein the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 becomes stronger the greater the weight of the loaded towed carriage 186.
  • the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the pitch section.
  • the lever rod 172 is pivoted due to the force acting on the lever rod 172 by gravity additional weight of the tow truck 186, as in a delay of the trolley 108 is the case.
  • Characterized the drive roller 136 is pressed stronger against the support rail 104, wherein the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 is stronger, the greater the weight of the loaded tow truck 186.
  • the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the slope section.
  • a transport hanger 160 is attached to the wagon 108 instead of the tow truck 186, as it is in the FIGS. 9 to 11 is shown at one in the Figures 10 11 and 11 gradient or incline travel in a corresponding manner an increase of the contact pressure of the drive roller 136 to the support rail 104, since in this case the weight of the loaded transport hanger 160 would bring the lever rod 172 always in a vertical position, if this could pivot freely , However, the force exerted by the transport hanger 160 weight is transmitted via the lever rod 172 on one of the coupling members 146 or 182, which in turn for the discussed increase of the contact pressure the drive roller 136 leads against the support rail 104.
  • the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 becomes stronger the greater the weight of the loaded transport hanger 160.
  • the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the slope or slope section.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Carriers, Traveling Bodies, And Overhead Traveling Cranes (AREA)
  • Chain Conveyers (AREA)

Description

Die Erfindung betrifft eine Elektrohängebahn zum Transport von Gegenständen mit

  1. a) einer Tragschiene, welche eine Antriebslauffläche umfasst, die unabhängig von einem Gefälle oder einer Steigung der Tragschiene stets vertikal verläuft;
  2. b) wenigstens einem Tragwagen mit einem Last aufnehmenden Fahrwerk, wobei das Fahrwerk wenigstens eine angetriebene Antriebsrolle umfasst, die auf der vertikalen Antriebslauffläche der Tragschiene abrollt.
The invention relates to a monorail conveyor for transporting objects with
  1. a) a support rail, which comprises a drive tread, which is always vertical regardless of a slope or a slope of the support rail;
  2. b) at least one wagon with a load-bearing chassis, wherein the chassis comprises at least one driven drive roller, which rolls on the vertical drive surface of the support rail.

Bei vom Markt her bekannten derartigen Elektrohängebahnen ist es für einen zuverlässigen Betrieb wichtig, dass die Reibungskräfte zwischen der Antriebsrolle und der Tragschiene stets ausreichend groß sind, damit der Tragwagen ohne ein Durchrutschen der Antriebsrolle auf der Tragschiene verfährt. In letzterem Fall können die gewünschten Antriebs- bzw. Verzögerungskräfte zwischen dem Tragwagen und der Tragschiene nicht mehr ausreichend sicher übertragen werden.In the case of such overhead monorail systems known from the marketplace, it is important for reliable operation that the frictional forces between the drive roller and the mounting rail are always sufficiently large for the carrier carriage to move without slippage of the drive roller on the mounting rail. In the latter case, the desired drive or deceleration forces between the wagon and the mounting rail can no longer be transmitted with sufficient security.

Je höher das Gewicht des zu transportierenden Guts ist, desto größer muss auch die zwischen Antriebsrolle und Tragschiene vorherrschende Reibung sein, um stets eine ausreichende Haftung der Antriebsrolle auf der Antriebslauffläche der Tragschiene zu gewährleisten. Bei einem Tragwagen nach dem Stand der Technik, bei dem der Anpressdruck der Antriebsrolle gegen die Tragschiene weitgehend konstant ist, kann es zu einem Durchrutschen der Antriebrolle kommen, wenn die zu transportierende Last ein bestimmtes Gewicht übersteigt. Umgekehrt muss bei einem solchen Tragwagen stets gegen die gleiche Reibung zwischen Antriebsrad und Tragschiene gearbeitet werden, auch wenn Lasten transportiert werden, bei denen ein geringerer Anpressdruck der Antriebsrolle gegen die Tragschiene ausreichen würde, ohne dass es zu einem Durchrutschen des Antriebsrades käme. Dies führt beim Transport von geringeren Lasten zu einem höheren Energiebedarf als nötig.The higher the weight of the material to be transported, the greater must also be the friction prevailing between the drive roller and the mounting rail in order to always ensure sufficient adhesion of the drive roller to the drive running surface of the mounting rail. In a wagon according to the prior art, in which the contact pressure of the drive roller against the mounting rail is largely constant, it can lead to slippage of the drive roller when the load to be transported exceeds a certain weight. Conversely, in such a cart always against the same friction between the drive wheel and mounting rail be worked, even if loads are transported in which a lower contact pressure of the drive roller would be sufficient against the support rail, without causing slippage of the drive wheel. This leads to a higher energy requirement when transporting lower loads than necessary.

Zudem kann es bei vom Markt her bekannten Elektrohängebahnen der eingangs genannten Art zu Schwierigkeiten in geneigten Abschnitten der Tragschiene kommen, die bei Elektrohängebahnen vorliegen, mit denen auch Höhenunterschiede überwunden werden sollen. Wenn sich der Tragwagen mit dem zu transportierenden Gegenstand in einem geneigten Abschnitt befindet, ist die von der Antriebsrolle auf die Tragschiene zu übertragende Kraft größer, da nicht nur die beim Verfahren des Tragwagens entstehenden Reibungskräfte zu überwinden sind, sondern auch eine Kraft in vertikaler Richtung aufgebracht werden muss, um eine Steigung zu bewältigen bzw. den Tragwagen gegen eine Hangabtriebskraft zu halten. Auch hier muss der Anpressdruck der Antriebsrolle gegen die Tragschiene umso größer sein, je höher das Gewicht des zu transportierenden Guts ist.In addition, difficulties in inclined sections of the mounting rail can occur in known from the market electric monorail systems of the type mentioned, which are present in electric monorail systems with which height differences are to be overcome. When the wagon with the object to be transported is in an inclined section, the force to be transmitted from the drive roller to the support rail is greater, since not only are the frictional forces arising during the method of the trolley to be overcome, but also a force applied in the vertical direction must be to master a slope or to keep the wagon against a downgrade force. Again, the contact pressure of the drive roller against the mounting rail must be greater, the higher the weight of the goods to be transported.

Aus DE 20 45 659 A1 , EP 0 866 021 A , DE 42 09 565 A1 und GB 1 248 490 A sind Hängebahnsystem bekannt, bei denen in Abkehr vom vorliegende interessierenden Antriebsprinzip eine Antriebsrolle auf einer horizontalen Antriebslauffläche abrollt. Im Gegensatz dazu beschreibt die GB 1 097 033 A1 ein Hängebahnsystem der eingangs genannten Art. Dort wird die Traktion dadurch eingestellt, dass die Anzahl der an der Tragschiene angreifenden Rollen verändert wird. Dies ist jedoch recht aufwendig und umständlich.Out DE 20 45 659 A1 . EP 0 866 021 A . DE 42 09 565 A1 and GB 1 248 490 A overhead conveyor system are known in which, in departure from the present interest drive principle, a drive roller rolls on a horizontal drive tread. In contrast, the describes GB 1 097 033 A1 a monorail system of the type mentioned. There, the traction is adjusted by the number of acting on the support rail rollers is changed. However, this is quite complicated and cumbersome.

Es ist daher Aufgabe der vorliegenden Erfindung, eine Elektrohängebahn der eingangs genannten Art zu schaffen, bei welcher Antriebs- bzw. Verzögerungskräfte zwischen dem Tragwagen und der Tragschiene auch bei Änderungen von Transportparametern, wie beispielsweise des Gewichts des zu transportierenden Guts oder des Neigungswinkels der Tragschiene, sicher übertragen werden können.It is therefore an object of the present invention, an electric monorail system of the type mentioned above, in which drive or deceleration forces between the wagon and the mounting rail can be safely transmitted even with changes in transport parameters, such as the weight of the goods to be transported or the inclination angle of the support rail.

Diese Aufgabe wird bei einer Elektrohängebahn der eingangs genannten Art dadurch gelöst, dass

  • c) eine Anpresseinrichtung vorgesehen ist, welche derart mit dem zu transportierenden Gegenstand koppelbar ist, dass der Abstand zwischen der Drehachse der Antriebsrolle und der Antriebslauffläche der Tragschiene abhängig vom Gewicht des zu transportierenden Gegenstandes veränderbar ist; und dass
  • d) die Anpresseinrichtung (68; 168) eine die Antriebsrolle (36; 136) tragende Tragkonsole (40; 140) umfasst, welche ihrerseits um eine Schwenkachse (44; 144) verschwenkbar am Fahrwerk (24; 124) des Tragwagens (8; 108) gelagert und mit dem zu transportierenden Gegenstand koppelbar ist.
This object is achieved in an electric monorail of the type mentioned fact that
  • c) a pressing device is provided which can be coupled to the object to be transported such that the distance between the axis of rotation of the drive roller and the drive running surface of the support rail is variable depending on the weight of the object to be transported; and that
  • d) the pressing device (68; 168) comprises a support bracket (40; 140) supporting the drive roller (36; 136), which in turn is pivotable about a pivot axis (44; 144) on the chassis (24; 124) of the carrier wagon (8; ) and coupled with the object to be transported can be coupled.

Durch eine Verringerung des Abstandes zwischen der Drehachse der Antriebsrolle und der Tragschiene wird der Anpressdruck der Antriebsrolle gegen die Tragschiene erhöht. Erfindungsgemäß wird also dafür Sorge getragen, dass der Anpressdruck der Antriebsrolle gegen die Lauffläche der Tragschiene erhöht wird, wenn der Tragwagen mit gegenüber einer vorher transportierten Last schwererem Transportgut beladen wird. Umgekehrt wird der Anpressdruck verringert, wenn der Tragwagen mit gegenüber einer vorher transportierten Last leichterem Transportgut beladen wird.By reducing the distance between the axis of rotation of the drive roller and the support rail of the contact pressure of the drive roller is increased against the support rail. According to the invention so care is taken that the contact pressure of the drive roller is increased against the tread of the support rail when the carrier car is loaded with respect to a previously transported load heavier cargo. Conversely, the contact pressure is reduced when the wagon is loaded with respect to a previously transported load lighter cargo.

Im Hinblick auf die Anpresseinrichtung ist es erfindungsgemäss vorgesehen, dass diese eine die Antriebsrolle tragende Tragkonsole umfasst, welche ihrerseits um eine Schwenkachse verschwenkbar am Fahrwerk des Tragwagens gelagert und mit dem zu transportiererenden Gegenstand koppelbar ist.With regard to the pressing device, it is provided according to the invention that this comprises a supporting console carrying the drive roller, which in turn is pivotably mounted about a pivot axis on the chassis of the carrier and can be coupled to the object to be transported.

Dadurch ist die Antriebsrolle auf einfache Weise so gelagert, dass ihr Abstand, und damit auch der Abstand ihrer Drehachse, gegenüber der Tragschiene verändert werden kann.As a result, the drive roller is mounted in a simple manner so that their distance, and thus the distance between their axis of rotation, relative to the mounting rail can be changed.

Vorteilhafte Weiterbildungen sind in den abhängigen Ansprüchen angegeben.Advantageous developments are specified in the dependent claims.

Es ist insbesondere vorteilhaft, wenn die Anpresseinrichtung ein Schwenkelement umfasst, welches an dem Fahrwerk um eine horizontale Schwenkachse verschwenkbar gelagert und an einem freien Abschnitt mit dem zu transportierenden Gegenstand verbindbar ist, wobei das Schwenkelement mit einer Koppeleinrichtung zusammenarbeitet, durch welche eine Verschwenkbewegung des Schwenkelements auf die Tragkonsole übertragen wird, so dass die Tragkonsole in Richtung auf die Tragschiene verschwenkt. Durch diese Ausbildung ist es möglich, dass das Ausmaß, in welchem das Schwenkelement verschwenkt und in welchem diese Verschwenkbewegung auf die Tragkonsole übertragen wird, von dem Gewicht des zu transportierenden Gegenstandes abhängt.It is particularly advantageous if the pressing device comprises a pivoting element, which is pivotally mounted on the chassis about a horizontal pivot axis and connectable at a free portion with the object to be transported, wherein the pivoting element cooperates with a coupling device through which a pivoting movement of the pivoting element the support bracket is transmitted, so that the support bracket pivoted in the direction of the support rail. With this design, it is possible that the extent to which pivots the pivot member and in which this pivoting movement is transmitted to the support bracket depends on the weight of the object to be transported.

Dabei ist es günstig, wenn die Koppeleinrichtung wenigstens ein Koppelglied umfasst, welches mit der Tragkonsole verbunden ist. An dieses Koppelglied kann das Schwenkelement anliegen und so seine Bewegung auf die Koppeleinrichtung übertragen.It is advantageous if the coupling device comprises at least one coupling member which is connected to the support bracket. At this coupling member may abut the pivot member and so transmit its movement to the coupling device.

Bei einem Ausführungsbeispiel ist das Schwenkelement vorzugsweise ein Wippenelement, welches zwischen einem ersten und einem zweiten Wippenabschnitt gelagert ist und an dem ersten freien Wippenabschnitt mit dem zu transportierenden Gegenstand verbindbar ist, wobei durch den zweiten freien Wippenabschnitt des Wippenelements eine Kraft auf das Koppelglied ausgeübt wird, wenn das Wippenelement verschwenkt. Durch das Gewicht des mit dem Wippenelement verbundenen Gegenstandes wird das Wippenelement verschwenkt und überträgt eine Kraft auf die Koppeleinrichtung und damit im Hinblick auf die Anpresskraft auch auf die Antriebsrolle, die von dem Gewicht des Gegenstandes abhängt.In one embodiment, the pivoting element is preferably a rocker element which is mounted between a first and a second rocker section and is connectable to the first free rocker section with the object to be transported, wherein a force is exerted on the coupling element by the second free rocker section of the rocker element, when the rocker element pivots. Due to the weight of the article connected to the rocker element, the rocker element is pivoted and transmits a force to the coupling device and thus in terms of the contact pressure on the drive roller, of the Weight of the object depends.

Bei einem alternativen Ausführungsbeispiel ist das Schwenkelement vorzugsweise ein Hebelelement, welches an einem ersten Ende verschwenkbar an dem Fahrwerk gelagert ist, wobei die Schwenkachse des Schwenkelements senkrecht zur Tragschiene verläuft, und an seinem gegenüberliegenden, nach unten weisenden Ende mit dem zu transportierenden Gegenstand verbindbar ist, wobei durch das Hebelelement eine Kraft auf das Koppelglied ausgeübt wird, wenn das Hebelelement verschwenkt. Bei Verwendung eines solchen Hebelelements ist es möglich, dass insbesondere bei einer Steigungs- oder Gefällefahrt der Anpressdruck der Antriebsrolle gegen die Tragschiene nicht nur abhängig vom Gewicht des zu transportierenden Gegenstandes erhöht wird, indem der Abstand der Drehachse der Antriebsrolle zur Tragschiene verringert wird. Der Anpressdruck der Antriebsrolle gegen die Tragschiene wird in diesem Fall auch abhängig von dem Neigungswinkel der Steigung oder des Gefälles der Tragschiene erhöht.In an alternative embodiment, the pivoting element is preferably a lever element, which is pivotably mounted on the chassis at a first end, wherein the pivot axis of the pivoting element is perpendicular to the mounting rail, and at its opposite, downwardly facing end is connectable to the object to be transported, wherein a force is exerted on the coupling member by the lever member when the lever member pivots. When using such a lever element, it is possible that, in particular in a gradient or downward travel, the contact pressure of the drive roller against the mounting rail is not only increased depending on the weight of the object to be transported by the distance of the axis of rotation of the drive roller is reduced to the mounting rail. The contact pressure of the drive roller against the support rail is increased in this case also depending on the inclination angle of the slope or the slope of the support rail.

Insbesondere, wenn die Koppeleinrichtung ein erstes Koppelglied und ein zweites Koppelglied umfasst und das Schwenkelement zwischen den Koppelgliedern angeordnet ist, kann der Anpressdruck sowohl bei Steigungs- als auch bei Gefällefahrten erhöht werden, da das Hebelelement so in jeder Verschwenkrichtung mit einem Koppelglied zusammenarbeitet.In particular, when the coupling device comprises a first coupling member and a second coupling member and the pivot member is disposed between the coupling members, the contact pressure can be increased both pitch and downhill, since the lever member so cooperates in each pivoting with a coupling member.

Ausführungsbeispiele der Erfindung werden nachfolgend anhand der Zeichnung näher erläutert. In dieser zeigen:

Figur 1
in einer Seitenansicht einen horizontalen Abschnitt einer Elektrohängebahn zum Transport von Gegenständen mit einem ersten Ausführungsbeispiel eines Tragwagens, an den ein Transportgehänge angehängt ist;
Figur 2
einen Schnitt durch die in Figur 1 gezeigte Elektrohängebahn entlang der dortigen Schnittlinie III-III, wobei die Tragschiene nicht gezeigt ist;
Figur 3
einen der Figur 2 entsprechenden Schnitt mit Tragschiene;
Figur 4
eine Seitenansicht der Elektrohängebahn nach den Figuren 1 bis 3, wobei der Tragwagen sich in einem Gefälleabschnitt befindet;
Figur 5
eine Seitenansicht der Elektrohängebahn nach den Figuren 1 bis 3, wobei der Tragwagen sich in einem Steigungsabschnitt befindet;
Figur 6
in einer Seitenansicht einen horizontalen Abschnitt der Elektrohängebahn mit einem zweiten Ausführungsbeispiel eines Tragwagens, an den ein Schleppwagen angehängt ist;
Figur 7
einen Schnitt durch die in Figur 6 gezeigte Elektrohängebahn entlang der dortigen Schnittlinie VIII-VIII, wobei die Tragschiene nicht gezeigt ist;
Figur 8
einen der Figur 7 entsprechenden Schnitt mit Tragschiene;
Figur 9
in einer Seitenansicht den horizontalen Abschnitt der Elektrohängebahn mit dem Tragwagen nach Figur 6, an welchen jedoch ein Transportgehänge angehängt ist;
Figur 10
eine Seitenansicht der Elektrohängebahn nach Figur 9, wobei der Tragwagen sich in einem Gefälleabschnitt befindet;
Figur 11
eine Seitenansicht der Elektrohängebahn nach Figur 9, wobei der Tragwagen sich in einem Steigungsabschnitt befindet.
Embodiments of the invention will be explained in more detail with reference to the drawing. In this show:
FIG. 1
in a side view of a horizontal portion of a monorail for transporting objects with a first embodiment of a trolley, to which a transport hanger is attached;
FIG. 2
a section through the in FIG. 1 shown overhead monorail along the section line III-III, wherein the support rail is not shown;
FIG. 3
one of the FIG. 2 corresponding section with mounting rail;
FIG. 4
a side view of the monorail after the FIGS. 1 to 3 wherein the wagon is located in a slope section;
FIG. 5
a side view of the monorail after the FIGS. 1 to 3 wherein the cart is in a pitch section;
FIG. 6
in a side view of a horizontal portion of the monorail system with a second embodiment of a trolley, to which a tow truck is attached;
FIG. 7
a section through the in FIG. 6 shown overhead monorail along the section line VIII-VIII, wherein the support rail is not shown;
FIG. 8
one of the FIG. 7 corresponding section with mounting rail;
FIG. 9
in a side view of the horizontal section of the monorail system with the wagon after FIG. 6 to which, however, a transport hanger is attached;
FIG. 10
a side view of the electric monorail after figure 9 wherein the wagon is located in a slope section;
FIG. 11
a side view of the electric monorail after FIG. 9 , wherein the wagon is located in a slope section.

Zunächst wird auf Figur 1 Bezug genommen. In dieser ist ein Ausschnitt einer Elektrohängebahn 2 gezeigt, welche eine Tragschiene 4, von der in Figur 1 ein horizontaler Abschnitt 6 gezeigt ist, und einen auf der Tragschiene 4 verfahrbaren Tragwagen 8 umfasst. Die Transportrichtung, in welcher zu förderndes Gut mittels der Elektrohängebahn 2 transportiert wird, ist in Figur 1 mit einem Pfeil 10 angedeutet.First, it will open FIG. 1 Referenced. In this a section of a monorail system 2 is shown, which a support rail 4, from the in FIG. 1 a horizontal section 6 is shown, and a movable on the support rail 4 carriage 8 includes. The transport direction, in which material to be conveyed is transported by means of the overhead monorail 2, is in FIG. 1 indicated by an arrow 10.

Die Tragschiene 4 ist in herkömmlicher Weise als I-Profil ausgeführt. Sie ist in an und für sich bekannter Weise an einer Deckenkonstruktion oder einem Stahlbau aufgehängt und verläuft über dem Niveau des Raumbodens. Die Tragschiene 4 hat eine nach oben weisende obere Lauffläche 12 und eine zum Boden weisende untere Lauffläche 14. Ferner hat die Tragschiene 4 zwei sich gegenüberliegende obere vertikale Führungslaufflächen 16, 18, eine unterhalb der oberen Führungslauffläche 16 angeordnete untere vertikale Führungslauffläche 20 und eine dieser gegenüberliegende vertikale Antriebslauffläche 22 (vgl. Figur 3). Die Führungslauffläche 18 verläuft in den Figuren 1, 4 und 5 jeweils hinter der Führungslauffläche 16 und der Zeichenebene.The support rail 4 is designed in a conventional manner as I-profile. It is suspended in a manner known per se on a ceiling construction or a steel structure and extends above the level of the room floor. Further, the support rail 4 has two opposing upper vertical guide surfaces 16, 18, a arranged below the upper guide surface 16 lower vertical guide surface 20 and one of these opposite vertical drive surface 22 (see. FIG. 3 ). The guide tread 18 extends in the FIGS. 1 . 4 and 5 behind the guide tread 16 and the drawing plane.

Entlang der Tragschiene 4 verlaufen nicht eigens gezeigte Schleifleitungen, welche der Stromversorgung des Tragwagens 8 sowie der Signalübermittlung zu diesem dienen. Derartige Schleifleitungen entsprechen dem Stand der Technik.Along the support rail 4 not specifically shown sliding lines, which serve the power supply of the carrier car 8 and the signal transmission to this. Such sliding lines correspond to the prior art.

Der Tragwagen 8 umfasst ein die Tragschiene 4 umgreifendes Fahrwerk 24. Dieses lagert an seiner Oberseite eine erste, dem Fahrwerk 24 in Transportrichtung 10 vorauseilende Tragrolle 26 und eine zweite, dem Fahrwerk 24 in Transportrichtung 10 nacheilende Tragrolle 28, welche auf der oberen Lauffläche 12 der Tragschiene 4 abrollen. Die beiden Tragrollen 26 und 28 nehmen zum einen die Last auf und verhindern zum anderen ein Verkippen des Tragwagens 8 um eine Achse senkrecht zur Tragschiene 4. Die Drehachsen der Tragrollen 26, 28 verlaufen in einer horizontalen Ebene senkrecht zur Tragschiene 4.This supports at its top a first, the chassis 24 in the transport direction 10 leading support roller 26 and a second, the chassis 24 in the transport direction 10 trailing support roller 28, which on the upper tread 12 of Unroll mounting rail 4. The two support rollers 26 and 28, on the one hand, take up the load and, on the other hand, prevent the support carriage 8 from tilting about an axis perpendicular to the support rail 4. The axes of rotation of the support rollers 26, 28 run in a horizontal plane perpendicular to the support rail 4.

Das Fahrwerk 24 lagert zudem zu beiden Seiten der Tragschiene 4 in an und für sich bekannter Weise vier seitliche obere Führungsrollen 30, welche sich um senkrecht zur oberen Lauffläche 12 der Tragschiene 4 verlaufende, in Figur 1 entsprechend vertikale Achsen drehen können und von denen jeweils zwei seitlich an den gegenüberliegenden oberen vertikalen Führungslaufflächen 16 und 18 abrollen.The chassis 24 also supports on both sides of the support rail 4 in a known manner four lateral upper guide rollers 30 which are perpendicular to the upper tread 12 of the support rail 4 extending, in FIG. 1 can rotate according to vertical axes and each of which two roll laterally at the opposite upper vertical guide surfaces 16 and 18.

Das Fahrwerk 24 lagert ferner zwei seitliche untere Führungsrollen 32, welche sich um Achsen drehen können, die parallel zu den Achsen der oberen Führungsrollen 30 verlaufen. Die unteren Führungsrollen 32 laufen auf der unteren Führungslauffläche 20 ab.The chassis 24 also supports two lateral lower guide rollers 32, which can rotate about axes that are parallel to the axes of the upper guide rollers 30. The lower guide rollers 32 run on the lower guide surface 20 from.

Eine dritte seitliche untere Führungsrolle 34 ist am Fahrwerk 24 entsprechend um eine Achse verdrehbar gelagert, die parallel zu den Achsen der oberen Führungsrollen 30 verläuft. Die dritte untere Führungsrolle 34 rollt auf der Antriebslauffläche 22 ab und ist gegenüber der unteren Führungsrolle 32 angeordnet, die in Transportrichtung 10 betrachtet vorne am Fahrwerk 24 gelagert ist.A third lateral lower guide roller 34 is rotatably mounted on the chassis 24 corresponding to an axis which extends parallel to the axes of the upper guide rollers 30. The third lower guide roller 34 rolls on the drive running surface 22 and is disposed opposite to the lower guide roller 32, which is viewed in the transport direction 10 is mounted front of the chassis 24.

Eine Antriebsrolle 36, welche um eine Drehachse 38 verdrehbar ist, die parallel zu den Drehachsen der Führungsrollen 30, 32 und 34 verläuft, rollt auf der Antriebslauffläche 22 der Tragschiene 4 ab. Die Drehachse 38 der Antriebsrolle 36 ist an einer Motorkonsole 40 gelagert, welche ihrerseits einen Elektromotor 42 trägt, der die Antriebsrolle 36 antreibt. Der Elektromotor 42 wird über die oben angesprochenen Schleifleitungen bestromt und angesteuert.A drive roller 36, which is rotatable about an axis of rotation 38 which runs parallel to the axes of rotation of the guide rollers 30, 32 and 34, rolls on the drive running surface 22 of the support rail 4. The axis of rotation 38 of the drive roller 36 is mounted on a motor console 40, which in turn carries an electric motor 42 which drives the drive roller 36. The electric motor 42 is energized and controlled via the above-mentioned sliding lines.

Bei dem Tragwagen 8 sind somit die Rollen, welche die zu transportierende Last aufnehmen, d.h. die Tragrollen 26 und 28, und die Rollen bzw. die einzelne Rolle, über welche der Tragwagen 8 angetrieben wird, d.h. hier die Antriebsrolle 36, funktionsmäßig voneinander getrennt ausgebildet.In the wagon 8 are thus the rollers which receive the load to be transported, i. the carrying rollers 26 and 28, and the rollers or the single roller over which the carrying carriage 8 is driven, i. here the drive roller 36, functionally separated from each other.

Die Motorkonsole 40 ist über eine Schwenkachse 44 verschwenkbar mit dem Fahrwerk 24 des Tragwagens 8 verbunden, welche parallel zur Drehachse 38 der Antriebsrolle 36, in Figur 1 somit vertikal, verläuft. Dadurch sind die Motorkonsole 40 sowie der Elektromotor 42 und die Antriebsrolle 36 relativ zum Fahrwerk 24 des Tragwagens 8 und zur Tragschiene 4 verschwenkbar.The engine console 40 is pivotable about a pivot axis 44 connected to the chassis 24 of the carrier carriage 8, which parallel to the axis of rotation 38 of the drive roller 36, in FIG. 1 thus vertically, runs. As a result, the motor console 40 and the electric motor 42 and the drive roller 36 relative to the chassis 24 of the support carriage 8 and the support rail 4 are pivotable.

An der Unterseite des Fahrwerks 24 ist ein Koppelglied 46 um eine Schwenkachse 48 verschwenkbar gelagert, welche parallel zur Schwenkachse 44 der Motorkonsole 40 verläuft. Das Koppelglied 46 erstreckt sich unterhalb der beiden unteren Führungsrollen 32 in seitliche Richtung von der Tragschiene 4 weg. Die Schwenkachse 48 des Koppelgliedes 46 ist auf der der Antriebslauffläche 22 gegenüberliegenden Seite der Tragschiene 4 angeordnet.On the underside of the chassis 24, a coupling member 46 is pivotally mounted about a pivot axis 48 which extends parallel to the pivot axis 44 of the engine console 40. The coupling member 46 extends below the two lower guide rollers 32 in the lateral direction of the support rail 4 away. The pivot axis 48 of the coupling member 46 is disposed on the drive running surface 22 opposite side of the support rail 4.

Auf der der Antriebsrolle 36 zugewandten Seite der Schwenkachse 48 des Koppelgliedes 46 trägt dieses eine Nocke 50, welche in eine Aussparung 52 der Motorkonsole 40 eingreift.On the drive roller 36 facing side of the pivot axis 48 of the coupling member 46, this carries a cam 50 which engages in a recess 52 of the motor console 40.

In Transportrichtung 10 vor dem Koppelglied 46 lagert das Fahrwerk 24 ein Wippenglied 54, welches um eine horizontale und senkrecht zur Transportrichtung 10 verlaufende Wippenachse 56 verschwenkbar ist. An das freie Ende eines in Transportrichtung 10 weisenden ersten freien und geradlinigen Wippenabschnitts 58 ist ein Transportgehänge 60 über eine nicht eigens mit einem Bezugszeichen versehene horizontale und senkrecht zur Tragschiene 4 verlaufende Schwenkachse angelenkt, in welches zu fördernde Gegenstände eingebracht werden können. Die Längsachsen dieser Schwenkachse und der Wippenachse 56 liegen in einer gemeinsamen horizontalen Ebene, wenn sich der Tragwagen 8 in einem horizontalen Abschnitt der Tragschiene 4 befindet, wie es in Figur 1 gezeigt ist.In the transport direction 10 in front of the coupling member 46, the chassis 24 supports a rocker member 54, which is pivotable about a horizontal and perpendicular to the transport direction 10 rocker axis 56. At the free end of a pointing in the transport direction 10 first free and rectilinear rocker section 58, a transport hanger 60 is articulated via a not specifically provided with a reference numeral horizontal and perpendicular to the support rail 4 extending pivot axis, in which to be conveyed objects can be introduced. The longitudinal axes of this pivot axis and the rocker axis 56 lie in a common horizontal plane when the carriage 8 is in a horizontal portion of the support rail 4, as in FIG. 1 is shown.

Der dem ersten Wippenabschnitt 58 gegenüberliegende zweite Wippenabschnitt 62 ist als zweischenkliger 90°-Winkel ausgebildet, wobei dessen freier Schenkel 64 parallel zum ersten Wippenabschnitt 58 verläuft, jedoch diesem gegenüber nach unten versetzt ist. Der freie Schenkel 64 des zweiten Wippenglieds 62 trägt an der Stirnseite seines freien Endes einen Stößel 66, über welchen das Wippenglied 54 an dem Koppelglied 46 anliegt.The first rocker section 58 opposite second rocker section 62 is formed as a two-legged 90 ° angle, with its free leg 64 is parallel to the first rocker section 58, but this is offset from the bottom. The free leg 64 of the second rocker member 62 carries on the end face of its free end a plunger 66, via which the rocker member 54 rests against the coupling member 46.

Das Wippenglied 54, das Koppelglied 46 und die verschwenkbare Motorkonsole 40 bilden gemeinsam eine Anpresseinrichtung 68, mit welcher der Anpressdruck der Antriebsrolle 36 gegen die Antriebslauffläche 22 der Tragschiene 4 abhängig von der vom Tragwagen 8 getragenen Last eingestellt werden kann, indem der Abstand zwischen der Drehachse 38 der Antriebsrolle 36 und der Antriebslauffläche 22 der Tragschiene 4 verändert wird.The rocker member 54, the coupling member 46 and the pivotable motor console 40 together form a pressing device 68, with which the contact pressure of the drive roller 36 against the drive surface 22 of the support rail 4 can be adjusted depending on the load carried by the wagon 8 by the distance between the axis of rotation 38 of the drive roller 36 and the drive surface 22 of the support rail 4 is changed.

Durch das Gewicht des beladenen Transportgehänges 60 verschwenkt das Wippenglied 54 und drückt mit seinem Stößel 66 gegen das Koppelglied 46. Dadurch wird das Koppelglied 46 um seine Schwenkachse 48 verschwenkt. Dabei bewegt sich die Nocke 50 am Koppelglied 46 auf einem Kreisbogen bezogen auf die Transportrichtung 10 nach vorne und drückt gegen die Innenmantelfläche der Aussparung 52 an der Motorkonsole 40. Dadurch wird diese in Richtung des in Figur 2 zu erkennenden Pfeils 70 auf die Tragschiene 4 zu verschwenkt, wodurch der Abstand zwischen der Drehachse 38 der Antriebsrolle 36 und der Antriebslauffläche 22 der Tragschiene 4 verringert und die Antriebsrolle 36 stärker an die Antriebslauffläche 22 der Tragschiene 4 angepresst wird.Due to the weight of the loaded transport hanger 60 pivots the rocker member 54 and presses with its plunger 66 against the coupling member 46. As a result, the coupling member 46 is pivoted about its pivot axis 48. In this case, the cam 50 moves on the coupling member 46 on a circular arc with respect to the transport direction 10 forward and presses against the inner circumferential surface of the recess 52 on the motor console 40. As a result, this is in the direction of in FIG. 2 to be recognized arrow 70 to the support rail 4 to be pivoted, whereby the distance between the axis of rotation 38 of the drive roller 36 and the drive surface 22 of the support rail 4 is reduced and the drive roller 36 is pressed more strongly against the drive surface 22 of the support rail 4.

Je größer das Gewicht des mit zu fördernden Gegenständen beladenen Transportgehänges 60 ist, desto größer ist der Anpressdruck der Antriebsrolle 36 gegen die Tragschiene 4.The greater the weight of the transport hanger 60 loaded with articles to be conveyed, the greater the contact pressure of the drive roller 36 against the mounting rail 4.

Mit dem oben erläuterten Tragwagen 8 sind zudem sowohl Steigungs- als auch Gefällefahrten möglich, was in den Figuren 4 und 5 gezeigt ist. In Figur 4 ist ein in Transportrichtung 10 nach unten geneigter Abschnitt 72 und in Figur 5 ein in Transportrichtung 10 nach oben geneigter Abschnitt 74 der Tragschiene 4 gezeigt. In der Darstellung der Figuren 4 und 5 ist das Wippenglied 54 zur Verdeutlichung von dessen Schwenkbewegung wesentlich stärker verschwenkt gezeigt, als dies in der Praxis der Fall ist. Durch die von dem Gewicht des beladenen Transportgehänges 60 abhängige Erhöhung des Anpressdruckes der Antriebsrolle 36 gegen die Tragschiene 4 können von dem Tragwagen 8 insbesondere mit hohen Lasten auch Steigungen oder Gefällstrecken mit großem Neigungswinkel überwunden werden, ohne dass es zu einem Durchrutschen der Antriebsrolle 36 kommt.With the above-described wagon 8 also both slope and downhill rides are possible, which in the FIGS. 4 and 5 is shown. In FIG. 4 is a downwardly inclined in the transport direction 10 section 72 and in FIG. 5 a in the transport direction 10 upwardly inclined portion 74 of the support rail 4 shown. In the presentation of the FIGS. 4 and 5 the rocker member 54 is shown significantly more pivoted to illustrate its pivotal movement, as is the case in practice. By dependent on the weight of the loaded transport hanger 60 increase the contact pressure of the drive roller 36 against the support rail 4 can be overcome by the wagon 8 in particular with high loads and gradients or slopes with large inclination angle, without causing the drive roller 36 to slip.

In den Figuren 6 bis 8 ist als zweites Ausführungsbeispiel eine Elektrohängebahn 102 gezeigt. Dort tragen Komponenten, die denjenigen der Elektrohängebahn 2 entsprechen, dieselben Bezugszeichen zuzüglich 100.In the FIGS. 6 to 8 is shown as a second embodiment, a monorail system 102. There carry components that correspond to those of the monorail system 2, the same reference numerals plus 100th

Die Elektrohängebahn 102 unterscheidet sich von der Elektrohängebahn 2 in der Ausbildung der Anpresseinrichtung 168. Anstelle des Wippengliedes 54 ist dort eine Hebelstange 172 vorgesehen. Diese ist an ihrem einem Lagerende über eine Hebelachse 174, welche in ihrer Ausrichtung und Position bezogen auf das Fahrwerk 124 des Tragwagens 108 mit der Wippenachse 56 übereinstimmt, an dem Fahrwerk 124 gelagert. An der Stirnseite des freien Endes eines ersten Seitenarms 176 der Hebelstange 172 ist ein Stößel 166 angebracht, welcher an dem Koppelglied 146 anliegt, wie es bei dem Stößel 66 und dem Koppelglied 46 der Anpresseinrichtung 68 der Fall ist.The monorail 102 differs from the monorail 2 in the formation of the pressing device 168. Instead of the rocker member 54, a lever rod 172 is provided there. This is at its one end of the bearing via a lever axis 174, which coincides in their orientation and position relative to the chassis 124 of the support carriage 108 with the rocker axis 56, mounted on the chassis 124. On the front side of the free end of a first side arm 176 of the lever rod 172, a plunger 166 is mounted, which rests against the coupling member 146, as is the case with the plunger 66 and the coupling member 46 of the pressing device 68.

Auf der dem ersten Seitenarm 176 gegenüberliegenden Seite weist die Hebelstange 172 einen zweiten Seitenarm 178 auf, welcher koaxial zum ersten Seitenarm 176 verläuft und an der Stirnseite seines freien Endes einen zweiten Stößel 180 trägt, der in Transportrichtung 110 weist.On the opposite side of the first side arm 176 The lever rod 172 has a second side arm 178 which runs coaxially with the first side arm 176 and carries on the end face of its free end a second plunger 180, which points in the transport direction 110.

Der zweite Stößel 180 liegt an einem zweiten Koppelglied 182 an, welches sich parallel zum ersten Koppelglied 146 erstreckt und starr mit der Motorkonsole 140 des Fahrwerks 124 verbunden ist.The second plunger 180 abuts against a second coupling member 182, which extends parallel to the first coupling member 146 and is rigidly connected to the engine console 140 of the chassis 124.

Am ihrem dem Lagerende gegenüberliegenden Tragende 173 ist die Hebelstange 172 über eine Schleppstange 184 gelenkig mit einem Schleppwagen 186 verbunden, welcher in an und für sich bekannter Weise auf dem Boden abrollt.At its end opposite the bearing end 173, the lever rod 172 is connected via a tow bar 184 articulated to a tow truck 186, which rolls in a manner known per se on the ground.

Die Anpresseinrichtung 168 ist durch die Hebelstange 172, das erste und das zweite Koppelglied 146 und 182 und die verschwenkbare Motorkonsole 140 gebildet. Durch die Anpresseinrichtung 168 wird der Anpressdruck der Antriebsrolle 136 gegen die Antriebslauffläche1 22 der Tragschiene 104 abhängig von der vom Schleppwagen 184 getragenen Last eingestellt.The pressing device 168 is formed by the lever rod 172, the first and the second coupling member 146 and 182 and the pivotable motor console 140. By the pressing device 168, the contact pressure of the drive roller 136 against the Antriebslauffläche1 22 of the support rail 104 is adjusted depending on the load carried by the tractor 184 load.

Durch die Trägheit und das Gewicht des beladenen Schleppwagens 184 verschwenkt die Hebelstange 172 bezogen auf die Transportrichtung 110 nach hinten und drückt mit ihrem Stößel 166 gegen das Koppelglied 146. Dadurch wird das Koppelglied 146 um seine Schwenkachse 148 verschwenkt. Dabei bewegt sich die Nocke 150 am Koppelglied 146 auf einem Kreisbogen bezogen auf die Transportrichtung 10 nach vorne und drückt gegen die Innenmantelfläche der Aussparung 152 an der Motorkonsole 140. Dadurch wird diese in Richtung des in Figur 7 zu erkennenden Pfeils 170 auf die Tragschiene 104 zu verschwenkt, wodurch die Antriebsrolle 136 an die Antriebslauffläche1 22 der Tragschiene 104 angepresst wird.Due to the inertia and the weight of the loaded tow truck 184 pivots the lever rod 172 relative to the transport direction 110 to the rear and pushes with its plunger 166 against the coupling member 146. As a result, the coupling member 146 is pivoted about its pivot axis 148. In this case, the cam 150 moves on the coupling member 146 on a circular arc with respect to the transport direction 10 to the front and presses against the inner surface of the recess 152 on the motor console 140. Thus, this in the direction of the arrow 170 to be recognized in Figure 7 on the mounting rail 104 to pivoted, whereby the drive roller 136 is pressed against the Antriebslauffläche1 22 of the support rail 104.

Darüber hinaus wird durch die Anpresseinrichtung 168 der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 erhöht, wenn der Tragwagen 108 beschleunigt oder verzögert wird. Bei einer Beschleunigung des Tragwagens 108 verschwenkt die Hebelstange 172 auf Grund der Trägheit des an diese angelenkten Schleppwagens 186 so um ihre Hebelachse 174, dass sich der Stößel 166 in Richtung auf das Koppelglied 146 bewegt. Dies führt in der oben erläuterten Weise dazu, das die Antriebsrolle 136 stärker gegen die Tragschiene 104 angepresst wird, wodurch ein Durchrutschen der Antriebsrolle 136 beim Beschleunigen des Tragwagens 108 unterbunden ist.In addition, the contact pressure of the drive roller 136 is increased by the pressing device 168 against the support rail 104 when the carriage 108 is accelerated or decelerated. Upon acceleration of the support carriage 108 pivots the lever rod 172 due to the inertia of the hinged to these tow truck 186 about its lever axis 174 that the plunger 166 moves in the direction of the coupling member 146. This leads in the manner explained above to the fact that the drive roller 136 is pressed more strongly against the support rail 104, whereby slippage of the drive roller 136 during acceleration of the support carriage 108 is prevented.

Bei einer Verzögerung des Tragwagens 108 schiebt der Schleppwagen 186 die Hebelstange 172 auf Grund seiner Trägheit bezogen auf die Transportrichtung 110 nach vorne, so dass sich der zweite Stößel 180 am zweiten Seitenarm 178 der Hebelstange 172 in Richtung des Pfeils 170 in Figur 7 auf das zweite Koppelglied 182 bewegt. Durch den auf das zweite Koppelglied 182 ausgeübten Druck wird die Motorkonsole 140 mit der Antriebsrolle 136 um ihre Schwenkachse 144 in Richtung auf die Tragschiene 104 geschwenkt, wodurch der Anpressdruck der Antriebsrolle 136 gegen die Antriebslauffläche 122 der Tragschiene 104 erhöht und ein Durchrutschen der Antriebsrolle 136 verhindert wird.In a delay of the cart 108 of the tractor 186 pushes the lever rod 172 due to its inertia relative to the transport direction 110 forward so that the second plunger 180 on the second side arm 178 of the lever rod 172 in the direction of arrow 170 in FIG. 7 moved to the second coupling member 182. By the force exerted on the second coupling member 182 pressure, the motor console 140 is pivoted to the drive roller 136 about its pivot axis 144 in the direction of the support rail 104, whereby the contact pressure of the drive roller 136 against the drive surface 122 of the support rail 104 increases and prevents slippage of the drive roller 136 becomes.

Bei einer hier nicht eigens gezeigten Steigungsfahrt in einem in Transportrichtung gegenüber einer horizontalen Ebene nach oben geneigten Abschnitt der Tragschiene 104 wird die Hebelstange 172 auf Grund der durch die Steigung zusätzlich auf die Hebelstange 172 wirkenden Gewichtskraft des Schleppwagens 186 verschwenkt, wie es bei einer Beschleunigung des Transportwagens 108 der Fall ist. Dadurch wird die Antriebsrolle 136 stärker gegen die Tragschiene 104 gepresst, wobei der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 bei gleichem Neigungswinkel der Tragschiene 104 umso stärker wird, je größer das Gewicht des beladenen Schleppwagens 186 ist. In entsprechender Weise erhöht sich der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 mit zunehmendem Neigungswinkel des Steigungsabschnitts.In a not shown here slope ride in a direction of transport relative to a horizontal plane upwardly inclined portion of the support rail 104, the lever rod 172 is pivoted due to the addition of the slope on the lever rod 172 weight force of the towing vehicle 186, as in an acceleration of the Dolly 108 is the case. As a result, the drive roller 136 is pressed more strongly against the support rail 104, wherein the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 becomes stronger the greater the weight of the loaded towed carriage 186. In a corresponding manner, the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the pitch section.

Bei einer hier ebenfalls nicht eigens gezeigten Gefällefahrt in einem in Transportrichtung gegenüber einer horizontalen Ebene nach unten geneigten Abschnitt der Tragschiene 104 wird die Hebelstange 172 auf Grund der durch des Gefälles zusätzlich auf die Hebelstange 172 wirkenden Gewichtskraft des Schleppwagens 186 verschwenkt, wie es bei einer Verzögerung des Transportwagens 108 der Fall ist. Dadurch wird die Antriebsrolle 136 stärker gegen die Tragschiene 104 gepresst, wobei der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 bei gleichem Neigungswinkel der Tragschiene 104 umso stärker wird, je größer das Gewicht des beladenen Schleppwagens 186 ist. In entsprechender Weise erhöht sich der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 mit zunehmendem Neigungswinkel des Gefälleabschnitts.In a here also not specifically shown downhill ride in a direction of transport relative to a horizontal plane downwardly inclined portion of the support rail 104, the lever rod 172 is pivoted due to the force acting on the lever rod 172 by gravity additional weight of the tow truck 186, as in a delay of the trolley 108 is the case. Characterized the drive roller 136 is pressed stronger against the support rail 104, wherein the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 is stronger, the greater the weight of the loaded tow truck 186. In a corresponding manner, the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the slope section.

Wenn an den Tragwagen 108 anstelle des Schleppwagens 186 ein Transportgehänge 160 angehängt ist, wie es in den Figuren 9 bis 11 gezeigt ist, erfolgt bei einer in den Figuren 10 bzw. 11 veranschaulichten Gefälle- bzw. Steigungsfahrt in entsprechender Weise eine Erhöhung des Anpressdruckes der Antriebsrolle 136 an die Tragschiene 104, da in diesem Fall die Gewichtskraft des beladenen Transportgehänges 160 die Hebelstange 172 stets in eine vertikale Lage bringen würde, wenn diese frei verschwenken könnte. Die von dem Transportgehänge 160 ausgeübte Gewichtskraft wird jedoch über die Hebelstange 172 auf eines der Koppelglieder 146 oder 182 übertragen, was wiederum zur erörterten Erhöhung des Anpressdruckes der Antriebsrolle 136 gegen die Tragschiene 104 führt. Auch bei einem Transportgehänge 160 wird der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 bei gleichem Neigungswinkel der Tragschiene 104 umso stärker, je größer das Gewicht des beladenen Transportgehänges 160 ist. In entsprechender Weise erhöht sich der Anpressdruck der Antriebsrolle 136 gegen die Tragschiene 104 mit zunehmendem Neigungswinkel des Steigungs- bzw. Gefälleabschnitts.If a transport hanger 160 is attached to the wagon 108 instead of the tow truck 186, as it is in the FIGS. 9 to 11 is shown at one in the Figures 10 11 and 11 gradient or incline travel in a corresponding manner an increase of the contact pressure of the drive roller 136 to the support rail 104, since in this case the weight of the loaded transport hanger 160 would bring the lever rod 172 always in a vertical position, if this could pivot freely , However, the force exerted by the transport hanger 160 weight is transmitted via the lever rod 172 on one of the coupling members 146 or 182, which in turn for the discussed increase of the contact pressure the drive roller 136 leads against the support rail 104. Even with a transport hanger 160, the contact pressure of the drive roller 136 against the support rail 104 at the same inclination angle of the support rail 104 becomes stronger the greater the weight of the loaded transport hanger 160. In a corresponding manner, the contact pressure of the drive roller 136 against the support rail 104 increases with increasing inclination angle of the slope or slope section.

In einem horizontalen Abschnitt 106 der Tragschiene 104 bewirkt das Transportgehänge 160 bei dem Tragwagen 108 keine Erhöhung des Anpressdruckes der Antriebsrolle 136 gegen die Tragschiene 104. In horizontalen Bereichen wird der Anpressdruck der Antriebsrolle 136 daher durch die Bauart des Tragwagens 108 oder ergänzende Maßnahmen, wie beispielsweise durch eine Federvorspannung der Antriebsrolle 136 gegen die Tragschiene 104, vorgegeben.In a horizontal portion 106 of the support rail 104 causes the Transportgehänge 160 in the wagon 108 no increase of the contact pressure of the drive roller 136 against the support rail 104. In horizontal areas of the contact pressure of the drive roller 136 is therefore by the design of the trolley 108 or additional measures, such as by a spring bias of the drive roller 136 against the support rail 104, predetermined.

Claims (6)

  1. Electric overhead conveyor for transporting articles, having
    a) a support rail (4; 104) which comprises a drive running surface (22; 122) which always extends vertically regardless of a gradient or pitch of the support rail (4; 104);
    b) at least one support carriage (8; 108) having a load-bearing chassis (24; 124), wherein the chassis (24; 124) comprises at least one driven drive roller (36; 136) which rolls on the vertical drive running surface (22; 122) of the support rail (4; 104);
    characterized in that
    c) a pressing device (68; 168) is provided, which is able to be coupled to the article to be transported such that the spacing between the rotary pin (38; 138) of the drive roller (36; 136) and the drive running surface (22; 122) of the support rail (4; 104) is variable depending on the weight of the article to be transported; and in that
    d) the pressing device (68; 168) comprises a support bracket (40; 140) supporting the drive roller (36; 136), said support bracket (40; 140) for its part being mounted on the chassis (24; 124) of the support carriage (8; 108) so as to be pivotable about a pivot pin (44; 144) and being able to be coupled to the article to be transported.
  2. Electric overhead conveyor according to Claim 1, characterized in that the pressing device (68; 168) comprises a pivoting element (54; 172) which is mounted on the chassis (24; 124) so as to be pivotable about a horizontal pivot pin (56; 174) and is connectable by a free portion (58; 173) to the article to be transported, wherein the pivoting element (54; 172) cooperates with a coupling device (46, 50, 52; 146, 150, 152, 182), by way of which a pivoting movement of the pivoting element (54; 172) is transmitted to the support bracket (40; 140) such that the support bracket (40; 140) pivots in the direction of the support rail (4; 104).
  3. Electric overhead conveyor according to Claim 2, characterized in that the coupling device (46, 50, 52; 146, 150, 152, 182) comprises at least one coupling member (46; 146, 182) which is connected to the support bracket (40; 140).
  4. Electric overhead conveyor according to Claim 3, characterized in that the pivoting element (54) is a rocker element (54) which is mounted between a first and a second rocker portion (58, 62) and is able to be connected by way of the first free rocker portion (58) to the article to be transported, wherein a force is exerted on the coupling member (46) by the second free rocker portion (62) of the rocker element (54) when the rocker element (54) pivots.
  5. Electric overhead conveyor according to Claim 3, characterized in that the pivoting element (172) is a lever element (172) which is mounted on the chassis (124) so as to be pivotable at a first end, wherein the pivot pin (174) of the pivoting element (172) extends perpendicularly to the support rail (104), and is connectable by way of its opposite, downwardly directed end (173) to the article to be transported, wherein a force is exerted on the coupling member (146, 182) by the lever element (172) when the lever element (172) pivots.
  6. Electric overhead conveyor according to Claim 5, characterized in that the coupling device (146, 150, 152, 182) comprises a first coupling member (146) and a second coupling member (182), and the lever element (172) is arranged between the coupling members (146, 182).
EP09011859.7A 2008-10-01 2009-09-17 Electric overhead conveyor Active EP2172380B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810049975 DE102008049975A1 (en) 2008-10-01 2008-10-01 Electric monorail

Publications (2)

Publication Number Publication Date
EP2172380A1 EP2172380A1 (en) 2010-04-07
EP2172380B1 true EP2172380B1 (en) 2017-03-08

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ID=41490370

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Application Number Title Priority Date Filing Date
EP09011859.7A Active EP2172380B1 (en) 2008-10-01 2009-09-17 Electric overhead conveyor

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DE (1) DE102008049975A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010055348B4 (en) 2010-12-20 2016-09-22 Eisenmann Se Transfer device for trolley and conveyor system with such
EP2487086B1 (en) 2011-02-14 2013-10-30 Siemens Aktiengesellschaft Electric track, in particular electric overhead track
DE102014010556B4 (en) 2014-07-16 2020-02-27 Eisenmann Se Drive car for a transport device and transport system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1097033A (en) 1963-06-19 1967-12-29 Becorit Res Ltd Improvements in and relating to vehicles adapted to run on a track such as for example for use in underground transport systems
GB1248490A (en) 1969-05-21 1971-10-06 Projects General Of America An improved monorail system and a vehicle therefor
DE2045659A1 (en) 1970-09-16 1972-03-23 Stierlen Werke Ag Conveyor with overhead trolleys
GB1469237A (en) * 1973-05-30 1977-04-06 Benndahl L Conveyor system including an overhead rail and a number of self propelled driving units
DE4209565C2 (en) 1992-03-20 1995-01-19 Mannesmann Ag Trolley, especially monorail with a short height
DE19713500C1 (en) 1997-03-17 1998-09-24 Mannesmann Ag Chassis of a lifting device that can be moved by rail

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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DE102008049975A1 (en) 2010-04-22
EP2172380A1 (en) 2010-04-07

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