EP0822872B2 - Roll stand - Google Patents

Roll stand Download PDF

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Publication number
EP0822872B2
EP0822872B2 EP96910844A EP96910844A EP0822872B2 EP 0822872 B2 EP0822872 B2 EP 0822872B2 EP 96910844 A EP96910844 A EP 96910844A EP 96910844 A EP96910844 A EP 96910844A EP 0822872 B2 EP0822872 B2 EP 0822872B2
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EP
European Patent Office
Prior art keywords
toothed
drive
coupling
spindle
component
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Expired - Lifetime
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EP96910844A
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German (de)
French (fr)
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EP0822872B1 (en
EP0822872A1 (en
Inventor
Rudolf Buchegger
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Primetals Technologies Austria GmbH
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Voest Alpine Industrienlagenbau GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
    • B21B35/142—Yielding spindle couplings; Universal joints for spindles
    • B21B35/143—Yielding spindle couplings; Universal joints for spindles having slidably-interengaging teeth, e.g. gear-type couplings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
    • B21B35/148—Spindle carriers or balancers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
    • B21B35/142—Yielding spindle couplings; Universal joints for spindles
    • B21B35/145—Hooke's joints or the like with each coupling part pivoted with respect to an intermediate member

Definitions

  • the invention relates to a rolling mill with two rolls forming a nip, the over Drive spindles are driven by their own drive motors, in particular quarto-framework, wherein for each roller in each case a drive train, each with a toothed coupling combined with another joint coupling is used.
  • the arrangement requires two drive motors - a so-called Twin drive - due to the large center distance of the motor drive shafts large diffraction angles of the drive spindles or, if one wants to avoid such correspondingly long drive spindles, but this would give a rotary soft drive.
  • a rolling mill is known in which the rollers each have a first toothed coupling with a first shaft and a second toothed coupling with a Connecting shaft and continue via a universal joint with a propeller shaft and another Universal joint is connected to a drive motor or another propeller shaft.
  • the Connecting shafts are in an adjustable guide in parallel arrangement stored. As a result, must be taken by the gear couplings relatively large angle be, because there must be a sufficiently large distance between the at the Connecting shafts arranged universal joints are created. This increases significantly the wear of the toothed couplings.
  • Another disadvantage of the known rolling mill is to see that the distance between the engine and roll stand is very large, which is a space consuming drive arrangement results. This also results in too soft Torque transmission from the drive motors to the work rolls.
  • the invention aims to avoid these disadvantages and difficulties and arises the task of creating a rolling stand, which also applies to rolls with small diameters and on the other hand a relatively large center distance of the motor drive shafts Drive spindles can be provided with a large diffraction angle - and so that with a relatively short length - can be arranged, but still very much high drive torques can be transmitted, for example, for rolling high-strength Rolled and rolled with large Stichief discretion.
  • This construction is particularly space-saving and enables optimal moments Dimensioning even with very narrow center distances of the rollers.
  • the toothed couplings crowned collaboratever leopardept on wherein to achieve a axial mobility of the driven rollers themselves the internal teeth of the toothed couplings in the axial direction over a multiple of the external toothing extend.
  • the optimal pressure angle of the Gear coupling i. the optimal angle between the Axle of the roller and its associated toothed spindle especially when changing the roll gap, is the part movable relative to a roller the toothed coupling of the toothed spindle, with the cardan shaft is connected via a balancing device to comply with a predetermined angular position on Foundation supported, with the compensation device from a trained as a lever system parallel guide is formed.
  • Fig. 1 is a Schrägrißansicht and Fig. 2 a through the axes of the drive spindles laid vertical section of a detail of FIG. 1 of an embodiment.
  • the only a relatively small diameter 10 having work rolls 1, 2 are each over a own drive spindle 11, 12 by means of its own Drive motor 13, 14 drivable.
  • the arrangement of Drive motors 13, 14 is made such that the Center distance 15 of the drive shafts 16 of the drive motors 13, 14 is as low as possible.
  • the drive spindles 11, 12 to each other arranged inclined.
  • each drive pin 4, 5 the work rolls 1, 2 rotatably connected to a sleeve 17, which has an internal toothing 18.
  • Internal toothing 18 engages a convex outer toothing 19, the outside of another sleeve 20 is arranged, a.
  • the sleeves 17 and 20 thus form one toothed coupling each.
  • the length of the internal toothing 18 is many times longer than the teeth of the External teeth 19, so that an axial mobility is possible.
  • the work rolls 1, 2 in Axial direction relative to the roll stand 7 shifted become. Different axial layers of the work rolls 1, 2 are shown in Fig. 2.
  • Sleeves 20 are each rotationally fixed to a spindle 21 and 22 mounted and form together with this spindle 21st or 22 a so-called toothed spindle.
  • the universal joints 24 could also be provided other articulated couplings to be high in transmission Torques are suitable, for example, flat-pin couplings.
  • the drive spindle 11 of the lower work roll 1 is up to the drive shaft 16 of the lower Drive motor 13 rigid formed and with the drive shaft 16th of the lower drive motor 13 via a toothed coupling 24 'coupled.
  • the axial positions of the toothed spindles 20, 21 and 20, 22 are chosen so that their axes with the axes of the associated work rolls 1, 2 a Angle between 0.5 and 1.5 °, preferably an angle of about 0.8 °.
  • the parallel guide 25 is of a toggle lever system formed, u.zw. grab something vertically oriented Tabs 27 on one the upper toothed spindle 20, 22nd surrounding and opposite the toothed spindle 20, 22nd by means of rotary bearing 28 supported housing 29, which Housing 29 against rotation against the foundation 26 is.
  • the tabs 27 are each at one Angle lever 30 articulated, the knee joint 31 on Foundation 26 is rotatably supported.
  • the others Lever arms 32 of the angle lever 30 are connected via a pull or pressure-absorbing tab 33 connected.
  • the arrangement of the toothed spindles 20, 21 and 20, 22 is in this case made so that these in the direction of the drive motors 13, 14 diverge, causing it succeeds that the propeller shaft 23 with the toothed spindle 20, 22 connecting universal joint 24 with maximum size to design.
  • This is important insofar as the to be transmitted moment with the third power the diameter of the universal joints 24 and the cardan shaft 23 enlarged.
  • the drive motors 13, 14 a very large torque to transfer, u.zw. a much higher than according to the prior art, wherein as additional Advantage even a torsionally rigid drive is realized.
  • Another advantage results from installation a designed as a spring cup 37 spring damper element in the lever system of the parallel guide 25th This will dynamically act as bending forces Walzapfen acting forces, caused by the Vertical accelerations of the drive train during Rolling stock entry or exit, to a fraction of the reduced to conventional values.
  • the spring cup 37 can provided on any lever of the lever system become.
  • the spring-damper element adjustable by force.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Crushing And Grinding (AREA)
  • Straightening Metal Sheet-Like Bodies (AREA)
  • Transmission Devices (AREA)
  • Manipulator (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)

Abstract

PCT No. PCT/AT96/00078 Sec. 371 Date Oct. 24, 1997 Sec. 102(e) Date Oct. 24, 1997 PCT Filed Apr. 23, 1996 PCT Pub. No. WO96/33823 PCT Pub. Date Oct. 31, 1996A roll stand with two rolls forming a gap has each roll connected to a separate drive motor by a drive train having a spindle with a toothed coupling to the drive roll. One of the drive trains includes two components connected to each other by a flexible coupling permitting a large angular shaft displacement with one of the components connected by a second flexible coupling to the drive motor and the other drive train includes the drive spindle being formed by a single component coupled to the drive shaft of the motor by a toothed coupling.

Description

Die Erfindung betrifft ein Walzgerüst mit zwei einen Walzspalt bildenden Walzen, die über Antriebsspindeln von jeweils eigenen Antriebsmotoren antreibbar sind, insbesondere Quarto-Gerüst, wobei für jede Walze jeweils ein Antriebsstrang mit jeweils einer Zahnkupplung kombiniert mit einer weiteren Gelenkkupplung zur Anwendung gelangt.The invention relates to a rolling mill with two rolls forming a nip, the over Drive spindles are driven by their own drive motors, in particular quarto-framework, wherein for each roller in each case a drive train, each with a toothed coupling combined with another joint coupling is used.

Bei einem Walzgerüst bedingt die Anordnung von zwei Antriebsmotoren - ein sogenannter Zwillingsantrieb (twin drive) - infolge des großen Mittenabstandes der Motorantriebswellen große Beugungswinkel der Antriebsspindeln oder, falls man solche vermeiden will, entsprechend lange Antriebsspindeln, was jedoch einen drehweichen Antrieb ergäbe. Diese Problematik stellt sich insbesondere bei Quarto-Reversiergerüsten, bei denen der vertikale Verstellweg der oberen Arbeitswalze groß ist.In a rolling stand, the arrangement requires two drive motors - a so-called Twin drive - due to the large center distance of the motor drive shafts large diffraction angles of the drive spindles or, if one wants to avoid such correspondingly long drive spindles, but this would give a rotary soft drive. These Problems arise in particular in quarto Reversiergerüsten in which the vertical Adjustment of the upper work roll is large.

Für die Anordnung von Antriebsspindeln mit größerem Beugungswinkel ist es bekannt, Kardanwellen mit Kreuzgelenken vorzusehen. Solche Antriebsspindeln mit großen Beugungswinkeln haben jedoch den Nachteil, daß sie bei vorgegebenem Durchmesser der Kreuzgelenke - dieser kann infolge des relativ kleinen Durchmessers der Arbeitswalzen ein bestimmtes Ausmaß nicht überschreiten - nur relativ kleine Drehmomente übertragen können. Dies deshalb, weil man bei der Dimensionierung der Kreuzzapfen der Kreuzgelenke beschränkt ist; insbesondere bei größeren Winkelstellungen erfordern die Kreuzzapfen große Außendurchmesser der Kreuzgelenke.For the arrangement of drive spindles with a larger diffraction angle it is known Provide cardan shafts with universal joints. Such drive spindles with large However, diffraction angles have the disadvantage that they at a given diameter of the Universal joints - this can be due to the relatively small diameter of the work rolls not exceed a certain amount - can transmit only relatively small torques. This is because of the dimensioning of the cross pins of the universal joints is limited; especially with larger angular positions require the cross pin large Outer diameter of the universal joints.

Aus der JP-A - 60-37205 ist ein Walzgerüst bekannt, bei dem die Walzen jeweils über eine erste Zahnkupplung mit einer ersten Welle und über eine zweite Zahnkupplung mit einer Verbindungswelle und weiter über ein Kreuzgelenk mit einer Gelenkwelle und ein weiteres Kreuzgelenk mit einem Antriebsmotor oder einer weiteren Gelenkwelle verbunden ist. Die Verbindungswellen sind in einer justierbaren Führung in zueinander paralleler Anordnung gelagert. Hierdurch müssen von den Zahnkupplungen relativ große Winkel aufgenommen werden, denn es muß ein ausreichend großere Abstand zwischen den an den Verbindungswellen angeordneten Kreuzgelenken geschaffen werden. Dies erhöht wesentlich den Verschleiß der Zahnkupplungen. Ein weiterer Nachteil des bekannten Walzgerüstes ist darin zu sehen, daß der Abstand zwischen Motor und Walzgerüst sehr groß ist, was eine platzaufwendige Antriebsanordnung ergibt. Hierdurch ergibt sich auch eine zu weiche Momentenübertragung von den Antriebsmotoren zu den Arbeitswalzen. From JP-A-60-37205 a rolling mill is known in which the rollers each have a first toothed coupling with a first shaft and a second toothed coupling with a Connecting shaft and continue via a universal joint with a propeller shaft and another Universal joint is connected to a drive motor or another propeller shaft. The Connecting shafts are in an adjustable guide in parallel arrangement stored. As a result, must be taken by the gear couplings relatively large angle be, because there must be a sufficiently large distance between the at the Connecting shafts arranged universal joints are created. This increases significantly the wear of the toothed couplings. Another disadvantage of the known rolling mill is to see that the distance between the engine and roll stand is very large, which is a space consuming drive arrangement results. This also results in too soft Torque transmission from the drive motors to the work rolls.

Aus der JP-A - 61-193711 ist ein Walzgerüst der eingangs beschriebenen Art bekannt, das ähnlich dem in der JP-A - 60-37205 beschriebenen Walzgerüst gestaltet ist. Beide Walzen sind jeweils über eine Zahnkupplung mit einer ersten Welle und über eine größere winkelige Abweichungen zulassende Gelenkkupplung, wie ein Kreuzgelenk, mit einer Gelenkwelle und eine weitere solche Gelenkkupplung mit jeweils einem Antriebsmotor bzw. Getriebe verbunden. Jeder Antriebsstrang ist somit von zwei Gelenkwellen gebildet, wodurch sich infolge der einen großen Platz benötigenden Gelenkkupplungen für größere winkelige Ausnehmungen ein großer Abstand zwischen Motor und Walzgerüst ergibt, was mit dem Nachteil einer weichen Momentenübertragung von den Antriebsmotoren zu den Arbeitswalzen einhergeht. Durch die gemäß dem bekannten Walzgerüst einander gegenüberliegenden Kreuzgelenke ergeben sich große Neigungswinkel der Gelenkwellen zueinander, die von den Kreuzgelenken aufgenommen werden müssen. Hierdurch treten erhöhte Verschleißerscheinungen auf, so daß die Lebensdauer der Kreuzgelenke nicht sehr hoch ist. Weiters ist die bekannte Konstruktion mit einem intensiven Wartungsaufwand verbunden.From JP-A - 61-193711 a rolling stand of the type described above is known, the similar to the rolling stand described in JP-A-60-37205. Both rolls each have a gear coupling with a first shaft and a larger angular one Deviations permitting joint coupling, such as a universal joint, with a propeller shaft and another such universal joint, each with a drive motor or gearbox connected. Each driveline is thus formed by two propeller shafts, resulting in due to the large space requiring joint couplings for larger angular Recesses a large distance between the engine and rolling mill results, what with the Disadvantage of a soft torque transmission from the drive motors to the Work rolls goes hand in hand. By according to the known rolling mill each other opposite universal joints arise large inclination angle of the propeller shafts to each other, which must be absorbed by the universal joints. This occurs increased wear on, so that the life of the universal joints are not very is high. Furthermore, the known construction with an intensive maintenance connected.

Die Erfindung bezweckt die Vermeidung dieser Nachteile und Schwierigkeiten und stellt sich die Aufgabe, ein Walzgerüst zu schaffen, bei dem auch bei Walzen mit kleinen Durchmessern und einem demgegenüber relativ großen Mittelabstand der Motorantriebswellen Antriebsspindeln vorgesehen werden können, die mit einem großen Beugungswinkel - und damit mit relativ kurzer Baulänge - angeordnet werden können, wobei jedoch trotzdem sehr hohe Antriebsmomente übertragen werden können, beispielsweise zum Walzen hochfesten Walzgutes und zum Walzen mit großen Stichabnahmen.The invention aims to avoid these disadvantages and difficulties and arises the task of creating a rolling stand, which also applies to rolls with small diameters and on the other hand a relatively large center distance of the motor drive shafts Drive spindles can be provided with a large diffraction angle - and so that with a relatively short length - can be arranged, but still very much high drive torques can be transmitted, for example, for rolling high-strength Rolled and rolled with large Stichiefnahmen.

Diese Aufgabe wird erfindungsgemäß durch eine Kombination folgender Merkmale gelöst:

  • lediglich eine einzige der Antriebsspindeln ist von zwei durch eine größere winkelige Wellenverlagerungen zulassende Gelenkkupplung miteinander verbundenen Teilen, von denen ein Teil über eine solche Gelenkkupplung mit dem Antriebsmotor verbunden ist, gebildet
  • die andere Antriebsspindel erstreckt sich als einteilige Zahnspindel von der Zahnkupplung bis zu einer an der Antriebswelle des Motors angeordneten, winkelige Wellenverlagerungen zulassenden Kupplung, vorzugsweise ebenfalls eine Zahnkupplung,
  • der erste Teil der zweiteiligen Antriebsspindel ist wesentlich kürzer ausgebildet als die einteilige Antriebsspindel und
  • die Achsen sowohl des ersten Teils als auch des zweiten Teils der zweiteiligen Antriebsspindel divergieren zur Achse der einteiligen Antriebsspindel.
This object is achieved according to the invention by a combination of the following features:
  • Only a single one of the drive spindles is formed by two interconnected parts, of which a part is connected to the drive motor via such an articulated coupling, by means of two articulated clutches permitting a larger angular shaft displacements
  • the other drive spindle extends as a one-piece toothed spindle from the toothed coupling to a arranged on the drive shaft of the motor, angular shaft displacements permitting coupling, preferably also a toothed coupling,
  • the first part of the two-part drive spindle is designed substantially shorter than the one-piece drive spindle and
  • the axes of both the first part and the second part of the two-part drive spindle diverge to the axis of the one-piece drive spindle.

Diese Konstruktion ist besonders platzsparend und ermöglicht eine momentenmäßig optimale Dimensionierung auch bei sehr engen Achsabständen der Walzen.This construction is particularly space-saving and enables optimal moments Dimensioning even with very narrow center distances of the rollers.

Zur Sicherstellung einer ausreichenden Schmierung der Zahnkupplungen ist vorteilhaft zwischen den Achsen der Walzen und den Achsen der gegenüber den Walzen beweglichen Teile der Zahnkupplungen jeweils eine Winkelstellung im Bereich zwischen 0,5 und 1,5°, vorzugsweise eine Winkelstellung von etwa 0,8°, eingehalten, wobei die Dimensionierung der Kardanwelle und auch der Zahnspindeln noch verbessert werden kann, wenn die Achsen der Zahnspindeln in Richtung zu den Antriebsmotoren divergieren.To ensure sufficient lubrication of the toothed couplings is advantageous between the axes of the rollers and the axes of the rollers movable relative to the rollers Parts of the toothed couplings one angular position each in the area between 0.5 and 1.5 °, preferably an angular position of about 0.8 °, adhering to the sizing the propeller shaft and the spindles even better can be when the axes of the toothed spindles diverge towards the drive motors.

Zweckmäßig weisen die Zahnkupplungen ballige Außenverzahnungen auf, wobei zur Erzielung einer axialen Bewegbarkeit der angetriebenen Walzen sich die Innenverzahnungen der Zahnkupplungen in Achsrichtung über ein Vielfaches der Außenverzahnung erstrecken.Appropriately, the toothed couplings crowned Außenverzahnungen on, wherein to achieve a axial mobility of the driven rollers themselves the internal teeth of the toothed couplings in the axial direction over a multiple of the external toothing extend.

Um stets den optimalen Eingriffswinkel der Zahnkupplung, d.h. den optimalen Winkel zwischen der Achse der Walze und der ihr zugeordneten Zahnspindel sicherzustellen, insbesondere bei Ändern des Walzspaltes, ist der gegenüber einer Walze bewegliche Teil der Zahnkupplung der Zahnspindel, die mit der Kardanwelle verbunden ist, über eine Ausgleichseinrichtung zur Einhaltung einer vorgegebenen Winkelstellung am Fundament abgestützt, wobei die Ausgleichseinrichtung von einer als Hebelsystem ausgebildeten Parallelführung gebildet ist.To always have the optimal pressure angle of the Gear coupling, i. the optimal angle between the Axle of the roller and its associated toothed spindle especially when changing the roll gap, is the part movable relative to a roller the toothed coupling of the toothed spindle, with the cardan shaft is connected via a balancing device to comply with a predetermined angular position on Foundation supported, with the compensation device from a trained as a lever system parallel guide is formed.

Zur Vermeidung zu großer Belastungen quer zur Achsrichtung sind vorteilhaft die Zahnspindeln über Drehlager mittels seitlich geführter Spindelbalancierungen gegenüber dem Fundament abgestützt.To avoid excessive loads across to the axial direction are advantageous about the tooth spindles Swivel bearing by means of laterally guided spindle balancers supported against the foundation.

Die Erfindung ist nachfolgend anhand in der Zeichnung näher erläutert, wobei Fig. 1 eine Schrägrißansicht und Fig. 2 einen durch die Achsen der Antriebsspindeln gelegten Vertikalschnitt eines Details der Fig. 1 einer Ausführungsform veranschaulichen.The invention is described below with reference to FIG Drawing explained in more detail, wherein Fig. 1 is a Schrägrißansicht and Fig. 2 a through the axes of the drive spindles laid vertical section of a detail of FIG. 1 of an embodiment.

Zwei Arbeitswalzen 1, 2 eines Quarto-Grobblechgerüstes, deren Achsabstand 3 sich auf die gewünschte Blechstärke einstellen läßt, sind gemäß Fig. 1 mit ihren Antriebszapfen 4, 5 über Lager, die generell mit 6 bezeichnet sind, am Walzgerüst 7 abgestützt. Zur Vermeidung von Durchbiegungen der Arbeitswalzen 1, 2 sind Stützwalzen 8 vorgesehen, die ebenfalls am Walzgerüst 7 über Lager 9 drehbar gelagert sind.Two work rolls 1, 2 of a quarto heavy plate stand, whose center distance 3 is on the set desired thickness, are according to Fig. 1 with their drive pins 4, 5 via bearings, the generally designated 6, supported on the roll stand 7. To avoid deflections of the Work rolls 1, 2 are provided support rollers 8, the also rotatably mounted on the rolling stand 7 via bearings 9 are.

Die nur einen relativ kleinen Durchmesser 10 aufweisenden Arbeitswalzen 1, 2 sind jeweils über eine eigene Antriebsspindel 11, 12 mittels eines eigenen Antriebsmotors 13, 14 antreibbar. Die Anordnung der Antriebsmotoren 13, 14 ist derart getroffen, daß der Achsabstand 15 der Antriebswellen 16 der Antriebsmotoren 13, 14 möglichst gering ist. Um die Antriebsspindeln 11, 12 nicht allzu lange bauen zu müssen, was eine zu weiche Momentenübertragung von den Antriebsmotoren 13, 14 zu den Arbeitswalzen 1, 2 ergäbe, sind die Antriebsspindeln 11, 12 zueinander geneigt angeordnet.The only a relatively small diameter 10 having work rolls 1, 2 are each over a own drive spindle 11, 12 by means of its own Drive motor 13, 14 drivable. The arrangement of Drive motors 13, 14 is made such that the Center distance 15 of the drive shafts 16 of the drive motors 13, 14 is as low as possible. To the drive spindles 11, 12 not too long to build what Too soft torque transmission from the Drive motors 13, 14 to the work rolls 1, 2 would give, the drive spindles 11, 12 to each other arranged inclined.

Erfindungsgemäß ist jeder Antriebszapfen 4, 5 der Arbeitswalzen 1, 2 mit einer Hülse 17 drehfest verbunden, die eine Innenverzahnung 18 aufweist. In diese Innenverzahnung 18 greift eine ballige Außenverzahnung 19, die an einer weiteren Hülse 20 außenseitig angeordnet ist, ein. Die Hülsen 17 und 20 bilden somit jeweils eine Zahnkupplung. Die Lange der Innenverzahnung 18 ist um ein Vielfaches länger als die Zähne der Außenverzahnung 19, so daß eine axiale Beweglichkeit möglich ist. Hierdurch können die Arbeitswalzen 1, 2 in Achsrichtung gegenüber dem Walzgerüst 7 verschoben werden. Unterschiedliche Axiallagen der Arbeitswalzen 1, 2 sind in Fig. 2 dargestellt.According to the invention, each drive pin 4, 5 the work rolls 1, 2 rotatably connected to a sleeve 17, which has an internal toothing 18. In these Internal toothing 18 engages a convex outer toothing 19, the outside of another sleeve 20 is arranged, a. The sleeves 17 and 20 thus form one toothed coupling each. The length of the internal toothing 18 is many times longer than the teeth of the External teeth 19, so that an axial mobility is possible. As a result, the work rolls 1, 2 in Axial direction relative to the roll stand 7 shifted become. Different axial layers of the work rolls 1, 2 are shown in Fig. 2.

Die mit der Außenverzahnung 19 versehenen Hülsen 20 sind jeweils drehfest an einer Spindel 21 bzw. 22 montiert und bilden zusammen mit dieser Spindel 21 bzw. 22 eine sogenannte Zahnspindel.The provided with the external teeth 19 Sleeves 20 are each rotationally fixed to a spindle 21 and 22 mounted and form together with this spindle 21st or 22 a so-called toothed spindle.

Gemäß dem dargestellten Ausführungsbeispiel ist die Antriebsspindel 12 der oberen Arbeitswalze 2 von der Zahnspindel 20, 22 und einer daran anschlie-Benden Kardanwelle 23 gebildet, die über ihre Kreuzgelenke 24 einerseits mit der Zahnspindel 20, 22 und andererseits mit der Antriebswelle 16 des oberen Antriebsmotors 14 verbunden ist. Anstelle der Kreuzgelenke 24 könnten auch andere Gelenkkupplungen vorgesehen sein, die zur Übertragung hoher Drehmomente geeignet sind, beispielsweise Flachzapfenkupplungen.According to the illustrated embodiment is the drive spindle 12 of the upper work roll 2 of the toothed spindle 20, 22 and a subsequent Benden Cardan shaft 23 formed over its universal joints 24 on the one hand with the toothed spindle 20, 22 and on the other hand with the drive shaft 16 of the upper Drive motor 14 is connected. Instead of the universal joints 24 could also be provided other articulated couplings to be high in transmission Torques are suitable, for example, flat-pin couplings.

Die Antriebsspindel 11 der unteren Arbeitswalze 1 ist bis zur Antriebswelle 16 des unteren Antriebsmotors 13 starr ausgebildet und mit der Antriebswelle 16 des unteren Antriebsmotors 13 über eine Zahnkupplung 24' gekuppelt. Die Achslagen der Zahnspindeln 20, 21 und 20, 22 sind so gewählt, daß deren Achsen mit den Achsen der zugehörigen Arbeitswalzen 1, 2 einen Winkel zwischen 0,5 und 1,5°, vorzugsweise einen Winkel von etwa 0,8°, einschließen. Für die untere Arbeitswalze 1, die im Walzgerüst 7 nur gering verstellbar angeordnet ist, wird dies durch entsprechende Anordnung des unteren Antriebsmotors 13 erreicht; für die obere Arbeitswalze 2 muß zur Einhaltung des optimalen Winkelbereiches die Zahnspindel 20, 22 mittels einer als Parallelführung 25 ausgebildeten Ausgleichseinrichtung gegenüber dem Fundament 26 abgestützt werden. Die Parallelführung 25 ist von einem Gelenkhebelsystem gebildet, u.zw. greifen etwa vertikal gerichtete Laschen 27 an einem die obere Zahnspindel 20, 22 umgebenden und gegenüber der Zahnspindel 20, 22 mittels Drehlager 28 abgestützten Gehäuse 29 an, welches Gehäuse 29 gegenüber dem Fundament 26 verdrehgesichert ist. Die Laschen 27 sind jeweils an einem Winkelhebel 30 angelenkt, dessen Kniegelenk 31 am Fundament 26 drehbar abgestützt ist. Die weiteren Hebelarme 32 der Winkelhebel 30 sind über eine Zug- bzw. Druckkräfte aufnehmende Lasche 33 verbunden. Hierdurch kann die Zahnspindel 20, 22 der oberen Arbeitswalze 2 gemeinsam mit dieser in vertikaler Richtung parallel zu sich selbst verstellt werden, beispielsweise zur Einstellung unterschiedlich hoher Walzspalte 34.The drive spindle 11 of the lower work roll 1 is up to the drive shaft 16 of the lower Drive motor 13 rigid formed and with the drive shaft 16th of the lower drive motor 13 via a toothed coupling 24 'coupled. The axial positions of the toothed spindles 20, 21 and 20, 22 are chosen so that their axes with the axes of the associated work rolls 1, 2 a Angle between 0.5 and 1.5 °, preferably an angle of about 0.8 °. For the lower work roll 1, in the rolling stand 7 only slightly adjustable is arranged, this is by appropriate arrangement reaches the lower drive motor 13; for the Upper work roll 2 must comply with the optimal Angular range the toothed spindle 20, 22 by means of a designed as a parallel guide 25 compensation device be supported against the foundation 26. The parallel guide 25 is of a toggle lever system formed, u.zw. grab something vertically oriented Tabs 27 on one the upper toothed spindle 20, 22nd surrounding and opposite the toothed spindle 20, 22nd by means of rotary bearing 28 supported housing 29, which Housing 29 against rotation against the foundation 26 is. The tabs 27 are each at one Angle lever 30 articulated, the knee joint 31 on Foundation 26 is rotatably supported. The others Lever arms 32 of the angle lever 30 are connected via a pull or pressure-absorbing tab 33 connected. As a result, the toothed spindle 20, 22 of the upper Work roll 2 together with this in the vertical direction be adjusted parallel to itself, for example for setting different high rolling nips 34th

Zur Vermeidung von Belastungen, hervorgeruten durch Gewichtskräfte der Antriebsspindeln 11, 12, sind die Zahnspindeln 20, 21 und 20, 22 mittels an einer seitlichen Führung 26' gestützter Spindelbalancierungen 35, 36, die nur in Fig. 2 eingezeichnet sind, gegenüber dem Fundament 26 abgestütztTo avoid stress, excite by weight forces of the drive spindles 11, 12, the toothed spindles 20, 21 and 20, 22 by means of a lateral guide 26 'supported spindle balancers 35, 36, which are shown only in Fig. 2, opposite the foundation 26 supported

Wie insbesondere aus Fig. 2 zu erkennen ist, gelingt es durch die erfindungsgemäße Gestaltung des Walzgerüstes, die Kreuzgelenke 24 der Kardanwelle 23 trotz sehr kleiner Durchmesser 10 der Arbeitswalzen 1, 2 sehr groß zu dimensionieren, u.zw. als Folge des Vorsehens der Zahnkupplungen 17, 20 und der Zahnspindeln 20, 21 und 20, 22.As can be seen in particular from FIG. 2, succeeds by the inventive design of Rolling stand, the universal joints 24 of the cardan shaft 23 despite very small diameter 10 of the work rolls 1, 2 very large to dimension, u.zw. as a result of the provision the toothed clutches 17, 20 and the toothed spindles 20, 21 and 20, 22.

Die Anordnung der Zahnspindeln 20, 21 und 20, 22 ist hierbei so getroffen, daß diese in Richtung zu den Antriebsmotoren 13, 14 divergieren, wodurch es gelingt, das die Kardanwelle 23 mit der Zahnspindel 20, 22 verbindende Kreuzgelenk 24 mit maximaler Größe zu gestalten. Dies ist insoferne von Bedeutung, als das zu übertragende Moment sich mit der dritten Potenz des Durchmessers der Kreuzgelenke 24 bzw. der Kardanwelle 23 vergrößert. Somit gelingt es, trotz der kleinen Durchmesser 10 der Arbeitswalzen 1, 2 und der relativ eng zum Walzgerüst 7 benachbarten Anordnung der Antriebsmotoren 13, 14, ein sehr großes Drehmoment zu übertragen, u.zw. ein wesentlich höheres als gemäß dem Stand der Technik, wobei als zusätzlicher Vorteil noch ein drehsteifer Antrieb verwirklicht ist.The arrangement of the toothed spindles 20, 21 and 20, 22 is in this case made so that these in the direction of the drive motors 13, 14 diverge, causing it succeeds that the propeller shaft 23 with the toothed spindle 20, 22 connecting universal joint 24 with maximum size to design. This is important insofar as the to be transmitted moment with the third power the diameter of the universal joints 24 and the cardan shaft 23 enlarged. Thus succeeds, despite the small Diameter 10 of the work rolls 1, 2 and the relatively close to the roll stand 7 adjacent arrangement the drive motors 13, 14, a very large torque to transfer, u.zw. a much higher than according to the prior art, wherein as additional Advantage even a torsionally rigid drive is realized.

Ein weiterer Vorteil ist noch darin zu sehen, daß durch die Anordnung der Zahnkupplungen 17, 20 eine nur geringe Verschiebekraft zum Verschieben der Arbeitswalzen 1, 2 erforderlich ist. Diese liegt weit unter der Verschiebekraft, die beispielsweise notwendig ist, um eine mittels einer herkömmlichen Gelenkwelle mit Längenausgleich angetriebene Arbeitswalze zu verschieben.Another advantage can still be seen in that by the arrangement of the toothed couplings 17, 20th a small displacement force to move the Work rolls 1, 2 is required. This is far below the displacement force, which is necessary, for example, by a means of a conventional PTO shaft with Length compensation driven working roller to move.

Ein weiterer Vorteil ergibt sich durch Einbau eines als Federtopf 37 ausgebildeten FederDämpferelementes in das Hebelsystem der Parallelführung 25. Hierdurch werden dynamisch als Biegekräfte aufden Walzzapfen wirkende Kräfte, hervorgerufen durch die Vertikalbeschleunigungen des Antriebsstranges beim Walzguteintritt bzw. -austritt, auf einen Bruchteil der herkömmlichen Werte reduziert. Der Federtopf 37 kann an einem beliebigen Hebel des Hebelsystems vorgesehen werden. Vorzugsweise ist das Feder-Dämpferelement kraftabhängig einstellbar.Another advantage results from installation a designed as a spring cup 37 spring damper element in the lever system of the parallel guide 25th This will dynamically act as bending forces Walzapfen acting forces, caused by the Vertical accelerations of the drive train during Rolling stock entry or exit, to a fraction of the reduced to conventional values. The spring cup 37 can provided on any lever of the lever system become. Preferably, the spring-damper element adjustable by force.

Claims (7)

  1. A roll stand comprising two rolls (1, 2) forming a roll gap (34), which rolls can be driven by their separate driving motors (13, 14) via drive spindles (11, 12), in particular a four-high stand, wherein for each roll (1, 2) a separate drive train is used, each comprising a toothed coupling (17) in combination with a further flexible coupling (24), characterized by the combination of the following features:
    one only of the drive spindles (12) is formed by two components connected with each other by a flexible coupling (24) permitting larger angular shaft displacements, a first one of said components (22) being connected with the toothed coupling (17, 20) and such a flexible coupling (24) and a second one of said components (23) being connected with the driving motor (14) via such a flexible coupling (24),
    the other drive spindle (11) in the form of a single-component toothed spindle (20, 21) extends from the toothed coupling (17, 20) to a coupling arranged on the drive shaft (16) of the motor (13) and permitting angular shaft displacements, said coupling preferably also being a toothed coupling (24'),
    the first component (22) of the rwo-component drive spindle (12) is designed so as to be substantially shorter than the single-component drive spindle (11) and
    the axes of both the first component (22) and the second component (23) of the two-component drive spindle (12) diverge toward the axis of the single-component drive spindle (11).
  2. A roll stand according to claim 1, characterized in that between the axes of the rolls (1, 2) and the axes of the components (20) of the toothed couplings (17, 20) that are movable relative to the rolls (1, 2), an angular position in the region between 0.5 and 1.5°, preferably an angular position of roughly 0.8°, is observed in each instance.
  3. A roll stand according to claim 2, characterized in that the axes of the toothed spindles (20, 21 and 20, 22) diverge toward the driving motors (13, 14).
  4. A roll stand according to one or several of claims 1 to 3, characterized in that the internal toothings (18) of the toothed couplings (17, 20) extend in axial direction over a multiple of the external toothing (19).
  5. A roll stand according to one or several of claims 1 to 4, characterized in that the component (20) of the toothed coupling (17, 20) of the toothed spindle (20, 21) connected with the universal shaft (23), which component is movable relative to a roll (2), is supported on the foundation via a compensating device (25) serving to maintain a predetermined angular position, which device is formed by a parallel guide (25) constructed as a system of levers.
  6. A roll stand according to one or several of claims 1 to 5, characterized in that the toothed spindles (20, 21 and 20, 22) are supported relative to the foundation (26) via a pivot bearing by means of laterally guided spindle balancing means (35, 36).
  7. A roll stand according to claim 5 or 6, characterized in that a spring-and-damper element is provided in the system of levers of the parallel guide (25), being adjustable in particular in dependence on the force.
EP96910844A 1995-04-25 1996-04-23 Roll stand Expired - Lifetime EP0822872B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT71195 1995-04-25
AT0071195A AT405619B (en) 1995-04-25 1995-04-25 ROLLING STAND
AT711/95 1995-04-25
PCT/AT1996/000078 WO1996033823A1 (en) 1995-04-25 1996-04-23 Roll stand

Publications (3)

Publication Number Publication Date
EP0822872A1 EP0822872A1 (en) 1998-02-11
EP0822872B1 EP0822872B1 (en) 1999-06-23
EP0822872B2 true EP0822872B2 (en) 2005-08-10

Family

ID=3497792

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96910844A Expired - Lifetime EP0822872B2 (en) 1995-04-25 1996-04-23 Roll stand

Country Status (7)

Country Link
US (1) US6062058A (en)
EP (1) EP0822872B2 (en)
JP (1) JPH11503975A (en)
KR (1) KR19990007799A (en)
AT (2) AT405619B (en)
DE (1) DE59602284D1 (en)
WO (1) WO1996033823A1 (en)

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DE102009031324A1 (en) 2009-06-30 2011-01-05 Voith Patent Gmbh Roller drive and rolling stand with such

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US20040022787A1 (en) 2000-07-03 2004-02-05 Robert Cohen Methods for treating an autoimmune disease using a soluble CTLA4 molecule and a DMARD or NSAID
DE102005054742A1 (en) * 2005-04-12 2006-10-19 Sms Demag Ag Drive spindle for the main drive of a rolling stand
CN101663107B (en) * 2007-05-01 2014-09-03 东芝三菱电机产业***株式会社 Driving device for motor of rolling mill roll
KR101103346B1 (en) * 2009-07-14 2012-01-11 주식회사 동방플랜텍 Processing line apparatus for cold rolled steel strip
EP2572810A1 (en) * 2011-09-22 2013-03-27 Siemens VAI Metals Technologies SAS Levelling equipment
AT515177B1 (en) * 2013-12-10 2015-08-15 Asmag Holding Gmbh Drive system and profiling system equipped therewith
DE102015223641A1 (en) * 2015-06-10 2016-12-15 Sms Group Gmbh Device for transmitting a torque from a drive device to a roller in a rolling stand
CN105013868A (en) * 2015-06-18 2015-11-04 太原重工股份有限公司 Eleven-roller straightener, main transmission system and universal spindle system of main transmission system

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Also Published As

Publication number Publication date
ATA71195A (en) 1999-02-15
ATE181520T1 (en) 1999-07-15
EP0822872B1 (en) 1999-06-23
AT405619B (en) 1999-10-25
DE59602284D1 (en) 1999-07-29
JPH11503975A (en) 1999-04-06
KR19990007799A (en) 1999-01-25
EP0822872A1 (en) 1998-02-11
WO1996033823A1 (en) 1996-10-31
US6062058A (en) 2000-05-16

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