EP0100957A1 - Roll head of a planetary cross-rolling mill - Google Patents

Roll head of a planetary cross-rolling mill Download PDF

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Publication number
EP0100957A1
EP0100957A1 EP83107359A EP83107359A EP0100957A1 EP 0100957 A1 EP0100957 A1 EP 0100957A1 EP 83107359 A EP83107359 A EP 83107359A EP 83107359 A EP83107359 A EP 83107359A EP 0100957 A1 EP0100957 A1 EP 0100957A1
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EP
European Patent Office
Prior art keywords
ring
support ring
bearing
axial
roller
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83107359A
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German (de)
French (fr)
Other versions
EP0100957B1 (en
Inventor
Friedhelm Böhmer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
Schloemann Siemag AG
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Publication date
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Priority to AT83107359T priority Critical patent/ATE23458T1/en
Publication of EP0100957A1 publication Critical patent/EP0100957A1/en
Application granted granted Critical
Publication of EP0100957B1 publication Critical patent/EP0100957B1/en
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/008—Skew rolling stands, e.g. for rolling rounds
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/18—Adjusting or positioning rolls by moving rolls axially

Definitions

  • Planetary diagonal rolling mills are used as so-called high-reduction rolling mills for rolling out full and hollow cross sections, in particular for reducing the cross section, in order to bring the material to be rolled out considerably in a single pass to the desired final cross section.
  • the rolling forces to be applied are correspondingly high.
  • the planetary diagonal rolling mills generally consist of three rolling heads, each of which carries a tapered roller and which. sit in a rotor with which they rotate around the rolling stock so that. the tapered rollers can reduce the cross-section.
  • the tapered rollers are arranged with their axes inclined to the rolling stock axis and their axes cross the rolling stock axis at a short distance.
  • a hollow shaft through which the rolling stock runs to the tapered rollers, there is a sun gear on which planet gears roll, each of which has an idler gear, a key.
  • the pinion gear and a bevel gear drive the respective roller shaft.
  • Roll adjustment and inclination, rolling stock diameter and speed of the rotor can only be set for one ratio so that the rolling stock does not rotate about its axis.
  • the hollow shaft passed through by the rolling stock is rotated forwards or backwards accordingly.
  • the rolling heads rotating around the rolling stock with the rotor are of particular importance as they are exposed to high rolling forces and high centrifugal forces.
  • the centrifugal forces are directly proportional to the distance at which the components are arranged to the rolling stock axis and they increase with the square of the angular velocity, which directly determines the throughput of the rolling mill. It follows from this that the arrangement of the components, in particular the heavy components, should take place at a small distance from the rolling stock axis, as is the case through the rolling stock. roller geometry and knife acceptance.
  • a design of the rolling head has proven to be favorable, as described in the preamble of claim 1 and through the conference report on the ILAFA Rolling Mill Congress, published by the Instituto Latinoamericano del Fierro y el Acero, May 1980, page H 9/10, Figura 26, is published.
  • a radial bearing and a thrust bearing are provided in a very powerful design, in which one end of the shaft is supported, which at this end carries the tapered roller while the roller shaft at its other end rotatably, but axially displaceably in that the bevel gear of the roller drive is seated in the roller head housing.
  • a support ring for the axial bearing is arranged between the bearings (radial and axial bearings) and the bevel gear, which is rotatably seated in the roller head housing and can be rotated for the axial adjustment of the roller. To rotate the support ring, this is via a clutch with which the roller driving bevel gear can be coupled, while the support ring is fixed non-rotatably during rolling in the roller head housing via the same clutch.
  • a bushing is used here as a support ring, which is provided on the outside with the adjusting thread and accommodates the bearings (radial and axial bearings) in its bore.
  • the design of the support ring as a bushing necessitates a roller head that is twice the wall thickness of the bushing or, given the dimensions of the roller head, only allows bearings that have to remain smaller than bearings of maximum conceivable diameters by twice the wall thickness of the bushing.
  • the aim of the invention is to design the mounting and adjustment of the shafts which carry the tapered rollers in a floating manner and which have an axially and radially compact construction, i.e. in the latter results in a construction without components that are not directly load-bearing.
  • This goal is achieved by the characterizing features of claim 1: construction of the roller heads. Further expedient refinements of the invention can be achieved with the features of the special designs specified in claims 2 to 6.
  • FIG. 1 show exemplary embodiments of the invention and are limited to the representation of the roller heads in axial section, the roller heads being seated in three in a rotor — indicated and indicated by 1 — and rotating with it in a stator (not shown).
  • Constructions of rotors and stators are known, for example from the prior art mentioned publication or the prior art according to DE-OS 31 12 781.9 or DE-OS 31 13 461.0.
  • a roller head 3 with its cylindrical extension 4 is pivotably seated in a bore 2 of a rotor indicated by 1.
  • an intermediate shaft 5 is mounted in the pivot axis, which engages with an intermediate gear 6 in a planet gear, not shown, mounted in the rotor 1 and rolling on a sun gear, also not shown, whereby the intermediate shaft 5 when the rotor 1 and / or the sun gear is rotated.
  • the intermediate shaft 5 is further provided with a bevel pinion 7 which engages in a bevel gear 8.
  • the bevel gear 8 is with a hollow shaft. 9 connected and supported with this by radial bearings 10 and 11 and an axial bearing 12 in the roller head housing 13.
  • the hollow shaft 9 is provided over the length of its bore with an internal toothing 14, in which the one correspondingly toothed end of a roller shaft 15 rotates but is longitudinally displaceable and centered.
  • the front end of the roller shaft 15 is supported in the roller head housing 13 via a radial bearing 16 and an axial bearing 17.
  • a pin 18 of the roller shaft 15 protruding from the radial bearing 16 carries a tapered roller 19 on the fly.
  • the tapered roller 19 is provided with an inserted ring 20, which has end teeth 21 and is secured against rotation by pins 22.
  • An internally toothed cap 23 is placed on the externally toothed pin 18 of the roller shaft 15, which cap defines the inner ring of the bearing 16 axially relative to the roller shaft 15.
  • the cap 23 is also with a spur gear Provided corresponding to the spur toothing 21 and thus produces the rotationally fixed connection of the tapered roller 19 with the roller shaft 15.
  • the tapered roller 19 is held on the roller shaft 15 by a screw 24 which is screwed into a nut piece 25, into which one end of a tie rod 26 is also screwed, the other end of which is screwed into a nut 27.
  • the nut piece 25 is designed as an annular cylinder for receiving an annular piston 28, by the action of which the tie rod 26 is stretched, so that after tightening the screw 24 and then relieving the annular piston 28, the tension force of the tie rod 26, the tapered roller 19 via the ring 20 and Cap 23 clamped against the end face of the roller shaft 15 at the pin 18 thereof.
  • the perforated roller shaft 15 is closed at the end facing away from the tapered roller 19 with a cover 29, the cover 29 having a bore as a passage for a spring bolt 30.
  • a spring 31 in the bore of the roller shaft 15 is clamped between the cover 29 and a collar 32 of the spring bolt 30, for which purpose the spring bolt 30 with a nut 34 seated on its threaded shaft 33 via an axial bearing 35 on a roller head housing 13 on that of the tapered roller 19 opposite end closing cover 36 supports.
  • a support ring 40 is provided for the axial bearing 17, which is provided with an external thread 41 and is rotatably seated in the threaded bore of an insert ring 42 relative to the roller head housing 13.
  • the insert ring 42 is secured against rotation in the roller head housing 13 and the pressure ring 17 ′ is in turn in the insert ring 42 the axial bearing 17 secured against rotation by round wedges 43.
  • the support ring 40 With the rotation of the support ring 40, the axial bearing 17 and with it the roller shaft 15 with the tapered roller 19 are axially adjusted.
  • the support ring 40 is provided with end teeth 44 and via a rotationally fixed but axially displaceable on the roller shaft 15 dome ring 45, which has a corresponding spur toothing to the spur toothing 44 of the support ring 40, can be coupled, so that the support ring 40 is also rotated with the rotation of the roller shaft 15.
  • a ring 46 is fastened on the roller shaft 15 and receives ring pistons on both end faces in turns, which, by alternating action, engage the coupling ring 45 in the front toothing 44 of the support ring 40 or disengage from it.
  • a support ring designated 50 is provided for the axial bearing 17, which is provided with an external thread 51 and is rotatably seated in the threaded bore of an insert ring 52 relative to the roller head housing 13.
  • the insert ring 52 is secured against rotation in the roller head housing 13 and in the insert ring 52 the pressure ring 17 ′ of the axial bearing 17 is in turn secured against rotation by round wedges 53.
  • the support ring 50 is divided, the inner ring 54 being seated in a rotationally fixed but axially movable manner with the support ring 50 and being provided with spur gears 55 and 56 on both end faces.
  • the axial adjustment takes place via a claw 57, which can be moved in a known manner, not shown here, parallel to the axis of the roller shaft 15 and acts on the clutch disc 58, which is part of the inner ring 54 of the support ring 50.
  • the spur toothing 55 of the inner ring 54 engages in a corresponding spur toothing of a coupling ring 59 on the inner edge of the ring of the bevel gear 8 and thus connects the bevel gear 8 with the support ring 50 for the axial adjustment of the axial bearing 17 with the roller shaft 15 and the bevel roller 19
  • the End toothing 56 in the corresponding end toothing on the coupling ring 60 which is held on the one hand in a rotationally fixed but axially displaceable manner in the pressure ring 17 'of the axial bearing 17 and on the other hand rotatable but axially immovable on a guide sleeve connected to the ring of the bevel gear 8, so that the support ring thereby 50 is secured against unintentional rotation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Support Of The Bearing (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Crushing And Grinding (AREA)
  • Rolling Contact Bearings (AREA)
  • Gear Transmission (AREA)
  • Metal Rolling (AREA)

Abstract

A roll head for a planetary crossrolling mill in which the roll shaft bearing the tapered roll is mounted at one end close to the tapered roll in a radial bearing and an axial bearing while the other end rests with teeth in a rotationally engaged but axially movable manner in a hollow shaft of a bevel wheel driving the roll shaft. To obtain a compact structure with arrangement of the components on paths of revolution with small radii, the support ring of the axial bearing is provided with two sets of facial teeth pointing in opposite directions and can be coupled alternately with one of two coupling rings, wherein one coupling ring with the support ring can be connected in a rotationally engaged manner for its axial adjustment with the roll shaft while the other coupling ring with the support ring for securing its position can be connected to the thrust collar of the axial bearing which, in turn, rests in a rotationally enaged but axially movable manner in the roll head housing, and the radial bearing arranged before the axial bearing accommodates the axial adjustment of the roll by a change in position between internal and external bearing rings or in its seat by changing position of the external ring in the roll head housing.

Description

Planeten-Schräg-Walzwerke werden zum Auswalzen von Voll- und Hohlquerschnitten, insbesondere zur starken Querschnittsreduzierung als sogenannte Hochreduktionswalzwerke eingesetzt, um das auszuwalzende Gut in einem einzigen Stich dem gewünschten Endquerschnitt erheblich nahe zu bringen. Entsprechend hoch sind die aufzubringenden Walzkräfte. Die Planeten-Schräg-Walzwerke bestehen in der Regel aus drei Walzköpfen, deren jeder eine Kegelwalze trägt und die. in einem Rotor einsitzen, mit dem sie um das Walzgut umlaufen, so daß. die Kegelwalzen die Querschnittsreduktion bewirken können. Die Kegelwalzen sind dazu mit ihren Achsen geneigt zur Walzgutachse angeordnet und ihre Achsen kreuzen die Walzgutachse-in geringem Abstand. Auf einer Hohlwelle, durch die das Walzgut den Kegelwalzen zuläuft, befindet sich ein Sonnenrad, auf dem sich Planetenräder abwälzen, die über je ein Zwischenrad, ein Ke-. gelritzel und ein Kegelrad die jeweilige Walzenwelle antreiben. Walzenanstellung und -schrägstellung, Walzgutdurchmesser und Drehzahl des Rotors können nur für jeweils ein Verhältnis so eingestellt werden, daß sich das Walzgut nicht um seine Achse dreht. Um eine Drehung des Walzgutes auch unter anderen Verhältnissen auszuschließen, wird die vom Walzgut durchlaufene Hohlwelle entsprechend vor oder zurückgedreht.Planetary diagonal rolling mills are used as so-called high-reduction rolling mills for rolling out full and hollow cross sections, in particular for reducing the cross section, in order to bring the material to be rolled out considerably in a single pass to the desired final cross section. The rolling forces to be applied are correspondingly high. The planetary diagonal rolling mills generally consist of three rolling heads, each of which carries a tapered roller and which. sit in a rotor with which they rotate around the rolling stock so that. the tapered rollers can reduce the cross-section. The tapered rollers are arranged with their axes inclined to the rolling stock axis and their axes cross the rolling stock axis at a short distance. On a hollow shaft, through which the rolling stock runs to the tapered rollers, there is a sun gear on which planet gears roll, each of which has an idler gear, a key. the pinion gear and a bevel gear drive the respective roller shaft. Roll adjustment and inclination, rolling stock diameter and speed of the rotor can only be set for one ratio so that the rolling stock does not rotate about its axis. To rotate the rolling stock also under to exclude other conditions, the hollow shaft passed through by the rolling stock is rotated forwards or backwards accordingly.

Den mit dem Rotor um das Walzgut umlaufenden Walzköpfen kommt dadurch eine besondere Bedeutung zu, als sie hohen Walzkräften und hohen Fliehkräften ausgesetzt sind. Die Fliehkräfte sind direkt proportional dem Abstand, auf dem die Bauteile zur Walzgutachse angeordnet werden und sie nehmen mit dem Quadrat der Winkelgeschwindigkeit, die unmittelbar den Durchsatz des Walzwerkes bestimmt, zu. Daraus ergibt sich, daß die Anordnung der Bauteile, insbesondere der schweren Bauteile auf so geringem Abstand zur Walzgutachse erfolgen soll, wie es dies die durch Walzgutdurch- . messer und Stichabnahme bedingte Walzengeometrie eben zuläßt. In diesem Sinne hat sich eine Ausbildung des Walzkopfes als günstig erwiesen, wie sie im Oberbegriff des Patentanspruches 1 beschrieben und durch den Tagungsbericht zum ILAFA-Walzwerkskongress, herausgegeben vom Instituto Latinoamericano del Fierro y el Acero, Mai 1980, Seite H 9/10, Figura 26, veröffentlicht ist. Gemäß diesem Stande der Technik werden ein Radiallager und ein Axiallager in sehr kräftiger Ausführung vorgesehen, in denen das eine Ende der Welle abgestützt ist, die an diesem Ende fliegend die Kegelwalze trägt, während die Walzenwelle an ihrem anderen Ende drehfest, jedoch axial verschiebbar in dem im Walzkopfgehäuse gelagerten Kegelrad des Walzenantriebes einsitzt. Zwischen den Lagern (Radial- und Axiallager) und dem Kegelrad ist ein Stützring für das Axiallager angeordnet, der drehbar im Walzkopfgehäuse einsitzt und zur axialen Anstellung der Walze drehbar ist. Zur Drehung des Stützringes ist dieser über eine Schaltkupplung mit dem die Walze antreibenden Kegelrad kuppelbar, während über die gleiche Schaltkupplung der Stützring während des Walzens im Walzkopfgehäuse undrehbar festgelegt ist. Als Stützring dient hier eine Büchse, die außen mit dem Stellgewinde versehen ist und in ihrer Bohrung die Lager (Radial- und Axiallager) aufnimmt.The rolling heads rotating around the rolling stock with the rotor are of particular importance as they are exposed to high rolling forces and high centrifugal forces. The centrifugal forces are directly proportional to the distance at which the components are arranged to the rolling stock axis and they increase with the square of the angular velocity, which directly determines the throughput of the rolling mill. It follows from this that the arrangement of the components, in particular the heavy components, should take place at a small distance from the rolling stock axis, as is the case through the rolling stock. roller geometry and knife acceptance. In this sense, a design of the rolling head has proven to be favorable, as described in the preamble of claim 1 and through the conference report on the ILAFA Rolling Mill Congress, published by the Instituto Latinoamericano del Fierro y el Acero, May 1980, page H 9/10, Figura 26, is published. According to this prior art, a radial bearing and a thrust bearing are provided in a very powerful design, in which one end of the shaft is supported, which at this end carries the tapered roller while the roller shaft at its other end rotatably, but axially displaceably in that the bevel gear of the roller drive is seated in the roller head housing. A support ring for the axial bearing is arranged between the bearings (radial and axial bearings) and the bevel gear, which is rotatably seated in the roller head housing and can be rotated for the axial adjustment of the roller. To rotate the support ring, this is via a clutch with which the roller driving bevel gear can be coupled, while the support ring is fixed non-rotatably during rolling in the roller head housing via the same clutch. A bushing is used here as a support ring, which is provided on the outside with the adjusting thread and accommodates the bearings (radial and axial bearings) in its bore.

Die Ausbildung des. Stützringes als Büchse bedingt einen um die doppelte Wandstärke der Büchse größeren Walzkopf bzw. läßt bei gegebenen Abmessungen des Walzkopfes nur Lager zu, die um die doppelte Wandstärke der Büchse im Durchmesser kleiner als Lager von maximal denkbaren Durchmessern bleiben müssen.The design of the support ring as a bushing necessitates a roller head that is twice the wall thickness of the bushing or, given the dimensions of the roller head, only allows bearings that have to remain smaller than bearings of maximum conceivable diameters by twice the wall thickness of the bushing.

Ziel der Erfindung ist eine Gestaltung von Lagerung und Anstellung der die Kegelwalzen fliegend tragenden Wellen, die eine axial wie radial gedrungene Bauweise, d.h. im letzteren eine Bauweise unter Verzicht auf nicht unmittelbar tragende Bauteile ergibt. Dieses Ziel wird durch die die kennzeichnenden Merkmale des Anspruches 1 aufweisende: Bauweise der Walzköpfe erreicht. Weitere zweckmäßige Ausgestaltungen der Erfindung sind mit den in den Ansprüchen 2 bis 6 benannten Merkmalen der besonderen Bauweisen zu erreichen.The aim of the invention is to design the mounting and adjustment of the shafts which carry the tapered rollers in a floating manner and which have an axially and radially compact construction, i.e. in the latter results in a construction without components that are not directly load-bearing. This goal is achieved by the characterizing features of claim 1: construction of the roller heads. Further expedient refinements of the invention can be achieved with the features of the special designs specified in claims 2 to 6.

Die Zeichnungen zeigen Ausführungsbeispiele der Erfindung und beschränken sich auf die Darstellung der Walzköpfe im Axialschnitt, wobei die Walzköpfe zu dritt in einem Rotor - andeutungsweise dargestellt und mit 1 bezeichnet - einsitzen und mit diesem sich in einem nicht dargestellten Stator drehen. Bauweisen von Rotoren und Statoren sind bekannt, beispielsweise aus der zum Stand der Technik bereits genannten Veröffentlichung oder dem Stand der Technik gemäß DE-OS 31 12 781.9 oder DE-OS 31 13 461.0.The drawings show exemplary embodiments of the invention and are limited to the representation of the roller heads in axial section, the roller heads being seated in three in a rotor — indicated and indicated by 1 — and rotating with it in a stator (not shown). Constructions of rotors and stators are known, for example from the prior art mentioned publication or the prior art according to DE-OS 31 12 781.9 or DE-OS 31 13 461.0.

Gemeinsam ist den Ausführungsbeispielen nach den Figuren 1, 2 und 3, daß in einer Bohrung 2 eines mit 1 bezeichneten, angedeuteten Rotors ein Walzkopf 3 mit seinem zylindrischen Ansatz 4 schwenkbar einsitzt. In dem zylindrischen Ansatz 4 ist in der Schwenkachse eine Zwischenwelle 5 gelagert, die mit einem Zwischenrad 6 in ein nicht dargestelltes, im Rotor 1 gelagertes und sich auf einem ebenfalls nicht dargestellten Sonnenrad abwälzendes Planetenrad eingreift, wodurch die Zwischenwelle 5 bei Drehung des Rotors 1 und/oder des Sonnenrades in Drehung versetzt wird. Die Zwischenwelle 5 ist ferner mit einem Kegelritzel 7 versehen, welches in ein Kegelrad 8 eingreift. Das Kegelrad 8 ist mit einer Hohlwelle. 9 verbunden und mit dieser durch Radiallager 10 und 11 sowie ein Axiallager 12 im Walzkopfgehäuse 13 gelagert. Die Hohlwelle 9 ist über die Länge ihrer Bohrung mit einer Innenverzahnung 14 versehen, in der sich das eine korrespondierend verzahnte Ende einer Walzenwelle 15 drehfest jedoch längsverschiebbar führt und zentriert. Das vordere Endeder Walzenwelle 15 stützt sich über ein Radiallager 16 und ein Axiallager 17 im Walzkopfgehäuse 13 ab. Ein aus dem Radiallager 16 vorstehender Zapfen 18 der Walzenwelle 15 trägt fliegend eine Kegelwalze 19. Die Kegelwalze 19 ist mit einem eingesetzten Ring 20 versehen, der eine Stirnverzahnung 21 aufweist und durch Stifte 22 gegen Drehung gesichert ist. Auf den außenverzahnten Zapfen 18 der Walzenwelle 15 ist eine innenverzahnte Kappe 23 aufgesetzt, die den Innenring des Lagers 16 axial gegenüber der Walzenwelle 15 festlegt. Die Kappe 23 ist ferner mit einer Stirnverzahnung korrespondierend zur Stirnverzahnung 21 versehen und stellt somit die drehfeste Verbindung der Kegelwalze 19 mit der Walzenwelle 15 her. Gehalten wird die Kegelwalze 19 auf der Walzenwelle 15 durch eine Schraube 24, die in ein Mutterstück 25 eingeschraubt ist, in das auch das eine Ende eines Zugankers 26 eingeschraubt ist, dessen anderes Ende in eine Mutter 27 eingeschraubt ist. Das Mutterstück 25 ist als Ringzylinder zur Aufnahme eines Ringkolbens 28 ausgebildet, durch dessen Beaufschlagung der Zuganker 26 gedehnt wird, so daß nach dem Anziehen der Schraube 24 und anschließenden Entlasten des Ringkolbens 28 die Spannkraft des Zugankers 26 die Kegelwalze 19 über den Ring 20 und die Kappe 23 gegen die Stirnseite der Walzenwelle 15 an deren Zapfen 18 verspannt. Um die ständige kraftschlüssige Anlage der Walzenwelle im Axiallager 17 sicherzustellen, ist die durchbohrte Walzenwelle 15 an dem der Kegelwalze 19 abgekehrten Ende mit einem Deckel 29 verschlossen, wobei der Deckel 29 eine Bohrung als Durchlaß für einen Federbolzen 30 aufweist. Eine Feder 31 in der Bohrung der Walzenwelle 15 ist zwischen dem Deckel 29 und einem Bund 32 des Federbolzens 30 eingespannt, wozu sich der Federbolzen 30 mit einer auf seinem Gewindeschaft 33 aufsitzenden Mutter 34 über ein Axiallager 35 an einem das Walzkopfgehäuse 13 an dem der Kegelwalze 19 abgekehrten Ende abschließenden Deckel 36 abstützt.Common to the exemplary embodiments according to FIGS. 1, 2 and 3 is that a roller head 3 with its cylindrical extension 4 is pivotably seated in a bore 2 of a rotor indicated by 1. In the cylindrical projection 4, an intermediate shaft 5 is mounted in the pivot axis, which engages with an intermediate gear 6 in a planet gear, not shown, mounted in the rotor 1 and rolling on a sun gear, also not shown, whereby the intermediate shaft 5 when the rotor 1 and / or the sun gear is rotated. The intermediate shaft 5 is further provided with a bevel pinion 7 which engages in a bevel gear 8. The bevel gear 8 is with a hollow shaft. 9 connected and supported with this by radial bearings 10 and 11 and an axial bearing 12 in the roller head housing 13. The hollow shaft 9 is provided over the length of its bore with an internal toothing 14, in which the one correspondingly toothed end of a roller shaft 15 rotates but is longitudinally displaceable and centered. The front end of the roller shaft 15 is supported in the roller head housing 13 via a radial bearing 16 and an axial bearing 17. A pin 18 of the roller shaft 15 protruding from the radial bearing 16 carries a tapered roller 19 on the fly. The tapered roller 19 is provided with an inserted ring 20, which has end teeth 21 and is secured against rotation by pins 22. An internally toothed cap 23 is placed on the externally toothed pin 18 of the roller shaft 15, which cap defines the inner ring of the bearing 16 axially relative to the roller shaft 15. The cap 23 is also with a spur gear Provided corresponding to the spur toothing 21 and thus produces the rotationally fixed connection of the tapered roller 19 with the roller shaft 15. The tapered roller 19 is held on the roller shaft 15 by a screw 24 which is screwed into a nut piece 25, into which one end of a tie rod 26 is also screwed, the other end of which is screwed into a nut 27. The nut piece 25 is designed as an annular cylinder for receiving an annular piston 28, by the action of which the tie rod 26 is stretched, so that after tightening the screw 24 and then relieving the annular piston 28, the tension force of the tie rod 26, the tapered roller 19 via the ring 20 and Cap 23 clamped against the end face of the roller shaft 15 at the pin 18 thereof. In order to ensure the permanent non-positive contact of the roller shaft in the axial bearing 17, the perforated roller shaft 15 is closed at the end facing away from the tapered roller 19 with a cover 29, the cover 29 having a bore as a passage for a spring bolt 30. A spring 31 in the bore of the roller shaft 15 is clamped between the cover 29 and a collar 32 of the spring bolt 30, for which purpose the spring bolt 30 with a nut 34 seated on its threaded shaft 33 via an axial bearing 35 on a roller head housing 13 on that of the tapered roller 19 opposite end closing cover 36 supports.

Bei dem Ausführungsbeispiel nach Figur 1 ist für das Axiallager 17 ein Stützring 40 vorgesehen, der mit einem Außengewinde 41 versehen ist und in der Gewindebohrung eines Einsatzringes 42 zum Walzkopfgehäuse 13 drehbar einsitzt. Der Einsatzring 42 ist im Walzenkopfgehäuse 13 gegen Drehung gesichert und im Einsatzring 42 ist wiederum der Druckring 17' des Axiallagers 17 gegen Drehung durch Rundkeile 43 gesichert. Mit der Drehung des Stützringes 40 wird somit das Axiallager 17 und mit ihm die Walzenwelle 15 mit der Kegelwalze 19 axial verstellte Hierzu ist der Stützring 40 mit einer Stirnverzahnung 44 versehen und über einen drehfest, jedoch axial verschiebbar auf der Walzenwelle 15 aufsitzenden Kuppelring 45, der eine korrespondierende Stirnverzahnung zur Stirnverzahnung 44 des Stützringes 40 aufweist, kuppelbar, so daß mit der Drehung der Walzenwelle 15 auch der Stützring 40 gedreht wird. Zur Betätigung des Kuppelringes 45 ist auf der Walzenwelle 15 ein Ring 46 befestigt, der an beiden Stirnseiten in Eindrehungen Ringkolben aufnimmt, die durch wechselweise Beaufschlagung den Kuppelring 45 in die Stirnverzahnung 44 des Stützringes 40 einrücken bzw. aus dieser ausrücken. In ausgerückter Stellung des Kuppelringes 45 folgt diesem unter der Wirkung der Feder 47 ein zweiter Kuppelring 48, der drehfest aber axialverschiebbar im Druckring 17' des Axiallagers 17 einsitzt, und der dabei mit einer korrespondierenden Stirnverzahnung in eine zweite Stirnverzahnung 49 des Stützringes 40 einrückt, so daß in dieser Position der Stützring 40 gegen unbeabsichtigte Drehung gesichert ist. Bei der axialen Verstellung der Walzenwelle 15 verschiebt sich der Innenring 16' des Radiallagers 16 gegenüber den im Außenring 1611 axial festliegenden Zylinderrollen. Der Außenring 16" des Axiallagers 16 ist in der Bohrung des Walzenkopfgehäuses 13 zwischen einem Distanzring 38 und einem das Walzenkopfgehäuse 13 walzenseitig abschließenden Deckel 37 gehalten.In the exemplary embodiment according to FIG. 1, a support ring 40 is provided for the axial bearing 17, which is provided with an external thread 41 and is rotatably seated in the threaded bore of an insert ring 42 relative to the roller head housing 13. The insert ring 42 is secured against rotation in the roller head housing 13 and the pressure ring 17 ′ is in turn in the insert ring 42 the axial bearing 17 secured against rotation by round wedges 43. With the rotation of the support ring 40, the axial bearing 17 and with it the roller shaft 15 with the tapered roller 19 are axially adjusted.To this end, the support ring 40 is provided with end teeth 44 and via a rotationally fixed but axially displaceable on the roller shaft 15 dome ring 45, which has a corresponding spur toothing to the spur toothing 44 of the support ring 40, can be coupled, so that the support ring 40 is also rotated with the rotation of the roller shaft 15. To actuate the coupling ring 45, a ring 46 is fastened on the roller shaft 15 and receives ring pistons on both end faces in turns, which, by alternating action, engage the coupling ring 45 in the front toothing 44 of the support ring 40 or disengage from it. In the disengaged position of the coupling ring 45, this is followed, under the action of the spring 47, by a second coupling ring 48, which is non-rotatably but axially displaceably seated in the pressure ring 17 'of the axial bearing 17, and which thereby engages with a corresponding spur toothing in a second spur toothing 49 of the support ring 40, so that in this position the support ring 40 is secured against unintentional rotation. During the axial adjustment of the roller shaft 15, the inner ring 16 'of the radial bearing 16 shifts in relation to the cylindrical rollers which are axially fixed in the outer ring 1611. The outer ring 16 ″ of the axial bearing 16 is held in the bore of the roller head housing 13 between a spacer ring 38 and a cover 37 that closes the roller head housing 13 on the roller side.

Das in Figur 2 dargestellte Ausführungsbeispiel entspricht dem in Figur 1 dargestellten. Lediglich das Radiallager 16 läßt keine axiale Verschiebung in sich zu, da sowohl der Innenring 16' und der Außenring 16" mit die Zylinderrollen axial festlegenden Schultern versehen sind. Dafür ist der Außenring 16" des Radiallagers 16 in der Bohrung 39 des bis zur Stirnseite des Walzenkopfgehäuses vorgezogenen Einsatzringes 42 axial verschiebbar eingepaßt.The embodiment shown in Figure 2 corresponds to that shown in Figure 1. Only the radial bearing 16 does not allow any axial displacement in itself, since both the inner ring 16 'and the outer ring 16 "are provided with shoulders which axially fix the cylindrical rollers. For this purpose, the outer ring 16" of the radial bearing 16 is in the bore 39 of the insert ring 42 which is drawn up to the end face of the roller head housing fitted axially displaceable.

Auch bei. dem Ausführungsbeispiel nach Figur 3 ist für das Axiallager 17 ein mit 50 bezeichneter Stützring vorgesehen, der mit einem Außengewinde 51 versehen ist und in der Gewindebohrung eines Einsatzringes 52 zum Walzkopfgehäuse 13 drehbar einsitzt. Der Einsatzring 52 ist im Walzenkopfgehäuse 13 gegen Drehung gesichert und im Einsatzring 52 ist wiederum der Druckring 17' des Axiallagers 17 gegen Drehung durch Rundkeile 53 gesichert. Mit der Drehung des Stützringes 50 wird somit das Axiallager 17 und mit ihm die Walzenwelle 15 mit der Kegelwalze 19 axial verstellt. Der Stützring 50 ist hierzu geteilt, wobei der Innenring 54 zum Stützring 50 in diesem drehfest aber axialbeweglich einsitzt und an beiden Stirnseiten mit Stirnverzahnungen 55 und 56 versehen ist. Die axiale Verstellung erfolgt über eine Klaue 57, die in bekannter, hier nicht näher dargestellter Weise parallel zur Achse der Walzenwelle 15 bewegbar ist und auf die Kupplungsscheibe 58 einwirkt, die Teil des Innenringes 54 des Stützringes 50 ist. In der einen Verschiebestellung rückt die Stirnverzahnung 55 des Innenringes 54 in eine korrespondierende Stirnverzahnung eines Kuppelringes 59 am Innenrand des Kranzes des Kegelrades 8 ein und verbindet somit das Kegelrad 8 mit dem Stützring 50 zur axialen Verstellung des Axiallagers 17 mit der Walzenwelle 15 und der Kegelwalze 19. In der anderen Verschiebestellung rückt die Stirnverzahnung 56 in die korrespondierende Stirnverzahnung am Kuppelring 60 ein, der einerseits drehfest, aber axial verschiebbar im Druckring 17' des Axiallagers 17 und andererseits drehbar, aber axial unverschiebbar auf einer mit dem Kranz des Kegelrades 8 verbundenen Führungshülse gehalten ist, so daß dadurch der Stützring 50 gegen unbeabsichtigte Drehung gesichert ist. Bei der axialen Verschiebung der Walzenwelle 15 bewegen sich die von den Schultern des Innenringes 16' des Radiallagers 16 axial gehaltenen Zylinderrollen in dem Außenring 16", der in der Bohrung des Walzenkopfgehäuses 13 von einem Distanzring 61 und dem Verschlußdeckel 37 axial festgelegt ist.Also at. In the exemplary embodiment according to FIG. 3, a support ring designated 50 is provided for the axial bearing 17, which is provided with an external thread 51 and is rotatably seated in the threaded bore of an insert ring 52 relative to the roller head housing 13. The insert ring 52 is secured against rotation in the roller head housing 13 and in the insert ring 52 the pressure ring 17 ′ of the axial bearing 17 is in turn secured against rotation by round wedges 53. With the rotation of the support ring 50, the axial bearing 17 and with it the roller shaft 15 with the tapered roller 19 is axially adjusted. For this purpose, the support ring 50 is divided, the inner ring 54 being seated in a rotationally fixed but axially movable manner with the support ring 50 and being provided with spur gears 55 and 56 on both end faces. The axial adjustment takes place via a claw 57, which can be moved in a known manner, not shown here, parallel to the axis of the roller shaft 15 and acts on the clutch disc 58, which is part of the inner ring 54 of the support ring 50. In one displacement position, the spur toothing 55 of the inner ring 54 engages in a corresponding spur toothing of a coupling ring 59 on the inner edge of the ring of the bevel gear 8 and thus connects the bevel gear 8 with the support ring 50 for the axial adjustment of the axial bearing 17 with the roller shaft 15 and the bevel roller 19 In the other shift position the End toothing 56 in the corresponding end toothing on the coupling ring 60, which is held on the one hand in a rotationally fixed but axially displaceable manner in the pressure ring 17 'of the axial bearing 17 and on the other hand rotatable but axially immovable on a guide sleeve connected to the ring of the bevel gear 8, so that the support ring thereby 50 is secured against unintentional rotation. During the axial displacement of the roller shaft 15, the cylindrical rollers held axially by the shoulders of the inner ring 16 'of the radial bearing 16 move in the outer ring 16 ", which is axially fixed in the bore of the roller head housing 13 by a spacer ring 61 and the sealing cap 37.

Claims (5)

1. Walzkopf eines Planeten-Schräg-Walzwerkes mit gegen die Walzgutachse geneigt gelagerter Walzenwelle, die an ihrem einen Ende von einem Radiallager und einem Axiallager abgestützt und mit einer fliegend auf dem Ende aufsitzenden Kegelwalze versehen und über das Axiallager in Achsrichtung zwecks Walzenanstellung verschiebbar ist, wobei die Walzenwelle mit ihrem anderen Ende drehfest jedoch axial verschiebbar in einem im Walzkopfgehäuse gelagerten Kegelrad einsitzt, während das die Walzenwelle axial stützende Lager in einem in Achsrichtung der Walzenwelle verstellbar im Walzkopfgehäuse einsitzenden Stützring einsitzt und der Stützring über eine zwischen ihm und dem Kegelrad angeordnete Schaltkupplung wahlweise entweder mit dem im Walzkopfgehäuse drehfest einsitzenden Muttergewindering zum Stützring während des Walzbetriebes oder mit dem Kegelrad zwecks axialer Verstellung der Walze über den Stützring kuppelbar ist, wobei ferner im Walzkopfgehäuse eine Zwischenwelle parallel zur Walzgutachse gelagert ist, die über ein Kegelritzel und ein Zwischenrad das Kegelrad mit dem zugehörigen Planetenrad getrieblich verbindet,
dadurch gekennzeichnet,
daß der Stützring (40, 50) unmittelbar den gehäuseseitigen Druckring (17') des Axiallagers (17) abstützt und mit zwei entgegengesetzt gerichteten Stirnverzahnungen (44/49, 55/ 56) versehen ist, die im Wechsel mit zwei Kuppelringen (45/48, 59/60) mit korrespondierenden Stirnverzahnungen durch relative Axialbewegung verbindbar sind, wobei der eine Kuppelring (45, 59) mit dem Stützring (40, 50) zur axialen Verstellung des Stützringes mit der Walzenwelle (15) bzw'. dem die Walzenwelle antreibenden Kegelrad (8) drehfest verbindbar ist, während der andere Kuppelring (48, 60) mit dem Stützring (40, 50) zur Sicherung der Position des Stützringes (40, 50) mit dem Druckring (171) des Axiallagers (17), der seinerseits drehfest, aber axial beweglich im Walzkopfgehäuse (13) (-einsatz) (42, 52) einsitzt, verbindbar ist, und daß das dem Axiallager (17) vorgeordnete Radiallager (16) in sich durch Lageveränderung zwischen Innen- (16') und Außenring (16") oder in seinem Sitz durch Lageveränderung des Außenrings (16") in der Bohrung (19) des Walzkopfgehäuses (13) (-einsatzes) (52) die axiale Verstellung der Walze (19) aufnimmt.
Walzkopf nach Anspruch 1,
dadurch gekennzeichnet,
daß der den Stützring (40) mit der Walzenwelle (15) drehfest verbindende Kuppelring (45) drehfest, jedoch axial verschiebbar auf der Walzenwelle (15) aufsitzt und bei seiner Axialverschiebung den zweiten Kuppelring (48), der frei drehbeweglich gegenüber dem ersten Kuppelring (45) ist, axial verschiebt und, daß die Kuppelringe (45, 48) in den extremen Positionen der Axialverschiebung wechselweise den gegenseitigen Eingriff der Stirnverzahnungen (44, 49) des Stützringes (40) mit der Stirnverzahnung (44) des einen (45) oder (49) des anderen (48) Kuppelringes bewirkt.1. Rolling head of a planetary inclined rolling mill with a roller shaft which is inclined against the rolling stock axis and which is supported at one end by a radial bearing and an axial bearing and is provided with a tapered roller which is seated on the end and can be displaced in the axial direction via the axial bearing for the purpose of roll adjustment. whereby the other end of the roller shaft is non-rotatably but axially displaceably seated in a bevel gear mounted in the roller head housing, while the bearing supporting the roller shaft axially is seated in a support ring which is adjustable in the axial direction of the roller shaft in the roller head housing and the support ring via a clutch arranged between it and the bevel gear either with the nut threaded ring, which is seated in the roll head housing in a rotationally fixed manner, for the support ring during rolling operation or with the bevel gear for the purpose of axially adjusting the roll via the support ring, an intermediate shaft also parallel to the rolling stock in the roll head housing axle is mounted, which connects the bevel gear with the associated planet gear via a bevel pinion and an intermediate gear,
characterized,
that the support ring (40, 50) directly supports the housing-side pressure ring (17 ') of the thrust bearing (17) and is provided with two opposing spur gear teeth (44/49, 55/56) which alternate with two coupling rings (45/48 , 59/60) with corresponding spur gears can be connected by relative axial movement, the one coupling ring (45, 59) with the support ring (40, 50) for axially adjusting the support ring with the roller shaft (15) or '. the bevel gear (8) driving the roller shaft can be connected in a rotationally fixed manner, while the other coupling ring (48, 60) with the support ring (40, 50) to secure the position of the support ring (40, 50) with the pressure ring (17 1 ) of the axial bearing ( 17), which in turn is non-rotatably but axially movable in the roller head housing (13) (insert) (42, 52), is connectable, and that the radial bearing (17) upstream of the axial bearing (17) is inherently damaged by changing the position between the inner ( 16 ') and outer ring (16 ") or in its seat by changing the position of the outer ring (16") in the bore (19) of the roller head housing (13) (insert) (52) takes up the axial adjustment of the roller (19).
Rolling head according to claim 1,
characterized,
that the support ring (40) with the roller shaft (15) rotatably connecting coupling ring (45) rotatably but axially displaceably on the roller shaft (15) and with its axial displacement the second coupling ring (48), which is freely rotatable relative to the first coupling ring ( 45), axially displaces and that the coupling rings (45, 48) in the extreme positions of the axial displacement alternately the mutual engagement of the spur gear teeth (44, 49) of the support ring (40) with the spur gear teeth (44) of one (45) or (49) of the other (48) coupling ring. 3. Walzkopf nach Anspruch 2,
dadurch gekennzeichnet,
daß die Walzenwelle (15) mit einem Bund bzw. aufgesetzten Bundring (46) versehen ist, an dem sich die Mittel zur Axialverschiebung des einen Kuppelringes (45) abstützen.3. Rolling head according to claim 2,
characterized,
that the roller shaft (15) is provided with a collar or an attached collar ring (46) on which the means for axially displacing the one coupling ring (45) are supported. 4..Walzkopf nach Anspruch 3,
dadurch gekennzeichnet,
daß als Mittel zur Axialverschiebung in einer Richtung ein Ringkolben und in der Gegenrichtung ein zweiter Ringkolben oder Federn angeordnet sind.4. Rolling head according to claim 3,
characterized,
that an annular piston and a second annular piston or springs are arranged as means for axial displacement in one direction. 5. Walzkopf nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, -
daß der zweite Kuppelring (48) sich über Federn (47) am Druckring des Axiallagers (17) abstützt, die Federn in Richtung Einrückstellung des zweiten Kuppelringes (48) wirken und in der die Einrückposition des ersten Kuppelringes (45) ergebenden Position des ersten Kuppelringes (45) dieser den zweiten Kuppelring (48) gegen die Federkraft (33) ausgerückt hält.5. Rolling head according to one of claims 2 to 4, characterized in that
that the second coupling ring (48) is supported by springs (47) on the thrust ring of the thrust bearing (17), the springs act in the direction of engagement of the second coupling ring (48) and in the position of engagement of the first coupling ring (45) resulting in the position of the first coupling ring (45) this keeps the second coupling ring (48) disengaged against the spring force (33). 6. Walzkopf nach Anspruch 1,
dadurch gekennzeichnet,
daß der Stützring (50) mit einem drehfest, jedoch axial in ihm verschiebbaren Einsatzring (54), der die beiden entgegengesetzt gerichteten Stirnverzahnungen (55, 56) trägt, versehen ist und der Stützring (50) durch axiale Verschiebung des Einsatzringes (54) wahlweise mit dem die Walzenwelle (15) antreibenden, zugleich als Kuppelring (59) ausgebildeten Kegelrad (8) oder dem drehfest, jedoch axial verschiebbar im Druckring (17') des Axiallagers (17) einsitzenden zweiten Kuppelring (60) verbindbar ist.6. Rolling head according to claim 1,
characterized,
that the support ring (50) is provided with a non-rotatable but axially displaceable insert ring (54), which carries the two oppositely directed spur gears (55, 56), and the support ring (50) by axial displacement of the insert ring (54) optionally with the bevel gear (8) driving the roller shaft (15) and at the same time designed as a coupling ring (59) or with the second coupling ring (60) seated in a rotationally fixed but axially displaceable manner in the pressure ring (17 ') of the axial bearing (17).
EP83107359A 1982-08-05 1983-07-27 Roll head of a planetary cross-rolling mill Expired EP0100957B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83107359T ATE23458T1 (en) 1982-08-05 1983-07-27 ROLLER HEAD OF A PLANETARY INCLINED ROLLING MILL.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3229211 1982-08-05
DE19823229211 DE3229211A1 (en) 1982-08-05 1982-08-05 ROLLING HEAD OF A PLANETE SCHRAEG ROLLING MILL

Publications (2)

Publication Number Publication Date
EP0100957A1 true EP0100957A1 (en) 1984-02-22
EP0100957B1 EP0100957B1 (en) 1986-11-12

Family

ID=6170179

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83107359A Expired EP0100957B1 (en) 1982-08-05 1983-07-27 Roll head of a planetary cross-rolling mill

Country Status (5)

Country Link
US (1) US4587820A (en)
EP (1) EP0100957B1 (en)
JP (1) JPS5945007A (en)
AT (1) ATE23458T1 (en)
DE (2) DE3229211A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2734318B1 (en) 2011-07-21 2017-01-04 Siempelkamp Maschinen- und Anlagenbau GmbH Roll for a ring rolling mill

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3531529A1 (en) * 1985-09-04 1987-03-12 Schloemann Siemag Ag Rolling head for planetary skew rolling mills
JPH0590312U (en) * 1991-09-09 1993-12-10 和義 国定 Both vertical and horizontal undulating level
US6792781B1 (en) * 1995-03-24 2004-09-21 Kocks Technik Gmbh & Co. Arrangement for inclined rolling of tube-shaped or bar shaped rolling products
FI109528B (en) * 1999-12-21 2002-08-30 Outokumpu Oy Rolling head for a planetary rolling device
DE10261057A1 (en) * 2002-12-24 2004-07-22 Sms Meer Gmbh Roll arrangement for a rolling mill
DE102012111655B3 (en) * 2012-11-30 2014-03-13 Siempelkamp Maschinen- Und Anlagenbau Gmbh & Co. Kg Axialwalzenvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3030052A1 (en) * 1980-08-08 1982-03-04 Schloemann-Siemag AG, 4000 Düsseldorf Roll head, esp. for stretch reducing mill - where roll shafts are supported by axial and radial thrust roller bearings permitting adjustment of roll gap
DE3125682A1 (en) * 1980-08-08 1982-04-15 SMS Schloemann-Siemag AG, 4000 Düsseldorf Rolling head of a cross-rolling mill
DE3112781A1 (en) * 1981-03-31 1982-10-07 SMS Schloemann-Siemag AG, 4000 Düsseldorf Slant rolling mill for reducing full and hollow cross-sections
DE3113461A1 (en) * 1981-04-03 1982-10-14 SMS Schloemann-Siemag AG, 4000 Düsseldorf BEARING ROLLING MILL FOR REDUCING FULL AND HOLLOW SECTIONS

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2748770A1 (en) * 1970-03-03 1979-05-10 Schloemann Siemag Ag Roll head with bevel rollers - has coupling bushings with intermediate position disengaging adjusting bushing from hollow shaft
DE2009867C3 (en) * 1970-03-03 1978-08-03 Schloemann-Siemag Ag, 4000 Duesseldorf Rolling head with overhung rolls inclined towards the rolling stock axis
US3735617A (en) * 1970-10-19 1973-05-29 Siemag Siegener Masch Bau Rolling mill

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3030052A1 (en) * 1980-08-08 1982-03-04 Schloemann-Siemag AG, 4000 Düsseldorf Roll head, esp. for stretch reducing mill - where roll shafts are supported by axial and radial thrust roller bearings permitting adjustment of roll gap
DE3125682A1 (en) * 1980-08-08 1982-04-15 SMS Schloemann-Siemag AG, 4000 Düsseldorf Rolling head of a cross-rolling mill
DE3112781A1 (en) * 1981-03-31 1982-10-07 SMS Schloemann-Siemag AG, 4000 Düsseldorf Slant rolling mill for reducing full and hollow cross-sections
DE3113461A1 (en) * 1981-04-03 1982-10-14 SMS Schloemann-Siemag AG, 4000 Düsseldorf BEARING ROLLING MILL FOR REDUCING FULL AND HOLLOW SECTIONS

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2734318B1 (en) 2011-07-21 2017-01-04 Siempelkamp Maschinen- und Anlagenbau GmbH Roll for a ring rolling mill

Also Published As

Publication number Publication date
ATE23458T1 (en) 1986-11-15
US4587820A (en) 1986-05-13
DE3367536D1 (en) 1987-01-02
JPS5945007A (en) 1984-03-13
EP0100957B1 (en) 1986-11-12
DE3229211A1 (en) 1984-02-09
JPS649083B2 (en) 1989-02-16

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