EP0354170B1 - Device for axially guiding the cylinders of rolling stands - Google Patents

Device for axially guiding the cylinders of rolling stands Download PDF

Info

Publication number
EP0354170B1
EP0354170B1 EP89730180A EP89730180A EP0354170B1 EP 0354170 B1 EP0354170 B1 EP 0354170B1 EP 89730180 A EP89730180 A EP 89730180A EP 89730180 A EP89730180 A EP 89730180A EP 0354170 B1 EP0354170 B1 EP 0354170B1
Authority
EP
European Patent Office
Prior art keywords
axial
rollers
roller
roll
chocks
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.)
Expired - Lifetime
Application number
EP89730180A
Other languages
German (de)
French (fr)
Other versions
EP0354170A2 (en
EP0354170A3 (en
Inventor
Wilhelm Ing. Schwerdt (Grad)
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.)
Vodafone GmbH
Original Assignee
Mannesmann AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6360518&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0354170(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Mannesmann AG filed Critical Mannesmann AG
Publication of EP0354170A2 publication Critical patent/EP0354170A2/en
Publication of EP0354170A3 publication Critical patent/EP0354170A3/en
Application granted granted Critical
Publication of EP0354170B1 publication Critical patent/EP0354170B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/08—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling structural sections, i.e. work of special cross-section, e.g. angle steel

Definitions

  • the invention relates to a device for the axial guidance of the rolls of roll stands for the production of section steel.
  • a device for the axial guidance of the rolls of roll stands for the production of section steel For the rolling of profiles, in particular non-symmetrical profiles in caliber rolls, it is necessary to ensure that a certain relative axial position of the opposing rolls is maintained and, if necessary, to make a correction by changing the axial position of the rolls relative to one another.
  • axial forces arise in the rolling caliber, which negatively influence the accuracy of the rolling and the straight running of the rolling stock.
  • the object of the present invention is, using the proven rigid conventional system, to carry out an axial guidance of the rolls in which the axial forces occurring in the roll calibres can be compensated directly on the rolls.
  • the invention undertakes direct axial force compensation where it arises, namely on the roller itself, without having to give up the rigid conventional system. All that is necessary is to provide at least two bearings that absorb axial forces on each roller, one of which has to transmit only relatively small axial forces in combination with a radial bearing.
  • An economical solution can be a four-row tapered roller bearing paired with a strong thrust bearing.
  • rollers are mounted in displaceable chocks, the axial forces causing a displacement being measured on the chocks or in the vicinity thereof.
  • a hydraulic unit then acts on the strong axial bearing provided on the journal of the rollers, with which the acting axial force is opposed by an equally large, oppositely directed compensation force.
  • the axial bearings on the roll journals of one roll stand side are connected to a cross-piece extending transversely to the roll axes, on the two free ends of which double-acting piston-cylinder units are articulated which are supported on the roller stand.
  • duo roll stands it is sufficient to introduce a pair of forces into the rolls, for which the heavy crossbar is sufficient. Since it is a pure balancing of forces, the components belonging to the traverse, including the thrust bearing, need only be dimensioned according to strength and not according to the deformation.
  • the cylinder supporting the crossmember against the roll stand can be acted upon by a rapidly acting pressure control with cylinder forces which can be changed in size and direction, so that the external forces which act on the rolls in the axial direction can be traced back to zero.
  • This solution ensures that the forces that the conventional axial guide system has to absorb remain very low. At that time, this low level of force led to very small deformations in the entire axial guide system of the rollers.
  • each horizontal roller is then provided with an independent system for balancing the forces; it is therefore possible to dispense with the traverse described above for connecting the adjacent rollers.
  • the rolls of the set of rolls of the profiled rolls are designated by 1, which are mounted in chocks 2 in the roll stand 3 and, as indicated at 4, can be adjusted horizontally by means of spindles.
  • the rollers are loaded in the axial direction by the axial forces F A , which act on the roller bearings in the direction of the arrow.
  • Figure 2 also shows schematically the storage of the rollers in the chocks 2.
  • the roller journals 6 run in the chocks 2, in which they are rotatably mounted in tapered roller bearings 7.
  • the tapered roller bearings 7 are also able to absorb axial force components from the rollers.
  • the chocks 2 are displaceable in the axial direction by means of adjusting devices in the form of piston-cylinder units 8 and 9, for this purpose the linear movement of the piston-cylinder units 8 and 9 via levers 10 and 11, which are articulated at 12 on the roller stand are diverted, the levers 10 and 11 each acting in different directions of movement on a collar projection 13 of the guide bush 5.
  • the piston-cylinder units 14 are arranged at the free ends of a crossmember 5, which at 15 and 16 is connected by bolts and joints to the heavy axial bearing 17 (FIG. 2), which rests on each elongated roller journal 6a the roller 1 is seated.
  • the piston-cylinder units 14 forces can be transmitted to the axial bearings 17 via the crossmember 5, but their size in the opposite direction corresponds to the axial forces that arise in the calibres when the rolling stock is rolled. It is thus possible to reduce the external forces acting on the rollers in the axial direction to zero, with compensation taking place directly where the forces arise, namely on the roller. Deformations of the inner parts of the chocks including the bearing deformations are eliminated.
  • the system is extremely stiff due to the use of conventional mechanical components and particularly precise due to the reduction in the axial forces acting on the actual displacement device. This enables optimal axial guidance of the rolls during the rolling process, which ensures the quality of the rolled product.

Description

Die Erfindung betrifft eine Vorrichtung zur Axialführung der Walzen von Walzgerüsten zur Herstellung von Profilstahl. Für das Walzen von Profilen, insbesondere nicht symmetrischen Profilen in Kaliberwalzen ist es erforderlich, die Einhaltung einer bestimmten relativen Axiallage der sich gegenüberliegenden Walzen sicherzustellen und gegebenenfalls durch Veränderung der Axiallage der Walzen zueinander eine Korrektur vorzunehmen. Besonders bei nicht symmetrischen Profilen entstehen Axialkräfte im Walzkaliber, die die Genauigkeit der Walzung und den Geradeauslauf des Walzgutes negativ beeinflussen. Gleiches gilt für die Horizontalwalzen eines Universalwalzgerüstes, da durch Axialverschiebung der Horizontalwalzen aufgrund unsymmetrischer Walzkräfte die Toleranz der Flanschabmessungen von Parallelflanschträgern nachteilig beeinflußt werden kann.The invention relates to a device for the axial guidance of the rolls of roll stands for the production of section steel. For the rolling of profiles, in particular non-symmetrical profiles in caliber rolls, it is necessary to ensure that a certain relative axial position of the opposing rolls is maintained and, if necessary, to make a correction by changing the axial position of the rolls relative to one another. In the case of non-symmetrical profiles, axial forces arise in the rolling caliber, which negatively influence the accuracy of the rolling and the straight running of the rolling stock. The same applies to the horizontal rolls of a universal rolling stand, since the tolerance of the flange dimensions of parallel flange carriers can be adversely affected by axial displacement of the horizontal rolls due to asymmetrical rolling forces.

Es ist bereits versucht worden, die Axialverschiebung der Walzen aufgrund hoher auftretender Axialkräfte dadurch zu unterbinden, daß an den Walzen Anlaufbunde vorgesehen wurden, die ein Axialverschieben der Walzen verhindern. Das führt an den Anlaufbunden zu hohem Verschleiß und damit zu beträchtlichen Walzenkosten.Attempts have already been made to prevent the axial displacement of the rollers due to the high axial forces which occur by providing thrust collars on the rollers which prevent axial displacement of the rollers. This leads to high wear on the start-up coils and thus to considerable rolling costs.

Zur Vermeidung dessen ist bereits vorgeschlagen worden (DE 36 28 733 A1) auf Anlaufbunde zu verzichten und die Axialführung der Walzen hydraulisch vorzunehmen. Diese Führung muß extrem steif ausgeführt sein und es ist erforderlich, eine hydraulische Positionsregelung vorzusehen, die mit einer genauen Istwerterfassung für die Walzenverschiebung unmittelbar an den Walzen versehen sein muß, wenn die Verformung der Innenteile der Einbaustücke einschließlich der Lagerverformungen mitberücksichtigt werden soll. Dies erscheint bei der bekannten Lösung aufgrund der Umgebungsbedingungen nur unzureichend lösbar zu sein, so daß nach einem anderen Weg zur Lösung des Problemes gesucht wurde.To avoid this, it has already been proposed (DE 36 28 733 A1) to dispense with starting collars and to perform the axial guidance of the rollers hydraulically. This guide must be extremely rigid and it is necessary to provide a hydraulic position control, which must be provided with an accurate actual value detection for the roll displacement directly on the rolls if the deformation of the inner parts of the chocks including the bearing deformations is to be taken into account. In the known solution, this appears to be insufficiently solvable due to the environmental conditions, so that another way to solve the problem was sought.

Aufgabe der vorliegenden Erfindung ist es, unter Verwendung des bewährten steifen konventionellen Systems eine Axialführung der Walzen vorzunehmen, bei der eine kompensation der in den Walzkalibern auftretenden Axialkräfte unmittelbar an den Walzen vorgenommen werden kann.The object of the present invention is, using the proven rigid conventional system, to carry out an axial guidance of the rolls in which the axial forces occurring in the roll calibres can be compensated directly on the rolls.

Zur Lösung der Aufgabe wird erfindungsgemäß die Kombination der im Patentanspruch 1 aufgeführten Merkmale vorgeschlagen.To achieve the object, the combination of the features listed in claim 1 is proposed according to the invention.

Im Gegensatz zum beschriebenen Stand der Technik wird bei der Erfindung eine direkte Axialkraftkompensation dort vorgenommen, wo sie entsteht, nämlich an der Walze selbst, ohne dabei das steife konventionelle System aufgeben zu müssen. Dazu ist es lediglich erforderlich, auf jeder Walze mindestens zwei Axialkräfte aufnehmende Lager vorzusehen, von denen das eine in Kombination mit einem Radiallager nur relativ kleine Axialkräfte zu übertragen hat. Eine wirtschaftliche Lösung kann dabei beispielsweise ein vier-reihiges kegelrollenlager darstellen, das mit einem starken Axiallager gepaart ist.In contrast to the described prior art, the invention undertakes direct axial force compensation where it arises, namely on the roller itself, without having to give up the rigid conventional system. All that is necessary is to provide at least two bearings that absorb axial forces on each roller, one of which has to transmit only relatively small axial forces in combination with a radial bearing. An economical solution can be a four-row tapered roller bearing paired with a strong thrust bearing.

In herkömmlicher Weise sind die Walzen in verschiebbaren Einbaustücken gelagert, wobei die eine Verschiebung bewirkenden Axialkräfte an den Einbaustücken oder in deren Nähe gemessen wird. An dem auf dem Zapfen der Walzen vorgesehenen kräftigen Axiallager greift dann eine Hydraulikeinheit an, mit der der wirkenden Axialkraft eine gleichgroße entgegengesetzt gerichtete Kompensationskraft entgegengesetzt wird.In a conventional manner, the rollers are mounted in displaceable chocks, the axial forces causing a displacement being measured on the chocks or in the vicinity thereof. A hydraulic unit then acts on the strong axial bearing provided on the journal of the rollers, with which the acting axial force is opposed by an equally large, oppositely directed compensation force.

Nach einem weiteren Merkmal der Erfindung ist zur Anwendung an einem Duo-Walzgerüst vorgesehen, daß die Axiallager auf den Walzenzapfen einer Walzgerüstseite mit einer sich quer zu den Walzenachsen erstreckenden Traverse verbunden sind, an deren beiden freien Enden doppelt wirkende Kolben-Zylinder-Einheiten angelenkt sind, die sich am Walzenständer abstützen.According to a further feature of the invention, it is provided for use on a duo roll stand that the axial bearings on the roll journals of one roll stand side are connected to a cross-piece extending transversely to the roll axes, on the two free ends of which double-acting piston-cylinder units are articulated which are supported on the roller stand.

Bei Duo-Walzgerüsten genügt die Einleitung eines Kräftepaares in die Walzen, wozu die schwere Traverse ausreicht. Da es sich um einen reinen Kräfteausgleich handelt, brauchen die zur Traverse gehörenden Bauteile einschließlich des Axiallagers nur nach Festigkeit und nicht nach der Verformung dimensioniert zu werden.With duo roll stands, it is sufficient to introduce a pair of forces into the rolls, for which the heavy crossbar is sufficient. Since it is a pure balancing of forces, the components belonging to the traverse, including the thrust bearing, need only be dimensioned according to strength and not according to the deformation.

Die die Traverse gegen den Walzenständer abstützenden Zylinder können durch einen schnell wirkende Druckregelung mit in Größe und Richtung veränderbaren Zylinderkräften beaufschlagt werden, so daß die äußeren Kräfte, die in axialer Richtung aus dem Kaliber auf die Walzen wirken, gegen Null zurückführbar sind. Durch diese Lösung wird gewährleistet, daß die Kräfte, die das herkömmliche axiale Führungssystem aufzunehmen hat, sehr gering bleiben. Dieses niedrige kraftniveau führt seinerzeit zu sehr kleinen Verformungen im gesamten axialen Führungssystem der Walzen.The cylinder supporting the crossmember against the roll stand can be acted upon by a rapidly acting pressure control with cylinder forces which can be changed in size and direction, so that the external forces which act on the rolls in the axial direction can be traced back to zero. This solution ensures that the forces that the conventional axial guide system has to absorb remain very low. At that time, this low level of force led to very small deformations in the entire axial guide system of the rollers.

Die Anwendung der Erfindung bei einem Universal-Trägergerüst ist gleichsam dadurch möglich, daß dann jede Horizontalwalze mit einem unabhängigen System zum Ausgleich der Kräfte versehen ist; also auf die vorstehend beschriebene Traverse zur Verbindung der benachbarten Walzen verzichtet werden kann.The application of the invention to a universal support frame is possible, as it were, in that each horizontal roller is then provided with an independent system for balancing the forces; it is therefore possible to dispense with the traverse described above for connecting the adjacent rollers.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend beschrieben. Es zeigt:

  • Fig. 1 eine schematische Ansicht eines Duo-Walzensatzes eines Walzgerüstes zur Herstellung von Profilstahl und
  • Fig. 2 die erfindungsgemäße Einrichtung zum Kraftausgleich der Axialkräfte.
An embodiment of the invention is shown in the drawing and is described below. It shows:
  • Fig. 1 is a schematic view of a duo-roll set of a roll stand for the production of section steel and
  • Fig. 2 shows the device according to the invention for balancing the axial forces.

In Figur 1 sind die Walzen des Walzensatzes der profilierten (nicht dargestellten) Walzen mit 1 bezeichnet, die in Einbaustücken 2 im Walzenständer 3 gelagert sind und über, wie bei 4 angedeutet, Spindeln horizontal anstellbar sind. Während des Walzprozesses werden die Walzen in Axialrichtung durch die Axialkräfte FA belastet, die in Pfeilrichtung auf die Walzenlager wirken.In FIG. 1, the rolls of the set of rolls of the profiled rolls (not shown) are designated by 1, which are mounted in chocks 2 in the roll stand 3 and, as indicated at 4, can be adjusted horizontally by means of spindles. During the rolling process, the rollers are loaded in the axial direction by the axial forces F A , which act on the roller bearings in the direction of the arrow.

Figur 2 zeigt ebenfalls schematisch die Lagerung der Walzen in den Einbaustücken 2. Wie dargestellt, laufen die Walzenzapfen 6 in den Einbaustücken 2, in denen sie in kegelrollenlagern 7 drehbar gelagert sind. Die kegelrollenlager 7 sind in der Lage, auch Axialkraftanteile aus den Walzen aufzunehmen. Die Einbaustücke 2 sind mit Hilfe von Anstellvorrichtungen in Form von kolben-Zylinder-Einheiten 8 und 9 um kleine Verschiebewege in Achsrichtung verschiebbar, wozu die Linearbewegung der kolben-Zylinder-Einheiten 8 und 9 über Hebel 10 und 11, die bei 12 am Walzenständer angelenkt sind, umgeleitet wird, wobei die Hebel 10 und 11 jeweils in unterschiedlichen Bewegungsrichtungen auf einen Bundvorsprung 13 der Führungsbuchse 5 wirken.Figure 2 also shows schematically the storage of the rollers in the chocks 2. As shown, the roller journals 6 run in the chocks 2, in which they are rotatably mounted in tapered roller bearings 7. The tapered roller bearings 7 are also able to absorb axial force components from the rollers. The chocks 2 are displaceable in the axial direction by means of adjusting devices in the form of piston-cylinder units 8 and 9, for this purpose the linear movement of the piston-cylinder units 8 and 9 via levers 10 and 11, which are articulated at 12 on the roller stand are diverted, the levers 10 and 11 each acting in different directions of movement on a collar projection 13 of the guide bush 5.

Mit Hilfe einer am Einbaustück 2 oder an den Kolben-Zylinder-Einheiten 8 und 9 vorgesehenen Meßeinrichtung, die mittels Dehnungsmeßstreifen, Kraftmeßdosen und/oder Druckveränderungen in den Hydraulikzylindern funktionieren kann, werden die aus den Kalibern resultierenden Axialkräfte erkannt und gemessen und in einem Steuersystem in eine hydraulische Kraft umgesetzt, mit der die doppelt beaufschlagbaren Kolben-Zylinder-Einheiten 14 der erfindungsgemäßen Einrichtung beaufschlagt werden.With the aid of a measuring device provided on the chock 2 or on the piston-cylinder units 8 and 9, which can function by means of strain gauges, load cells and / or pressure changes in the hydraulic cylinders, the axial forces resulting from the calibres are recognized and measured and in a control system in implemented a hydraulic force with which the double-acting piston-cylinder units 14 of the device according to the invention are applied.

Wie aus Figur 1 ersichtlich, sind die Kolben-Zylinder-Einheiten 14 an den freien Enden einer Traverse 5 angeordnet, die bei 15 und 16 über Bolzen und Gelenke mit dem schweren Axiallager 17 (Figur 2) verbunden ist, das auf jedem verlängerten Walzenzapfen 6a der Walzen 1 aufsitzt. Durch Beaufschlagung der Kolben-Zylinder-Einheiten 14 lassen sich somit über die Traverse 5 Kräfte auf die Axiallager 17 übertragen, die in ihrer Größe jedoch in entgegengesetzter Richtung, den in den Kalibern entstehenden Axialkräften beim Walzen des Walzgutes entsprechen. Somit ist es möglich, die in axialer Richtung auf die Walzen wirkenden äußeren Kräfte gegen Null zurückzuführen, wobei eine Kompensation unmittelbar dort erfolgt, wo die Kräfte entstehen, nämlich an der Walze. Verformungen der Innenteile der Einbaustücke einschließlich der Lagerverformungen werden dabei ausgeschaltet. Das System ist, wegen der Verwendung herkömmlicher mechanischer Bauteile äußerst steif und durch die Reduzierung der an der eigentlichen Verschiebeeinrichtung wirkenden Axialkräfte besonders exakt. Auf diese Weise wird eine optimale Axialführung der Walzen während des Walzprozesses ermöglicht, durch die die Qualität des Walzproduktes gewährleistet ist.As can be seen from FIG. 1, the piston-cylinder units 14 are arranged at the free ends of a crossmember 5, which at 15 and 16 is connected by bolts and joints to the heavy axial bearing 17 (FIG. 2), which rests on each elongated roller journal 6a the roller 1 is seated. By acting on the piston-cylinder units 14, forces can be transmitted to the axial bearings 17 via the crossmember 5, but their size in the opposite direction corresponds to the axial forces that arise in the calibres when the rolling stock is rolled. It is thus possible to reduce the external forces acting on the rollers in the axial direction to zero, with compensation taking place directly where the forces arise, namely on the roller. Deformations of the inner parts of the chocks including the bearing deformations are eliminated. The system is extremely stiff due to the use of conventional mechanical components and particularly precise due to the reduction in the axial forces acting on the actual displacement device. This enables optimal axial guidance of the rolls during the rolling process, which ensures the quality of the rolled product.

Claims (1)

  1. A device for axially guiding the rollers (1) of roll stands for producing sectional steel, in which the journals (6) of the rollers (1) are mounted so as to be rotatable radially and axially in chocks (2) which are axially displaceable by means of adjusting devices (8, 9) therein, which devices are supported on the roll housing (3), with an axial bearing (17) being located on at least one journal (6) of each roller (1), which bearing can be acted upon with a force acting in the axial direction by means of a hydraulic unit (14) supported against the roll housing (3),
    characterised in that
    the axial bearings (17) on the roller journals (6) of one side of the roll stand are connected to a crossbar (5) extending transversely to the roller axes, on the two free ends of which crossbar piston-cylinder units (14) which can be doubly acted upon are articulated, which units are supported directly on the roll housing (3) and are connected via a control means to a means for detecting the axial force acting on the rollers (1), which means is located on the chocks (2) and/or adjusting devices (8, 9).
EP89730180A 1988-08-05 1989-08-02 Device for axially guiding the cylinders of rolling stands Expired - Lifetime EP0354170B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3827018A DE3827018A1 (en) 1988-08-05 1988-08-05 DEVICE FOR THE AXIAL GUIDE OF THE ROLLS OF WHEEL RODS FOR THE PRODUCTION OF PROFILE STEEL
DE3827018 1988-08-05

Publications (3)

Publication Number Publication Date
EP0354170A2 EP0354170A2 (en) 1990-02-07
EP0354170A3 EP0354170A3 (en) 1990-11-22
EP0354170B1 true EP0354170B1 (en) 1992-09-23

Family

ID=6360518

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89730180A Expired - Lifetime EP0354170B1 (en) 1988-08-05 1989-08-02 Device for axially guiding the cylinders of rolling stands

Country Status (3)

Country Link
EP (1) EP0354170B1 (en)
JP (1) JP2651939B2 (en)
DE (2) DE3827018A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003048006A (en) * 2001-08-02 2003-02-18 Mitsubishi Heavy Ind Ltd Fluid-pressure cylinder and rolling mill
DE102007042896A1 (en) * 2007-03-15 2008-09-18 Sms Demag Ag rolling device
CN104209330B (en) * 2014-08-14 2016-05-11 湖州倍格曼新材料有限公司 For the production of the shaped device of band

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE551021C (en) * 1932-05-25 Anton Schoepf Dipl Ing Device for caliber drag mills for adjusting the drag rollers in the axial direction
IT941182B (en) * 1970-11-18 1973-03-01 Nippon Kokan Kk COLD ROLLING APPARATUS AND ITS WORKING METHOD
US4203310A (en) * 1978-12-28 1980-05-20 Krylov Nikolai I Mill stand roll assembly
DE3628733A1 (en) * 1986-08-23 1988-02-25 Schloemann Siemag Ag DEVICE FOR AXIAL POSITIONING OF THE ROLLS OF ROLLING MILLS FOR THE PRODUCTION OF PROFILE STEEL

Also Published As

Publication number Publication date
JP2651939B2 (en) 1997-09-10
EP0354170A2 (en) 1990-02-07
DE3827018C2 (en) 1992-06-04
JPH02142606A (en) 1990-05-31
EP0354170A3 (en) 1990-11-22
DE3827018A1 (en) 1990-02-08
DE58902329D1 (en) 1992-10-29

Similar Documents

Publication Publication Date Title
DE2942002A1 (en) PRESSURE TREATMENT ROLLER
EP0348711B1 (en) Device for axially shifting rolls in the stand of a rolling mill
DE19924860B4 (en) Rolling mill for sheet metal
DE3329595C2 (en) Roll for a film drawing calender
EP1181114B1 (en) Bending device for the working rolls of a hot-rolling frame
EP0354170B1 (en) Device for axially guiding the cylinders of rolling stands
DE2441307B2 (en) Universal rolling mill with cap stand
EP0293670B1 (en) Device for axial shifting of rotating cylinders
DE1809262C3 (en) Roll stand
DE1809260A1 (en) Rolling mill
DE2832966A1 (en) Rolling mill forming roller coupling - has intermediate bush and roller forming clearance fit on shaft
DE2335809C2 (en) Roll stand
EP2763801B1 (en) Installation and method for continuously moulding longitudinally slotted pipes
EP1114890A2 (en) Roll arrangement and roll
EP0962668B1 (en) Pressure roll
DE2150323B2 (en) Roll stand with axial adjustment of at least one roll
DE19653023B4 (en) Device for balancing the roll position in rolling stands with two work rolls each of longitudinal roll trains
EP0734794B1 (en) Rolling stand with back-up and work rolls for rolling sheets and strips
AT390741B (en) ROLLING MILL, IN PARTICULAR COLD ROLLING MILL
DE2947250A1 (en) IMMEDIATELY AFTER AN EXTRUDER PUT ROLLING MILL
DE2034490A1 (en) Roller pivot bearing compensator - hydraulically operated
EP3999259B1 (en) Cold rolling of rolled material
DE1936769A1 (en) Controlling the camber of working rollers - of double high metal rolling mill
AT390742B (en) ROLLING MILL, IN PARTICULAR COLD ROLLING MILL
DE2618828A1 (en) ROLLING FRAMEWORK WITH HYDRAULIC ADJUSTMENT

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE GB IT

17P Request for examination filed

Effective date: 19910218

17Q First examination report despatched

Effective date: 19911217

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE GB IT

REF Corresponds to:

Ref document number: 58902329

Country of ref document: DE

Date of ref document: 19921029

ITF It: translation for a ep patent filed

Owner name: GUZZI E RAVIZZA S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930106

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: SMS SCHLOEMANN-SIEMAG AG

Effective date: 19930608

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 19940917

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19980713

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19980916

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990802

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19990802

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050802