EP0238377B1 - Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen - Google Patents

Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen Download PDF

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Publication number
EP0238377B1
EP0238377B1 EP87400319A EP87400319A EP0238377B1 EP 0238377 B1 EP0238377 B1 EP 0238377B1 EP 87400319 A EP87400319 A EP 87400319A EP 87400319 A EP87400319 A EP 87400319A EP 0238377 B1 EP0238377 B1 EP 0238377B1
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EP
European Patent Office
Prior art keywords
bending
jacks
plane
chock
rolling mill
Prior art date
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Expired - Lifetime
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EP87400319A
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English (en)
French (fr)
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EP0238377A1 (de
Inventor
Jean Perret
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Clecim SAS
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Clecim SAS
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/42—Control of flatness or profile during rolling of strip, sheets or plates using a combination of roll bending and axial shifting of the rolls
    • 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
    • B21B13/001—Convertible or tiltable stands, e.g. from duo to universal stands, from horizontal to vertical stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
    • B21B2203/36—Spacers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/24—Roll wear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/02—Roll bending; vertical bending of rolls
    • B21B2269/04—Work roll bending
    • 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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/203—Balancing rolls

Definitions

  • the subject of the invention is a method for adjusting the profile of cylinders which can be moved axially in a rolling mill and also covers the rolling mill which has been improved for implementing the method.
  • the bending device consists, for each chock, of two sets of jacks placed symmetrically on either side of the rolling plane and each acting, in the desired direction, on a support part integral with the chock .
  • each support part of the chock rests on two cylinders spaced in the axial direction symmetrically on either side of the median plane of the chock bearings so that the bending force is well distributed over the bearings.
  • the rolling mill stand is symmetrical with respect to a median plane perpendicular to the rolling plane and which corresponds to that of the rolled product. Normally the cylinders are therefore centered on this plane with respect to which the chocks are arranged symmetrically.
  • the torque is generally applied to a single pair of cylinders, for example the working cylinders, and transmitted to the corresponding support cylinders by friction.
  • the subject of the invention is a new device which, without substantially modifying the constitution of the rolling mill, makes it possible at the same time to bend and to move axially the working rolls or the intermediate rolls.
  • the cambering force is exerted by means of fixed jacks bearing, on one side on a support integral with the cage and on the other on a sliding face formed on the corresponding chock parallel to the axial direction of movement, and, to achieve the camber of the displaceable cylinder, the displacement of the latter is measured at all times relative to the centering position of the cylinder on the median plane of the product and is continuously adjusted for each chock, the individual pressure exerted by each cylinder as a function of the measured offset and the position at the same instant of the cylinder considered with respect to the median plane of the bearing so that, in each choke, the result of the cambering forces exerted by the he set of cylinders remains steered at all times along the median plane of the bearing.
  • the invention also covers an improved rolling mill for implementing the method in which the camber cylinders of each chock are mounted on a fixed support integral with the cage and bear, in the direction of the cambering force, on a sliding face formed on the chock, parallel to the axial direction of movement; in addition, the rolling mill is associated with a balancing device comprising a means for measuring the offset of the cylinder considered relative to its centering position relative to the median plane of the product and means for individual adjustment, at each instant, of the pressure exerted by each vee cambering rinse, as a function of the measured offset and of the position, at the same instant of the jack considered with respect to the median plane of the bearing, so that the result of the cambering forces exerted by all of the jacks remains directed, at each instant following the median plane of the bearing.
  • a balancing device comprising a means for measuring the offset of the cylinder considered relative to its centering position relative to the median plane of the product and means for individual adjustment, at each instant, of the pressure exert
  • the two chocks of each movable cylinder being each associated with two symmetrical sets of camber cylinders, arranged on either side of the rolling plane, the jacks placed respectively, in each of the sets, in the same relative positions relative to the median plane of their respective bearings are connected in parallel to the same branch of a common circuit for supplying pressurized fluid comprising as many branches as there are jacks in each assembly, each branch being provided with a means for individual adjustment of the fluid pressure with maintenance of equal flow rates in all branches.
  • the means for individually adjusting the pressures in the jacks comprise, on each branch of the supply circuit, a servo-valve controlled by a means of calculating the corrections to be made to the pressures as a function of the offset measured and displayed on the means of calculation and respective positions in cylinders supplied by the branch in question.
  • each block consists of a solid support piece comprising a projecting central part framed by two longitudinal recesses in which the support ears of the chock engage, these being each provided with a continuous sliding face parallel to the axis and said sliding faces are placed opposite the lateral faces of the central part on which are arranged opposing bores two by two along an axis parallel to the rolling plane and each forming a cylinder body in which slides a piston secured to a rod opening into the corresponding recess to rest on the sliding surface of the chock.
  • the rods of the jacks are capped by bearing pads on the sliding surfaces associated with columns for taking up the axial forces mounted slidingly, parallel to the rod of the jack, in guide bores made in the hydraulic block, elastic washers being advantageously interposed between the support pads and the sliding surfaces.
  • FIG 1 there is shown schematically a quarto rolling mill comprising two working rolls 1 and 1 'and two support rolls 2 and 2'.
  • the axes of the cylinders are parallel and arranged along a rolling plane P1 passing through the contact generators.
  • the rolled product 20 passes between the working rolls 1 and 1 'and its median plane P2 corresponding to the plane of symmetry of the assembly of the rolling mill stand and in particular of the support rolls 2 and 2'.
  • the cylinders are all aligned and centered on the plane P2.
  • the working rolls 1 and l ' can be moved axially relative to the centering position so that their respective transverse plane of symmetry is offset on one side or the other. with respect to the median plane P2.
  • an axial displacement force F1 is applied to the working rolls 1 and 1 '.
  • cambering forces F2 are applied to the ends of the shafts of the working cylinders 1 and 1 ', by means of their chocks so as to camber a corresponding cylinder.
  • the working rolls 1 and 1 ′ can be subjected at the same time to an axial displacement force F1 and to the bending forces F2.
  • the rolling mill is provided with positive and negative bending means.
  • the positive bending means consist, for each chock, of two pairs of jacks 6 placed on either side of the median plane P1 in the central parts 53 of the support pieces 5, the bending jacks of the two working cylinders 1 and the being opposite two by two by forming two lines centered in planes P3, P4 parallel to the median plane P2 and spaced axially from each other by a distance a ( Figure 2).
  • Figure 3 is a section through the axial plane of a line, for example P3.
  • central part 53 of the support piece 5 are therefore provided, for each row of jacks, two opposite bores 57, 57 ′ centered on the axis 60 of the positive bending jacks 6 and 6 ′ and opening respectively on the lateral faces 55, 55 'of the central part 53.
  • the two bores 57, 57' are separated by a central partition 58 and constitute the bodies of the two jacks 6 and 6 'inside which pistons 61, 61' slide, extended by rods 62, 62 'which pass through partitions 63, 63' sealingly closing the bores 57, 57 '.
  • each pad 64 has a diamond shape comprising two points on which are fixed the ends of guide columns 65 slidably mounted, parallel to the axis 60 of the cylinder in bores made in the central part 53. Furthermore, the shoe 64 rests on the face 34 of the support part 32 of the chock 3 via a pad 66 and an elastic washer 67.
  • each chock 3, 3 ' is also associated with negative cambering cylinders 7, 7' placed in bores 59, 59 'formed in the lateral parts 54, 54' of the support piece (5) and opening out on the lateral faces 56, 56 '.
  • Each bore 59 constitutes the body of the jack 7 inside which slides a piston 71 secured to a rod 72 which passes in leaktight manner through a partition 73 closing the bore 59 inside which the piston 71 therefore limits two chambers of cylinders connected to a hydraulic circuit arranged in the support part 5.
  • each chock 3 can slide parallel to the axis 10 of the cylinder along the guide faces 51 ′ of the support piece 5.
  • the two chocks 3 of each cylinder 1 are secured to the latter in the axial direction by means of caps 13 for closing the bearing cages 12, the latter being liable to withstand axial forces, for example tapered bearings. In this way, the two chocks 3 of each cylinder 1 follow the movements of axial displacement of the cylinder.
  • Several devices for axial displacement of the cylinders are already known, which therefore need not be described in detail. It is possible, for example, to use a jack bearing on a lifting beam making it possible to apply the axial displacement force on the two sides of the chock 3.
  • the displaced cylinder 1 is a driving cylinder
  • two displacement cylinders 42 supplied in synchronism placed symmetrically on either side of the drive means 43 in rotation of the cylinder 1 and bearing on the supports 32 of the corresponding chock 3, each jack 42 being centered in a plane parallel to the rolling plane and passing through the axes of the camber jacks 6 and 7 and supplying it in synchronism .
  • the offset of the displaced cylinder 1 is measured relative to the median plane P1 by means of a displacement sensor 44 made up of two parts sliding relative to each other, fixed, for example on the two parts of one of the cylinders 42 and providing an analog signal proportional to the offset of the working cylinder relative to the centering position in the median plane of the product and of sign corresponding to the direction of the offset.
  • This signal is used for balancing the pressures in the cambering cylinders by means of a device 8 shown diagrammatically in FIG. 5.
  • a displaceable cylinder 1 and its two bending devices each consisting of two sets of jacks placed in hydraulic blocks 5a, 5b, 5'a, 5'b each set comprising two jacks 6a, 66a and 6b, 66b, (6'a, 66 'a, 6'b, 66'b).
  • the hydraulic blocks 5a, 5b and 5'a, 5'b of the two chocks are connected by a single supply circuit 80 to a source of pressurized fluid not shown.
  • the circuit 80 is divided into two branches 81 and 82.
  • the branch 81 supplies the jacks 6a, 6b, 6'a, 6'b of the two wires P3 and P'3 in parallel while the branch 82 supplies the jacks 66a in parallel. , 66b, 66'a, 66 'of the two lines P4 and P'4.
  • the hydraulic circuit is designed so that all the cylinders are supplied with the same flow rate, making it possible to determine equal movements at the same speed.
  • Each branch 81, 82 of the supply circuit 8 is provided with a pressure regulator 83 which, depending on the signals received on its input 84 regulates the pressure in the corresponding circuit while maintaining a constant flow there.
  • the sensor 44 for the axial displacements of the cylinder 1 provides an analog signal proportional to the displacement which is applied to a computing unit 85. From the signals received, the latter develops the pressure setpoints S1 and S2 applied to the inputs 84 of the sensors 83 of the two branches 81 and 82 according to a law programmed in advance to ensure a pressure distribution such that the result of the thrust forces applied by the camber cylinders in the planes P3 and P4 always remains directed at each instant following the median plane of the corresponding bearings. In this way, as shown in FIG.
  • the two rows of cylinders P3 and P4 are not necessarily symmetrical with respect to the median plane P5 of the bearing and this makes it possible to arrange the jacks in the most adequate manner inside the hydraulic blocks 5 whose plane of symmetry does not necessarily coincide with that of the bearing.
  • the various members used for balancing the pressures could be replaced by means fulfilling the same functions, these means being able to be hydraulic, electrical or even mechanical (cam, lever arm, etc.).
  • any technology for measuring displacements, calculating corrections and balancing pressures can be used to obtain the desired result.
  • the fixed bending devices according to the invention can adapt to different cylinder diameters and / or adapt to a variation in diameter due to wear in the limit of the stroke of the cylinders.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)

Claims (9)

1. Walzwerk mit axial verschiebbaren Zylindern und mindestens zwei Arbeitszylindern (1, 1') im Inneren eines Ständers, die sich in einer Ebene P1 auf mindestens zwei Stützzylindern (2, 2') abstützen, und deren Enden über Wälzlager (12) in innerhalb des Ständers parallel zur Ebene P1 des Walzvorgangs verschiebbaren Zapfenlagem gelagert sind und von denen mindestens ein Arbeitszylinder (1) einerseits mit Einrichtungen (42) zum Verschieben des Zylinders (1) in Richtung seiner Achse (10) zu beiden Seiten einer Zentrierposition des Arbeitszylinders auf der Mittelebene P2 des Walzprodukts (20) und andererseits mit Einrichtungen (6) zum Verstellen des Arbeitszylinders (1) verbunden ist, die an jedem Zapfenlager (3) zwei symmetrische Einheiten von wenigstens zwei Stelltrieben (6, 66) zum Auseinanderrücken im axialen Sinn aufweisen, dadurch gekennzeichnet, daß die Stelltriebe (6) eines jeden Zapfenlagers auf einem fest mit dem Ständer verbundenen Support (5) angeordnet sind und sich in Richtung der Verstellkraft an einer Gleitfläche (34) abstützen, die an dem Zapfenlager (3) parallel zur axialen Verschieberichtung vorgesehen ist und daß das Walzwerk mit einer Ausgleichseinrichtung (8) versehen ist, die eine Einrichtung (44) zur Ermittlung der Verschiebung des Zylinders (1) gegenüber der Zentrierstellung und Einrichtungen (83) zur Einzelverstellung des in jedem Moment von jedem Stelltrieb (6) ausgeübten Druck in Abhängigkeit von der ermittelten Verschiebung und der momentanen Stellung des Stelltriebs gegenüber der Mittelebene P5 des Lagers (12) aufweist, und zwar derart, daß die Resultierende der durch die Einheit der Stelltriebe (6, 66) ausgeübten Stellkräfte in jedem Moment entlang der Mittelebene P5 des Lagers (12) gerichtet bleibt.
2. Walzwerk nach Anspruch 1, dadurch gekennzeichnet, daß die beiden Zapfenlager (3) eines jeden verschiebbaren Zylinders je mit zwei symmetrischen Einheiten von Stelltrieben verbunden sind, die zu beiden Seiten der Ebene P1 des Walzvorgangs angeordnet sind, wobei die Stelltriebe (6a, 6b) (66a, 66b) in jeder Einheit in der gleichen Relativstellung gegenüber der Mittelebene P5 der entsprechenden Wälzlager angeordnet und parallel an den gleichen Zweig (81, 82) eines gemeinsamen Druckmittelkreislaufs (80) angeschlossen sind, der ebensoviel Zweige wie Stelltriebe (6, 66) in jeder Einheit aufweist, wobei jeder Zweig mit einem Organ (83) zur individuellen Regelung des Flüssigkeitsdrucks unter Aufrechterhaltung gleicher Leistung in allen Zweigen versehen ist.
3. Walzwerk nach Anspruch 2, dadurch gekennzeichnet, daß die Organe zur individuellen Druckregelung in den Stelltrieben in jedem Zweig (81) des Speisekreislaufs ein Servoventil (83) aufweisen und die Servoventile (83) durch einen Rechner (85) nach einem Programm zur Korrektur der in Abhängigkeit von der ermittelten und durch den Rechner angezeigten Verschiebung und der jeweiligen Stellung der von dem jeweiligen Zweig gespeisten Steiltriebe, um eine korrekte Druckverteilung zu erzielen.
4. Walzwerk nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß jedes Zapfenlager (3) mit positiven (6) und negativen (7) Stelltrieben versehen ist, von denen jeder zwei entgegengerichtete Einheiten von wenigstens zwei Stelltrieben aufweist, die bei positiver Verstellung im Sinne eines Auseinanderrückens der Zylinder und bei negativer Verstellung im Sinne eines Zusammenrückens wirken.
5. Walzwerk nach wenigstens einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Steiltriebeinheiten in hydraulischen Baugruppen (5) zusammengefaßt sind, die zu beiden Seiten der Walzebene P1 in in dem Ständer (4) vorgesehenen Fenstern untergebracht sind, in welchen die Stelltriebe (3) gleiten und jede Baugruppe aus einem massiven Support (5) besteht, der einen mittleren vorspringenden Teil (53) aufweist, der von zwei langgestreckten Ausnehmungen (52) eingefaßt ist, in die Stützlager (32) der Stelltriebe (3) eingreifen, die an jeder Seite mit achsparallelen Gleitflächen (34) versehen sind, die ihrerseits gegenüber den Seitenflächen (55) des Mittelvorsprungs (53) liegen, in denen paarweise nach einer Achse (60) parallel zur Ebene P1 einander gegenüberliegende Bohrungen (57, 57') vorgesehen sind, deren jede ein Stelltriebgehäuse bildet, in der ein Kolben (61) gleitet, dessen mit ihm fest verbundene Kolbenstange (62) in eine Erweiterung (52) hineinragt und sich an der Gleitfläche (34) des Stelltriebs (3) abstützt.
6. Walzwerk nach Anspruch 5, dadurch gekennzeichnet, daß die Kolbenstangen (62) der Stelltriebe mit einer Stützkappe (64) gegenüber der Gleitfläche (34) versehen sind, die mit zur Druckaufnahme dienenden Stützsäulen (65) verbunden sind, welche parallel zu der Kolbenstange des Stelltriebs in den Ausnehmungen der hydraulischen Baugruppe (53) axial gleitend angebracht sind.
7. Walzwerk nach Anspruch 6, dadurch gekennzeichnet, daß zwischen der Stützkappe (64) und der Gleitfläche (34) elastische Scheiben (67) angeordnet sind.
8. Walzwerk nach Anspruch 5, dadurch gekennzeichnet, daß jedes Stützlager (32) des Stelltriebs an einer dem Mittelteil (53) gegenüberliegenden Seite mit einer zweiten Gleitfläche (33) versehen ist, die einer Seitenfläche der Ausnehmung (54) des Teils der Baugruppe (5) gegenüberliegt, in welcher die Bohrungen (59) mit paralleler Achse zur Ebene P1 angeordnet sind, die das Gehäuse der Stelltriebe (7) zur Negatiwerstellung bilden, in denen die Kolben (71) gleiten, deren fest damit verbundenen Kolbenstangen (72) sich auf der zweiten Gleitfläche (33) beim Einspannen der Zapfenlager abstützen.
9. Verfahren zum Einstellen des Profils der axial verschiebbaren Zylinder eines Walzwerks, welches in seinem Ständer (4) mindestens zwei Arbeitszylinder (1, 1') aufweist, die sich entlang einer Ebene P1 auf mindestens zwei Stützzylindern (2, 2') abstützen und deren Enden über Wälzlager (12) in parallel zur Ebene P1 beweglich im Ständer (4) angeordneten Zapfenlagern gelagert sind, wobei gleichzeitig einerseits wenigstens ein Arbeitszylinder (1) gegenüber einer Mittelstellung, in welcher sich die beiden Arbeitszylinder (1, 1') symmetrisch zur Mittelebene P2 des Walzprodukts befinden, verstellbar ist und andererseits eine Verstellung des axial verschobenen Zylinders durch Aufbringen einer Stellkraft auf die Zylinderenden ermöglicht wird, wobei diese Stellkraft auf jedes Zapfenlager (3) durch zwei Einheiten von mindestens zwei axial getrennten Stelltrieben bewirkt wird, dadurch gekennzeichnet, daß die Stellkraft mittels fester Stelltriebe aufgebracht wird, die sich einerseits an einer Seite eines fest mit dem Ständer (4) verbundenen Supports (5), andererseits auf einer Gleitfläche (34) abstützen, die über dem Zapfenlager angeordnet und parallel zur axialen Verschieberichtung verläuft, und daß zur Durchführung der Verstellung des Zylinders während seiner Verschiebung ständig die Verschiebung des verschiebbaren Zylinders gegenüber der Mittelposition ermittelt und laufend für jedes Zapfenlager (3) der durch jeden Stelltrieb (6, 66) einzeln ausgeübten Druck gesteuert wird, und zwar in Abhängigkeit von der ermittelten Verschiebung und von der jeweiligen Stellung des Stelltriebs (6, 66) gegenüber der Mittelebene P5 des Lagers (12), so daß in jedem Zapfenlager (3) die Resultierende der von den Stelltrieben ausgeübten Stellkraft jederzeit entlang der Mittelebene P5 des Lagers (12) ausgeglichen wird.
EP87400319A 1986-02-14 1987-02-12 Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen Expired - Lifetime EP0238377B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8602044 1986-02-14
FR8602044A FR2594359B1 (fr) 1986-02-14 1986-02-14 Procede de reglage du profil de cylindres deplacables dans un laminoir et laminoir perfectionne pour la mise en oeuvre du procede

Publications (2)

Publication Number Publication Date
EP0238377A1 EP0238377A1 (de) 1987-09-23
EP0238377B1 true EP0238377B1 (de) 1990-04-18

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US (1) US4773246A (de)
EP (1) EP0238377B1 (de)
DE (1) DE3762320D1 (de)
FR (1) FR2594359B1 (de)

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FR2648372A1 (fr) * 1989-06-19 1990-12-21 Clecim Sa Procede de changement de configuration d'un laminoir et installation de laminage pour la mise en oeuvre du procede
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DE19500336A1 (de) * 1995-01-07 1996-07-11 Schloemann Siemag Ag Verfahren zur Regelung des Walzspaltprofils
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DE19618712B4 (de) * 1996-05-09 2005-07-07 Siemens Ag Regelverfahren für ein Walzgerüst zum Walzen eines Bandes
US5752404A (en) * 1996-12-17 1998-05-19 Tippins Incorporated Roll shifting system for rolling mills
DE19730262C1 (de) * 1997-07-09 1998-10-22 Mannesmann Ag Verfahren zum Walzen von Flachmaterial und Band
IT1297585B1 (it) * 1997-12-24 1999-12-17 Danieli Off Mecc Blocco di curvatura per gabbia di laminazione a quarto
JP6979437B2 (ja) * 2019-10-25 2021-12-15 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機および圧延方法
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US3334506A (en) * 1964-04-24 1967-08-08 Nat Steel Corp Rolling mill
JPS527425B2 (de) * 1972-07-07 1977-03-02
US3943742A (en) * 1973-08-24 1976-03-16 Hitachi, Ltd. Rolling mill
JPS57199505A (en) * 1981-06-03 1982-12-07 Hitachi Ltd Work roll moving type rolling mill
BR8300010A (pt) * 1982-01-06 1983-08-30 Hitachi Ltd Laminador
JPS6018210A (ja) * 1983-07-13 1985-01-30 Ishikawajima Harima Heavy Ind Co Ltd 圧延機

Also Published As

Publication number Publication date
EP0238377A1 (de) 1987-09-23
US4773246A (en) 1988-09-27
FR2594359A1 (fr) 1987-08-21
FR2594359B1 (fr) 1988-06-10
DE3762320D1 (de) 1990-05-23

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