EP0143166B1 - Cage de laminoir avec appui des cylindres de travail à l'aide de rouleaux d'appui - Google Patents

Cage de laminoir avec appui des cylindres de travail à l'aide de rouleaux d'appui Download PDF

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Publication number
EP0143166B1
EP0143166B1 EP84108263A EP84108263A EP0143166B1 EP 0143166 B1 EP0143166 B1 EP 0143166B1 EP 84108263 A EP84108263 A EP 84108263A EP 84108263 A EP84108263 A EP 84108263A EP 0143166 B1 EP0143166 B1 EP 0143166B1
Authority
EP
European Patent Office
Prior art keywords
rolls
roll
backing
chocks
blocks
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
Application number
EP84108263A
Other languages
German (de)
English (en)
Other versions
EP0143166A1 (fr
Inventor
Wilfried Bald
Erich Stoy
Hans Römmen
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
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
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT84108263T priority Critical patent/ATE33950T1/de
Publication of EP0143166A1 publication Critical patent/EP0143166A1/fr
Application granted granted Critical
Publication of EP0143166B1 publication Critical patent/EP0143166B1/fr
Expired legal-status Critical Current

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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
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/145—Lateral support devices for rolls acting mainly in a direction parallel to the movement of the product
    • 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
    • B21B31/08—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts

Definitions

  • the invention relates to a roll stand with two work rolls, two intermediate rolls and two support rolls (six-high roll stand), in which at least the axes of the support rolls and those of the intermediate rolls lie essentially one above the other in a common vertical plane, in which furthermore the intermediate rolls between the support rolls and the work rolls are arranged axially displaceable, and in which the chocks of the work rolls and the chocks of the intermediate rolls are held laterally by them form-fitting axially guiding guide pieces, of which the guide pieces provided for the chocks of the work rolls on blocks provided in the stand window and having adjusting means and those for the chocks the intermediate rollers effective guide pieces within the soffit of the stator window are each vertically displaceable and optionally acted upon by pretensioning means, and finally the work rolls additionally against the support w vertical and salt axes with the intermediate roller axes can be adjusted horizontally in the rolling direction and can be supported essentially in this direction by support rollers which can be adjusted against them from support bridges connected to the
  • the optimal diameter of the work rolls depends on a number of factors. For example, work rolls with a larger diameter are used for dressing than for the usual reduction, and with decreasing strip thickness and increasing strength of the rolling stock, the diameter of the work rolls is also expediently reduced. With increasing slenderness of the work roll, however, the necessity of its support arises not only in the vertical direction by intermediate or backup rolls, but also in accordance with the type-determining publication “production of cold-rolled strip”, Part 1, Verlag Stahleisen mbH, Düsseldorf, 1970, Pages 309 to 314, also in an essentially horizontal direction, in or against the rolling direction by horizontal adjustment, by hydraulic cushions and / or by intermediate rollers supported by further rollers and / or pressure rollers.
  • a certain spread of the work roll diameter is provided for practically all roll stands in order to be able to rework new work rolls with the maximum diameter in accordance with the wear and tear occurring in the company; in general, differences between the original, largest and the smallest permissible diameter of, for example, 50 mm are provided. Such differences can be taken into account within the roll stand without major modifications to the same. In addition, however, there may be a desire to be able to use more differing work rolls with respect to their bale diameters, for example to pre-roll within a stand optionally with work rolls of larger diameter and finish rolls with work rolls of very small diameter.
  • the invention is therefore based on the object to provide a roll stand of the type described, which can be converted in terms of the diameter of its effective work rolls into diameter ranges in which the work rolls require lateral support within considerably shorter times, which are in the range of normal work roll change times .
  • cassettes are expediently designed such that they can be inserted horizontally into stand recesses and recesses in the support bridges, the cassettes each consisting of two lateral cheeks which connect the parts of the support roller arrangement which extend from stand to stand.
  • these cassettes also have the guide plates at the same time, so that the work roll installation is completely released after the cassettes have been removed.
  • the support roller arrangement can then be moved into the working position, and even when using thick work rolls for long periods, it is not absolutely necessary, but only advisable, to replace the cassette with one that does not contain a support roller arrangement, and also that The cassette can be exchanged easily, unhindered and quickly.
  • the support bridges in the number of hydraulic cylinders corresponding to the support rollers and that of the two bearing arms of the horizontal intermediate roller, the piston rods of which have recesses into which projections of the elements adjusting the support rollers and the intermediate roller can be inserted horizontally . It is hereby achieved that the support roller arrangement can be removed easily and in a few simple steps, while the hydraulic cylinders equipped with hydraulic connections and adjusting these remain within the support bridges.
  • the replacement of the work rolls is further simplified if the drive spindles of a comb roll stand provided on the drive side of the stand or corresponding separate drives are connected to the pins of the support rolls or else of the intermediate rolls.
  • Such a backup roll or intermediate roll drive which is maintained regardless of the diameter of the work roll used, further reduces changeover times.
  • the work rolls can also be driven if necessary.
  • the guide elements guiding the chocks of at least the intermediate rollers in the axial direction of the mutually supporting surfaces of the guide pieces and the chocks are formed symmetrically with respect to a horizontal plane, and the axes of the roller journals supported by the chocks are offset from this horizontal plane.
  • a chock can be picked up by the guide pieces in a first as well as in a second position rotated by 180 °, the displacement of the axes in lower
  • FIG. 1 shows a top view of a stand 1 shown broken off, in the stand window 2 of which the chocks of support rolls 3 and 4 are held displaceably in a central vertical section through a roll stand.
  • Recessing recesses 5 of the stator in the height range of the work rolls form extensions of the stator window, in which horizontal adjustment devices 6 are provided, the adjustment stamps of which are connected to a carrier 7 of a block 8.
  • adjusting means not shown in the figure, which are expediently designed as hydraulic cylinders, vertically provided guide pieces 9 and 10 are supported on the block, the chocks 11 being horizontally displaceable between their guide surfaces. and 12 of the work rolls 13 and 14 lead small diameter.
  • displaceable guide pieces 15 and 16 for example subjected to bending forces, are vertically displaceable, the end faces of which form a horizontal guide guide the chocks 17 and 18 of intermediate rolls 19 and 20.
  • Sufficiently rigid support bridges 21 and 22 are provided between the stands, in which the essential parts of the support roller arrangement are provided within a cassette 23.
  • hydraulic cylinders 24 and 25 are provided in the support bridges, the pistons 26 of which are arranged on freely projecting piston rods 57, the free ends of which have a recess in the form of an annular groove 39.
  • fork rams 27 In the cassette are fork rams 27, the free ends of which are equipped with a continuous undercut horizontal slot 28 so that the protruding claws engage in the groove of the piston rods.
  • the fork plungers 27 At its opposite end, as can be seen in detail from FIG. 3, the fork plungers 27 have forks 29, the outer sides of which have grooves or transverse strips which are guided along profile strips 30 each arranged between two forks.
  • On the bolt penetrating the fork support rollers 32 On the bolt penetrating the fork support rollers 32 are mounted.
  • the inner partition walls of the cassette are equipped with guide plates 31 for the rolling stock which can be pivoted along swivel bars.
  • 4 which shows a top view of the support bridge 21, can be seen in the broken part, two hydraulic cylinders 25 are provided on both sides of the row of hydraulic cylinders 24 in the support bridge, the piston rods of which can be connected to fork plungers 40, the forks of which have pivot pins 41 the bearing arms 33 are pivotable, the free ends of which have the bearings of horizontal intermediate rollers 34.
  • the bearing arms can be pivoted between guide pieces 9 and 10 and guide plates 11.
  • the guide pieces 9 and 10 and the guide plates in this case have bolts 42 and 43, which are surrounded by stones, which are essentially longitudinally displaceable in scenes 46 and 47 of the bearing arm.
  • the bearing 45 is held for the journal of the horizontal intermediate roller 34.
  • FIG. 3 - are to be replaced by work rolls 35 of larger diameter, as shown in section in FIGS. 2 and 3, the pistons are first of all 26 all hydraulic cylinders 24 and 25 retracted into their extreme left position, the extended position of the cassette 23.
  • the forks 29 are taken along and both the support rollers 32 and, via the bearing arms 33, the horizontal intermediate rolls 34 are withdrawn from the supported work roll.
  • both the work rolls and the vertical intermediate rolls can be moved out of the stand and replaced by a second set of work rolls 35 of larger diameter with associated backup rolls.
  • the work rolls are each held in their chocks in such a way that their operating position also results when the guide pieces 9 and 10 are in the middle position.
  • the guide pieces are equipped with grooves 49 and the chocks with guide strips 48.
  • the chocks are therefore adapted at least in the areas guided between the guide pieces, and the adaptation to the respective work roll diameter takes place by appropriately removing the axis of the bearings of the work rolls from the central plane penetrating the guide strips 48 of the chocks.
  • the intermediate rolls can be provided essentially continuously with the same diameter; only with work rolls of extremely large diameters can it prove advantageous to use them in connection with intermediate rolls of smaller diameters.
  • the position of the intermediate rolls changes according to the distance between them, which corresponds to the roll gap, increased by twice the diameter of the work rolls. With the use of larger work rolls, even if intermediate rolls of the same diameter are still used, they must be stored in chocks whose bearing axes are further apart from one another in accordance with the increase in the diameter of the work rolls.
  • Pushing the roller set in and out is very simple due to the guide pieces which guide the chocks horizontally, so that no greater difficulties arise here than with a normal work roll and intermediate roll change. Operation can be resumed immediately after the work and intermediate rolls have been replaced, the pistons 26 of the hydraulic cylinders 24 and 25 remaining in their extended position shown on the extreme left, and the horizontal intermediate rolls of the pressure roller arrangement also being clearly lifted from work rolls of larger diameter.
  • the pivot angle of both the bearing arms 33 and the guide plates 31 is also determined automatically. This can be achieved by the shape and arrangement of the scenes 46 and 47, by means of which the bearing arms 33 are guided from the inclined working position into the practically horizontal retracted position. By appropriate shaping of the opposite backdrop, the optimal adjustment of the guide plate can also be brought about and when the guide pieces 9, 10 are moved vertically, they are transferred to the bearing arms 33 and the guide plates 31. Another possibility arises from the stronger extension of the support roller arrangement when using work rolls of smaller diameter. Here, too, an adaptation to the work roll diameter can be achieved by appropriately guiding the links 46, 47.
  • the intermediate rolls can be kept largely independent of the work roll change; only with work rolls of extremely large diameters it may be advisable to use intermediate rolls of smaller diameters.
  • FIGS. 1 and 2 in front of the block 8 shows spray bars 50 shown cut with guide pieces 9 and 10, which may optionally be designed to be pivotable with the movement of the guide pieces, while between the guide pieces the piston rod 51 of a hydraulic cylinder serving to balance the work rolls and acting between the guide pieces can be seen.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Metal Rolling (AREA)
  • Press Drives And Press Lines (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Spinning Or Twisting Of Yarns (AREA)

Claims (7)

1. Cage de laminoir comportant deux cylindres de travail (13, 14), deux cylindres intermédiaires (19, 20) et deux cylindres d'appui (3, 4) (cage sexto), dans laquelle les axes des cylindres d'appui et ceux des cylindres intermédiaires au moins sont essentiellement superposés dans un plan vertical commun, dans laquelle, de plus, les cylindres intermédiaires sont placés, de manière à pouvoir être déplacés dans le sens axial, entre les cylindres d'appui et les cylindres de travail et dans laquelle les empoises (11. 12) des cylindres de travail ainsi que les empoises (17, 18) des cylindres intermédiaires sont maintenues latéralement par des pièces de guidage (9, 10, 15, 16) qui les guident dans le sens axial avec adaptation des formes, celles de ces pièces de guidage (9,10) qui sont associées aux empoises des cylindres de travail étant maintenues dans des blocs (8) montés dans la fenêtre de montant (2) et comportant des moyens de réglage et les pièces de guidage (15, 16) qui sont associées aux empoises (17, 18) des cylindres intermédiaires (19, 20) étant montées à l'intérieur de l'indrados de la fenêtre de montant (2) de manière à pouvoir être déplacées verticalement et à être éventuellement soumises à l'action de moyens de précontrainte et les cylindres de travail, enfin, pouvant être. de plus. placés, dans la direction de laminage, contre le plan vertical contenant les axes des cylindres d'appui et des cylindres de travail et pouvant être soutenus essentiellement dans cette direction par des rouleaux d'appui qui peuvent être placés contre lui à partir de ponts d'appui (21, 22) reliés aux montants, caractérisée en ce que les chapiteaux des montants (1) comportent, sur leurs côtés tournés vers les fenêtres (2) des montants, des évidements dans lesquels sont montés des dispositifs (6) de réglage horizontal agissant sur les cylindres de travail et les mettant en place dans la direction du laminage en ce que les poussoirs de réglage (38) des dispositifs de réglage horizontal sont reliés au bloc (8) qui comportent les moyens de réglage, en ce que le dispositif de rouleau d'appui (32 à 34) peut être ramené sur les points d'appui (21, 22) et peut être écarté d'au moins 50 mm des cylindres de travail et en ce que les dispositifs de rouleaux d'appui avec les dispositifs (6) de réglage horizontal déplacés vers l'avant dans la direction du côté d'entraînement ou du dispositif de manoeuvre avec les blocs (8) portés par eux de manière à réaliser une cassette amovible (23) peuvent être extraits comme un tout et peuvent être remplacés par une cassette comportant des dispositifs de réglage horizontal avec blocs situés en avant.
2. Cage de laminoir selon la revendication 1. caractérisée en ce que les ponts d'appui (21, 22) contiennent des vérins hydrauliques cylindriques (24, 25) qui sont en nombre correspondant à celui des rouleaux d'appui (32) et à celui des deux bras (33) du cylindre intermédiaire (34) dont les tiges de piston (57) comportent des évidements (rainure 28) dans lesquels peuvent s'engager horizontalement les parties saillantes d'éléments (poussoir en fourche 27, 40) qui assurent le réglage des rouleaux d'appui (32) et des cylindres intermédiaires (34).
3. Cage de laminoir selon l'une des revendications 1 ou 2, caractérisée par des bras (33) qui peuvent pivoter dans des plans verticaux, dont les chevilles de pivotement peuvent être déplacées en avant vers les cylindres de travail (13, 14) et dont les extrémités libres portent les paliers (45) des cylindres intermédiaires (34) sur lesquels les cylindres de travail prennent appui essentiellement horizontalement.
4. Cage de laminoir selon l'une des revendications 1 à 3, caractérisée en ce que les bras comportent des coulisses (46, 47) dans lesquelles des chevilles (42, 43) des pièces de guidage (9) et/ou des plaques de guidage (31) sont guidées de telle manière qu'au moment du réglage des bras leur angle de mise en place ainsi que celui des plaques de guidage sont déterminés.
5. Cage de laminoir selon l'une des revendications 1 à 4, caractérisée en ce que les broches d'entraînement d'une cage à pignon montée du côté entraînement de la cage ou des dispositifs d'entraînement séparés correspondants sont reliées aux tourillons des cylindres d'appui (3, 4) ou des cylindres intermédiaires (19, 20).
6. Cage de laminoir selon l'une des revendications 1 à 5, caractérisée en ce que des cylindres de travail (13, 14) qui prennent appui sur des rouleaux d'appui (32) sont décalés hors du plan vertical contenant les axes des cylindres d'appui (3, 4) et/ou ceux des cylindres intermédiaires (19, 20) suffisamment loin pour réaliser un appui solide contre le cylindre intermédiaire (34) agissant sur le profil de laminage.
7. Cage de laminoir selon l'une des revendications 1 à 6, caractérisée en ce que les empoises (11, 12, 17, 18) au moins des éléments de guidage (48, 49) dans le sens axial des cylindres intermédiaires (19, 20) des surfaces d'appui réciproque des pièces de guidage (9, 10, 15, 16) et des empoises sont symétriques par rapport à un plan horizontal et en ce que les axes des tourillons de cylindres qui prennent appui sur les empoises sont décalés vers ce plan horizontal.
EP84108263A 1983-10-03 1984-07-13 Cage de laminoir avec appui des cylindres de travail à l'aide de rouleaux d'appui Expired EP0143166B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84108263T ATE33950T1 (de) 1983-10-03 1984-07-13 Walzgeruest mit mittels stuetzrollen abstuetzbarer arbeitswalzen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3335857 1983-10-03
DE3335857A DE3335857A1 (de) 1983-10-03 1983-10-03 Walzgeruest mit mittels stuetzrollen abstuetzbarer arbeitswalzen

Publications (2)

Publication Number Publication Date
EP0143166A1 EP0143166A1 (fr) 1985-06-05
EP0143166B1 true EP0143166B1 (fr) 1988-05-04

Family

ID=6210801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84108263A Expired EP0143166B1 (fr) 1983-10-03 1984-07-13 Cage de laminoir avec appui des cylindres de travail à l'aide de rouleaux d'appui

Country Status (6)

Country Link
US (1) US4563888A (fr)
EP (1) EP0143166B1 (fr)
JP (1) JPS6076209A (fr)
KR (1) KR910005829B1 (fr)
AT (1) ATE33950T1 (fr)
DE (2) DE3335857A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3503756A1 (de) * 1984-03-13 1985-09-19 SMS Schloemann-Siemag AG, 4000 Düsseldorf Sechswalzengeruest
JPH0620561B2 (ja) * 1985-04-03 1994-03-23 株式会社日立製作所 圧延機のロ−ルベンデイング装置
JPH0719602Y2 (ja) * 1988-11-04 1995-05-10 川崎重工業株式会社 カセツト式圧延機
JPH0747122Y2 (ja) * 1990-03-16 1995-11-01 川崎重工業株式会社 圧延機
DE19944612C1 (de) * 1999-09-17 2000-11-23 Sundwig Gmbh Walzgerüst
DE10121078A1 (de) * 2001-04-25 2002-10-31 Sms Demag Ag Walzgerüst für bahnförmiges Walzgut
DE10243677A1 (de) * 2002-09-20 2004-04-01 Sms Demag Ag Reibungsarmes Biegesystem in einem Mehrwalzen-Walzgerüst
US8329079B2 (en) * 2009-04-20 2012-12-11 Entrochem, Inc. Method and apparatus for continuous production of partially polymerized compositions and polymers therefrom
AT523437B1 (de) * 2020-12-09 2021-08-15 Andritz Metals Gemany Gmbh Walzgeruest

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2651954A (en) * 1949-09-27 1953-09-15 Frank P Dahlstrom Method of and means for rolling strip material
AT260843B (de) * 1966-03-30 1968-03-25 Schloemann Ag Mehrwalzengerüst
DE1527713A1 (de) * 1966-06-28 1970-01-15 Schloemann Ag Mehrwalzengeruest
JPS5038389B2 (fr) * 1972-05-17 1975-12-09
SU599865A1 (ru) * 1974-07-12 1978-03-30 Предприятие П/Я А-7697 Прокатна клеть
IN150120B (fr) * 1978-05-19 1982-07-24 Sendzimir Inc T
JPS5666307A (en) * 1979-10-04 1981-06-04 Hitachi Ltd Rolling mill
JPS57106412A (en) * 1980-12-23 1982-07-02 Ishikawajima Harima Heavy Ind Co Ltd Rolling mill
DE3107693A1 (de) * 1981-02-28 1982-09-16 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest
AT382801B (de) * 1981-03-16 1987-04-10 Escher Wyss Ag Walzgeruest mit arbeitswalzen
AT370347B (de) * 1981-03-24 1983-03-25 Voest Alpine Ag Walzgeruest
JPS57165104A (en) * 1981-04-02 1982-10-12 Ishikawajima Harima Heavy Ind Co Ltd Multiple stages rolling mill having shape controlling function

Also Published As

Publication number Publication date
ATE33950T1 (de) 1988-05-15
DE3335857A1 (de) 1985-04-18
EP0143166A1 (fr) 1985-06-05
KR850004021A (ko) 1985-07-01
US4563888A (en) 1986-01-14
DE3470853D1 (en) 1988-06-09
KR910005829B1 (ko) 1991-08-05
JPH0377008B2 (fr) 1991-12-09
JPS6076209A (ja) 1985-04-30

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