EP0181474B1 - Cage de laminoir à six cylindres - Google Patents

Cage de laminoir à six cylindres Download PDF

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Publication number
EP0181474B1
EP0181474B1 EP85112324A EP85112324A EP0181474B1 EP 0181474 B1 EP0181474 B1 EP 0181474B1 EP 85112324 A EP85112324 A EP 85112324A EP 85112324 A EP85112324 A EP 85112324A EP 0181474 B1 EP0181474 B1 EP 0181474B1
Authority
EP
European Patent Office
Prior art keywords
rolls
chocks
screw
backing
roll
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
EP85112324A
Other languages
German (de)
English (en)
Other versions
EP0181474A3 (en
EP0181474A2 (fr
Inventor
Johannes Jansen
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 AT85112324T priority Critical patent/ATE42483T1/de
Publication of EP0181474A2 publication Critical patent/EP0181474A2/fr
Publication of EP0181474A3 publication Critical patent/EP0181474A3/de
Application granted granted Critical
Publication of EP0181474B1 publication Critical patent/EP0181474B1/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

Definitions

  • the invention relates to a six-roll mill stand with chocks guided in windows of stands with their axes within a common vertical plane by means of adjusting devices supported by the yokes of the stands adjustable work, intermediate and backup rolls, in which the bale lengths of the intermediate rolls are those of Support rollers exceed and the bale length of the support rollers falls below the maximum rolling stock width, and wherein the two yokes of the stand in the rolling axis direction each have two separately adjustable adjusting devices, the inner of which support the chocks of the support rollers and the outer of which support the intermediate rollers.
  • DE-OS 1 752 752 and DE-AS 21 38 894 additional pressure rollers are therefore employed in a closed circuit against middle areas of back-up rolls, by finally a six-roll stand is known from DE-OS 1 809 474 with chocks guided in windows of stands of work rolls, intermediate rolls and backup rolls which can be adjusted with their axes within a common vertical plane by means of adjusting devices which support the yokes of the stands.
  • the bale lengths of the intermediate rolls exceed those of the backup rolls.
  • the bale length of the support rollers is less than the maximum width of the rolling stock.
  • the two yokes of the stator each have two separate adjusting devices in the rolling axis direction, the inner of which support the chocks of the support rollers and the outer of which support the intermediate rollers.
  • the short upper or lower support roller is used as a counter-bending roller and this is pressed so strongly against the intermediate rollers when the rolling forces occur that the deflection of the work and support rollers is eliminated or at least considerably reduced.
  • the adjusting devices cannot be turned on separately and this is also not provided, so that a controlled change in the roll gap contour cannot be carried out with this roll stand.
  • the pressure rollers are supported against crossbeams, the ends of which are supported by the roller journals of the support rollers to be preloaded. This results in an undesirably high additional effort both for a crossbeam and the required additional bearings and the overall height provided for the crossbeam, without prejudice to whether the crossbeam according to DE-OS 1 752 752 is arranged within the column window and correspondingly longer column bars be required, or is provided according to DE-AS 21 38 894 beyond the stator yokes.
  • one of the support rollers with a large diameter and thus stiff and the opposite with a smaller diameter and thus more flexible should be executed in a four-roller stand, and only the more flexible of the support rollers should be performed by an engaging support roller engaging behind them are additionally supported in such a way that when rolling rolled material high deformation resistance under the influence of the support roller, the slimmer of the support rollers bends as much as the stiff, much larger diameter, while when rolling rolled material with low deformation resistance the rolling force is distributed over the thinner support roller and its support roller Should be that the thinner back-up roll bends more than the stronger and therefore stiffer.
  • the bale length of the backup rolls is selected to be relatively short and is preferably in the range from 55 to 90% of the maximum belt width B of the rolled strip, not shown.
  • the bale length of the work rolls 4 and 5 is adapted in the usual way to the maximum bandwidth B and exceeds this by a small amount.
  • the bale lengths of the intermediate rolls 3 and 6 exceed that of the work rolls.
  • the chocks 14 of the lower support roller 7 are supported by means of a wedge 15 on the lower horizontal surface of the window.
  • the chocks 16 of the lower intermediate rollers 6 are acted upon by pressure stilts 17 and hydraulic adjusting devices 18 arranged upstream thereof.
  • the chocks 19 and 20 of the work rolls 4 and 5 are not acted upon by rolling forces, but they are connected to one another by punches 21, 22 of a bending device which is able to produce both positive and negative forces.
  • Such a roll stand is shown schematically in the schematic illustration in FIG. 2.
  • the rolling force applied to the rollers is transmitted in the upper window area by the forces F w1 to F W4 .
  • the partial forces F w2 and Fw3 are exerted on the chocks of the upper support roller 2 as portions of the total rolling force, and the respective additional forces F w1 and F W4 . which act on the upper intermediate roller 3 are brought about by separate adjusting devices.
  • An assigned control device is able to distribute the total rolling force on one side of the stator to the partial forces F w1 and F w2 or F w3 and F w4 in such a way that the desired bend is set or regulated via downstream stressometer rollers.
  • a fine adjustment can be brought about by additionally provided bending forces, the bending forces F b1 and F b4 acting on the intermediate rolls 3 and 6 only having to carry out so-called “positive bends, which reinforce the tendency of the conventional roll crowning.
  • the forces caused when such bending forces are exerted in the adjusting devices must be reduced accordingly, since in this case the hydraulic adjusting devices 13 not only have to absorb a partial rolling force, but also these bending forces. Another possibility is to pre-bend the work rolls.
  • the actuating devices causing the bending forces of the work rolls are designed in such a way that they are both positive , ie, are able to apply spreading bending forces as well as negative bending forces which occur as tensile forces between the chocks of the work rolls.
  • the support roll 7 is in turn advantageously supported by wedge positions 15.
  • FIGS. 3 and 4 schematically shows the view on a stator side, in which the internals have been cut in the central region in order to show the pressure medium cylinders 21 and 22, by means of which the chocks 19 and 20 of the work rolls 4 and 5 can be bent positively and negatively, , while the pressure medium cylinders 25 are provided for positive bends of the intermediate rolls 3 and 6.
  • FIG. 3 shows the widening of the stator yokes in the middle area in order to make space, for example, for the hydraulic adjusting devices 9 and 13 provided one behind the other, and the contours of the covered support roller 2 can only be seen in regions behind the plunger 12.
  • the associated control device which can be designed in accordance with the block diagram of FIG. 5, is essential for working the six-roll stand.
  • the starting point here is two control devices, namely the control device 26 for the thickness control and the control device 27 for the flatness control.
  • a target position transmitter 28 is provided, which can be set manually or depending on the pass schedule and whose setting can be corrected by the control device 26 for the thickness control.
  • the position specified by the target position transmitter 28 is transmitted to the position transmitter 29 for the support roller adjustment and the position transmitter 30 for the intermediate roller adjustment.
  • the symmetrical adjustment is monitored by an encoder 31 “roller geometry”, which in turn is controlled by a synchronous encoder 32.
  • the predefined position is regulated by position regulators 33 and 41.
  • the position regulator 33 for the support roller is given the setpoint by a position transmitter 29, while the actual value of the position is transmitted by the transmitter 36.
  • the output of the position controller 33 is connected to a control valve 35 which determines the application of the hydraulic adjusting device 9.
  • the pressure acting on the hydraulic adjusting device 9 is monitored by a pressure transmitter 37, just as the pressure transmitter 38 determines the pressure acting on the hydraulic adjusting device 13.
  • the measured values of the pressure transmitters 37 and 38 are fed to a totalizer 39, as is the measured value of the pressure transmitter 37 to a pressure regulator 57 and the measurement result of the pressure transmitter 38 to a pressure regulator 44.
  • the position controllers 41 and 46 for the intermediate rolls 3 and 6 receive their setpoint from the position transmitter 30, while the associated actual values are supplied by the position transmitters 43 and 47.
  • the position regulators 41 and 46 control the pressure regulators 44 and 48 via the pressure limiters 59 and 60, which act on the hydraulic adjusting devices 13 and 16 of the intermediate rollers via the regulating valves 45 and 49.
  • the pressure values developed in this way are recorded by the pressure transmitters 38 and 50 and the pressure regulators 44 and 48 are specified as actual values.
  • the synchronizer 32 influences the synchronizer 42 provided on each stand side, which in turn takes additional setpoints on the position controllers 33 and 41 on the two stands.
  • the swivel controller 51 can be used to specify unequal positions on the two sides of the scaffold either manually or as part of the flatness control; so that the axes can be pivoted slightly or wedge-shaped manually or as part of the flatness control.
  • the control device 26 for the thickness control is influenced by a thickness gauge 52 which measures the thickness of the rolled strip 61.
  • the control device 27 for the flatness control is supplied with measured values of a strip tension measuring device 62 which detects the respective strip tension in different zones of a rolled strip 61 and, for example, by a so-called stressometer role can be formed.
  • the lower support roller 7 can be moved to the predetermined height by means of the wedge adjustment 15, and by means of the position controller 33 the upper support roller 2 can be regulated to the predetermined height detected by means of the position transmitter 36.
  • the intermediate rollers 3 and 6 are also first adjusted to the predetermined height by means of the position controllers 41 and 46, however, in order to set the predetermined roll gap profile or a tension-free state, the intermediate rollers position is adjusted from this position by means of the pressure controllers 44 and 48 due to the acceptance of the A portion of the rolling force determined by the distributor 40, while the possibly additional bending forces are brought about by means of the pressure medium cylinders 21, 22, possibly also 24 and 25 of FIG. 1 by means of the pressure regulators 53 with associated control valves 54.
  • Correction values can be effected by means of the target position transmitter 28 via the position transmitter 29 for the support rollers and 30 for the intermediate rollers, which correction values are supplied to the position controllers 33 or 41 and 46 as correction values.
  • the output values of the corresponding position controllers of the different stands are each recorded in synchronous controllers 65 and 66, which provide correction values for the pressure controllers 44 and 48, respectively. So that the position of the support roller 7 is fixed and that of the support roller 2 by means of the position wheels 33 to a predetermined Setpoint value is adjusted, while the values of the bending forces given via line 64 via pressure limiters 59 and 60 and the pressure regulators 44 and 48 arranged downstream of them determine the pressurization of hydraulic adjusting devices 13 and 18 and thus the bending action of intermediate rolls 3 and 6.
  • the pressure medium cylinders 24 and 25 can additionally cause negative forces or other forces can be introduced by acting on the pressure medium cylinders 21 and 22 of FIG. 1 by means of the pressure regulator 53.
  • the scaffold designed according to the invention can be used in different operating modes, in the interest of a so-called flatness control or a control to a minimum of stresses occurring in the strip, bending processes of the work rolls are possible to a relatively large extent without having to apply separate bending forces , or wherein additional bending forces to be applied can be reduced to a minimum.
  • the control device according to FIG. 1 In the first of the possible modes of operation with the control device according to FIG.
  • the adjustment takes place essentially without a predetermined crowning and the roll shape can be influenced both by the central support of the intermediate rolls by means of backup rolls and by roll bending.
  • the roll gap can be changed in many ways in the interest of flatness control, whereby not only the respective amplitude of the deflection of the work roll can be changed, but also the course of the function as such, so that there is a variety of possible influencing forms.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Metal Rolling (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Replacement Of Web Rolls (AREA)

Claims (9)

1. Cage sexto comportant, dans des fenêtres de montants (4), des empoises de cylindres de travail (1), de cylindres intermédiaires (8) et de cylindres d'appui (10, 11,) qui, par leurs axes situés dans un plan vertical commun, peuvent être réglés par des dispositifs de réglage qui prennent appui sur les traverses (5) des montants, les longueurs de table des cylindres intermédiaires dépassant celles des cylindres d'appui, la longueur de table des cylindres d'appui (10, 11) étant inférieure à la largeur maximale du produit laminé et les deux traverses (5) du montant comportant, juxtaposés dans le sens du laminage, deux dispositifs de réglage réglables séparément, le dispositif intérieur (9, 12) servant d'appui aux empoises des cylindres d'appui et le dispositif extérieur servant d'appui à celles des cylindres intermédiaires, caractérisée en ce que les longueurs de tables des cylindres intermédiaires (3, 6) dépassent celles des cylindres de travail (4, 5), en ce que les dispositifs de réglage (9, 13) peuvent être réglés séparément et en ce que le dispositif de commande (Figure 5) qui est placé en avant d'eux assure leur réglage en répartissant d'une manière déterminée à l'avance la force de laminage correspondant à chaque côté de la cage entre le dispositif de réglage (9,13) correspondant aux cylindre d'appui (2, 7) et aux cylindres intermédiaires (9, 13).
2. Cage de laminoir selon la revendication 1, caractérisée en ce que la longueur de table des cylindres d'appui (2, 7) représente de 55 à 90 % de la largeur maximale (8) de la bande à laminer.
3. Cage de laminoir selon l'une des revendications 1 ou 2, caractérisée en ce que les cylindres de travail (4, 5) et les cylindres d'appui (2, 7) au moins sont cylindriques.
4. Cage de laminoir selon l'une des revendications 1 à 3, caractérisée en ce que les empoises (11) des cylindres intermédiaires (3, 6) sont équipées d'un dispositif de flexion (vérin à milieu de pression 24, 25) qui développe des efforts d'écartement.
5. Cage de laminoir selon l'une des revendications 1 à 4, caractérisée en ce que les empoises (19, 20) des cylindres de travail (4, 5) sont équipées d'un dispositif de flexion (vérin à milieu de pression 21, 22) qui peut développer aussi bien des efforts d'écartement que des efforts de traction.
6. Cage de laminoir selon l'une des revendications 1 à 5, caractérisée en ce que les empoises (14) de l'un des cylindres d'appui (7) sont équipées d'un dispositif de réglage mécanique (2) et que les empoises (8) de l'autre cylindres d'appui (2) et les empoises (11, 16) des cylindres intermédiaires (3, 4) sont équipées de dispositifs de réglage hydrauliques (9, 13, 18)
7. Cage de laminoir selon l'une des revendications 1 à 6, caractérisée en ce que les empoises (14) des cylindres d'appui inférieur (7) sont montées dans des dispositifs de réglage (15) comportant des coins.
8. Cage de laminoir selon l'une des revendications 1 à 7, caractérisée en ce qu'aux dispositifs de réglage hydrauliques (9, 13, 18) sont associés des indicateurs de position (36, 43, 47) et des indicateurs de pression (37, 38, 50), en ce que le dispositif de commande (Figure 5) assure, pour le réglage, la commande des dispositifs de réglage hydrauliques correspondants d'après la grandeur de guidage donnée par un dispositif de commande (26) du réglage de l'épaisseur et/ou d'après la grandeur de guidage donnée par un dispositif de commande (27) du réglage de la planéité et en ce qu'après la première passe ou pendant le laminage du produit laminé le réglage des cylindres intermédiaires au moins fait intervenir en plus un réglage de la pression.
9. Cage de laminoir selon la revendication 8, caractérisée en ce que le dispositif de commande (Figure 5) peut être commuté, au moyen d'un commutateur (34), pour différents modes de laminage dont l'un est un pur réglage de position et l'autre un pur réglage de pression et dont les autres sont des modes intermédiaires échelonnés entre ces deux modes.
EP85112324A 1984-10-13 1985-09-28 Cage de laminoir à six cylindres Expired EP0181474B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112324T ATE42483T1 (de) 1984-10-13 1985-09-28 Sechs-walzen-walzwerk.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3437601 1984-10-13
DE3437601A DE3437601A1 (de) 1984-10-13 1984-10-13 Sechs-walzen-walzwerk

Publications (3)

Publication Number Publication Date
EP0181474A2 EP0181474A2 (fr) 1986-05-21
EP0181474A3 EP0181474A3 (en) 1987-01-07
EP0181474B1 true EP0181474B1 (fr) 1989-04-26

Family

ID=6247827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112324A Expired EP0181474B1 (fr) 1984-10-13 1985-09-28 Cage de laminoir à six cylindres

Country Status (4)

Country Link
EP (1) EP0181474B1 (fr)
JP (1) JPS6195704A (fr)
AT (1) ATE42483T1 (fr)
DE (2) DE3437601A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW207967B (fr) * 1990-07-13 1993-06-21 Ube Industries
JPH059430U (ja) * 1991-07-18 1993-02-09 新光金属株式会社 酒類の収納容器
DE29603117U1 (de) * 1996-02-23 1996-04-11 Achenbach Buschhuetten Gmbh Mehrwalzengerüst
US5842368A (en) * 1996-02-23 1998-12-01 Achenbach Buschhutten Gmbh Multiroll stand

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2039959A (en) * 1933-12-28 1936-05-05 Mesta Machine Co Rolling mill
BE558778A (fr) * 1956-06-29
US2985042A (en) * 1959-04-30 1961-05-23 United Eng Foundry Co Rolling mill
DE1452152B2 (de) * 1965-11-17 1973-01-04 Moeller & Neumann Gmbh, 6670 St. Ingbert Walzwerk zur Herstellung von Flachprodukten, insbesondere von Blechen und Bändern
DE1752752A1 (de) * 1968-07-10 1971-05-19 Schloemann Ag Vorrichtung zur Biegung der Walzen von Walzgeruesten gegen den Walzdruck
DE1809474A1 (de) * 1968-11-18 1970-06-11 Demag Ag Einrichtung zum Gegenbiegen der Walzen eines Blech- oder Band-Walzgeruestes
GB1351074A (en) * 1971-02-15 1974-04-24 Hitachi Ltd Rolling mills
DE2138894B2 (de) * 1971-08-04 1976-10-07 Demag Ag, 4100 Duisburg Gegendruckeinrichtung fuer ein walzgeruest mit arbeits- und stuetzwalzen
DE2624876A1 (de) * 1976-06-03 1977-12-15 Schloemann Siemag Ag Walzgeruest fuer bleche und baender
JPS5366849A (en) * 1976-11-26 1978-06-14 Hitachi Ltd Rolling machine
BR8300010A (pt) * 1982-01-06 1983-08-30 Hitachi Ltd Laminador

Also Published As

Publication number Publication date
ATE42483T1 (de) 1989-05-15
DE3437601A1 (de) 1986-04-17
JPS6195704A (ja) 1986-05-14
EP0181474A3 (en) 1987-01-07
DE3569686D1 (en) 1989-06-01
EP0181474A2 (fr) 1986-05-21

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