EP0049798B1 - Laminoir - Google Patents

Laminoir Download PDF

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Publication number
EP0049798B1
EP0049798B1 EP81107692A EP81107692A EP0049798B1 EP 0049798 B1 EP0049798 B1 EP 0049798B1 EP 81107692 A EP81107692 A EP 81107692A EP 81107692 A EP81107692 A EP 81107692A EP 0049798 B1 EP0049798 B1 EP 0049798B1
Authority
EP
European Patent Office
Prior art keywords
roll
rolls
rolling mill
barrel
mill according
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
EP81107692A
Other languages
German (de)
English (en)
Other versions
EP0049798A3 (en
EP0049798A2 (fr
Inventor
Hugo Dr. Feldmann
Friedrich Dr. Hollmann
Gerd Beismann
Horst Gärtner
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6114391&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0049798(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT81107692T priority Critical patent/ATE7114T1/de
Publication of EP0049798A2 publication Critical patent/EP0049798A2/fr
Publication of EP0049798A3 publication Critical patent/EP0049798A3/de
Application granted granted Critical
Publication of EP0049798B1 publication Critical patent/EP0049798B1/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
    • 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
    • B21B13/142—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 by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC

Definitions

  • the invention relates to a rolling mill with work rolls, which are optionally supported on back-up rolls or back-up rolls and intermediate rolls, the work rolls and / or back-up rolls and / or intermediate rolls being axially displaceable relative to each other and each roll of at least one of these pairs of rolls running towards a bale end , curved contour is provided, which extends on the two rollers on opposite sides in each case over part of the width of the rolling stock.
  • Rolling mills of this type are already part of the prior art through US-A-2776586 and DE-A1-2919105. They are designed in such a way that, in rolling operation, the shape of the roll gap and thus the profile of the rolled strip can be influenced by the axial displacement of the rolls having the curved contour and a bending stress acting on them at the same time.
  • a disadvantage of such a known rolling mill is that, in addition to the device for the axial displacement, additional rolls bending devices must be assigned to the rolls having a curved contour over part of their bale length.
  • roll bending devices are required in order to be able to bend the ends of the rolls provided with the curved contour away from the roll gap or from the rolling strip (positive bending), and on the other hand, roll bending devices are also required which allow the ends of the rolls provided with the curved contour to be bent guaranteed against the roll gap or the rolled strip (negative bending). In one case this reduces the rolling pressure on the strip edges, while in the other case an increase in the rolling pressure in the area of the strip edges can be achieved.
  • a change in the roll gap contour is only possible to a limited extent in the known rolling mill without roll bending devices and only in the sense of a concave strip shape.
  • the present invention aims to overcome these drawbacks. It is therefore her aim to create a rolling mill of the generic type in which the shape of the roll gap and thus the rolled strip cross section can be influenced practically exclusively by the axial displacement of the rolls provided with the curved contour and, if necessary, the strip edge pressure can be reduced without any effort.
  • This object can be achieved in a simple manner in that the curved contour extends over the entire bale length of both rollers and has a shape in which the two bale contours complement each other exclusively in a certain relative axial position of these rollers.
  • the measures according to the present invention can also be implemented in duo rolling mills, that is to say they are not restricted to rolling mills with backup rolls or backup and intermediate rolls, as is the case according to D E-A 1-2919 105.
  • the advantage has been shown that the shape of the roll gap and thus the cross-sectional shape of the rolled strip can be influenced even by small displacement paths of the rollers having the curved contour and that no direct adjustment of the position of the displaceable rollers to the width of the rolling stock has to take place, as is the case, for example, with is the case with another known rolling mill according to DE-A-2 260 256.
  • the effective crowning of the roller set to the rolling force and the width of the rolling stock can be set quickly and specifically due to the small displacement paths, whereby rectangular, concave and convex rolling stock cross-sections can be achieved depending on the displacement direction and degree.
  • a particularly simple construction of a rolling mill according to the invention can be achieved by the features of claim 2.
  • the design of the rollers specified in claim 3 has proven particularly useful.
  • a particularly simple construction of a rolling mill according to the invention is achieved by using the identification features specified in claim 7. Irrespective of or simultaneously with this configuration, the features of claim 8 can also be used in practice.
  • the shape of the roll gap and thus the roll strip cross section can also be influenced by the measures that are set out in claims 9 and 10.
  • the shape of the rollers having the curved contour can be freely selected, so that the effective crowning can be adapted to the respective requirements.
  • the axial displacement of these rollers can, if necessary, be carried out in the same or in opposite directions.
  • the axial displacement paths of both rollers can be the same or different.
  • 1 shows a duo rolling mill 1, in the roll stands 2 of which a pair of work rolls 3, 4 are each guided by means of chocks 5, 6. Using conventional adjusting devices 7, the pair of work rolls 3, 4 can be set against the rolling strip 9 running through the roll gap 8.
  • Both work rolls of the pair of work rolls 3, 4 are mounted axially displaceably in the chocks 5, 6 via their pins 10, 11, the devices for axial adjustment 'each engaging a roll neck 10 or 11.
  • the roll bales 12 of both work rolls 3 and 4 of the work roll pair 3, 4 have a curved contour over their entire length, for example in such a way that this contour in the case of the upper work roll 3 over the the left half of the roll barrel 12 is convex and concave over the right half thereof, while in the lower work roll 4 it is concave over the left half of the roll barrel 12 and convex over the right half of the same. Both sections of the rolled bales 12 are determined by the same curvature curves.
  • both work rolls 3 and 4 of the work roll pair 3, 4 have an identical - here bottle-like - shape of the roll barrel 12 and are provided in the roll stand of the duo rolling mill 1 relative to each other in an installed position turned through 180 °.
  • Fig. 1 the average axial setting of both work rolls 3 and 4 of the work roll pair 3, 4 is shown, and it can be seen that with this axial setting the roll gap 8 at least over the width of the roll belt 9, but preferably over the entire bale length, a constant Cross-sectional height, although it runs slightly S-shaped.
  • FIG. 2 shows a four-high rolling mill 21 according to the invention, in which the two support rolls 23 and 24 of a pair of support rolls 23, 24 are guided in the roll stands 22 via chocks 25, 26.
  • a work roller pair 23 ', 24' is provided, which delimits the roll gap 28 for the rolled strip 29.
  • the adjustment of the work rolls 23 'and 24' to determine the height of the roll gap 28 is carried out by adjusting devices 27 which act on the chocks 25 and 26 of the support rolls 23 and 24.
  • both support rollers 23 and 24 of the support roller pair 23, 24 are held axially displaceably in the chocks 25 and 26 via their roller journals 30 and 31, respectively, with the devices not shown on each of the roller journals 30 and 31 attack for axial adjustment.
  • the roll bales 32 of the two support rolls 23 and 24 have the curved contour over their entire length, in the same way as the work rolls 3 and 4 in the work roll pair 3, 4 of the duo rolling mill 1 1.
  • the left half of the roll barrel 32 of the upper support roller 23 thus has the convexly curved contour, while the right half of the same is provided with the concave curved contour.
  • the left half of the roll barrel 32 of the lower support roller 24 has the concavely curved contour and the right half thereof has the convexly curved contour.
  • both bale sections are determined by the same curvature curves.
  • the roll bales of the work rolls 23 'and 24' are cylindrical in themselves, but are given a slightly S-shaped bend due to the interaction with the support rolls, so that the roll gap 28, which the roll band 29 passes through, receives a correspondingly slightly S-shaped cross-sectional shape.
  • FIG. 3 shows a six-high rolling mill 41 in which, in the roll stands 42, in addition to the two support rolls 43 and 44 of the support roll pairs 43, 44 and the two work rolls 43 'and 44' of the work roll pair 43 ', 44', two intermediate rolls 43 “ and 44 "of an intermediate roll Paares 43 “, 44” are arranged.
  • the support rollers 43 and 44 of the support roller pair 43, 44 are guided by chocks 45 and 46 in the roller stands 42, while the intermediate rollers 43 “and 44” of the intermediate roller pair 43 “, 44” in turn in chocks 45 "and 46", respectively be guided in the chocks 45 and 46 for the support rollers 43 and 44.
  • Both the support rolls 43 and 44 of the support roll pair 43, 44 and the work rolls 43 ', 44' of the work roll pair 43 ', 44' have cylindrical rolls.
  • the intermediate rolls 43 "and 44" of the pair of intermediate rolls 43 ", 44" are equipped with roll bales which have a curved contour over the entire length of the bale.
  • the bale contour of the intermediate rolls 43 "and 44" can basically correspond to that of the two work rolls 3 and 4 of the duo rolling mill 1 according to FIG. 1 or that of the backup rolls 23 and 24 of the four-high rolling mill 21 according to FIG. 2. However, it can be limited by curvature curves with larger radii, because the intermediate rolls 43 "and 44" are each supported on the cylindrical roll balls of the support rolls 43 and 44.
  • the intermediate rolls 43 ′′ and 44 ′′ are subjected to a deformation, which results in a greater curvature of the bale contour in the direction of the work rolls 43 ′ and 44 ′.
  • a slightly S-shaped curvature is then forced onto the cylindrical roll bales of the work rolls 43 'and 44', which in turn determines the shape of the roll gap 48 for the rolled strip 49.
  • the shape of the roll gap 8 is determined directly by axial displacement of one or both work rolls 3 and 4.
  • a corresponding axial displacement of one or both support rolls 23 and 24 takes place to change the shape of the roll gap 28.
  • the shape of the roll gap 48 is finally influenced solely by the axial displacement of one or both intermediate rolls 43 "and 44".
  • the pair of rolls having the curved bale contour are the work rolls 3 and 4 of the duo rolling mill 1 according to FIG. 1.
  • FIG. 4 shows the mean axial sliding position for both rollers 3 and 4 of the pair of rollers 3, 4, which corresponds to that of FIG. 1.
  • the roll gap 8 between the two rolls 3 and 4 has a constant height over the entire bale length, so that the roll strip 9 is rolled out over its entire width with a uniform thickness, although the roll gap 8 has a slightly S-shaped curvature.
  • rollers 3 and 4 are designed completely identically and their shape can be freely selected so that the effective crowning optimally meets the respective requirements can be adjusted.
  • the axial displacement of the two rollers 3 and 4 of the pair of rollers 3, 4 can take place in the same direction or in opposite directions, as required, and the axial displacement paths can also be the same or different.
  • the shape of the roll gap 8 can, of course, also be additionally influenced by the fact that the axes of the cooperating pair of rolls 3, 4 are installed in the roll plane in a mutually inclined manner. An additional influence on the shape of the roll gap 8 leaves but can also be achieved if the axes of the cooperating pair of rollers are set inclined to one another transversely to the roller plane. It is essential, however, that the shape of the roll gap 8 can be determined mainly by axially displacing the two rolls of the roll pair, the roll balls of which have the curved contour over their entire length.
  • FIGS. 4 to 6 are intended to illustrate that the invention is not fundamentally limited to the bottle-like curved contour of the rolled bales shown in FIGS. 4 to 6, in which the course of curvature is convex over one half of the bale and concave over the other half of the bale, but also it is possible to use a pair of rollers 3, 4 in which the bales of both rollers 3 and 4 have different shapes, but also here in such a way that the two bale contours complement each other exclusively in a certain relative axial position of the rollers 3 and 4.
  • the method of operation according to the invention for determining the shape of the roll gap has the considerable advantage that it can be used in two- and multi-roll stands as well as in cold and hot rolling. Furthermore, it can be used just as well for one-way scaffolding and reversing scaffolding as for tandem streets and reversing streets.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)

Claims (10)

1. Laminoir avec cylindres de travail (3, 4; 23', 24'; 43', 44') qui éventuellement prennent appui sur des cylindres de soutien (23, 24) ou des cylindres de soutien (43, 44) et des cylindres intermédiaires (43", 44"), les cylindres de travail et/ou les cylindres de soutien et/ou les cylindres intermédiaires pouvant être déplacés axialement les uns par rapport aux autres et chaque cylindre d'au moins une de ces paires de cylindres étant muni d'un contour incurvé dirigé vers une extrémité du corps de cylindre et s'étendant sur les deux cylindres vers des côtés opposés sur une partie de la largeur du produit à laminer, caractérisé par le fait que le contour incurvé s'étend sur toute la longueur du corps des deux cylindres (3, 4 resp. 23, 24 resp. 43", 44") et a une forme telle que les deux contours de corps de cylindre sont complémentaires l'un de l'autre exclusivement dans une position axiale déterminée (p.ex. fig. 4) de ces cylindres (3, 4 resp. 23,24 resp. 43", 44").
2. Laminoir selon la revendication 1, caractérisé par le fait que les deux cylindres (3 et 4; 23 et 24; 43" et 44") de la paire de cylindres (3, 4; 23, 24; 43", 44") ont une forme identique et, dans leur position d'installation, sont disposés retournés de 180° l'un par rapport à l'autre (Fig. 1, 2 et 3).
3. Laminoir selon la revendication 1 ou 2, caractérisé par le fait que les corps de cylindre (12, 23', 24', 43', 44' resp. 32, 43, 44 resp. 43", 44") présentent sur une moitié de leur longueur un contour convexe et, sur l'autre moitié, un contour concave, les deux tronçons de corps étant définis par les mêmes courbures (fig. 4 à 6).
4. Laminoir selon la revendication 1, caractérisé par le fait que les deux cylindres de la paire de cylindres ont une forme différente (12', 12"; fig. 7).
5. Laminoir selon la revendication 1 ou 4, caractérisé par le fait que le corps de cylindre (12') d'un cylindre (3) a un contour convexe sur toute sa longueur et le corps de cylindre (12") de l'autre cylindre (4) a un contour concave sur toute sa longueur.
6. Laminoir selon la revendication 1 ou 4, caractérisé par le fait que le corps de cylindre (12') d'un cylindre (3) a un contour alternant plusieurs fois convexe-concave-convexe et le corps de cylindre (12") de l'autre cylindre a un contour inverse correspondant concave-convexe-concave (fig. 7).
7. Laminoir selon au moins une des revendications 1 à 6, caractérisé par le fait que le contour des corps de cylindre (12; 12', 12"; 32) est déterminé mécaniquement, par exemple est formé par rectifiage du profil.
8. Laminoir selon au moins une des revendications 1 à 7, caractérisé par le fait que le contour des corps de cylindre (12; 12', 12"; 32) est modifié thermiquement, par exemple par chauffage et/ou refroidissement.
9. Laminoir selon au moins une des revendications 1 à 8, caractérisé par le fait que les axes de la paire de cylindres (3, 4; 23', 24'; 43', 44') déterminant l'emprise (8; 28; 48) peuvent basculer dans le plan de laminage l'un par rapport à l'autre.
10. Laminoir selon au moins une des revendications 1 à 9, caractérisé par le fait que les axes des cylindres de la paire de cylindres dont le corps présente le contour incurvé (3, 4; 23, 24; 43", 44") ont, en travers du plan de laminage, une inclinaison réglable l'un par rapport à l'autre.
EP81107692A 1980-10-15 1981-09-28 Laminoir Expired EP0049798B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81107692T ATE7114T1 (de) 1980-10-15 1981-09-28 Walzwerk.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3038865 1980-10-15
DE3038865A DE3038865C1 (de) 1980-10-15 1980-10-15 Walzgeruest mit axial verschiebbaren Walzen

Publications (3)

Publication Number Publication Date
EP0049798A2 EP0049798A2 (fr) 1982-04-21
EP0049798A3 EP0049798A3 (en) 1982-06-02
EP0049798B1 true EP0049798B1 (fr) 1984-04-18

Family

ID=6114391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107692A Expired EP0049798B1 (fr) 1980-10-15 1981-09-28 Laminoir

Country Status (6)

Country Link
US (1) US4440012A (fr)
EP (1) EP0049798B1 (fr)
JP (3) JPS5791807A (fr)
AT (1) ATE7114T1 (fr)
DE (2) DE3038865C1 (fr)
SU (1) SU1306468A3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3624241A1 (de) * 1986-07-18 1988-01-28 Schloemann Siemag Ag Walzwerk zur herstellung eines walzgutes, insbesondere eines walzbandes
DE19736767A1 (de) * 1997-08-23 1999-03-04 Schloemann Siemag Ag Walzgerüst zum Walzen von Bändern
DE19830033C1 (de) * 1998-06-26 1999-07-08 Mannesmann Ag Walzwerk

Families Citing this family (64)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4519233A (en) * 1980-10-15 1985-05-28 Sms Schloemann-Siemag Ag Roll stand with noncylindrical rolls
DE3213496A1 (de) * 1982-04-10 1983-10-20 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren walzen
DE3038865C1 (de) * 1980-10-15 1982-12-23 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren Walzen
DE3245090A1 (de) * 1982-12-06 1984-06-07 SMS Schloemann-Siemag AG, 4000 Düsseldorf Verfahren und einrichtung zum walzen von metallbaendern
DE3331055C2 (de) * 1983-08-29 1994-11-03 Schloemann Siemag Ag Walzgerüst mit axial verschieblichen Arbeitswalzen
DE3585164D1 (de) * 1984-02-29 1992-02-27 Kawasaki Steel Co Warmwalzverfahren.
DE3409221A1 (de) * 1984-03-14 1985-09-19 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren arbeitswalzen
DE3411853A1 (de) * 1984-03-30 1985-10-10 SMS Schloemann-Siemag AG, 4000 Düsseldorf Angetriebene stuetzwalzen aufweisendes vier- oder sechswalzengeruest
JPS61209705A (ja) * 1985-03-14 1986-09-18 Ishikawajima Harima Heavy Ind Co Ltd 圧延方法および装置
DE3602698A1 (de) * 1985-04-16 1986-10-16 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren walzen
JPS61296904A (ja) * 1985-06-26 1986-12-27 Nippon Steel Corp 圧延機
EP0212002A3 (fr) * 1985-08-13 1987-06-03 MANNESMANN Aktiengesellschaft Cage de laminoir
US4656859A (en) * 1985-08-21 1987-04-14 Wean United, Inc. Rolling mill stand employing variable crown rolls and associated method
DE3600144A1 (de) * 1986-01-07 1987-07-09 Schloemann Siemag Ag Anordnung zum entfernen von zunder von warmgewalzten stahlbaendern
DE3785778D1 (de) * 1986-03-03 1993-06-17 Schloemann Siemag Ag Walzgeruest.
JPS62244501A (ja) * 1986-04-16 1987-10-24 Kawasaki Heavy Ind Ltd 圧延スタンド
US4735116A (en) * 1986-05-06 1988-04-05 United Engineering Rolling Mills, Inc. Spreading rolling mill and associated method
JPS62263805A (ja) * 1986-05-08 1987-11-16 Kawasaki Heavy Ind Ltd 圧延ロール及び圧延方法
JPH0688053B2 (ja) * 1986-05-30 1994-11-09 川崎重工業株式会社 圧延方法
DE3620197A1 (de) * 1986-06-16 1987-12-17 Schloemann Siemag Ag Walzwerk zur herstellung eines walzgutes, insbesondere eines walzbandes
JPS6316802A (ja) * 1986-07-10 1988-01-23 Kawasaki Heavy Ind Ltd 圧延方法
JPS6320106A (ja) * 1986-07-11 1988-01-27 Kawasaki Heavy Ind Ltd 圧延機のロール及びその製造方法
DE3626516C1 (en) * 1986-08-05 1987-04-02 Sundwiger Eisen Maschinen Multi-roll rolling stand with intermediate rolls which have tapered ends and can be displaced in opposite directions in pairs
JPH069686B2 (ja) * 1986-08-05 1994-02-09 ズンドビガ− アイゼンヒユツテ マシ−ネンフアブリク グラ− ウント コンパニ− 多ロ−ル圧延スタンド
JPS6356306A (ja) * 1986-08-25 1988-03-10 Nippon Steel Corp 金属帯の圧延機
JPS6360006A (ja) * 1986-08-29 1988-03-16 Kawasaki Heavy Ind Ltd 圧延スタンド
DE3634367A1 (de) * 1986-10-09 1988-04-21 Schloemann Siemag Ag Walzen-anordnung zur verformungsfreien behandlung von bewegten bandfoermigen erzeugnissen
DE3707560A1 (de) * 1987-03-10 1988-09-22 Schloemann Siemag Ag Walzgeruest
DE3712043C2 (de) * 1987-04-09 1995-04-13 Schloemann Siemag Ag Walzgerüst mit axial verschiebbaren Walzen
DE3819303A1 (de) * 1988-06-03 1989-12-07 Mannesmann Ag Flachwalzwerk
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DE4309986A1 (de) * 1993-03-29 1994-10-06 Schloemann Siemag Ag Verfahren und Vorrichtung zum Walzen eines Walzbandes
JP3348503B2 (ja) * 1994-02-25 2002-11-20 石川島播磨重工業株式会社 圧延機用のワークロールとロールシフト式圧延機
DE4409299A1 (de) * 1994-03-18 1995-09-21 Schloemann Siemag Ag Verfahren und Vorrichtung zum Walzen von Bändern
DE4424613B4 (de) * 1994-07-13 2007-03-29 Sms Demag Ag Verfahren zum Betreiben eines Walzgerüstes
AT402267B (de) * 1995-04-25 1997-03-25 Voest Alpine Ind Anlagen Verfahren zum herstellen eines stranges in form eines metallbandes sowie einrichtung zur durchführung des verfahrens
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US6119500A (en) * 1999-05-20 2000-09-19 Danieli Corporation Inverse symmetrical variable crown roll and associated method
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US6314776B1 (en) * 2000-10-03 2001-11-13 Alcoa Inc. Sixth order actuator and mill set-up system for rolling mill profile and flatness control
JP3747786B2 (ja) † 2001-02-05 2006-02-22 株式会社日立製作所 板材用圧延機の圧延方法及び板材用圧延設備
AT410765B (de) 2001-09-12 2003-07-25 Voest Alpine Ind Anlagen Walzgerüst zur herstellung von walzband
DE102004020132A1 (de) 2003-12-23 2005-07-28 Sms Demag Ag Verfahren und Walzgerüst zur mehrfachen Profilbeeinflussung
JP4818680B2 (ja) * 2005-10-17 2011-11-16 新日本製鐵株式会社 圧延方法
JP4960009B2 (ja) 2006-05-09 2012-06-27 スチールプランテック株式会社 圧延ロール、圧延機および圧延方法
US8881569B2 (en) 2006-06-14 2014-11-11 Siemens Vai Metals Technologies Gmbh Rolling mill stand for the production of rolled strip or sheet metal
DE102006051728B4 (de) * 2006-10-30 2013-11-21 Outokumpu Nirosta Gmbh Verfahren zum Walzen von Metallbändern, inbesondere von Stahlbändern
DE102008015828A1 (de) * 2007-09-26 2009-04-02 Sms Demag Ag Walzvorrichtung und Verfahren für deren Betrieb
US8607847B2 (en) * 2008-08-05 2013-12-17 Nucor Corporation Method for casting metal strip with dynamic crown control
US8607848B2 (en) * 2008-08-05 2013-12-17 Nucor Corporation Method for casting metal strip with dynamic crown control
US8505611B2 (en) 2011-06-10 2013-08-13 Castrip, Llc Twin roll continuous caster
JP5625749B2 (ja) * 2010-10-28 2014-11-19 Ｊｆｅスチール株式会社 圧延機および圧延方法
JP5644418B2 (ja) * 2010-11-24 2014-12-24 株式会社Ihi ロールプレス装置
DE102012212532B4 (de) 2012-07-18 2016-12-15 Achenbach Buschhütten GmbH & Co. KG Walzgerüst mit konturierten Walzen
CN103447312B (zh) * 2013-09-03 2015-08-12 首钢京唐钢铁联合有限责任公司 一种热轧板板型的控制方法
JP6119731B2 (ja) * 2014-03-24 2017-04-26 Ｊｆｅスチール株式会社 ２段式圧延機及びロールシフト方法
EP3124130A1 (fr) * 2015-07-28 2017-02-01 Primetals Technologies Austria GmbH Meule de cylindre destinee a l'evitement cible de quarts d'onde

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DE3624241A1 (de) * 1986-07-18 1988-01-28 Schloemann Siemag Ag Walzwerk zur herstellung eines walzgutes, insbesondere eines walzbandes
DE3624241C2 (de) * 1986-07-18 1996-07-11 Schloemann Siemag Ag Verfahren zum Betrieb eines Walzwerkes zur Herstellung eines Walzbandes
DE19736767A1 (de) * 1997-08-23 1999-03-04 Schloemann Siemag Ag Walzgerüst zum Walzen von Bändern
DE19736767C2 (de) * 1997-08-23 2003-10-30 Sms Demag Ag Walzgerüst zum Walzen von Bändern
DE19830033C1 (de) * 1998-06-26 1999-07-08 Mannesmann Ag Walzwerk

Also Published As

Publication number Publication date
JPH0616885B2 (ja) 1994-03-09
SU1306468A3 (ru) 1987-04-23
JPH0411281B2 (fr) 1992-02-28
ATE7114T1 (de) 1984-05-15
JPS5791807A (en) 1982-06-08
DE3038865C1 (de) 1982-12-23
EP0049798A3 (en) 1982-06-02
JPH01266901A (ja) 1989-10-24
JPH0669578B2 (ja) 1994-09-07
EP0049798A2 (fr) 1982-04-21
DE3163226D1 (en) 1984-05-24
JPH01266902A (ja) 1989-10-24
US4440012A (en) 1984-04-03

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