EP0235769B1 - Cage de laminoir - Google Patents

Cage de laminoir Download PDF

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Publication number
EP0235769B1
EP0235769B1 EP87102865A EP87102865A EP0235769B1 EP 0235769 B1 EP0235769 B1 EP 0235769B1 EP 87102865 A EP87102865 A EP 87102865A EP 87102865 A EP87102865 A EP 87102865A EP 0235769 B1 EP0235769 B1 EP 0235769B1
Authority
EP
European Patent Office
Prior art keywords
rolls
annular
working rolls
roll stand
stand 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 - Lifetime
Application number
EP87102865A
Other languages
German (de)
English (en)
Other versions
EP0235769A2 (fr
EP0235769A3 (en
Inventor
Hugo Dr. Feldmann
Gerd Beisemann
Tilmann Dr. Schultes
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
Priority claimed from DE19863606857 external-priority patent/DE3606857A1/de
Priority claimed from DE19863609916 external-priority patent/DE3609916A1/de
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT87102865T priority Critical patent/ATE89200T1/de
Publication of EP0235769A2 publication Critical patent/EP0235769A2/fr
Publication of EP0235769A3 publication Critical patent/EP0235769A3/de
Application granted granted Critical
Publication of EP0235769B1 publication Critical patent/EP0235769B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/12—Axial shifting the rolls
    • B21B2269/14—Work rolls

Definitions

  • the invention relates to a roll stand with at least two support rolls and two work rolls arranged between and supported by them, in which the work rolls are axially displaceable and the length of the bales of these work rolls exceeds the bale of the rolls supporting them by at least the displacement distance of the work rolls, so that the work rolls are supported in all displacement phases by the full bale length of the rolls supporting them.
  • the work rolls When rolling strips, the work rolls, even if they are supported by rolls that engage behind them, are bent outwards under the influence of the rolling force. If, in order to compensate for or avoid deformation of the roll gap, work rolls are cambered and / or rolls are subjected to bending force, the roll gap can be brought to a predetermined profile over its essential length, but disadvantageously high bending forces have to be applied, and the supporting forces occurring over the length of the surface lines of the rolls have undesirably high extreme values. Stress peaks exerted on the rolling stock in the strip edge area result in the profile of the roll gap narrowing disadvantageously in the area of the strip edges toward the latter.
  • rollers of special shape which can be displaced axially relative to one another, the cross sections of which are convex in one length range and concave in another.
  • the diameters modified as a function of the bale length are compensated, the sum of the roller diameters decreasing in the center when the rollers are displaced in one direction, while increasing in the opposite direction when the rollers are displaced.
  • the shape of the roll gap can essentially be influenced directly by axially displacing the rolls essentially with regard to their parabolic component, but the force distribution along the surface lines also leads to an increase in tension in the area of the strip edges and thus to a decrease in the strip thickness in the edge region.
  • EP-A-0 112 969 discloses a four-roll stand according to the preamble of claim 1, in which at least the work rolls are designed to be axially displaceable and are each equipped with roll bending devices which are capable of applying both positive and negative moments.
  • roll bending devices which are capable of applying both positive and negative moments.
  • the invention has for its object to provide work rolls, by using them with optimal axial adjustment both the thickness drop in the band edge area and the usual tension maxima in the band edge area are avoided, so that the high stresses of the rolls in the band edge area are reduced and longer service lives of the same are achieved .
  • the required ring trough can be placed over the belt edge in such a way that the work roll is not forced into the desired contour of the working gap even under load in this area is, especially since the support of the work roll on the support or intermediate roll engaging behind it is secured by the following end of the bale beyond the width of the rolling stock.
  • This not only results in the desired reduction in the thickness of the rolled material in the strip edge area, but also the forces occurring between the work roll and the roll supporting it do not have any extreme stress peaks, even if there is a slight relief in the area of the trough and less in the area of the adjacent bale section Increase.
  • FIG. 1 shows schematically a four-roll stand, in which support rolls 1 and 2 support work rolls 3 and 4, which enclose the rolling stock 5 between them.
  • the work rolls 3 and 4 each have a flat, annular depression 8 in an end region of their bales 6.
  • This ring trough 8 is placed over a strip edge of the rolling stock 5 such that the usual tendency to reduce the thickness of the rolling stock 5 in the strip edge region is compensated for.
  • the bottom of the ring troughs only steps back about 0.2 to at most 1.0 mm behind the continuous lines of the bales 6 of the work rolls 3, 4.
  • depths between 0.2 and 0.4 mm are preferred.
  • the ring troughs are therefore relatively flat, and their flanks run quite flat at the specified width. This width can be between a tenth of the diameter of the work roll and the full diameter, and the distance from the free bale end can be between 0.1 times and 1 times the diameter of the work roll, but can also be chosen to be larger.
  • An embodiment of a work roll is shown in Fig. 2, wherein a representation with suppressed zero point was selected to detect the height differences. With a roller length of 1600 mm and a nominal diameter of 500 mm, the trough depth is approximately 1/6 mm with a width of the trough of almost 100 mm and a distance from the adjacent free bale end of approximately 300 mm.
  • FIG. 3 a four-roll stand is shown schematically, which largely corresponds to that of Fig. 1, the designations of which are also used here.
  • the bales 6 of the work rolls 3 and 4 supported by support rolls 1 and 2 also have annular grooves 8 here, which, in order to be recognized at all in the drawing, are exaggerated.
  • the work rolls 3 and 4 are shifted in opposite directions so that the annular groove 8 is in the region of mutually opposite strip edges of the rolling stock 5.
  • the work rolls 3 and 4 are apparently supported solely by the annular reinforcements 7; since in practice they have a very small height of about 0.2 to at most 1.2 mm, the bales 6 of the work rolls lie practically continuously on the bales of the support rolls 1, 2, and due to the elasticity of the rolls and the elastic Even in the area of the ring troughs 7, roll flattening usually only relieves, but does not lift off the bale of the support rolls.
  • FIG. 4 An exemplary embodiment of a work roll according to FIG. 3 is shown in FIG. 4, which diagrammatically represents the course of a surface line of one of the work rolls.
  • a representation with suppressed zero point was chosen as in FIG. 2.
  • a roller length of 1600 mm and a nominal diameter of the roller of 500 mm this results in a crown height of the ring-shaped reinforcement of approximately 1/6 mm, which is also approximately Corridor depth corresponds to the ring trough.
  • the contour that grips the reinforcement and the annular recess has a length of almost 200 mm, and the distance of the contour from the free end of the bale is of the same order of magnitude.
  • the distribution of the supporting forces supporting the work rolls can also be seen in FIG. 6 for a predetermined bandwidth B. It rises from about 4.5 kN / mm flat at the end of the support to about 8 kN / mm approximately in the middle of the band, drops to about 3 kN / mm in the area of the ring troughs and reaches a maximum in the area of the annular reinforcement 7 , which corresponds approximately to the central load.
  • the influence of slight axial displacements is shown by branching the curve into a family of curves.
  • the ring troughs 8 are each provided with an approximately equally wide and flat reinforcement 7. As shown, this reinforcement is provided on the side of the ring trough facing the near end of the bale; it improves the tension field as well as the central running of the rolled strip.
  • contours according to the invention can be applied to otherwise cylindrical work rolls.
  • the work rolls can also be cambered and / or have a so-called CVC cut, as well as intermediate rolls can optionally also be provided and the different roll profiles can be provided in any combination and can be applied in any desired combination to any of the rolls.

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

Claims (8)

  1. Cage de laminoir comprenant au moins deux cylindres de support (1, 2) et deux cylindres de travail (3, 4) disposés entre et supportés par ces cylindres de support, les cylindres de travail (3, 4) étant déplaçables axialement et la longueur des corps des cylindres de travail dépassant la longueur des corps des cylindres de support (3, 4) qui les supportent d'au moins la distance de déplacement, de telle sorte que dans toutes les phases de déplacement les cylindres de travail (3, 4) soient supportés par toute la longueur des cylindres (1, 2) qui les supportent, caractérisée en ce que chaque cylindre de travail (3, 4) comporte une dépression annulaire plane (8) dans une seule des régions d'extrémité de son corps (6), en ce que la dépression annulaire a une profondeur de 0,2 à 1,0 mm, une largeur comprise entre 0,1 D et 1 D et est située à une distance d'au moins 0,1 D de l'extrémité du corps, D étant le diamètre des cylindres de travail (3, 4), en ce que l'un des cylindres de travail présente sa dépression annulaire côté entraînement et l'autre cylindre présente sa dépression côté actionnement, et en ce qu'il est prévu entre chaque dépression annulaire (8) et l'extrémité de corps voisine un renfort annulaire plan (7) dont la largeur est comprise entre 0,15 D et 1 D et dont l'épaisseur est comprise entre 0,2 et 1,2 mm.
  2. Cage de laminoir selon la revendication 1, caractérisée en ce que ses deux cylindres de travail (3, 4) sont réalisés avec les mêmes corps et/ou les mêmes formes de profil et/ou les mêmes dimensions, considérés suivant une symétrie plane.
  3. Cage de laminoir selon l'une ou l'autre des revendications 1 ou 2, caractérisée en ce que, en dehors de leur profil imposé par la dépression annulaire (8) et le renfort annulaire (7), les corps (6) des cylindres de travail (3, 4) sont réalisés de manière cylindrique.
  4. Cage de laminoir selon l'une ou l'autre des revendications 1 ou 2, caractérisée en ce que, en dehors de leur profil imposé par la dépression annulaire (8) et le renfort annulaire (7), les corps (6) des cylindres de travail (3, 4) sont réalisés de manière bombée.
  5. Cage de laminoir selon l'une quelconque des revendications 1 à 4, caractérisée en ce que, en dehors de leur profil imposé par la dépression annulaire (8) et le renfort annulaire (7), les corps (6) des cylindres de travail (3, 4) ont un diamètre qui évolue suivant un meulage CVC et qui présente un profil convexe sur une partie de la longueur et un profil concave sur une autre partie de la longueur.
  6. Cage de laminoir selon la revendication 5, caractérisée en ce que la dépression annulaire (8) ainsi que le renfort annulaire (7) sont respectivement prévus à l'intérieur de la partie convexe de l'évolution du diamètre suivant un meulage CVC du cylindre de travail (3, 4).
  7. Cage de laminoir selon l'une quelconque des revendications 1 à 6, caractérisée en ce que tout au moins les cylindres de support (1, 2) et/ou des cylindres intermédiaires sont de plus réalisés de manière réglable axialement et présentent en option, outre un bombage, un diamètre qui évolue suivant un meulage CVC.
  8. Cage de laminoir selon l'une quelconque des revendications 1 à 7, caractérisée en ce que des dispositifs de flexion sont associés au moins aux composants de l'une des paires de cylindres.
EP87102865A 1986-03-03 1987-02-27 Cage de laminoir Expired - Lifetime EP0235769B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87102865T ATE89200T1 (de) 1986-03-03 1987-02-27 Walzgeruest.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19863606857 DE3606857A1 (de) 1986-03-03 1986-03-03 Walzgeruest
DE3606857 1986-03-03
DE19863609916 DE3609916A1 (de) 1986-03-24 1986-03-24 Walzgeruest
DE3609916 1986-03-24

Publications (3)

Publication Number Publication Date
EP0235769A2 EP0235769A2 (fr) 1987-09-09
EP0235769A3 EP0235769A3 (en) 1989-04-12
EP0235769B1 true EP0235769B1 (fr) 1993-05-12

Family

ID=25841535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87102865A Expired - Lifetime EP0235769B1 (fr) 1986-03-03 1987-02-27 Cage de laminoir

Country Status (2)

Country Link
EP (1) EP0235769B1 (fr)
DE (1) DE3785778D1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS517635B2 (fr) * 1971-12-10 1976-03-09
DE3038865C1 (de) * 1980-10-15 1982-12-23 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren Walzen
JPS591005A (ja) * 1982-06-28 1984-01-06 Kawasaki Steel Corp 圧延機
DE3245090A1 (de) * 1982-12-06 1984-06-07 SMS Schloemann-Siemag AG, 4000 Düsseldorf Verfahren und einrichtung zum walzen von metallbaendern
EP0153849B1 (fr) * 1984-02-29 1992-01-15 Kawasaki Steel Corporation Procédé de laminage à chaud

Also Published As

Publication number Publication date
DE3785778D1 (de) 1993-06-17
EP0235769A2 (fr) 1987-09-09
EP0235769A3 (en) 1989-04-12

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