EP1648626B1 - Dispositif de laminage - Google Patents

Dispositif de laminage Download PDF

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Publication number
EP1648626B1
EP1648626B1 EP04763370A EP04763370A EP1648626B1 EP 1648626 B1 EP1648626 B1 EP 1648626B1 EP 04763370 A EP04763370 A EP 04763370A EP 04763370 A EP04763370 A EP 04763370A EP 1648626 B1 EP1648626 B1 EP 1648626B1
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EP
European Patent Office
Prior art keywords
roll
working
chock
axial
rolls
Prior art date
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Active
Application number
EP04763370A
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German (de)
English (en)
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EP1648626A1 (fr
Inventor
Bernd Zieser
Achim Klein
Florian Lindner
Stefan Wendt
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 Demag AG
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Publication date
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Publication of EP1648626A1 publication Critical patent/EP1648626A1/fr
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Classifications

    • 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
    • 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
    • B21B2269/00—Roll bending or shifting
    • 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

Definitions

  • the invention relates to a rolling device with two work rolls, which are mounted in each case by means of work roll chocks in a rolling stand, wherein the work roll chocks in the rolling stand via at least one Agriculturewalzenverriegelung are locked and unlocked, at least two other rollers, in particular two support rollers, each supported by means of roll chocks in the rolling mill are, wherein both at least one of the work rolls and at least one of the other rolls in the roll stand for setting a desired roll gap relative to the other work roll or the other further roll, in particular in the vertical direction, are adjustable, the work rolls with Axialverschiebeschn for axial displacement are provided, with which the work rolls can be brought relative to the rolling stand in a desired axial position and held there, and wherein the work rolls with bending means in operative connection with which they can be acted upon with a bending moment.
  • a rolling apparatus of this kind is well known in the art. It is exemplified on the EP 0 256 408 A2 , the EP 0 256 410 A2 , the DE 38 07 628 C2 and the EP 0 340 504 B1 pointed. Rolling devices are known from these documents, in which two work rolls, which are located at a defined distance from one another, form the roll gap required for rolling and are supported on support rolls or intermediate rolls. The thus formed rolling device is thus equipped as a device with four or six rollers, wherein the individual rollers are positioned relative to each other in the vertical direction to produce the desired nip.
  • the work rolls are arranged axially displaceable, whereby it is possible to effect an influence of the strip profile in strip lines by a variable roll gap profile.
  • Vorstrassen wins the procedural possibility for axial displacement of the work rolls in importance, on the one hand for targeted Bandprofilbeeinlung, on the other hand to extend the roll travel through targeted wear distribution.
  • Another important embodiment of the rolling apparatus is that there are means for bending or balancing the work rolls. Through this, a bending moment can be introduced into the work rolls, which has procedural advantages, as can be seen from the aforementioned literature.
  • the work roll bending and displacement systems usually have stationary blocks in which the adjusting means required for bending and balancing or axial displacement are arranged. These offer the advantage of fixed pressure medium supply lines, which do not have to be separated during the work roll change.
  • the required plunger are either stationary in stationary blocks arranged, which leads disadvantageously to not negligible tilting moments in the axial displacement, or they are designed as with the axial displacement mitverschiebenden cartridges to the tilting moments or friction forces better to master.
  • the prior art rolling devices reach their limits in terms of process engineering when high roll uprights are required, as required, for example, in sheet metal or pre-lines.
  • the plunger of the bending or Balancierzylinder must be performed over much longer lengths and thus require a lot of space to ensure the lever ratios occurring at long distances, even with fully extended ram.
  • Short guide lengths of the plunger of the bending or Balancierzylinder be achieved again when the bending or Balancierzylinder with the system Häwalzen- / Stützwalzeneinbau the ride, so to speak "flying" between in downwardly projecting arms of the support or Eisenwalzeneinbau matterss and laterally cantilevered tabs of the work roll chock are arranged.
  • the plunger can be arranged either in the support or Eisenwalzeneinbau 1:1 or in the work roll chock; its arrangement in the support or intermediate roll chock offers the advantage that the Druckstoffzuschreibtechnischtechnischmaschinen need not be separated when changing work rolls.
  • Such a solution with "flying" arranged bending or Balanciersystem in combination with an axial displacement is from the DE 101 50 690 A1 known.
  • the axial displacement of the work roll is realized by a coaxially arranged on the work roll chock displacement cylinder.
  • the displacement cylinder and the work roll set thereby form a structural unit and are installed together in the rolling stand.
  • the invention is therefore based on the object to provide a rolling device with bending and Axialverschiebesystem for the work rolls, which on the one hand permits high roll uprights, on the other hand, is characterized by a small space requirement in relation to the stand window height. Furthermore, a good guidance of the plunger of the bending or Balancierstoff should be ensured, while at the same time care should be taken that the number the operating change parts in the case of a work roll change is as low as possible. In addition, the related requirements of the axial Häwalzenverriegelung and the position measurement of Axialverschiebeweges should be met.
  • This object is achieved in that the Axialverschiebesch between rolling stand and work roll locking are arranged or act and the bending means between the work roll chock and the other roll chock are arranged or act.
  • a first further development provides that the further roll chock, that is to say that of the support roll, has a guide in which the work roll chock is arranged so as to be displaceable relative to the further roll chock and fixable.
  • the axial displacement means are preferably fixedly arranged on the roll stand and have at least one linear guide on which the work roll chock is arranged to be displaceable relative to the axial displacement means in a direction transverse to the axial displacement direction, in particular displaceable in the vertical direction, and fixable.
  • this has two webs extending on both sides of the axis of the work roll, which webs can be locked with one axial displacement means each.
  • the linear guide is fixedly mounted on Axialverschiebesch and in a direction transverse to Axialverschiebichtung, in particular in the horizontal direction, displaceable, preferably plate-shaped, bar, which together with the linear guide for the end of the web forms a receiving slot.
  • the bolt can be in communication with actuating means, by means of which it is positionable in two layers, namely in a locking position and in an unlocking position.
  • the actuating means per Axialverschiebesch preferably consists of two hydraulic piston-cylinder systems, which are arranged parallel to each other and can move the bolt, the piston-cylinder systems on the side facing away from the work roll chock side of the bolt attack on this.
  • the Axialverschiebesch are equipped according to a development with means for preventing twisting, which prevent rotation of the axial ends of the Axialverschiebesch.
  • At least one bending means designed as a hydraulic linear actuator is arranged in a cantilever arm of the further roll chock and presses on a laterally projecting tab of the work roll chock. It can be arranged between the bending means and the laterally projecting tab of the work roll chock a sliding surface.
  • FIG. 1 the section of a rolling device 1 according to a first embodiment is shown in perspective.
  • Figures 2 to 5 show views and sections of this embodiment.
  • the rolling device 1 has work rolls 2, not shown in greater detail, which are mounted in work roll chocks 3, which are arranged in a rolling stand 4, which in turn is sketched only schematically.
  • the work roll chock 3 can be locked or unlocked relative to the rolling stand 4 by means of a work roll lock 5.
  • the work roll 2 is supported by a further roller 6 in the form of a support roller. This further roller 6 is mounted in further roll chocks 7, which are also fixed to the roll stand 4 or can be locked there.
  • the rolling device 1 may also comprise further rollers, namely intermediate rollers which are arranged between the work rolls 2 and the support rollers 6.
  • Axialverschiebesch 8 are provided, the structure will be explained later in detail.
  • Axialverschiebesch 8 is provided on both sides of the center of the work roll 2, these means are fixed with its one axial end 23 fixed to the rolling stand 4.
  • the work roll latch 5 is fixed at the other axial end 22 of the Axialverschiebeschs 8 .
  • the work roll chock 3 has two webs 12 and 13, which extend symmetrically from the axis of the work roll 2 from.
  • the webs 12, 13 are received at their end 15 and 16 in the locked state in a receiving slot 17 which extends in the vertical direction and offers the possibility that the work roll chock 3 and thus the work roll 2 vertically positioned at that level in the rolling stand 4 and can be set, which corresponds to the required roll gap.
  • the receiving slot 17 is limited on the one hand by a linear guide 11, which has the work roll latch 5, on the other hand limits him later described in detail latch 14th
  • Fig. 2 the front view of the rolling device 1 - viewed in Walzenachsplatz - can be seen.
  • the partially sectioned view can be seen that the further roll chock 7 for the support roller 6 in its lower region has a rectangular recess and thus forms a guide 10 for the insertable into the recess work roll chock 3.
  • the work roll 2 together with its work roll chock 3 can be positioned in the vertical direction relative to the further roll chock 7 or to the support roll 6.
  • bending means 9 are provided in the form of hydraulic linear actuators in a conventional manner, which act between the work roll chock 3 and the further roll chock 7.
  • the structure of the Axialverschiebeschs 8 is shown in Fig. 3, where the section A-A shown in FIG. 2 can be seen.
  • the Axialverschiebesch 8 is arranged with its one axial end 23 fixed to the rolling mill 4.
  • the work roll latch 5 is arranged.
  • the Axialverschiebesch 8 consists of a permanently connected to the roll stand 4 fixed block 27 which projects in a cylindrical shape and forms the bottom of a sliding cylinder.
  • On the outer diameter of this cylindrical projection a sliding sleeve 28 is slidably disposed.
  • the sliding sleeve 28 consists of a sliding tube with guide bushes and a cubically shaped lid 29. With this cover 29 of the displacement piston 30 is coaxially fixed.
  • the sliding tube of the sliding sleeve 28 has laterally projecting guide straps 31 which slide on a T-piece 32 connected to the fixed block 27 (see Fig. 1).
  • means 21 for preventing twisting of the axial displacement means 8 are provided, i. H. a torsion of one axial end 22 relative to the other axial end 23 of the Axialverschiebeschs 8 is excluded.
  • a displacement measuring system 33 is arranged between the base of the T-piece 32 and one of the guide plates 31. With this it is possible to measure the current axial position of the work rolls 2.
  • the work roll latch 5 On the outside of the lid 29 of the sliding sleeve 28, the work roll latch 5 is attached. This consists essentially of a base plate 34 (see Fig. 1 and 4), the latch 14 and actuating means 18 for the bolt 14. In the locked state, the work roll latch 5 is positively connected to the webs 12, 13 of the work roll chock 3.
  • the Axialverschiebesch 8, consisting of fixed block 27, sliding sleeve 28, Wegmesssystem 33 and work roll locking 5 is arranged at the inlet and outlet side substantially mirror-inverted on the roll stand 4.
  • the work roll latch 5 can be attached to the work roll set 2 by the base plate 34, the actuating means 18 for the bolt 14 and the bolt 14 itself are placed on the bearing cap of the work roll set 2 and corresponding elements for producing the positive connection to the sliding sleeve 28 of Axialverschiebesch 8 are located.
  • Fig. 5 can be seen how the bending means 9 are installed in the rolling device 1 in the form of hydraulically actuated linear actuators.
  • the bending means 9 are on the inlet side and outlet side effectively between work roll chock 3 and further roll chock 7 for the support roller 6.
  • the further roll chock 7 has a cantilevered arm 24 which carries the bending means 9. They rest on the work roll chock 3 on a cantilevered tab 25, which is integrally formed on the work roll chock 3.
  • Fig. 5 only one bending means 9 is shown; From Fig. 3 it can be seen that in the embodiment, two successively arranged bending means 9 are provided.
  • the plunger 35 (movable part) represents a piston coaxially disposed in a corresponding bore of a cylinder 36.
  • the fixed part of the bending means 9 consists essentially of a guide bushing with a corresponding bore, which is incorporated in the downwardly projecting arm 24, as well as a cover and various sealing and stripping elements.
  • the plunger 35 is supported on the laterally projecting tab 25 of the work roll chock 3.
  • the tab 25 slides over the contact surface of the plunger 35.
  • a sliding surface 26 is arranged in the contact region of the plunger 35 to the tab 25.
  • a cylinder 36 may be integrated into the laterally projecting lug 25 of the work roll chock 3. Then the plunger 35 is supported on the cantilevered arm 24 of the further roll chock 7.
  • FIGS. 6a, 6b to 14 show an alternative embodiment of the rolling device 1 according to the invention.
  • the reference numerals correspond to those of the first embodiment according to FIGS. 1 to 5.
  • the Axialverschiebesch 8 are also here above and below the rolling line and on the input and on the outlet side of the operating side stand 4. Solutions for work roll displacement devices above the roll line are problematic at high altitude. Solutions for work roll shifters under the rolling line can be built conventionally or as such for large rises.
  • the devices on the inlet and on the outlet side are substantially identical and symmetrical to each other, so that - as already in the case of the first embodiment - are described here only representative of the rolling line Axialverschiebesch 8 with high rising.
  • the configuration of the Axialverschiebeschs 8 also corresponds to that of the embodiment described above. Referring to FIGS. 8 to 12, it can be seen that the lid 29 is fixed to the displacement piston 30 connected is. He stands at least in the direction of the work roll chock 3 against the local outer contour of the sliding sleeve 28 before. Between the cover 29 and arranged on the sliding sleeve 28 plate 37 of the bolt 14 is installed, which surrounds the sliding sleeve 28 and can be moved to close the locking in approximately horizontal direction transverse to the axis of the sliding sleeve 28. Between the plate 37 and the latch 14 is formed by the closing of the bolt 14 of the vertically extending receiving slot 17, in which the laterally projecting web 12, 13 of the work roll chock 3 is guided. For this purpose, a recess is incorporated in the plate 37 or between plate 37 and bolt 14, a spacer is inserted with a comparable recess.
  • the vertically extending receiving slot 17 receives the axial displacement forces that must be passed through the laterally projecting webs 12, 13 of the work roll chock 3, while allowing large relative movements in the vertical direction. This allows a large roll rise as a result.
  • the contact surfaces of the webs 12, 13 on the plate 37 and the bolt 14 thereby form two abutments for the webs 12, 13 of the work roll chock 3.
  • the vertically extending receiving slot 17 is opened to the work roll removal by the bolt 14 is withdrawn. Then the work roll set can be pulled out to the operating side.
  • the plate 37 on the sliding sleeve 28 has two main functions. On the one hand, it serves as one of the two abutments for the webs 12, 13. On the other hand, it is part of means 21 for preventing a rotation of the Axialverschiebesch. 8
  • a component which is mounted outside the central axis, the sliding sleeve 28 fixed to the stand. This sticks out in one Opening of the plate 37 on the sliding sleeve 28 into it, or a component attached to the plate 37 of the sliding sleeve 28 protrudes into a stationary opening.
  • the anti-rotation device must have a guide of sufficient length, so that a rotation between the two axial ends 22 and 23 of the Axialverschiebeschs 8 is prevented for the entire maximum displacement.
  • the sliding sleeve 28 and the displacement piston 30 may be formed so that they do not slide on each other with cylindrical surfaces, but with such surfaces that prevent rotation to each other.
  • the fulfillment of the two main functions of the plate 37 on the sliding sleeve 28, namely to be both abutment and part of the rotation, can be achieved by two separate, worked on the sliding sleeve 28 or welded plates.
  • the combination of the two functions by means of the plate is easy to manufacture and therefore advantageous.
  • the detailed embodiment of the work roll latch 5 by means of the bolt 14 is shown in Figures 10 and 12.
  • the latch 14 may have an O- or U-shaped recess (in Fig. 10, the recess is O-shaped).
  • the latch 14 is not arranged in front of the head 29, but it surrounds the sliding sleeve 28.
  • the recess in the bolt 14 is so large that the bolt for mounting in training in the O-shape axially or when executed in U-shape axially or radially can be pushed onto the sliding sleeve 28.
  • the U-shape is as a closed mold, the stiffer design of the bolt 14.
  • the U-shape has the advantage that the cover 29 can be permanently connected to the sliding sleeve 28 or that the cover 29 and the sliding sleeve 28 may consist of one piece ,
  • the latch 14 When executed in U-shape, the latch 14 is open on the side of the sliding sleeve 28 which is opposite to the work roll chock 3. Because the latch 14 surrounds the sliding sleeve 28, the web 12, 13 of the Work roll chock 3 - measured from the middle of the work roll bearings - shorter than if the bar 14 were located in front of the head 29. Thus, the lever arm between the work roll bearing and the guide, which is formed by the two abutment bar 14 and plate 37 decreases. A smaller lever arm has the consequence that the frictional forces in the guide exercise only relatively small additional moments on the work roll bearings. The work roll bearing thus has a longer life.
  • the closing and opening of the receiving slot 17 for the laterally projecting webs 12, 13 of the work roll chock 3 is accomplished by a horizontal or approximately horizontal movement of the bolt 14, the locking stroke. Therefore, the recess in the bolt 14 in the direction of movement (horizontal) at least by the locking stroke is greater than is required for assembly.
  • the movement of the bolt 14 is effected by actuating means 18.
  • This is z. B. one or more actuators in the form of piston-cylinder systems 19, 20 (hydraulic cylinder with continuous piston rods).
  • the piston-cylinder systems 19, 20 expediently put on the side facing away from the work roll chock 3 of the bolt 14. It is particularly space-saving, if two piston-cylinder systems 19, 20 find space at the top and bottom in recesses of the bolt 14 and on the plate 37 or on the lid 29 are attached.
  • FIG. 10 Fig. 12 shows a piston-cylinder system 19, 20 in detail.
  • the bolt 14 has three recesses in the embodiment of FIG. 10, a large for the sliding sleeve 28, two smaller for the piston-cylinder systems 19, 20 and another to avoid collision with the means 21 for preventing the rotation of the Axialverschiebeschs 8.
  • the latch 14 is held by the piston-cylinder systems 19, 20 in the open or closed position. But it must also be secured against rotation against an axis parallel or identical to the central axis of the sliding sleeve 28.
  • strips 38, 39 are mounted, which prevent such rotation.
  • the strips 38, 39 can also form a common component with the plate 37 or with the plate 37 and the displacement sleeve 28.
  • An alternative embodiment of the rotation is obtained when 29 horizontal grooves are formed in the plate 37 or in the lid, in which raised strips of the bolt 14 are guided. Furthermore, it is possible to mold the grooves in the bar 14 and to attach the raised strips on the plate 37 or on the lid 29. Variants in which the rotation against the plate 37 are mounted, have the advantage that the lid 29 is then not additionally claimed to twist.
  • the cover 29 of the sliding sleeve 28 is shaped so that two functions can be fulfilled: First, the sliding piston 30 is coaxially fixedly connected to the cover 29 (see Fig. 8), so that the piston above the cover the sliding sleeve 28 including attachments and thus also the vertically extending receiving slot 17 for the work roll chock 3 can move axially.
  • the lid 29 forms an abutment for the bolt 14, especially with its part projecting towards the work roll chock 3.
  • the bolt 14 can be supported there and also above and below the sliding sleeve 28 on the cover 29 or surround the sliding sleeve 28.
  • the lid 29 may have a recess to allow elements of the rotation to pass and thus to prevent a collision with them. To the To make lid 29 shorter, it is also possible to install an intermediate piece between the lid and latch.
  • Either in the lid 29 or in this intermediate piece can also be a fuse against rotation of the same on the sliding sleeve 28 are provided.
  • One possibility for this is to provide on the sliding sleeve 28 one or more flat surfaces which do not point in the direction of the axis of the sliding piston 30 and to provide corresponding counter surfaces on the cover 29 or in the above intermediate piece.
  • the lid 29 must then be secured against rotation relative to the sliding sleeve 28 in any case, when the bolt 14 is secured against rotation to the cover 29.
  • the measurement of the Axialverschiebewegs is made possible by a out of or within the Axialverschiebesch 8 unit.
  • the arrangement of the transmitter within the printing system is avoided as possible due to risk inclination during maintenance.
  • the displacement measuring system 33 can be formed as an external unit or as an internal unit. In the case of an external unit, protection against harmful environmental influences is required, which can be achieved by a sealed, hydraulic cylinder-like system.
  • a type of piston fixedly mounted on the stator slides through a cylinder tube fixed to the moving parts of the axial displacement. Coaxially with the cylinder tube, the transmitter moves and generates the corresponding path signal. With appropriate sealing and stripping elements a sufficient protection of the system is achieved.
  • the position sensor is - seen from the end face of the moving parts - inserted into the sliding sleeve.
  • the required encapsulation is produced by the displacement system itself.
  • a suitably sealed housing protects the electronic part of the position sensor.
  • a position transmitter 40 for controlling the displacement stroke of the displacement sleeve 28 is arranged in the axial displacement means 8.
  • the position sensor 40 is mounted on the lid 29, the position sensor rod 41 is passed through a bore in the lid 29 and immersed in a bore in an inner lid 42 a.
  • the inner lid 42 is part of the rolling stand 4 fixed part of the Axialverschiebeschs 8, so that the measurement of the relative displacement of the lid 29 to the roll stand 4 is possible.
  • the bending means 9 are in downwardly projecting arms 24 of the further roll chock 7 of the upper support roll set.
  • the movable plunger 35 is essentially a piston, which is supported on the laterally projecting tab 25 of the work roll chock 3.
  • the design of the bending means 9 thus corresponds substantially to that shown in Fig. 5.
  • the plunger 35 may be housed in the laterally projecting tabs 25 of the work roll chock 3.
  • the plunger 35 would be supported on the downwardly projecting arms 24 of the further roll chock 7. In this case, the work roll bearing would only be loaded centrally.
  • the lower bending means 9 may be in fixed blocks on the stand. Alternatively, they can also in upwardly projecting arms of the further roll chock of the lower support or intermediate roll set or be housed in laterally projecting tabs of the work roll chock.
  • a "flying" arrangement of the bending means 9 can thus be achieved, whereby the tilting moments which occur in the case of the axial displacement of the work rolls can be optimally accommodated with the proposed structural design.
  • the design of the rolling device excludes collisions of the various components with each other, even when large roll outruns are driven. Nevertheless, no large space is needed in the rolling stand.

Claims (11)

  1. Dispositif de laminage (1) comprenant
    deux cylindres de travail (2), qui sont à chaque fois logés au moyen d'empoises (3) pour cylindres de travail dans une cage de laminage (4), les empoises (3) pour cylindres de travail pouvant être verrouillées et déverrouillées dans une cage de laminage (4) via au moins un dispositif de verrouillage (5) des cylindres de travail,
    au moins deux autres cylindres (6), en particulier deux cylindres d'appui, qui sont à chaque fois logés au moyen d'empoises (7) pour les autres cylindres dans la cage de laminage (4),
    au moins un des cylindres de travail (2) ainsi qu'au moins un des autres cylindres (6) étant réglables dans la cage de laminage (4) par rapport à l'autre cylindre de travail (2) ou, selon le cas, à l'autre cylindre (6), en particulier dans le sens vertical, pour le réglage d'une fente de laminage souhaitée,
    les cylindres de travail (2) étant pourvus de moyens de déplacement axiaux (8) pour le déplacement axial, grâce auxquels les cylindres de travail (2) peuvent être amenés et maintenus dans une position axiale souhaitée par rapport à la cage de laminage (4), et
    les cylindres de travail (2) interagissant activement avec des moyens de flexion (9) grâce auxquels ils peuvent être soumis à un moment de flexion, caractérisé,
    en ce que les moyens de déplacement axial (8) sont disposés ou agissent entre la cage de laminage (4) et le dispositif de verrouillage (5) des cylindres de travail et les moyens de flexion (9) sont disposés ou, selon le cas, agissent entre l'empoise (3) pour cylindre de travail et l'empoise (7) pour les autres cylindres.
  2. Dispositif de laminage selon la revendication 1, caractérisé,
    en ce que l'empoise (7) pour les autres cylindres présente un dispositif de guidage (10), dans lequel l'empoise (3) pour cylindres de travail est disposée de manière à pouvoir être déplacée par rapport à l'autre l'empoise (7) pour les autres cylindres et fixée.
  3. Dispositif de laminage selon la revendication 1 ou 2, caractérisé,
    en ce que les moyens de déplacement axiaux (8) sont disposés de manière fixe sur la cage de laminage (4) et présentent au moins un dispositif de guidage linéaire (11), sur lequel l'empoise (3) pour cylindres de travail est disposée de manière à pouvoir être déplacée par rapport aux moyens de déplacement axiaux (8) dans un sens transversal par rapport au sens de déplacement axial, en particulier dans le sens vertical, et être fixée.
  4. Dispositif de laminage selon l'une quelconque des revendications 1 à 3, caractérisé
    en ce que l'empoise (3) pour cylindres de travail présente deux âmes (12, 13) s'étendant des deux côtés des axes des cylindres de travail (2), qui peuvent être verrouillées à chaque fois à l'aide d'un moyen de déplacement axial (8).
  5. Dispositif de laminage selon la revendication 3 et 4, caractérisé,
    en ce que le dispositif de guidage (11) est disposé de manière fixe sur les moyens de déplacement axial (8) et présente un verrou (14) pouvant être déplacé dans un sens transversal par rapport au sens de déplacement axial, en particulier dans le sens horizontal, de préférence réalisé sous forme de plaque, qui forme, avec le dispositif de guidage linéaire (11) pour l'extrémité (15, 16) de l'âme (12, 13) une fente de réception (17).
  6. Dispositif de laminage selon la revendication 5, caractérisé,
    en ce que le verrou (14) s'agrippe autour d'un manchon de déplacement (28).
  7. Dispositif de laminage selon la revendication 5 ou 6, caractérisé,
    caractérisé en ce que le verrou (14) est relié à des moyens d'action (18) au moyen desquels il peut être positionné dans deux positions, notamment une position de verrouillage et une position de déverrouillage.
  8. Dispositif de laminage selon la revendication 7, caractérisé,
    en ce que le moyen d'action (18), par moyen de déplacement axial (8), est formé par deux systèmes à piston-cylindre hydrauliques (19, 20), qui sont disposés parallèlement l'un à l'autre et qui peuvent déplacer le verrou (14), les systèmes à piston-cylindre (19, 20) s'agrippant sur le côté du verrou (14) opposé à l'empoise (3) pour cylindres de travail.
  9. Dispositif de laminage selon l'une quelconque des revendications 1 à 8, caractérisé
    en ce que les moyens de déplacement axial (8) sont équipés de moyens (21) pour empêcher une rotation, qui empêchent une rotation des extrémités axiales (22, 23) des moyens de déplacement axial (8).
  10. Dispositif de laminage selon l'une quelconque des revendications 1 à 9, caractérisé
    en ce qu'au moins un moyen de flexion (9) réalisé sous forme d'un actionneur linéaire hydraulique est disposé dans un bras (24) en saillie de l'empoise (7) pour les autres cylindres et pousse sur un élément de raccord (25) latéralement en saillie de l'empoise (3) pour cylindres de travail.
  11. Dispositif de laminage selon la revendication 10, caractérisé,
    en ce qu'on a disposé, entre le moyen de flexion (9) et l'élément de raccord (25) latéralement en saillie de l'empoise (3) pour cylindres de travail une surface de glissement (26).
EP04763370A 2003-07-30 2004-07-21 Dispositif de laminage Active EP1648626B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10334727A DE10334727A1 (de) 2003-07-30 2003-07-30 Walzvorrichtung
PCT/EP2004/008129 WO2005011884A1 (fr) 2003-07-30 2004-07-21 Dispositif de laminage

Publications (2)

Publication Number Publication Date
EP1648626A1 EP1648626A1 (fr) 2006-04-26
EP1648626B1 true EP1648626B1 (fr) 2007-11-14

Family

ID=34088942

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04763370A Active EP1648626B1 (fr) 2003-07-30 2004-07-21 Dispositif de laminage

Country Status (17)

Country Link
US (1) US7299673B2 (fr)
EP (1) EP1648626B1 (fr)
JP (1) JP4564008B2 (fr)
KR (1) KR101109451B1 (fr)
CN (1) CN100506413C (fr)
AT (1) ATE378118T1 (fr)
AU (1) AU2004261384B2 (fr)
BR (1) BRPI0413108A (fr)
CA (1) CA2533693C (fr)
DE (2) DE10334727A1 (fr)
ES (1) ES2293315T3 (fr)
MX (1) MXPA06001150A (fr)
RU (1) RU2346771C2 (fr)
TW (1) TWI314880B (fr)
UA (1) UA83056C2 (fr)
WO (1) WO2005011884A1 (fr)
ZA (1) ZA200509783B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018202404A1 (fr) 2017-05-03 2018-11-08 Sms Group Gmbh Cage de laminoir pour le laminage d'un produit métallique
DE102019200005A1 (de) 2019-01-02 2020-07-02 Sms Group Gmbh Walzvorrichtung

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100797368B1 (ko) * 2001-11-12 2008-01-22 주식회사 포스코 조질압연기의 롤 간격조정장치
DE102007042896A1 (de) * 2007-03-15 2008-09-18 Sms Demag Ag Walzvorrichtung
DE102008027494A1 (de) * 2007-06-14 2008-12-18 Sms Demag Ag Mehrteilige Walze
DE102007058729A1 (de) * 2007-08-07 2009-02-19 Sms Demag Ag Walzvorrichtung mit Verstellvorrichtung
DE102008035702A1 (de) * 2008-07-30 2010-02-04 Sms Siemag Aktiengesellschaft Walzvorrichtung
ITMI20101502A1 (it) * 2010-08-05 2012-02-06 Danieli Off Mecc Sistema integrato di bending e shifting sotto carico per gabbie ad elevata apertura tra i rulli di lavoro
CN105107846B (zh) * 2015-09-24 2017-05-17 新余钢铁集团有限公司 一种工作辊轴向锁紧结构

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FR2093412A5 (fr) * 1970-06-12 1972-01-28 Spidem Ste Nle
US4453393A (en) * 1981-08-13 1984-06-12 Mitsubishi Jukogyo Kabushiki Kaisha Four high mill of the paired-roll-crossing type
BR8300010A (pt) * 1982-01-06 1983-08-30 Hitachi Ltd Laminador
JPS59130607A (ja) * 1983-01-14 1984-07-27 Hitachi Ltd 圧延機
FR2547216A1 (fr) * 1983-06-10 1984-12-14 Sacilor Dispositif perfectionne de manoeuvre et de reglage axial de cylindres horizontaux de cage de laminoir a profiles
JPS617007A (ja) * 1984-06-20 1986-01-13 Ishikawajima Harima Heavy Ind Co Ltd 圧延機
JPH0749124B2 (ja) * 1986-03-20 1995-05-31 株式会社日立製作所 ロールシフト式圧延機
DE3638330A1 (de) * 1986-11-10 1988-05-19 Schloemann Siemag Ag Walzgeruest mit einer vorrichtung zum axialen verschieben von anstellbaren walzen
DE3843387A1 (de) * 1988-12-23 1990-07-05 Schloemann Siemag Ag Vorrichtung zum walzenwechsel insbesondere der horizontal verschieblichen arbeitswalzen in einem walzgeruest
US5752404A (en) * 1996-12-17 1998-05-19 Tippins Incorporated Roll shifting system for rolling mills
DE10150690A1 (de) * 2001-10-17 2003-04-30 Sms Demag Ag Walzvorrichtung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018202404A1 (fr) 2017-05-03 2018-11-08 Sms Group Gmbh Cage de laminoir pour le laminage d'un produit métallique
CN110621421A (zh) * 2017-05-03 2019-12-27 Sms集团有限公司 用于轧制金属物料的轧机机架
CN110621421B (zh) * 2017-05-03 2021-07-09 Sms集团有限公司 用于轧制金属物料的轧机机架
DE102019200005A1 (de) 2019-01-02 2020-07-02 Sms Group Gmbh Walzvorrichtung
WO2020141033A1 (fr) 2019-01-02 2020-07-09 Sms Group Gmbh Dispositif de laminage

Also Published As

Publication number Publication date
TW200512051A (en) 2005-04-01
RU2006106200A (ru) 2006-07-10
TWI314880B (en) 2009-09-21
CA2533693A1 (fr) 2005-02-10
CN100506413C (zh) 2009-07-01
JP4564008B2 (ja) 2010-10-20
JP2007500079A (ja) 2007-01-11
EP1648626A1 (fr) 2006-04-26
AU2004261384A1 (en) 2005-02-10
US7299673B2 (en) 2007-11-27
KR20060054205A (ko) 2006-05-22
KR101109451B1 (ko) 2012-01-31
UA83056C2 (en) 2008-06-10
CN1832817A (zh) 2006-09-13
BRPI0413108A (pt) 2006-10-03
US20070107482A1 (en) 2007-05-17
MXPA06001150A (es) 2006-04-24
AU2004261384B2 (en) 2010-02-25
ZA200509783B (en) 2006-09-27
WO2005011884A1 (fr) 2005-02-10
DE10334727A1 (de) 2005-02-24
ES2293315T3 (es) 2008-03-16
ATE378118T1 (de) 2007-11-15
DE502004005516D1 (de) 2007-12-27
CA2533693C (fr) 2010-11-09
RU2346771C2 (ru) 2009-02-20

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