EP1648625B1 - Walzvorrichtung - Google Patents

Walzvorrichtung Download PDF

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Publication number
EP1648625B1
EP1648625B1 EP04741182A EP04741182A EP1648625B1 EP 1648625 B1 EP1648625 B1 EP 1648625B1 EP 04741182 A EP04741182 A EP 04741182A EP 04741182 A EP04741182 A EP 04741182A EP 1648625 B1 EP1648625 B1 EP 1648625B1
Authority
EP
European Patent Office
Prior art keywords
roll
working
transmission element
working roll
bending
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.)
Active
Application number
EP04741182A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1648625A1 (de
Inventor
Bernd Zieser
Achim Klein
Florian Lindner
Christian Diehl
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
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 Demag AG filed Critical SMS Demag AG
Publication of EP1648625A1 publication Critical patent/EP1648625A1/de
Application granted granted Critical
Publication of EP1648625B1 publication Critical patent/EP1648625B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • 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
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • 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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/203—Balancing rolls

Definitions

  • the invention relates to a rolling device with at least two work rolls, which are each mounted by means of a work roll chock in a rolling stand, wherein at least one of the work rolls in the rolling stand for setting a desired roll gap relative to the other work roll, in particular in the vertical direction, is adjustable, wherein at least one Working roll is in operative connection with bending means, with which it can be acted upon by a bending moment, and wherein the work roll chock for receiving the force generated by the bending means from the axis of the work roll seen from side cantilevered arms.
  • a rolling apparatus of this kind is well known in the art. It is for example 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 can thus be 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 roll gap.
  • the work rolls are arranged axially displaceable, whereby it is possible to achieve 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 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 rams.
  • the plunger can be arranged either in the support or insectsbau published in the work roll chock; its arrangement in the support or intermediate roll chock offers the advantage that the DruckstoffzuSciencetechnischen need not be separated when changing work rolls.
  • Such a solution with "fly” arranged bending or Balanciersystem in combination with an axial displacement is from the DE 101 50 690 A1 known.
  • a coaxially arranged on the work roll chock shift cylinder is provided for the axial displacement of the work roll.
  • 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 an object of the invention to provide a rolling device of the type mentioned, which does not have the disadvantages mentioned.
  • a rolling device with bending and axial displacement system for the work rolls is to be created, which permits high roll runs.
  • This object is achieved in that between a compressive force generating element of the bending means, in particular a piston, and the cantilever arm of the work roll chock a relative to the rolling stand, in particular in the vertical direction, displaceable pressure transmitting element is arranged, wherein the pressure force generating element of the bending means and the projecting arm of the work roll chock are positioned so that the center axis of the pressure force generating element intersects the cantilever arm, wherein the bending means are arranged in a fixedly arranged on the rolling mill block and the pressure transmitting element by means of a guide, in particular by means of a vertical guide, is mounted on the block and wherein the pressure transmission element is formed in a horizontal section U-shaped and surrounds the block from three sides at least partially and the pressure transmission element in a perpendicular to the axis of the work roll vertical section L-shaped is formed and at least partially surrounds the block on its upper side.
  • a further development provides that a sliding surface is arranged between the pressure force generating element of the bending means and the pressure transmission element and / or between the pressure transmission element and the cantilever arm of the work roll chock.
  • the guide is further improved by varying the roller distance, characterized in that the pressure-transmitting element is mounted on the rolling stand by means of a guide, in particular with a vertical guide. It has also been proven that holding means are arranged between the block and the pressure-transmitting element, which hold the pressure-transmitting element immovably in the direction of the work roll on the block.
  • the work rolls are usually provided with Axialverschiebeschn for axial displacement, with which the work rolls can be brought relative to the rolling stand in a desired axial position and held there.
  • a particularly good mode of operation is achieved when the extension of the cantilevered arm of the work roll chock in the direction of the axis of the work roll is large in relation to the dimension measured in the direction of the axis the pressure transmitting element at its part connected to the cantilever arm, preferably at least twice as large.
  • the extension of the cantilever arm of the work roll chock in the direction of the axis of the work roll is small in relation to the axis measured in the direction of the extension of the pressure transmitting member at its associated with the cantilever arm part, preferably at most half as large ,
  • the work roll bending device may be equipped with fixed blocks in which although long bending or Balancierzylinder can work, but are relieved of the overturning moments by the said additional measures.
  • the proposed rolling device is suitable for high roller rising and still executable in a compact design.
  • a rolling device 1 is shown, are arranged in the two cooperating work rolls 2 and 3, which are each mounted in a work roll chock 4 and 5, in a rolling mill 6.
  • the upper work roll chock 4 is made adjustable in the vertical direction; It can therefore be moved in the vertical direction relative to the rolling stand 6.
  • the work rolls 2, 3 are supported respectively on support rollers 21 and 22, which are each mounted in a support roll chock 23 and 24 respectively.
  • the illustrated rolling device 1 thus has a total of four rollers. It should be noted that it may also comprise further rolls, namely intermediate rolls, which are arranged between the work rolls 2, 3 and the support rolls 21, 22.
  • bending means 7 are provided to initiate a bending moment in the work rolls 2, 3 bending means 7 are provided. As can be seen in particular from FIG. 2, the bending means 7 are arranged in both axial end regions of the work rolls 2, 3 and, moreover, both on the feed side and on the discharge side on the rolling stand 6. A total of four bending means 7 are provided.
  • the bending means 7 have a block 16 which is fixedly arranged on the roll stand 6, as can be seen in particular in Fig. 1.
  • the block 16 has cylindrical bores in which compressive force generating elements 11, d. H. Piston, are arranged, which can be acted upon by hydraulic pressure.
  • the pistons 11 have a center axis 13 which extends in the vertical direction.
  • each work roll chock 4, 5 has cantilevered arms 9 and 10, which are arranged laterally of the axis 8 of the work roll 2, 3.
  • the projecting arms 9, 10 extend - from the work roll 2, 3 away - laterally outwards and overlap the piston 11 beyond the center axis 13 out.
  • a pressure transmission element 12 arranged between the bending means 7 and in particular the piston 11 and the cantilevered arms 9, 10 of the work roll chocks 4, 5 is a pressure transmission element 12 arranged.
  • This is equipped with two sliding surfaces 14 and 15, which ensure good sliding conditions between the piston 11 and the pressure transmission element 12 on the one hand and between the pressure transmission element 12 and cantilever arm 9, 10.
  • the piston 11 and cantilevered arm 9, 10 are positioned so that the center axis 13 of the piston 11 intersects the cantilevered arm 9, 10.
  • the pressure transmission element 12 is arranged via a vertical guide 17 on the block 16 and can thus move in the vertical direction relative to the block 16 and thus to the rolling stand 6.
  • a further vertical guide 18 is provided which guides the pressure transmission element 12 in the upper region of the rolling stand 6, namely a crosshead 28 of the pressure transmission element 12th
  • the pressure transmission element 12 is designed as a "bending hood". That is, it is U-shaped in a horizontal section and at least partially surrounds the block 16 from three sides, as best seen in FIG. From Fig. 1 it is apparent that the pressure transmitting element 12 is formed in a perpendicular to the axis 8 of the work roll 2, 3 vertical section L-shaped and partially surrounds the block 16 on its upper side. With the two legs 26 and 27 (see Fig. 2), the pressure transmitting element 12 is arranged against axial displacement forces vertically sliding but tilt-proof on the sides of the block 16. In addition, it is supported on the working roll 2 facing end face of the block 16 and thus can accommodate large horizontal forces that may be directed in the inlet against and in the outlet with the rolling direction.
  • the pressure transmitting member 12 is provided in or against the rolling direction with further sliding surfaces, which are located on the legs 26 and 27, on which a support to the working roll 2 facing side surfaces of the roll stand 6 can be done. So that the pressure transmission element 12 remains in position with the work roll 2, 3 removed and does not fall off the rolling stand 6 or the block 16, holding means 19 are provided (see FIG. prevent the pressure transmitting element 12 is displaceable in the direction R to the roll axis 8.
  • Fig. 3 it can be seen that in addition to the upward pressure force generating elements 11 (piston) of the bending means 7, which act on the upper work roll chock 4, further force-generating elements 25 are provided which generate a downward force and the lower work roll chock 5 act on a bending force.
  • FIGS. 4 and 5 A modified rolling device 1 is shown in FIGS. 4 and 5. From Fig. 5 shows that again both work rolls 2, 3 are each provided with Axialverschiebeschn 20.
  • a "bending hood” is also provided there only.
  • the lower pressure force generating elements 25 without “bending hood” pressure transmission element 12
  • a pressure-transmitting element 12 between piston 25 and work roll chock 5 can also be provided here.
  • the proposed "bending hood" in the form of the pressure transmission element 12 ensures good guidance of the work roll chocks 4, 5, even at high and very high roll emergence. At the same time the frictional forces are absorbed, otherwise in the axial displacement of the work rolls the support roll chocks 23, 24 skewed and would cause additional tilting moments.
  • the contact surface of the cantilever arm 9, 10 may be formed short in Axialverschiebeiques and are centric to the work roll bearing 29, while the mating surface of the crosshead 28 is formed long.
  • the work roll bearing 29 is advantageously loaded centric even after the axial displacement.
  • the contact surface associated with the crosshead 28 may be made short in the direction of axial displacement and thus only centric to the work roll bearing 29 in the unshifted position.
  • the counter surface under the cantilever arm 9, 10 may be formed long. In the axial displacement of the pressure force generating elements 11 of the bending means 7 are now loaded evenly in an advantageous manner as before, but now the work roll bearing 29 is no longer centrally loaded.
  • the blocks 16 of the upper bending means 7 are enclosed by the pressure transmission elements 12.
  • the nip is set substantially over the upper work roll 2.
  • the upper work roll 2 is pressed over the upper bending means 7 and the pressure transmission element 12 against the preset by means of mechanical adjustment upper support roller 21.
  • the blocks 16 can also be enclosed in the region of the lower bending means 7 of pressure transmission elements 12 shown in FIGS. 1 and 3.
  • a so-called negative work roll bending can be realized via additional piston-cylinder systems 30, 31 to increase the setting range for the profile influencing (see FIG.
  • the described bending system can be combined with different variants of work roll displacement systems.
  • This can z. B. Axialverschiebesysteme be with two separate Axialschiebeticianen per work roll set, z. B. with a special, suitable for high roller catch locking and translational locking movement or with a conventional locking and rotary locking movement.
  • FIGS. 6 and 7 the axial displacement means 20 can initially be seen in two different perspectives.
  • the side view of the Axialverschiebeschs 20 is shown in Fig. 8.
  • the axial displacement means 20 are located above and below the rolling line and on the infeed and outfeed sides of the rolling mill 6. Solutions for work roll shifting devices above the mill line are problematic at high rises. Solutions for work roll shifters under the rolling line can be conventionally built or like those for large rises become.
  • the devices on the inlet and on the outlet side are substantially identical and symmetrical to each other, so that here representatively only lying above the rolling line Axialverschiebesch 20 are described with high rising.
  • an axial displacement means 20 is provided on either side of the center of the work roll 2, 3, said means being firmly fixed to the rolling stand 6 by one axial end 32 thereof.
  • a work roll lock In the region of the section F-F according to FIG. 8 of the axial displacement means 20, there is a work roll lock, with which the work roll chock 4, 5 can be releasably fixed.
  • the work roll chock 4, 5 has two webs 33, 34 (see Fig. 2), which extend symmetrically from the axis 8 of the work roll 2, 3 from.
  • the webs 33, 34 are received at their end in the locked state in a receiving slot in Axialverschiebesch 20, which extends in the vertical direction and offers the possibility that the work roll chock 4, 5 and thus the work roll 2, 3 vertically in the same height in the rolling stand 6 can be positioned and set, which corresponds to the required roll gap.
  • the receiving slot is on the one hand by a linear guide 54, s. Fig. 15, limited, which has the work roll lock, on the other hand limits him later described in detail latch 35th
  • the Axialverschiebesch 20 consists of a fixedly connected to the roll stand 6 flange 36 which protrudes and forms the bottom of a guide tube 37. On the outer diameter of the guide tube 37, a sliding head 38 is slidably disposed.
  • the sliding head 38 consists of a sliding tube 39 with guide bushes and a cover 40. With this cover 40, a sliding piston 41 is fixedly connected coaxially.
  • a component can be provided which is mounted outside the central axis on the displacement tube 39.
  • the anti-rotation device must have a guide of sufficient length, so that a rotation of the Axialverschiebeschs 20 is prevented for the entire maximum displacement.
  • FIG. 9 a displacement measuring system sketched in FIG. 9 is provided, with which it is possible to measure the current axial position of the work rolls 2, 3.
  • the work roll locking is attached on the Axialverschiebesch 20, the work roll locking is attached.
  • An essential part of this lock is a coupling 42 with the latch 35; the latter is shown in Fig. 11 cut.
  • the latch 35 is connected to actuating means 43, 44.
  • the work roll lock is positively connected to the webs 33, 34 of the work roll chock 4, 5.
  • the Axialverschiebesch 20 are inlet and outlet side arranged substantially mirror-inverted on the roll stand 6.
  • the coupling 42 is designed so that it forms a chamber together with the displacement tube 39, in which the bolt 35 is securely guided. Furthermore, it relies so with their flanks on Verschieberohr 39 that vertical forces and torques are intercepted over the axis of the Verschieberohrs 39 to the flanks. When the latch 35 presses on one flank of the coupling 42, the other flank is supported on a further surface of the displacement tube 39 and vice versa.
  • the bolt 35 is arranged on the coupling 42, which surrounds the Verschieberohr 39 and 39 can be moved to close the locking in approximately horizontal direction transverse to the axis of the Verschieberohrs 39.
  • a vertically extending receiving slot in which the laterally projecting webs 33, 34 of the work roll chock 4, 5 are guided.
  • the vertically extending receiving slot receives the axial displacement forces that must be passed through the laterally projecting webs 33, 34 of the work roll chock 4, 5, while allowing large relative movements in the vertical direction. This creates a large roll rise as a result.
  • the vertically extending receiving slot is opened for work roll removal by the latch 35 is retracted. Then the work roll set can be pulled out to the operating side.
  • the detailed embodiment of the work roll locking by means of the bolt 35 can be seen from Figures 11 to 14.
  • the latch 35 may have an O- or U-shaped recess (in FIG. 11 the recess is O-shaped).
  • the latch 35 is not arranged in front of the top of the lid 40, but it surrounds the displacement tube 39.
  • the recess in the latch 35 is so large that the bolt for mounting in training in O-shape axially or when executed in U-shape axially or radially can be pushed onto the Verschieberohr 39.
  • the O-shape is a closed form, the stiffer version of the bolt 35th
  • the latch 35 When executed in U-shape, the latch 35 is open on the side of the displacement tube 39 which is opposite to the work roll chock 4, 5. Because the latch 35 engages the shifting tube 39, the work roll bending arm (measured from the middle work roll bearing 29) may be shorter than if the latch 35 were located in front of the head 40. Thus, advantageously, the lever arm between the work roll bearing 29 and the vertical guide on the displacement head 38 is reduced. A smaller lever arm has the result that the frictional forces in the guide exert only comparatively small additional moments on the work roll bearing 29, which increases the service life of the bearing.
  • Another advantage of the short design is that the displacement system in front of the rolling mill requires less space for the withdrawn and the newly set sets of rolls, especially when a transverse displacement of the sets of work rolls is provided during the roll change.
  • the closing and opening of the receiving slot for the laterally projecting webs 33, 34 of the work roll chock 4, 5 is effected by a horizontal or approximately horizontal movement of the bolt 35 with a corresponding locking stroke. Therefore, the recess in the bolt 35 in the direction of movement (horizontal) at least by the locking stroke is greater than is required for assembly.
  • the movement of the bolt 35 is effected by the actuating means 43, 44.
  • actuating means 43, 44 These are, for. B. one or more actuators in the form of piston-cylinder systems (hydraulic cylinder with continuous piston rods) - s. for this purpose the section GG according to FIG. 11 shown in FIG. 12.
  • the piston-cylinder systems are expediently arranged on the side of the bolt 35 facing away from the work roll chock 4, 5. Particularly space-saving, it is when two piston-cylinder systems 43, 44 above and below find in recesses of the bolt 35 place. This embodiment is shown in FIG. 11; Fig. 12 shows a piston-cylinder system 43, 44 in detail.
  • the latch 35 has in the embodiment of FIG. 11 three recesses, a large one for the Verschieberohr 39, two smaller for the piston-cylinder systems 43, 44 and another to avoid collision with the means for preventing the rotation of the Axialverschiebeschs 20 ,
  • the recesses for the piston-cylinder systems 43, 44 are closed in an advantageous manner with brackets 45 in the bolt 35, so that the piston-cylinder systems 43, 44 can be expanded to the side without disassembling the clutch 42 or other parts to have to.
  • the latch 35 is held by the piston-cylinder systems 43, 44 in the open or closed position. But it must also be secured in a suitable manner against rotation against an axis parallel or identical to the central axis of the displacement tube 39. This is accomplished by the flanks 46 and 47 of the coupling 42, which in turn are supported on the displacement tube 39.
  • the rotation is thereby intercepted by a short path.
  • one or more flat surfaces 48 can be provided, which clears some space for the locking movement.
  • the position of the bolt 35 can be checked by two position sensors 49, 50, which are installed in a suitable manner in the coupling 42 and thereby protected against environmental influences by a protective housing 51.
  • the position sensor 49, 50 check the end position of the bolt 35, in the special grooves 52 are incorporated.
  • Such a groove 52 has a deep groove in the middle, which is about twice as long as the locking movement, as well as at the two ends of each only shallow furrow.
  • one of the position sensors 49, 50 is located above one of the shallow grooves and continues to report the current lock position.
  • the shallow grooves have the particular advantage that theoretically flush mounted position sensors 49, 50 are not sheared off, should they actually survive a bit. If a position sensor 49, 50 is located above one of the deep grooves, it can no longer recognize the latch 35.
  • the corresponding holes and recesses can advantageously be mounted symmetrically above and below, so that the position sensor 49, 50 can be screwed at a suitable location, the empty position z. B. can be closed with a lid 53 (see Fig. 11).
  • the measurement of the Axialverschiebewegs is made possible by an out of or within the Axialverschiebesch 20 unit.
  • the arrangement of the transmitter within the printing system is avoided as possible due to hazards during maintenance.
  • the displacement measuring system can be designed 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 an encapsulated system similar to a hydraulic cylinder.
  • 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 or tube.
  • the required encapsulation is provided by the displacement system self made.
  • a suitably sealed housing protects the electronic part of the position sensor.
  • the position sensor can be mounted on the lid 40, the position sensor rod can be passed through a hole in the lid 40 and immerse in a hole in an inner lid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Metal Rolling (AREA)
  • Actuator (AREA)
EP04741182A 2003-07-30 2004-07-21 Walzvorrichtung Active EP1648625B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10334682A DE10334682A1 (de) 2003-07-30 2003-07-30 Walzvorrichtung
PCT/EP2004/008130 WO2005011885A1 (de) 2003-07-30 2004-07-21 Walzvorrichtung

Publications (2)

Publication Number Publication Date
EP1648625A1 EP1648625A1 (de) 2006-04-26
EP1648625B1 true EP1648625B1 (de) 2007-09-12

Family

ID=34071978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04741182A Active EP1648625B1 (de) 2003-07-30 2004-07-21 Walzvorrichtung

Country Status (17)

Country Link
US (1) US7895871B2 (es)
EP (1) EP1648625B1 (es)
JP (1) JP5013866B2 (es)
KR (1) KR101121500B1 (es)
CN (1) CN100506412C (es)
AT (1) ATE372835T1 (es)
AU (1) AU2004261385B2 (es)
BR (1) BRPI0413042A (es)
CA (1) CA2532522C (es)
DE (2) DE10334682A1 (es)
ES (1) ES2289530T3 (es)
MX (1) MXPA06001143A (es)
RU (1) RU2346768C2 (es)
TW (1) TWI324092B (es)
UA (1) UA83058C2 (es)
WO (1) WO2005011885A1 (es)
ZA (1) ZA200509912B (es)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
US9802231B2 (en) 2009-01-23 2017-10-31 Sms Group Gmbh Bending and balancing device for axially shiftable work rolls of a rolling mill

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Publication number Priority date Publication date Assignee Title
EP1772203A1 (en) 2005-10-10 2007-04-11 VAI Industries (UK) Limited Roll bending device
AT504208B1 (de) 2006-04-21 2008-04-15 Siemens Vai Metals Tech Gmbh Biegevorrichtung für zwei arbeitswalzen eines walzgerüstes
DE102007042896A1 (de) * 2007-03-15 2008-09-18 Sms Demag Ag Walzvorrichtung
KR100951262B1 (ko) * 2007-05-15 2010-04-02 주식회사 포스코 압연롤의 위치 조정장치
DE102007058729A1 (de) 2007-08-07 2009-02-19 Sms Demag Ag Walzvorrichtung mit Verstellvorrichtung
DE102008009902A1 (de) * 2008-02-19 2009-08-27 Sms Demag Ag Walzvorrichtung, insbesondere Schubwalzengerüst
DE102008015826A1 (de) * 2008-03-27 2009-10-01 Sms Siemag Aktiengesellschaft Walzgerüst
DE102008035702A1 (de) * 2008-07-30 2010-02-04 Sms Siemag Aktiengesellschaft Walzvorrichtung
DE102008049179A1 (de) * 2008-09-26 2010-04-01 Sms Siemag Aktiengesellschaft Walzvorrichtung
NL2005046C2 (nl) * 2010-07-07 2012-01-10 Jean Henry Robert Madern Lagerbloksamenstel, alsmede walsinrichting voorzien van dergelijke lagerbloksamenstellen.
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
ITMI20120598A1 (it) * 2012-04-12 2013-10-13 Danieli Off Mecc Sistema integrato di piegatura e di bilanciamento per gabbie di laminazione
DE102017220560A1 (de) * 2017-05-03 2018-11-08 Sms Group Gmbh Walzgerüst zum Walzen eines metallischen Guts
EP3560615A1 (de) * 2018-04-27 2019-10-30 Primetals Technologies Austria GmbH Walzgeruest
IT201900000713A1 (it) * 2019-01-17 2020-07-17 Danieli Off Mecc Sistema di bending e shifting per gabbie di laminazione

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FR2611541B1 (fr) 1987-02-27 1994-04-29 Clecim Sa Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement
GB2202173B (en) 1987-03-19 1991-08-14 Davy Mckee Rolling mill
DE3815454A1 (de) * 1988-05-06 1989-11-16 Schloemann Siemag Ag Biege- und ausbalanciervorrichtung fuer axial verschiebbare walzen eines walzgeruestes
DE19922373A1 (de) * 1999-05-14 2000-11-16 Sms Demag Ag Biegevorrichtung für die Arbeitswalzen eines Warmwalzgerüstes

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9802231B2 (en) 2009-01-23 2017-10-31 Sms Group Gmbh Bending and balancing device for axially shiftable work rolls of a rolling mill

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MXPA06001143A (es) 2006-04-24
DE502004004968D1 (de) 2007-10-25
JP2007533455A (ja) 2007-11-22
ES2289530T3 (es) 2008-02-01
BRPI0413042A (pt) 2006-10-17
JP5013866B2 (ja) 2012-08-29
UA83058C2 (en) 2008-06-10
CN100506412C (zh) 2009-07-01
US20070129228A1 (en) 2007-06-07
RU2346768C2 (ru) 2009-02-20
DE10334682A1 (de) 2005-02-17
US7895871B2 (en) 2011-03-01
ZA200509912B (en) 2006-11-29
WO2005011885A1 (de) 2005-02-10
TW200517196A (en) 2005-06-01
AU2004261385A1 (en) 2005-02-10
KR20060120395A (ko) 2006-11-27
RU2006106184A (ru) 2006-06-27
AU2004261385B2 (en) 2009-08-20
CN1829575A (zh) 2006-09-06
ATE372835T1 (de) 2007-09-15
KR101121500B1 (ko) 2012-03-15
CA2532522A1 (en) 2005-02-10
CA2532522C (en) 2010-11-09
EP1648625A1 (de) 2006-04-26

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