EP2271444B1 - Cage de laminoir - Google Patents

Cage de laminoir Download PDF

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Publication number
EP2271444B1
EP2271444B1 EP09724287.9A EP09724287A EP2271444B1 EP 2271444 B1 EP2271444 B1 EP 2271444B1 EP 09724287 A EP09724287 A EP 09724287A EP 2271444 B1 EP2271444 B1 EP 2271444B1
Authority
EP
European Patent Office
Prior art keywords
roll
roll stand
bending
stand according
chock
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
EP09724287.9A
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German (de)
English (en)
Other versions
EP2271444A1 (fr
Inventor
Hans-Georg Hartung
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
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SMS Siemag AG
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Filing date
Publication date
Application filed by SMS Siemag AG filed Critical SMS Siemag AG
Publication of EP2271444A1 publication Critical patent/EP2271444A1/fr
Application granted granted Critical
Publication of EP2271444B1 publication Critical patent/EP2271444B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • 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
    • B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting

Definitions

  • the invention relates to a rolling stand with at least one roller having a rotation axis, which is arranged in two axially arranged in the end regions of the roller and each having a center plane chocks, wherein the roller can be employed with at least one adjusting element in the direction perpendicular to the conveying direction of the rolling stock ,
  • the DE 24 28 823 A1 uses a spindle system with which a bending moment can be applied to the two roll chocks by displacing the spindle onto two cup-shaped shell elements. As a result, a bending moment is introduced into the roll chocks, which counteracts the bending moment caused by the deflection of the roll.
  • a toggle-type linkage is used to exert on the two chocks of the roller a bending moment, which in turn counteracts the bending moment by which the roller is bent by rolling force.
  • Axially displaceable intermediate rollers with non-cylindrical outer contour are in the solution according to the DE 30 00 187 A1 and according to the DE 22 06 912 A1 used.
  • the principle used is based on the introduction of transverse and bending forces and thus bending moments in the corresponding rolls.
  • the effect is usually not sufficient to compensate for the different deflection states of a rolling mill due to different Walzgutfesttechniken and widths. Therefore, additionally different crowned ground rolls are used or roll shifting systems are provided.
  • These axial displacement systems operate either on the principle of internal load transfer or the variable equivalent crowning of two rolls (so-called Continuous Variable Crown - CVC system).
  • the use of different spherical rollers is cumbersome. Displacement systems are also expensive and lead in particular in the case of load transfer to unwanted pivoting movements of the framework. The same applies to principles that work with slightly intersecting rolls.
  • the present invention has the object, a rolling stand of the type mentioned in such a way that it is possible in a simpler and less expensive manner and with as few elements as possible to initiate a bending moment counteracting the bending moment in the roll. It should be possible to dispense with elaborate mechanisms, while still ensuring that bending of the roller, which stem from the rolling forces, can be compensated as well as possible.
  • each chock is connected to a bending lever and the adjusting element is arranged so that its contact force is introduced at a remote from the center plane of the chock in the bending lever and on this on the chock.
  • the positioning element acts on a cross-member, which is connected via two joints, each with a bending lever.
  • two adjusting elements are provided, which are arranged mirrored to a center plane of the roller. These can be connected via two joints, each with a bending lever. The two joints can be connected to each other via a crossbar.
  • the at least one adjusting element is preferably a hydraulic piston-cylinder system.
  • the one or more Anstellelemente can be supported on a stationary crosshead of the rolling stand.
  • a structurally advantageous solution provides that the roller together with chocks and bending levers in the direction perpendicular to the conveying direction of the rolling stock in the rolling stand between two side cheeks of the roll stand is slidably disposed.
  • the bending levers can surround the chocks laterally and form a sliding surface to the side cheeks.
  • bending levers and the chocks means may be provided which are suitable for introducing a torque from the bending lever in the chock.
  • this is a tongue-and-groove connection extending in the direction of the axis of rotation of the roller.
  • the rolls mentioned here may be work rolls in duo-stands or back-up rolls.
  • the proposed solution thus provides that the rolling force induced deflections of the set of rolls and the associated imperfections of the roll gap geometry are largely avoided by the rolling force itself bending moments on the rollers (especially on the back-up rolls and the work rolls) are constructed, the bending effect of the rolling force-induced deflection of the rolls is opposite.
  • the present invention is based on a scaffold principle that prevents the unwanted rolling force-induced roller deformations predominantly and almost independently of rolling force and thus has the potential to manage with a minimum of active flatness adjustment systems.
  • Fig. 1 is a section of a rolling stand to see that has a work roll 1 with a rotation axis A, which is mounted in two chocks 2 and 3 in a known manner.
  • the work roll rolls a rolling stock, not shown, that is rolled in the conveying direction F (perpendicular to the drawing plane).
  • the work roll 1 is pressed by means of a hydraulic adjusting element 4 against the rolling stock.
  • the deflection of the roller 1 due to the contact with the rolling stock is superimposed on a counter-bending moment, which is generated by two bending levers 5 and 6.
  • the two bending levers 5, 6 are rotatably connected to the chocks 2, 3. They are connected in the central region of the device at two articulation points G by means of two joints 8 and 9 with a traverse 7, on which the adjusting element 4 acts.
  • the adjusting element 4 is supported on a crosshead 10 of the roll stand.
  • the roller length is indicated by L B and is smaller than the distance L of the center planes M E of the two chocks 2, 3. Also given is the distance l two rolling bearings, which are arranged in the chock 2, 3 and store the roll neck.
  • the arrangement is symmetrical overall, ie a mirror image of a central plane M W of the roller. 1
  • Fig. 3 is in the view A according to Fig. 1 to see how the roller 1 together with chocks 2, 3 and bending levers 5, 6 is arranged displaceably in the vertical direction in the rolling stand.
  • the roll stand on two side cheeks 11 and 12, the respective sliding surfaces 13 and 14 have, so that the bending lever 5, 6 can slide vertically up and down.
  • still means 15 - here in the form of a tongue and groove joint - with which a bending moment of the bending levers 5, 6 can be introduced into the chock 2, 3.
  • a scaffold loaded by a rolling force distribution would be set up in the same manner - centrically and in the same width - as the rolling stock acting on the work roll.
  • a rotating roller can not be employed in the center by one or more stationary setting cylinders - the location of the introduction of rolling force can only be the chock with the roller bearing.
  • the aim of the present solution is to use the basic principle of ideal rolling force application, namely along the roll mantle.
  • the loaded in the same way as employed roller experiences no bending moment - both locally and as a whole.
  • the roll axis remains straight.
  • the fact that the rolling force can be initiated only on the chocks and not along the roll shell, means that a compensating bending-back torque can not be initiated locally, but also only on the chock in the roll.
  • the Anstellzylinderkraftkraft is not centrally applied to the chocks or roller bearings, but at a suitable distance. The resulting moment must be initiated by a sufficiently stable mechanism in the chock.
  • Fig. 1 shows such an arrangement with a central adjusting cylinder.
  • the contact force can also be applied by several cylinders, as in Fig. 2 is shown with two Anstellzylindern. It is essential that a suitably dimensioned distance of the load application point to the chock is present and the connection of the bending lever with the chock can transmit a moment.
  • the combination of chock and bending lever must be designed so that the chock can not be wedged in the stator window and can not be moved in the sequence for employment. Furthermore, the changeability of the support roller must be ensured.
  • the movability of the roller can be achieved, for example, by the fact that the cheeks of the bending lever comprise the outer sides of the component and the movement takes place between the cheeks and the roll stand, as shown in FIG Fig. 3 you can see.
  • the chock is designed so that the compensating bending moment is introduced by a superimposed on the other forces pair of forces on the chock, the lines of action of the force pair should correspond approximately to the positions of the radial roller bearings to largely avoid torque loads on the bearings.
  • the adjusting cylinder bears on the one hand on the force-transmitting bridge, consisting of the two bending levers (including traverse), on the other hand, it relies on the crosshead of the rolling mill.
  • the adjusting cylinder can be replaced by a pass line adjustment or simply by a fixed pressure piece.
  • the pivoting of the framework takes place, at least in the case of a central adjusting cylinder, preferably by the appropriately equipped balancing cylinder. Due to the lower hysteresis of these small cylinders, this also requires more precise pivoting.
  • the Zylinderanstellkraft F A acts centrally on the traverse 7 of the bending bridge, which comprises the two bending levers 5 and 6 in addition to the traverse 7, wherein the connection between the bending levers 5, 6 and the traverse 7 via joints 8 and 9 takes place.
  • the platen 1 is simplified as a round bar over the length of constant cross-section shown in the middle and loaded with a single force F W from the rolling process.
  • the system does not experience any asymmetries in this simplified representation and is weight-free, so that the balancing forces F B1 and F B2 compensating the weight of the roller and its attachments are equal to zero.
  • the bending levers 5, 6 and the roll chocks 2, 3 are combined to form a body - ultimately, a division into two components is optionally only a lighter structural design.
  • the connection of roll chock / bending bridge takes place in this replacement system by simple fixed bearing whose distance in the chock l is.
  • the chock centers (center planes M E ) have the bearing center distance L, the distance of the joints 8, 9 from the respective chock centers is S.
  • E is the modulus of elasticity of the roll material
  • I is the area moment of inertia.
  • S / L 0.5 means that the bending lever has the maximum length, ie half the bearing center distance, and thus the rebound moment is greatest.
  • Fig. 5 shows for this simplified example that a substantial compensation for bending lever lengths of about 30% of the bearing center distance L is to be expected. For real, so not (as in the example) deliberately idealized conditions such. B. offset stepped rollers, other optimal lever lengths are to be expected, the principle remains the same.
  • the system according to the invention is preferably also used in combination with the previously known systems for roll gap influencing.
  • variable lever lengths S that is, locations of the hinge points G
  • active control can be used for active control.
  • the invention enables a simple scaffolding design, with the property that the roll force induced deformations of the set of rolls are compensated automatically, without external intervention and properly dimensioned.
  • the same would be achieved with conventional construction only with significantly thicker back-up rolls or a complex, active flatness correction system.
  • the roll would have to be more than 70% thicker in order to have a similar behavior to the mechanism according to the invention. This would have an enormous enlargement of the framework with corresponding additional costs.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Metal Rolling (AREA)

Claims (12)

  1. Cage de laminoir comprenant au moins un rouleau (1) présentant un axe de rotation (a), qui est monté dans deux empoises (2, 3) disposées dans les zones terminales axiales du rouleau (1) et présentant respectivement un plan médian (ME), le rouleau (1) pouvant être réglé avec au moins un élément de réglage (4) dans une direction perpendiculaire à la direction de transport (F) des matières à laminer, caractérisée en ce que chaque empoise (2, 3) est reliée à un levier de pliage (5, 6) et l'élément de réglage (4) est disposé de telle sorte que sa force de réglage est guidée jusque dans le levier de pliage (5, 6), à un endroit (G) éloigné du plan médian (ME) de l'empoise (2, 3) et, via ledit levier, sur l'empoise (2, 3).
  2. Cage de laminoir selon la revendication 1, caractérisée en ce qu'un seul élément de réglage (4) est présent, qui est disposé en position médiane entre les empoises (2, 3).
  3. Cage de laminoir selon la revendication 2, caractérisée en ce que l'élément de réglage (4) agit sur une traverse (7) qui est reliée via deux articulations (8, 9) à respectivement un levier de pliage (5, 6).
  4. Cage de laminoir selon la revendication 1, caractérisée en ce que deux éléments de réglage (4) sont présents, qui sont disposés en position spéculaire par rapport au plan médian (Mw) du rouleau (2).
  5. Cage de laminoir selon la revendication 4, caractérisée en ce les éléments de réglage (4) sont reliés via deux articulations (8, 9) à respectivement un levier de pliage (5, 6).
  6. Cage de laminoir selon la revendication 5, caractérisée en ce les deux articulations (8, 9) sont reliées l'une à l'autre via une traverse (7).
  7. Cage de laminoir selon l'une quelconque des revendications 1 à 6, caractérisée en ce qu'au moins un élément de réglage (4) représente un système hydraulique à piston-cylindre.
  8. Cage de laminoir selon l'une quelconque des revendications 1 à 7, caractérisée en ce qu'au moins un élément de réglage (4) s'appuie contre une entretoise transversale (10) de la cage de laminoir, montée à demeure.
  9. Cage de laminoir selon l'une quelconque des revendications 1 à 8, caractérisée en ce que le rouleau (1), ensemble avec les empoises (2, 3) et les leviers de pliage (5, 6), est disposé en coulissement dans une direction perpendiculaire à la direction de transport (F) des matières à laminer dans la cage de laminoir entre deux joues latérales (11, 12) de la cage de laminoir.
  10. Cage de laminoir selon la revendication 9, caractérisée en ce que les leviers de pliage (5, 6) entourent latéralement les empoises (2, 3) et forment une surface de glissement (13, 14) par rapport aux joues latérales (11, 12).
  11. Cage de laminoir selon l'une quelconque des revendications 1 à 10, caractérisée en ce qu'on prévoit, entre les leviers de pliage (5, 6) et les empoises (2, 3), des moyens (15) pour faire passer un couple de rotation depuis le levier de pliage (5, 6) jusque dans l'empoise (2, 3).
  12. Cage de laminoir selon la revendication 11, caractérisée en ce que les moyens (15) sont formés via une liaison rainure-ressort (13) s'étendant dans la direction de l'axe de rotation (a) du rouleau (1).
EP09724287.9A 2008-03-27 2009-03-16 Cage de laminoir Active EP2271444B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008015826A DE102008015826A1 (de) 2008-03-27 2008-03-27 Walzgerüst
PCT/EP2009/001911 WO2009118117A1 (fr) 2008-03-27 2009-03-16 Cage de laminoir

Publications (2)

Publication Number Publication Date
EP2271444A1 EP2271444A1 (fr) 2011-01-12
EP2271444B1 true EP2271444B1 (fr) 2013-05-15

Family

ID=40801956

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09724287.9A Active EP2271444B1 (fr) 2008-03-27 2009-03-16 Cage de laminoir

Country Status (10)

Country Link
US (1) US8544308B2 (fr)
EP (1) EP2271444B1 (fr)
JP (1) JP2010528868A (fr)
KR (1) KR101151248B1 (fr)
CN (1) CN101687234B (fr)
CA (1) CA2686437C (fr)
DE (1) DE102008015826A1 (fr)
RU (1) RU2405642C1 (fr)
UA (1) UA94013C2 (fr)
WO (1) WO2009118117A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101787618B (zh) * 2009-12-10 2014-03-12 常州市武进广宇花辊机械有限公司 一种拉弯轧辊式热轧机
DE102019202691A1 (de) * 2019-02-28 2020-09-03 Sms Group Gmbh Walzgerüst zum Walzen metallischen Guts

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1860931A (en) 1928-02-23 1932-05-31 Bethlehem Steel Corp Rolling mill
FR1488213A (fr) * 1964-07-31 1967-07-13 Spidem Ste Nle Procédé de flexion des cylindres d'appui dans les laminoirs multicylindres et dispositif pour sa mise en oeuvre
US3426567A (en) * 1965-06-28 1969-02-11 Kaiser Aluminium Chem Corp Roll bending device for a rolling mill
DE1652557A1 (de) * 1968-02-27 1971-04-15 Siemag Siegener Maschb Gmbh Stuetzwalzen-Rueckbiegevorrichtung fuer Walzwerke
DE1752752A1 (de) * 1968-07-10 1971-05-19 Schloemann Ag Vorrichtung zur Biegung der Walzen von Walzgeruesten gegen den Walzdruck
US3621695A (en) * 1968-10-24 1971-11-23 Blaw Knox Co Rolling mill crown prevention and control means
GB1256907A (fr) * 1969-02-25 1971-12-15
DE2034490A1 (en) 1970-07-11 1972-01-27 SIEMAG Siegener Maschinenbau GmbH, 5912 Hilchenbach Dahlbruch Roller pivot bearing compensator - hydraulically operated
GB1351074A (en) 1971-02-15 1974-04-24 Hitachi Ltd Rolling mills
DE2428823A1 (de) 1974-06-14 1976-01-02 Schloemann Siemag Ag Walzgeruest mit einer einrichtung fuer zusaetzliche biegemomente mindestens einer walze
JPS5597806A (en) * 1979-01-17 1980-07-25 Hitachi Ltd Method and apparatus for correcting asymmetry of rolling mill
JPS59223102A (ja) * 1983-06-01 1984-12-14 Hitachi Ltd 作業ロ−ルベンデイング装置
JPS6015404U (ja) * 1983-07-07 1985-02-01 石川島播磨重工業株式会社 圧延機の軸箱
JPS61140313A (ja) * 1984-12-14 1986-06-27 Ishikawajima Harima Heavy Ind Co Ltd ロ−ルベンデイング制御方法
JPH0679730B2 (ja) * 1985-07-08 1994-10-12 株式会社日立製作所 ロ−ルベンデイング装置
KR100215676B1 (ko) 1992-11-10 1999-08-16 스스무 이찌미 폭가변압연롤의폭조정장치
KR200243132Y1 (ko) 1997-06-04 2001-11-30 이구택 압연롤 교체를 위한 롤센터조정 및 표면검사장치
FR2774929B1 (fr) 1998-02-13 2000-06-09 Kvaerner Metals Clecim Installation de laminage de produits plats et son procede de mise en oeuvre
IT1315121B1 (it) * 2000-09-25 2003-02-03 Danieli Off Mecc Dispositivo per assorbire i carichi assiali generati sui cilindri diuna gabbia di laminazione
DE10334682A1 (de) * 2003-07-30 2005-02-17 Sms Demag Ag Walzvorrichtung
CN2790617Y (zh) * 2005-03-25 2006-06-28 昆明钢铁集团有限责任公司 一种轧机轧辊控制装置
AT504208B1 (de) * 2006-04-21 2008-04-15 Siemens Vai Metals Tech Gmbh Biegevorrichtung für zwei arbeitswalzen eines walzgerüstes

Also Published As

Publication number Publication date
US8544308B2 (en) 2013-10-01
UA94013C2 (en) 2011-03-25
DE102008015826A1 (de) 2009-10-01
RU2405642C1 (ru) 2010-12-10
CN101687234A (zh) 2010-03-31
CN101687234B (zh) 2013-01-09
KR20090130326A (ko) 2009-12-22
KR101151248B1 (ko) 2012-06-14
WO2009118117A1 (fr) 2009-10-01
CA2686437C (fr) 2012-05-22
US20110232350A1 (en) 2011-09-29
EP2271444A1 (fr) 2011-01-12
CA2686437A1 (fr) 2009-10-01
JP2010528868A (ja) 2010-08-26

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