EP2277637A1 - Laminoir et laminoir tandem le comprenant - Google Patents

Laminoir et laminoir tandem le comprenant Download PDF

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Publication number
EP2277637A1
EP2277637A1 EP10007529A EP10007529A EP2277637A1 EP 2277637 A1 EP2277637 A1 EP 2277637A1 EP 10007529 A EP10007529 A EP 10007529A EP 10007529 A EP10007529 A EP 10007529A EP 2277637 A1 EP2277637 A1 EP 2277637A1
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EP
European Patent Office
Prior art keywords
rolling mill
rolls
roll
work
modulus
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.)
Granted
Application number
EP10007529A
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German (de)
English (en)
Other versions
EP2277637B1 (fr
Inventor
Takashi Norikura
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.)
Primetals Technologies Holdings Ltd
Original Assignee
Mitsubishi Hitachi Metals Machinery Inc
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Publication date
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Publication of EP2277637A1 publication Critical patent/EP2277637A1/fr
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Publication of EP2277637B1 publication Critical patent/EP2277637B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/021—Rolls for sheets or strips
    • 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
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/025—Quarto, four-high stands
    • 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
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/02—Roll dimensions
    • B21B2267/06—Roll diameter

Definitions

  • This invention relates to a rolling mill, which can render the diameter of work rolls small, and a tandem rolling mill equipped with the rolling mill.
  • the minimum value of the work roll diameter is determined by the flexural rigidity value of the work rolls, which withstands the tangential force of the intermediate roll drive, if there are no support (supporting) rolls inside and outside the rollable strip width of the work rolls.
  • this value is 180 mm to 380 mm in the case of a 4-feet width material upon the intermediate roll drive.
  • the above-mentioned tangential force does not act, but differential tension, or a tension difference, between the inlet side and the outlet side of the rolling mill works.
  • the minimum value of the work roll diameter is determined by the flexural rigidity value of the work rolls, which withstands the differential tension, and at least the work roll diameter comparable to that mentioned above is feasible.
  • the work roll drive moreover, at least the work roll diameter comparable to the above one can be achieved from this point of view, even in a four-high rolling mill (hereinafter referred to as a four-high mill).
  • a conventional six-high mill may have support rolls inside the rollable strip width of the work rolls. Further, a six-high mill, which has support bearings provided outside the rollable strip width of the work rolls, and applies horizontal bending to the work rolls via these support bearings, is disclosed in Patent Document 1.
  • a six-high mill or four-high mill having support rolls inside the rollable strip width of the work rolls has involved the following problems: A space for the support roll portion is so small that sufficient strength and rigidity are difficult to ensure. Since there are support bearings for supporting the support rolls inside the rollable strip width of the work roll, moreover, marks of the support bearings are transferred to or produced in the plate via the support rolls and the work rolls, depending on their material.
  • a rolling mill having support bearings provided outside the rollable strip width of the work rolls has the following problems: Since the upper and lower support bearings are of the same phase, the bearings of a large size cannot be used, and the bearings applied cannot be adopted for heavy load, high torque rolling of a hard material which causes a great horizontal force.
  • the present invention has been proposed in the light of these circumstances. It is an object of the present invention to provide a rolling mill, which can render work rolls of a smaller diameter usable for the purpose of rolling a hard material, and can thereby obtain a strip with high productivity and of high product quality, and a tandem rolling mill equipped with the rolling mill.
  • the six- or four-high rolling mill is characterized in that the ratio of the high longitudinal modulus material to the conventional material (longitudinal modulus ratio), K, is 1.2 to 3.0. If the work roll is a composite material roll, an equivalent modulus of longitudinal elasticity is preferably used as the modulus of longitudinal elasticity.
  • the present invention further provides a tandem rolling mill including a plurality of rolling mill stands arranged therein, characterized in that the six-high rolling mill or the four-high rolling mill is provided as at least one of the stands.
  • the high longitudinal modulus material is used for the work roll.
  • the flexural rigidity of the work roll is ensured, and the diameter of the work roll can be rendered small by an amount corresponding to the high rigidity. Consequently, edge drops can be reduced, surface gloss can be improved, and the minimum rollable strip thickness can be decreased.
  • the rolling mill and the tandem rolling mill can be applied to a heavy load, high torque rolling mill for a hard material. They are preferred particularly for cold rolling.
  • Fig. 1 is a front sectional view of a six-high mill showing Embodiment 1 of the present invention.
  • Fig. 2 is a sectional view taken along line II-II in Fig. 1 .
  • Fig. 3 is an explanation drawing of a composite roll.
  • Fig. 4 is an explanation drawing of inlet side-outlet side differential tension.
  • Fig. 5 is an explanation drawing of the deflection of a work roll.
  • Fig. 6 is a graph showing a comparison between the work roll minimum diameter upper limits Dmax' s in Embodiment 1 and a conventional example.
  • Fig. 7 is a graph showing a comparison between the work roll minimum diameter lower limits Dmin' s in them.
  • Fig. 1 is a front sectional view of a six-high mill showing Embodiment 1 of the present invention.
  • Fig. 2 is a sectional view taken along line II-II in Fig. 1 .
  • Fig. 3 is an explanation drawing of a composite roll
  • FIG. 8A is an explanation drawing of a work roll offset showing an applied example of Embodiment 1.
  • Fig. 8B is an explanation drawing of load imposed on the work roll in the applied example.
  • Fig. 9A is an explanation drawing of an intermediate roll offset showing another applied example of Embodiment 1.
  • Fig. 9B is an explanation drawing of load imposed on the work roll in the another applied example.
  • Fig. 10 is an explanation drawing of a work roll shift of a six-high mill showing still another applied example of Embodiment 1.
  • a strip 1 which is a material to be rolled, is rolled by upper and lower work rolls 2 as a pair.
  • These paired upper and lower work rolls 2 are in contact with, and supported by, upper and lower intermediate rolls 3 as a pair.
  • These paired upper and lower intermediate rolls 3 are in contact with, and supported by, upper and lower back-up rolls 4 as a pair.
  • the upper back-up roll 4 is supported by bearing housings 17a, 17c via bearings (not shown), and these bearing housings 17a, 17c are supported by housings 7 (7a, 7b) via pass line adjusting devices 5a, 5b such as worm jacks or taper wedges and stepped rocker plates.
  • pass line adjusting devices 5a, 5b such as worm jacks or taper wedges and stepped rocker plates.
  • load cells may be incorporated inside the pass line adjusting devices 5a, 5b to measure a rolling load.
  • the lower back-up roll 4 is supported by bearing housings 17b, 17d via bearings (not shown), and these bearing housings 17b, 17d are supported by the housings 7a, 7b via hydraulic cylinders 6 (6a, 6b).
  • a material having a high modulus of longitudinal elasticity is used for the paired upper and lower work rolls 2.
  • An example of the material having the high modulus of longitudinal elasticity is a cemented carbide such as tungsten carbide (modulus of longitudinal elasticity: 53,000 kg/mm 2 ), or a ceramic (modulus of longitudinal elasticity: 31,000 kg/mm 2 ).
  • Special forged steel (modulus of longitudinal elasticity: 21,000 kg/mm 2 ) or the like has been used as a conventional material.
  • the ratio of the high longitudinal modulus material to the conventional material (longitudinal modulus ratio), K, be set at 1.2 to 3.0.
  • a roll composite material using a high longitudinal modulus material as a roll surface layer material 2A and a conventional material as a roll internal layer material 2B may be used for the paired upper and lower work rolls 2.
  • the modulus of longitudinal elasticity used in this case is an equivalent modulus of longitudinal elasticity shown below.
  • d2 is the outer diameter of the roll surface layer material 2A
  • E2 is the modulus of longitudinal elasticity of the roll surface layer material 2A
  • d1 is the outer diameter of the roll internal layer material 2B
  • E1 is the modulus of longitudinal elasticity of the roll internal layer material 2B.
  • bearing housings 13a to 13d are mounted on roll neck portions of the paired upper and lower work rolls 2 via bearings (not shown). These bearing housings 13a to 13d are furnished with bending cylinders 14a to 14d for imparting roll bending. By so doing, roll bending is imparted to the work rolls 2.
  • the paired upper and lower intermediate rolls 3 have roll shoulders 3a, whose roll diameter decreases, at the positions of the roll barrel ends in vertical point symmetry with respect to the center of the strip width of the strip 1.
  • the paired upper and lower intermediate rolls 3 are supported by bearing housings 15a to 15d via bearings (not shown).
  • the paired upper and lower intermediate rolls 3 are axially movable by shifting devices (not shown) via the drive-side bearing housings 15c, 15d. Further, these bearing housings 15a to 15d are furnished with bending cylinders 16a to 16d for imparting roll bending. By so doing, roll bending is imparted to the intermediate rolls 3.
  • Dr Dc / K 1 / 4
  • the minimum roll diameter of the work roll is intermediate between the minimum diameter upper limit Dmax1 and the minimum diameter lower limit Dmin1, and these parameters are expressed by the following equation (5):
  • Minimum diameter upper limit Dmax ⁇ 1 D ⁇ 4 ⁇ max ⁇ B / K 1 / 4 where D4max; minimum diameter upper limit of conventional work roll with strip width of 1,300 mm: 380 mm B; strip width (mm)/1,300 mm K; high longitudinal modulus material/conventional material ratio (modulus of longitudinal elasticity of high longitudinal modulus material/modulus of longitudinal elasticity of conventional material (21,000 kg/mm 2 ))
  • the minimum diameter upper limit Dmax1 per strip width in Embodiment 1 is shown in Fig. 6 .
  • K 2.5, provided that the material for the work roll was a cemented carbide.
  • Minimum diameter lower limit Dmin ⁇ 1 D ⁇ 4 ⁇ min ⁇ B / K 1 / 4 where D4min; minimum diameter lower limit of conventional work roll with strip width of 1,300 mm: 180 mm
  • the minimum diameter lower limit Dmin1 per strip width in the present embodiment is shown in Fig. 7 .
  • K 2.5, provided that the material for the work roll was the cemented carbide.
  • the work roll 2 composed of a cemented carbide or a ceramic material as a high longitudinal modulus material is used in the six-high mill having no supporting rolls inside and outside the rollable strip width of the work rolls 2.
  • the flexural rigidity of the work roll is ensured, and the diameter of the work roll can be rendered small by an amount corresponding to the high rigidity. Consequently, the strip 1 of high product quality can be obtained with high productivity by the rolling of a hard material.
  • the work rolls 2 of the high longitudinal modulus material may be offset variably, according to the magnitude of the inlet side-outlet side differential tension (Tf-Tb)/2, toward the inlet side in the rolling direction in the horizontal direction (see an offset amount ⁇ in Fig. 8A ).
  • the inlet side-outlet side differential tension (Tf-Tb)/2 is decreased by the offset horizontal component force Fa of the rolling load Q, so that the total force in the horizontal direction exerted on the work roll 2 is decreased.
  • Fb represents the offset vertical component force of the rolling load Q.
  • the intermediate rolls 3 may be offset variably, according to the magnitude of the inlet side-outlet side differential tension (Tf-Tb)/2, toward the outlet side in the rolling direction in the horizontal direction (see an offset amount ⁇ in Fig. 9A ).
  • the inlet side-outlet side differential tension (Tf-Tb)/2 is decreased by the offset horizontal component force Fa of the rolling load Q, so that the total force in the horizontal direction exerted on the work roll 2 of the high longitudinal modulus material is decreased.
  • Fb represents the offset vertical component force of the rolling load Q.
  • the paired upper and lower work rolls 2 are not structured to be shifted in the axial direction.
  • the work roll 2 may have a structure in which it can be shifted in the axial direction.
  • the shift structure for the work roll is, for example, a structure as shown in Patent Document 2.
  • the upper and lower work rolls 2 as a pair have roll shoulders 2a, which taper, at the positions of the roll barrel ends in vertical point symmetry with respect to the center of the strip width of the strip 1.
  • Roll neck portions of the paired upper and lower work rolls 2 are mounted with bearings (not shown) on the operating side and on the drive side.
  • the paired upper and lower work rolls 2 are movable in the axial direction by shift cylinders (not shown) via the drive-side bearings (not shown).
  • the work rolls 2 are provided with the tapered roll shoulders 2a in vertical point symmetry, and the distances from the positions of the roll shoulders to the plate ends are designated as ⁇ w and ⁇ d.
  • a strip thickness gauge (not shown) is provided for measuring the strip thickness at one point or a plurality of points in the vicinity of strip edge portions on the operating side and the drive side on the outlet side of the rolling mill.
  • the upper work roll 2 is shifted in the direction of the roll shaft width narrowing. That is, the upper work roll 2 is shifted in a direction in which ⁇ w is increased. Conversely, if the measured strip thickness at the site in the vicinity of the strip edge portion is larger than the predetermined strip thickness, the upper work roll 2 is shifted in the direction of the roll shaft width broadening. That is, the upper work roll 2 is shifted in a direction in which ⁇ w is decreased.
  • the lower work roll 2 is similarly shifted so that the above strip thickness equals the predetermined strip thickness.
  • the work roll diameter can be rendered small by applying the work roll 2 of the high longitudinal modulus material.
  • the rolling load can be decreased in conformity with the small diameter. This makes it possible to curtail a sharp decrease in thickness at the strip edge portion, which is called an edge drop becoming the cause of a decreased yield.
  • Fig. 10 describes the mill of Fig. 1 as a representative, but the mill with the variably offset work rolls in Figs. 8A, 8B or the mill with the variably offset intermediate rolls in Figs. 9A, 9B may be used.
  • the present embodiment shows an example in which the paired upper and lower intermediate rolls 3 have the roll shoulders 3a, which decrease in roll diameter, at the positions of the roll barrel ends in vertical point symmetry with respect to the center of the strip width of the strip 1.
  • the paired upper and lower intermediate rolls 3 may be structured to have S-curved roll crowns in vertical point symmetry with respect to the center of the strip width of the strip 1, and to be shifted in the axial direction, as shown in Non-Patent Document 1.
  • the ability to control shape is lower than in the six-high mill having the roll shoulder 3a, but is higher than in the four-high mill.
  • the aforementioned work roll shift shown in Fig. 10 may be applied to this mill.
  • Fig. 11 is a front sectional view of a four-high mill showing Embodiment 2 of the present invention.
  • Fig. 12 is a sectional view taken along line XII-XII in Fig. 11 .
  • Fig. 13 is an explanation drawing of a work roll shift of a four-high mill showing an applied example of Embodiment 2.
  • the rolling mill of the present embodiment is a four-high rolling mill, and is configured to remove the set of the paired upper and lower intermediate rolls 3, the bearing housings 15a to 15d, and the bending cylinders 16a to 16d from the six-high rolling mill which represents Embodiment 1, as shown in Figs. 11 and 12 .
  • the plate shape control ability declines greatly, but the structure is further simplified.
  • the paired upper and lower work rolls 2 do not show a structure for shift in the axial direction.
  • the work rolls 2 may be structured to have roll shoulders 2a, which taper, at the positions of the roll barrel ends in vertical point symmetry with respect to the center of the strip width of the strip 1, and to be shiftable in the axial direction. According to this configuration, edge drops can be decreased using a simpler structure.
  • the above-mentioned applied example is an example of a structure in which the paired upper and lower work rolls 2 have the tapered roll shoulders 2a at the positions of the roll barrel ends in vertical point symmetry with respect to the center of the strip width of the strip 1, and are shiftable in the axial direction.
  • the paired upper and lower work rolls 2 may be structured to have S-curved roll crowns in vertical point symmetry with respect to the center of the strip width of the strip 1, and to be shifted in the axial direction, as shown in Non-Patent Document 1.
  • the ability to control shape is higher than in the four-high mill shown in Fig. 13 .
  • the rolling mill with the small-diameter work rolls according to the present invention is applied to a tandem rolling mill, its application to No. 1 stand, as shown in Fig. 14 , enables the small-diameter work rolls of the high longitudinal modulus material to impart a great reduction in thickness.
  • a thinner strip can be rolled by the small-diameter work rolls of the high longitudinal modulus material.
  • the rolling mills with the small-diameter work rolls according to the present invention may be applied to all of No. 1 stand to No. 4 stand. This makes it possible to roll a thinner, harder material.
  • Fig. 14 illustrates the six-high mill as a representative of the rolling mill with the small-diameter work rolls according to the present invention, but a four-high mill can be applied similarly.

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  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
EP10007529A 2009-07-22 2010-07-20 Laminoir et laminoir tandem le comprenant Active EP2277637B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009170815A JP5568261B2 (ja) 2009-07-22 2009-07-22 圧延機及びそれを備えたタンデム圧延機

Publications (2)

Publication Number Publication Date
EP2277637A1 true EP2277637A1 (fr) 2011-01-26
EP2277637B1 EP2277637B1 (fr) 2013-03-27

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EP10007529A Active EP2277637B1 (fr) 2009-07-22 2010-07-20 Laminoir et laminoir tandem le comprenant

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EP (1) EP2277637B1 (fr)
JP (1) JP5568261B2 (fr)
CN (1) CN101961729B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130408A1 (fr) * 2015-07-08 2017-02-15 Primetals Technologies Japan, Ltd. Laminoir et procédé de laminage

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5683082B2 (ja) * 2009-07-29 2015-03-11 三菱日立製鉄機械株式会社 作業ロールシフト機能を具備した圧延機
CN104209325A (zh) * 2014-09-10 2014-12-17 中冶南方工程技术有限公司 适合于双机架平整兼二次冷轧机组的大小辊系及弯辊系统
CN111318569B (zh) * 2020-03-24 2021-08-24 河北东海特钢集团有限公司 一种钢板冷轧设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60238021A (ja) 1984-05-10 1985-11-26 Ishikawajima Harima Heavy Ind Co Ltd 圧延機
JPH0550109A (ja) 1991-08-26 1993-03-02 Hitachi Ltd 圧延機及び圧延方法
EP0987065A1 (fr) * 1998-03-23 2000-03-22 Kawasaki Steel Corporation Procede de fabrication de tole
DE10208389A1 (de) * 2001-07-11 2003-06-26 Hitachi Ltd Walzgerüst, Walzanlage und Walzverfahren

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Publication number Priority date Publication date Assignee Title
JP3209705B2 (ja) * 1997-03-25 2001-09-17 川崎製鉄株式会社 冷間圧延用複合ロール
JP2002066608A (ja) * 2000-08-30 2002-03-05 Hitachi Ltd 冷間圧延機及び圧延方法
DE10046426A1 (de) * 2000-09-20 2002-03-28 Sms Demag Ag Kombinierter Antrieb für ein Vierwalzen- bzw. Sechswalzengerüst sowie Betriebsverfahren hierfür
JP2003275803A (ja) * 2002-03-20 2003-09-30 Jfe Steel Kk 光沢の優れた金属板の冷間圧延方法
JP5138398B2 (ja) * 2008-01-25 2013-02-06 三菱日立製鉄機械株式会社 圧延機及びそれを備えたタンデム圧延機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60238021A (ja) 1984-05-10 1985-11-26 Ishikawajima Harima Heavy Ind Co Ltd 圧延機
JPH0550109A (ja) 1991-08-26 1993-03-02 Hitachi Ltd 圧延機及び圧延方法
EP0987065A1 (fr) * 1998-03-23 2000-03-22 Kawasaki Steel Corporation Procede de fabrication de tole
DE10208389A1 (de) * 2001-07-11 2003-06-26 Hitachi Ltd Walzgerüst, Walzanlage und Walzverfahren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
INDUSTRIAL MACHINERY, May 1991 (1991-05-01), pages 56 - 60

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130408A1 (fr) * 2015-07-08 2017-02-15 Primetals Technologies Japan, Ltd. Laminoir et procédé de laminage
EP3130408B1 (fr) 2015-07-08 2018-12-12 Primetals Technologies Japan, Ltd. Laminoir et procédé de laminage
US10421106B2 (en) 2015-07-08 2019-09-24 Primetals Technologies Japan, Ltd. Rolling mill and rolling method

Also Published As

Publication number Publication date
JP2011025253A (ja) 2011-02-10
EP2277637B1 (fr) 2013-03-27
JP5568261B2 (ja) 2014-08-06
CN101961729A (zh) 2011-02-02
CN101961729B (zh) 2012-12-26

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