EP2572808B1 - Cold-rolling mill, tandem rolling system, reversing rolling system, modification method of rolling system, and operating method of cold-rolling mill - Google Patents

Cold-rolling mill, tandem rolling system, reversing rolling system, modification method of rolling system, and operating method of cold-rolling mill Download PDF

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Publication number
EP2572808B1
EP2572808B1 EP12184124.1A EP12184124A EP2572808B1 EP 2572808 B1 EP2572808 B1 EP 2572808B1 EP 12184124 A EP12184124 A EP 12184124A EP 2572808 B1 EP2572808 B1 EP 2572808B1
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Prior art keywords
rolling
rolling mill
roll
rolls
cold
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German (de)
English (en)
French (fr)
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EP2572808A1 (en
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Shinichi Yasunari
Fumihisa Shimaya
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Primetals Technologies Holdings Ltd
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Mitsubishi Hitachi Metals Machinery Inc
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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
    • 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
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • 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
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B21B1/24—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process
    • B21B1/28—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process by cold-rolling, e.g. Steckel cold mill
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B21B1/30—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process
    • B21B1/32—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process in reversing single stand mills, e.g. with intermediate storage reels for accumulating work
    • B21B1/36—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process in reversing single stand mills, e.g. with intermediate storage reels for accumulating work by cold-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/142—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • 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
    • B21B2261/00—Product parameters
    • B21B2261/02—Transverse dimensions
    • B21B2261/06—Width
    • 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
    • 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
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills

Definitions

  • the present invention relates to a cold-rolling mill, a tandem rolling system, a reversing rolling system, a modification method for a rolling system, and an operating method for a cold-rolling mill.
  • a cold-rolling mill as described in the preamble portion of patent claim 1 has been known from DE 102 08 389 A1 .
  • Non-Patent Document 1 "Cold Strips Manufacturing Equipment Specifications and Plant Equipment Layout in Japan", compiled/revised by the Iron and Steel Institute of Japan (Collaborative Research Workshop, Working Group on Steel Strips, Sub-Committee on Cold-Rolled Steel Strips)
  • the mild steel strips and/or high strength steel strips mainly used for automobiles are produced in large quantities by the tandem rolling systems of the four-high or six-high rolling mills with the work roll diameters nearly of 420-630 mm.
  • the demand for these steel strips is expanding particularly in high strength steel strip markets.
  • a first method is to reduce the work roll diameter of the rolling mill.
  • the cluster type rolling mill discussed earlier herein as a typical rolling mill having a work roll diameter of 200 mm or less is an example of such a rolling mill.
  • a second method is to increase the number of stands of tandem rolling mills of conventional specifications. Even if one stand remains unchanged in rolling capabilities, increasing the number of stands improves a total rolling reduction capability of the tandem rolling mill. In other words, it becomes possible, while maintaining a feature of high productivity of the tandem rolling mill, to roll harder steel strips and to implement rolling at higher reduction ratios. Increase in the number of stands of the rolling mills, however, means significantly increasing an initial investment in new installation work or an additional investment in modification work.
  • An object of the present invention is to provide a cold-rolling mill, tandem rolling system, reversing rolling system, rolling system modification method, and cold-rolling mill operating method in which, by reducing the work roll in diameter, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed, while preventing decrease in productivity due to the use of the small-diameter work roll mill as used in the cluster type rolling mill.
  • Another object of the present invention is to provide a cold-rolling mill, tandem rolling system, rolling system modification method, and cold-rolling mill operating method in which high productivity as of the conventional tandem rolling system can be maintained and without increasing the stands, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • a first aspect of the present invention provides a cold-rolling mill for rolling a steel strip of minimum width not less than 600 mm and maximum width not less than 1,500 mm but not greater than 1,900 mm, the mill including: a pair of upper and lower work rolls; a pair of upper and lower intermediate rolls supporting the work rolls, respectively; a pair of upper and lower buck-up rolls supporting the intermediate rolls, respectively; an axial direction roll shifting device for the intermediate roll; and bending devices for each of the work rolls and the intermediate rolls, wherein the work rolls each have a diameter not less than 300 mm but not greater than 400 mm, and the intermediate rolls each have a diameter not less than 560 mm but not greater than 690 mm.
  • the present inventors after studying combinations of roll diameters that allow in a six-high cold-rolling mill a strip shape to be appropriately maintained and a contact pressure between rolls to be maintained within a allowable range (critical), have discovered such a combination of work roll diameters and intermediate roll diameters as mentioned above, and have thus found it to be possible to obtain a higher reduction ratio than the prior art. As a result, rolling of a harder steel strip than ever to be rolled and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • tandem rolling system when a tandem rolling system is constructed using at least one stand of a cold-rolling mill according to the present invention, by using work rolls smaller than conventional ones in diameter, high productivity as of the conventional tandem rolling system can be maintained and without increasing the stands, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • a second aspect of the present invention provides the cold-rolling mill wherein in the first aspect of the invention, a work roll drive unit for rotationally driving the work rolls is provided as a drive unit for the rolling mill.
  • the driving of the work roll causes no potential slipping between rolls, compared with indirect drive of the intermediate roll or buck-up roll.
  • the overload preventive device is immediately activated to enable the rolling mill to be stopped.
  • the rolling mill is free of a driving tangential force likely to be exerted upon the work roll in case of the intermediate-roll drive, and this prevents the work roll from deflecting in a horizontal direction and thus enables the rolling mill to develop its original shape control ability.
  • a third aspect of the present invention provides the cold-rolling mill wherein in the second aspect of the invention, the work roll drive unit includes gear spindles adapted to transmit a driving force of an electric motor to each of the work rolls.
  • a fourth aspect of the present invention provides the cold-rolling mill wherein in the second or third aspect of the invention, the work roll drive unit includes an overload preventive device adapted to prevent damage to the spindles.
  • the overload preventive device is immediately activated to enable the rolling mill to be stopped without damaging the spindle.
  • a fifth aspect of the present invention provides the cold-rolling mill wherein in any one of the first to fourth aspects of the invention, the rolling mill further includes a roll offset device adapted to offset either one of the work rolls and the intermediate rolls relative to axes of the other rolls to an entry or exit side in a rolling direction.
  • the horizontal deflection of the work roll in a rolling direction can be suppressed as small as possible, so that more stable mill operation can be assured.
  • a sixth aspect of the present invention provides the cold-rolling mill wherein in the first aspect of the invention, an intermediate roll drive unit for rotationally driving the intermediate rolls is provided as a drive unit for the rolling mill.
  • the drive spindle can be designed as well so as to stay within a range of the intermediate roll diameter. This enables a drive spindle of the drive unit to be manufactured to sufficient strength against a necessary torque.
  • a seventh aspect of the present invention provides the cold-rolling mill wherein in the sixth aspect of the invention, the intermediate roll drive unit includes universal joints adapted to transmit a driving force of an electric motor to each of the intermediate rolls.
  • the roll drive unit can be manufactured at a lower cost than in a case that it uses a gear spindle.
  • An eighth aspect of the present invention provides the cold-rolling mill wherein in the sixth or seventh aspect of the invention, the rolling mill further includes a roll offset device adapted to offset either one of the work rolls and the intermediate rolls relative to axes of the other rolls to an entry or exit side in a rolling direction.
  • the horizontal deflection of the work roll in a rolling direction can be suppressed as small as possible, so that more stable mill operation can be assured.
  • a ninth aspect of the present invention provides a tandem rolling system comprises a row of plural stands of rolling mills, wherein the plural stands of rolling mills include at least one stand of the cold-rolling mill according to any one of the first to eighth aspects of the present invention.
  • the plural stands of rolling mills may be all the cold-rolling mill according to any one of the first to eighth aspects of the present invention.
  • a tenth aspect of the present invention provides a reversing rolling system comprising at least one reversing rolling mill, wherein the reversing rolling mill includes at least one cold-rolling mill according to any one of the first to eighth aspects of the present invention.
  • An eleventh aspect of the present invention provides a modification method of a rolling system having one or plural stands of rolling mills, the method comprising modifying at least one stand of the rolling mill into the cold-rolling mill according to any one of the first to eighth aspects of the present invention.
  • tandem rolling system high productivity as of the conventional tandem rolling system can be maintained and without increasing the stands, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • a twelfth aspect of the present invention provides an operating method of a cold-rolling mill, the method comprising rolling the steel strip at a reduction ratio higher than 12% by using the cold-rolling mill according to any one of the first to eighth aspects of the present invention.
  • high productivity as of the conventional tandem rolling system can be maintained and without increasing the stands, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • Fig. 1 is a side view of the six-high rolling mill
  • Figs. 2 and 3 are external views of the six-high rolling mill, taken from directions of arrows A and B, respectively, in Fig. 1 .
  • the six-high rolling mill 51 includes: a pair of upper and lower work rolls 2 for rolling a material to be roll (steel strip) 1 that is a metallic material by coming into direct contact therewith; a pair of upper and lower intermediate rolls 3 supporting the work rolls 2, respectively; and a pair of upper and lower buck-up rolls 4 supporting the intermediate rolls 3, respectively.
  • Bearing housings 8 and 9 are mounted at ends of each of the work rolls 2 and the intermediate rolls 3, and as shown in Fig. 2 , work roll bending devices 10 and intermediate roll bending devices 11 are arranged to bend the work rolls and the intermediate rolls by exerting a vertical force upon the bearing housings 8 and 9.
  • Housings 5 function as a support structure that uses bearing housings 6 of the buck-up rolls 4.
  • each housing 5 At a lower region of each housing 5 is installed a hydraulic screw down device 7 as rolling reduction means, which moves the bearing housing 6 of each lower buck-up roll 4 vertically to reduce the thickness of the material 1 to be rolled.
  • the work roll bending devices 10 can provide the work rolls with increase bending and decrease bending.
  • each intermediate roll 3 is mounted so as to enable the intermediate rolls to move in an axial direction of the rolls.
  • An example of a roll shifting device 23 is described below using Fig. 3 .
  • the bearing housing 9 of each intermediate roll 3 is sandwiched between intermediate roll offset devices 19, and the intermediate roll offset devices 19 are each fitted in a project block 17 and mounted in a shift block 12 movable in the roll axial direction.
  • each of the intermediate roll offset devices 19 is placed to move the intermediate roll 3 in a horizontal direction and change a relative position of the intermediate roll 3 with respect to the corresponding work roll 2.
  • the details of the arrangement, purpose and operation of the intermediate roll offset device 19 will be explained later.
  • the shift blocks 12 are coupled to the intermediate roll bearing housing 9 via keeper plates 14 each actuated by a hydraulic cylinder 15, and the shift blocks 12 at an operating side are coupled to the shift blocks 12 of the driving side via stays 18.
  • Hydraulic cylinders 16 are installed on shift frames 24 fixed to the housings 5, and are coupled to the shift blocks 12 at the driving side. With such an arrangement, by driving the hydraulic cylinders 16, the intermediate roll 3 and the shift blocks 12 can be moved to a desired position in the roll axial direction.
  • each intermediate roll offset device 19 contains an intermediate roll bending device 11, a point at which a bending force acts remains unchanged, even when the intermediate roll 3 is shifted in the roll axial direction and/or the intermediate roll 3 is moved in the horizontal direction.
  • a tapered chamfer 3a nearly of 1,000 R is provided at the end of each intermediate roll 3.
  • a distance from a starting point of the chamfer 3a and an end of the material 1 to be rolled is termed "UC ⁇ ".
  • the UC ⁇ is expressed with a plus sign when the starting point of the chamfer 3a is positioned outside of the strip end and with a minus sign when the starting point is positioned inside of the strip end.
  • Figs. 26 and 27 show more specific examples.
  • the appropriate strip shape is such a strip crown shape as shown in Fig. 26 , in which, a portion of the strip other than a central portion is the same in thickness as the central portion or smaller in thickness than the central portion (expression 1), and in which up to the position of 2/3 of the strip width from the center thereof, the strip crown is zero (expression 2).
  • a shape in which the portion of the strip other than the central portion is greater in thickness than the central portion or in which the strip crown is not zero from a position more central than the position of 2/3 of the strip width from the center thereof (expression 2), is not considered to be the appropriate strip crown shape.
  • Fig. 4 is a graph that represents the critical rolling loads enabling the strip shape to be maintained appropriately in combinations of various intermediate roll diameters for work rolls.
  • the horizontal axis represents the intermediate roll diameters, and the vertical axis represents rolling loads (here, rolling load per strip width: tons/mm).
  • a certain intermediate roll diameter was varied for each of work roll diameters of 250 mm, 300 mm, 330 mm, 340 mm, 380 mm, 400 mm, 450 mm, and 475 mm, and the critical rolling loads enabling the strip shape to be maintained appropriately were calculated.
  • Data that was obtained using the work rolls of 330 mm and 340 mm in diameter is shown as one integrated set of data since there was substantially no difference between both. This results in the following being derived.
  • Data in parentheses in Fig. 4 is optimal intermediate roll diameters for each work roll diameter.
  • Allowable rolling loads (here, each load per unit strip width, in tons/mm) in the combinations of work roll diameters and corresponding optimal intermediate roll diameters in Fig. 4 were calculated by simulation based on contact pressures (Hertz stresses) between rolls allowed from roll strength. Results of the simulation are shown in a graph of Fig. 5 .
  • the vertical axis represents the work roll diameters, and the horizontal axis represents the rolling loads (load per strip width: tons/mm).
  • An increase in contact pressures (Hertz stresses) between rolls causes rolling contact fatigue, thereby leading to the roll surface spalling and/or to other problems occurring.
  • studies were conducted from a viewpoint of preventing these problems from occurring.
  • the result is Fig. 6 .
  • An allowable rolling loads to serve as indicators for actual rolling are obtained from Fig. 6 . That is to say, the smaller of data in two graphs of Fig. 6 is the allowable rolling loads for the work roll diameter. For example, it follows from the limits of contact pressure that the allowable rolling load for the work roll diameter of 475 mm is nearly 1.22 tons/mm, and it follows from the limits of strip shape that the allowable rolling load for the work roll diameter of 250 mm is nearly 0.95 ton/mm.
  • the rolling reduction ratio obtained increases progressively, then before too long, peaking in a neighborhood of the 340-mm work roll diameter. It can also be seen that further reducing the work roll diameter lowers the rolling reduction ratio on the contrary. It can be additionally seen that while the rolling reduction ratio remains substantially equal, nearly 14.5-15.0 %, in a work roll diameter range of 300-400 mm, the rolling reduction ratio decreases more for both of work roll diameters smaller than 300 mm, and those greater than 400 mm. The rolling reduction ratios of about 14.5-15.0 %, obtained in the work roll diameter range of 300-400 mm, are nearly 21-25 % as high as those of about 12% obtained for conventional work roll diameters.
  • the present inventors After thus conducting synthetic reviews from both standpoints of the limits of the rolling load enabling the strip shape to be maintained appropriately, and the limits of the rolling load restricted from the contact pressures between rolls, the present inventors have found that the work roll diameters of 300-400 mm are appropriate in that a high rolling reduction ratio can be obtained.
  • the work roll diameters range nearly 320-360 mm, in which case, it can be seen that high rolling reduction ratios nearly of 15.0%, substantially equal to the peak value of the rolling reduction ratio, are obtainable. In terms of obtaining a higher rolling reduction ratio, therefore, the present inventors have found it optimal that the work roll diameter be confined to a range of 320-360 mm (nearly 340 ⁇ 5%).
  • the above is the study results relating to the critical rolling loads for the contact pressures between rolls ( Fig. 5 ), the critical rolling loads for the strip shape ( Fig. 6 ), and rolling reduction ratios ( Fig. 7 ), in combinations of work roll diameters and optimal intermediate roll diameters.
  • the intermediate roll diameter used does not always need to be an optimal value. That is to say, as described above, the appropriate work roll diameter range in the present invention is 300-400 mm, and the facts that the optimal intermediate roll diameter for the work roll diameter of 300 mm is 630 mm and that the optimal intermediate roll diameter for the work roll diameter of 400 mm is 600 mm are as shown in Fig. 4 .
  • the intermediate roll diameter of 400 mm if the intermediate roll diameter is at least 600 mm, effects equivalent to those achievable for 600 mm can also be obtained.
  • a minimal intermediate roll diameter necessary to obtain maximal effects for work rolls of 300-400 mm is 600 mm or 630 mm, whichever is the greater, and that 630 mm, in particular, is more preferable for better results.
  • Rolls on the other hand, have their operating ranges, which are generally some 10%. It follows from this that the intermediate roll diameter of 630 mm x 1.1 times is about 690 mm, from which it would be fair to say that maximum allowable intermediate roll diameters of 630-690 mm for the work roll diameters of 300-400 mm are optimal.
  • Fig. 8 is a diagram that shows results of studies which, in combinations of different fixed intermediate roll diameters and various work roll diameters, were conducted in a manner similar to that of Fig. 7 .
  • the intermediate roll diameters are 530 mm, 550 mm, 560 mm, 630 mm, and 690 mm.
  • Fig. 8 indicates that as described above as to the study results on the critical rolling loads for the contact pressures between rolls, the critical rolling loads for the strip shape, and rolling reduction ratios allowed in the combinations of work roll diameters and optimal intermediate roll diameters, when the intermediate roll diameter is varied in the range of 630-690 mm, the peak value of the rolling reduction ratio can be obtained in the work roll diameter range of 300-400 mm.
  • Figs. 4 to 8 apply to a case in which the strip material is a high strength steel strip of 1,650 mm in strip width
  • Fig. 9 is a diagram that shows results of studies which, in combinations of work roll diameters and corresponding optimal intermediate roll diameters, were conducted with two different strip widths, 600 mm and 1,900 mm, in a manner similar to that of Fig. 7 .
  • Fig. 9 shows results of studies which, in combinations of work roll diameters and corresponding optimal intermediate roll diameters, were conducted with two different strip widths, 600 mm and 1,900 mm, in a manner similar to that of Fig. 7 .
  • the buck-up roll diameter that was used for the simulation is 1,370 mm, which is adopted in the conventional rolling mills ranging nearly 1,500-1,900 mm in maximum strip width.
  • the buck-up roll diameter of 1,370 mm is just an example, and any other buck-up roll diameter may be used, only if it is determined from the buck-up roll neck diameter and neck bearing size enabling a rolling mill of the above strip widths to support a maximum necessary rolling load.
  • the tendency of changing critical rolling loads and rolling reduction ratios in the combinations of work roll diameters and corresponding optimal intermediate roll diameters in Figs. 4 to 9 also remains invariant.
  • a higher reduction ratio can be achieved in the present invention than in the conventional combinations of work roll diameters and intermediate roll diameters.
  • the optimal intermediate roll diameter in this case is 620 mm, according to Fig. 4 .
  • the optimal intermediate roll diameter in a tandem rolling system with 475-mm diameter work rolls is 580 mm, according likewise to Fig. 4 .
  • Fig. 10 is a diagram that shows comparative study results on the number of stands required for 780-MPa high strength steel strip rolling with the 340-mm diameter work rolls and with prior-art 475-mm diameter work rolls. Looking at the smaller values of the allowable rolling loads depending on the contact pressures between rolls and the critical rolling load enabling the strip shape to be maintained appropriately, one can see that 1.22 tons/mm is applied when the work roll diameter is 475 mm while 1.13 tons/mm is applied when the work roll diameter is 340 mm. These values are used as indicators for limitation as the allowable rolling loads for each work roll diameter. As a result, it can be seen that for the work roll diameter of 475 mm, desired rolling within the allowable rolling loads is possible by using five stands of rolling mills. For the work roll diameter of 340 mm, on the other hand, the five stands allow desired rolling with margins with respect to the allowable loads, and even four stands reducing one stand also enables desired rolling.
  • Line graphs represent the cumulative rolling reduction ratios after passage through each stand, shown with a solid line in the case of the present invention and with a dashed line in the case of the prior art.
  • the present invention provides cumulative rolling reduction ratios as high as about 10%, over figures of the prior art, the fact of which explicitly indicates that the number of stands can be reduced in the invention.
  • Fig. 12 shows comparative study results on the number of stands required for 1,180-MPa high strength steel strip rolling with the 340-mm diameter work rolls and with the prior-art 475-mm diameter work rolls.
  • the rolling is tried with five stands, when the rolling loads at each stand are controlled successively from the preceding stands to stay within a tolerance, the load at the final fifth stand will inevitably increase, which will end in desired rolling being infeasible. If the number of stands is increased to six, the loads at all stands can be controlled to stay within the tolerance, thus making rolling possible.
  • Bar graphs represent rolling reduction ratios in respective stands, which are shown by shading or masking in the case of the present invention, and in outline typeface form (non-shaded or non-masked) in the case of the prior art. These graphs indicate that the present invention provides 2-3 % higher rolling reduction ratios in each stand than the prior art does.
  • Line graphs represent the cumulative rolling reduction ratios after passage through each stand, shown with a solid line in the case of the present invention and with a dashed line in the case of the prior art. By comparison of both, upon passing through four stands, the present invention provides cumulative rolling reduction ratios as high as about 8%, over figures of the prior art, the fact of which explicitly indicates that the number of stands can be reduced in the invention.
  • the present invention enables rolling at reduction ratios higher than those obtainable in the prior art, and can even enjoy a great advantage in that the number of stands in a tandem rolling system can be reduced.
  • cold-rolling mill of the present invention may adopt either work roll drive or intermediate roll drive as the drive type for the rolling mill, work roll drive is preferred for the following reasons.
  • work roll drive directly drives the work rolls that roll the steel strip, this drive type is not likely to cause inter-roll slipping, compared with indirect drive of the intermediate rolls or the buck-up rolls.
  • work roll drive as viewed from a standpoint of tandem rolling system operation is described below. If strip breakage occurs, the broken steel strip may become jammed between the upper and lower work rolls or become wound around one work roll, thus bringing the work roll(s) into an abrupt stop. Once this state has arisen, work roll drive will immediately impose an overload to the drive system that transmits torque from an electric motor to a gearbox (a speed reducer or a reduction gear) first and then to spindles.
  • a gearbox a speed reducer or a reduction gear
  • Overload preventive devices provided midway in the drive system will then be activated to cut off the torque transmitted to the work rolls, and enable the rolling mill to be stopped.
  • overload preventive devices may be implemented using, for example, hydraulic torque limiters or pins, called shear pins, that will cut off torque in case of overloading.
  • work roll drive because of direct work roll drive, the rolling mill does not develop a driving tangential force likely to be exerted upon the work roll during intermediate roll drive. This characteristic prevents the work roll from deflecting in the horizontal direction. Since the rolling mill prevents the work roll from deflecting in the horizontal direction, the mill can display its original ability to control shape, this characteristic becoming a great advantage in product quality control.
  • intermediate roll drive since the intermediate rolls are usually designed to have a greater diameter than the work rolls, drive spindles can also be designed to have a diameter staying within the intermediate roll diameter range, and can therefore be manufactured to high enough strength against the torque required.
  • the intermediate roll may continue to rotate while slipping against the work roll, so these rolls are likely to suffer significant damage.
  • strip breakage occurs in a tandem rolling mill, adverse effects extend to more than one stand.
  • the driving tangential force acts upon the work roll, causing the work roll to deflect in the horizontal direction. The deflection of the work roll in the horizontal direction leads to the strip shape deteriorating, which in turn poses a big problem associated with product quality.
  • the present embodiment therefore, assigns priority to system operational advantages and employs work roll drive as the drive type for the rolling mill.
  • Fig. 14 is an external view that shows the drive system of the work roll drive type, the external view having been taken from a side of the rolling mill.
  • Fig. 15 is a schematic view showing a gear spindle in longitudinal section.
  • the cold-rolling mill 51 has a work roll drive unit 21 as its drive.
  • the work roll drive unit 21 includes a pair of upper and lower spindles 20, a gearbox 52, a coupling 53, and an electric motor 54, and a driving force of the motor 54 is transmitted to the upper and lower paired work rolls 2 while the driving speed is decreased or increased at a predetermined rate or not changed in the gearbox 52 and any vertical changes in position is absorbed by means of the upper and lower paired spindles 20.
  • the upper and lower paired spindles 20 each include, as shown in Fig. 15 , an intermediate shaft 61 and gear couplings 62, 63 provided at both ends of the intermediate shaft 61.
  • the gear couplings 62, 63 include respective sleeves 64, 65 with internal teeth 64a, 65a, respectively, formed therein, and respective Hubs 66, 67 with external teeth 66a, 67a, respectively, formed therein to mesh with the internal teeth 64a, 65a of the sleeves 64, 65.
  • axial recesses 68, 69 of the oval shape in cross-section are formed, and by inserting the respective axial ends of one work roll 2 and an output shaft of the gearbox 52 into the recesses 68, 69, the gear couplings 62, 63 are connected to the work roll 2 and the output shaft of the gearbox 52, respectively.
  • Figs. 16A and 16B show a universal joint for comparison purposes.
  • Fig. 16A is a schematic view showing the universal joint in longitudinal section
  • Fig. 16B is a sectional view thereof, taken along line A-A in Fig. 16A .
  • the universal joint 20A includes universal joint crosses 72, 73 each fitted with a cross joint 76 at one end of an intermediate shaft 71.
  • axial recesses 74 or 75 of the oval shape in cross-section are formed, and by inserting the respective axial ends of one work roll 2 and an output shaft of the gearbox 52 into the recesses 74, 75, the universal joint crosses 72, 73 are connected to the work roll 2 and the output shaft of the gearbox 52.
  • FIG. 17 A relationship between a maximum transmittable torque of a spindle of a work roll and an outer diameter of the spindle coupling in a one way tandem rolling mill in the prior art is shown in Fig. 17 .
  • a solid line denotes gear spindle data
  • a dashed line denotes universal joint data.
  • the gear spindle has an ability to transmit about 1.7 times the torque that the universal joint can.
  • the diameter of the work rolls is reduced and work roll drive is employed, and resultantly, diameters of the spindles are reduced, so the gear spindle is preferable that can transmit larger torque even if the spindle diameter is reduced.
  • Fig. 18A shows general layout of couplings of upper and lower paired spindles
  • Fig. 18B shows layout of couplings that enables spindle strength to be improved.
  • Single-dotted lines in the figures each denote a central position of a gear of one gear coupling.
  • gear couplings of the upper and lower paired spindles 20, located closer to the rolling mill are constructed so that as shown in Fig. 18A , axial positions of the upper and lower gear couplings 62 are vertically matched so that the central positions of the gears are vertically aligned.
  • gear couplings in the present embodiment are constructed such that as shown in Fig. 18B , the positions of gear couplings 62A of the upper and lower paired spindles 20A are vertically deviated into a staggered manner so that the central positions of the gears are vertically misaligned.
  • Fig. 19A shows a work roll drive unit provided with hydraulic torque limiters of a spindle type as the overload preventive devices.
  • the work roll drive unit 21A includes the hydraulic torque limiters 85 between the gear couplings 63 of the upper and lower paired spindles 20 and upper and lower output shafts of the gearbox 52, the gear couplings 63 being connected to the upper and lower output shafts of the gearbox 52 via the hydraulic torque limiters 85.
  • Fig. 19B shows a work roll drive unit provided with a hydraulic torque limiter of a coupling type as an overload preventive device.
  • the work roll drive unit 21B includes the hydraulic torque limiter 86 between an input shaft of the gearbox 52 and an output shaft of the motor 54.
  • the input shaft of the gearbox 52 is connected to the output shaft of the motor 54 via the coupling 53 and the hydraulic torque limiter 86.
  • Fig. 19C shows a configuration in which a coupling for connecting an input shaft of a gearbox to an electric motor is provided with a shear pin as an overload preventive device.
  • the coupling 53 has coupling half-bodies 53c, 53d that each include a flange portion 53a or 53b, and the shear pin 87 is provided on the flange portion 53a, 53b.
  • the overload preventive devices shown in Figs. 19A, 19B, 19C are effective for protecting the spindles under the situation that the strength of the spindles themselves has to be reduced along with the reduction in the diameter of the work rolls.
  • the overload preventive devices may instead be applied to the universal joints.
  • the rolling mill of the present embodiment is provided with the intermediate roll offset devices 19 in the roll shifting devices 23 (see Fig. 3 ).
  • the intermediate roll offset devices 19 are once again described below.
  • one intermediate roll offset device 19 is built in the shift block 12 of each roll shifting device 23.
  • a hydraulic cylinder, a screw jack, a wedge plate, or the like would be useable to actuate the intermediate roll offset device 19.
  • the intermediate roll offset device 19 contains the intermediate roll bending device 11 that further provides the intermediate roll with vertical bending.
  • the intermediate roll 3, the shift block 12, and the intermediate roll offset device 19 are constructed to shift in a longitudinal direction of the roll at the same time.
  • the intermediate roll offset device 19 is actuated in the rolling direction by the hydraulic cylinder, the screw jack, the wedge plate, or other means, and an amount of the actuation is detected by a position detector.
  • the upper and lower intermediate roll offset devices 19 in each shifting device 23 are controlled independently or simultaneously.
  • the offset device in the present invention is of a layout in which, even if the intermediate roll 3 becomes offset in the rolling direction, the vertical roll-bending device 11 is fixed at a position to always maintain a constant distance "L1" from a central portion of the intermediate roll 3.
  • the offset device is also of a layout in which the intermediate roll offset device 19 and the bearing housing 9 have respective central portions matched in the longitudinal direction of the roll, thereby avoiding an unbalanced load upon an internal bearing of the bearing housing 9.
  • this offset device may be replaced by a work roll offset device.
  • this work roll offset device contains a roll-bending device and can use either a hydraulic cylinder, a screw jack, a wedge plate, or other means, as its actuator.
  • the work roll offset device has its amount of actuation detected by a position detector.
  • the present invention concerns reducing the diameter of the work rolls. It is generally known that reducing the diameter of a work roll makes the work roll easily deflect in a horizontal direction. As described previously herein, it is effective from a viewpoint of stable system operation to take any appropriate measures necessary to minimize such horizontal deflection.
  • the forces (a), (b) and (c) are determined by the rolling conditions used in the actual operation, and the values of these forces can be perceived, but are difficult to intentionally change.
  • the remaining force (d) is determined by the rolling load and the offset, and the rolling load is difficult to intentionally change as with forces (a) to (c), but the force (d) is the type of a horizontal force whose value can be changed if the offset can be changed.
  • the rolling mill with an offset device and make operable the horizontal force acting upon the work roll. More specifically, the horizontal force acting upon the work roll can be made nil in theory by deriving the value of the resultant of forces (a), (b), (c) and the rolling load beforehand and then determining a magnitude of the offset such that force (d) and the resultant of forces (a), (b), (c) become balanced with each other.
  • the offset device can use one of two major kinds of offsetting methods.
  • Figs. 20A and 20B show the two kinds of offsetting methods.
  • offsetting is to shift the center of the work roll and that of the intermediate roll in relative form. This can be implemented by, as shown in Fig. 20A , moving the work roll in the horizontal direction and thus providing the offset, or by as shown in Fig. 20B , moving the intermediate roll in the horizontal direction and thus providing the offset.
  • intermediate roll drive has an advantage of causing no such inconveniences. That is to say:
  • the cold-rolling mill of the present invention can employ either work roll offsetting or intermediate roll offsetting, but in consideration of the comparison results as described above, intermediate roll offsetting is preferred.
  • Fig. 21 is an external view that shows a drive system of an intermediate roll drive type, the external view having been taken from a side of the rolling mill.
  • a cold-rolling mill 51A has substantially the same roll configuration as that of the embodiment shown in Figs. 1 to 3 .
  • the cold-rolling mill 51A in the present embodiment includes an intermediate roll drive unit 22 as a drive for the mill.
  • the intermediate roll drive unit 22 includes a pair of upper and lower spindles 90, a gearbox (reduction gear) 94, a coupling 95, and an electric motor 96, with a driving force of the motor 96 being decremented or incremented at a predetermined rate in the gearbox 94 or causing no change in speed, and being transmitted to upper and lower paired intermediate rolls 3 while absorbing any vertical changes in position by means of the upper and lower paired spindles 90.
  • the upper and lower paired spindles 90 are, for example, universal joints described in Figs. 14A and 14B , and the spindles each including an intermediate shaft 91 and universal joint crosses 92, 93 provided at both ends of the intermediate shaft 91.
  • the universal joints 90 are advantageous in that they are less expensive than gear spindles.
  • the cold-rolling mill 51A includes a roll offset device adapted to offset either one of the work rolls 2 and the intermediate rolls 3 relative to axes of the other rolls in the entry or exit side in a rolling direction.
  • This roll offset device is preferably an intermediate roll offset device, as with that of the embodiment shown in Figs. 1 to 3 .
  • the roll offset device may however be a work roll offset device.
  • Fig. 22 is a diagram showing an embodiment of a tandem rolling system constructed using a cold-rolling mill of the present invention.
  • the tandem rolling system includes a row of five stands of rolling mills 100a to 100e, all of which include one of the above-described cold-rolling mills of the present invention, for example the cold-rolling mill 51 shown in Fig. 14 .
  • high productivity as of the conventional tandem rolling system can be maintained and without increasing the stands, rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • the rolling mills 100a-100e may be of a configuration including at least one stand of cold-rolling mill of the present invention, and even in this case, the rolling system can implement rolling at high reduction ratios compared with those of a rolling system whose rolling mills are all prior-art ones.
  • Fig. 23 is a diagram showing an embodiment of a reversing rolling system constructed using a cold-rolling mill of the present invention.
  • the reversing rolling system includes a single stand of reversing rolling mill 110, with coiling/uncoiling devices 111, 112 arranged at entry/exit sides of the rolling mill 110 and with deflector rolls 113, 114 further arranged between the coiling/uncoiling devices 111, 112.
  • the rolling mill 110 includes one of the above-described cold-rolling mills of the present invention, for example the cold-rolling mill 51 shown in Fig. 14 .
  • the reversing rolling system may have two stands of rolling mills, and at least one of the two stands may be one of the cold-rolling mills of the present invention, for example the cold-rolling mill 51, whereby the rolling system will be able to implement rolling at high reduction ratios compared with those of a rolling system whose rolling mills are all prior-art ones.
  • Fig. 24 is a diagram showing an example of modifying a tandem rolling system using a cold-rolling mill of the present invention.
  • the unmodified tandem rolling system includes a row of five stands of prior-art rolling mills 120a to 120e.
  • the rolling mill 120e of a final stand is changed into one of the cold-rolling mills of the present invention, for example the cold-rolling mill 51.
  • This change may be performed by replacing one stand of rolling mill or partly modifying one stand of rolling mill.
  • high productivity as of the tandem rolling system before modified can be maintained and without increasing the number of stands, rolling of a harder steel strip than the system before modified and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • the number of the modified rolling mills may be two stands or more.
  • Fig. 25 is a diagram showing another example of modifying a tandem rolling system using a cold-rolling mill of the present invention.
  • the unmodified tandem rolling system includes a row of five stands of prior-art rolling mills 120a to 120e.
  • one of the cold-rolling mills of the present invention for example the cold-rolling mill 51, is additionally installed at an exit side of the row of rolling mills.
  • high productivity as of the tandem rolling system before modified can be maintained and rolling of a harder steel strip than the system before modified and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.
  • the position at which the rolling mill of the present invention is additionally installed may instead be an entry side or both sides of the rolling mill array.
  • reversing rolling system shown in Fig. 23 can be modified similarly to a tandem rolling system, by changing the reversing cold-rolling mill 110 into one of the cold-rolling mills of the present invention.
  • rolling of a harder steel strip than ever and rolling of a steel strip of the same hardness as before at a higher reduction ratio can be performed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
EP12184124.1A 2011-09-20 2012-09-12 Cold-rolling mill, tandem rolling system, reversing rolling system, modification method of rolling system, and operating method of cold-rolling mill Active EP2572808B1 (en)

Applications Claiming Priority (1)

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PCT/JP2011/071391 WO2013042204A1 (ja) 2011-09-20 2011-09-20 冷間圧延機、タンデム圧延設備、可逆圧延設備、圧延設備の改造方法および冷間圧延機の運転方法

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EP2572808B1 true EP2572808B1 (en) 2014-05-21

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JP (1) JP4928653B1 (ja)
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CN103639202A (zh) * 2013-11-29 2014-03-19 四川省川威集团有限公司 轧机
DE102014226326B4 (de) * 2014-12-17 2017-06-08 Achenbach Buschhütten GmbH & Co. KG Walzgerüst mit Verschiebeeinrichtung
JP6470134B2 (ja) 2015-07-08 2019-02-13 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機および圧延方法
JP6354718B2 (ja) * 2015-09-25 2018-07-11 Ｊｆｅスチール株式会社 冷間タンデム圧延機及び高強度冷延鋼板の製造方法
DE102019200005A1 (de) 2019-01-02 2020-07-02 Sms Group Gmbh Walzvorrichtung
JP6992783B2 (ja) * 2019-03-28 2022-01-13 Ｊｆｅスチール株式会社 タンデム圧延設備におけるロールオフセット量の上限値の設定方法及び設定装置
JP7313768B2 (ja) * 2019-05-23 2023-07-25 スチールプランテック株式会社 圧延機、並びに圧延方法及びワークロールの運用方法
EP4072747B1 (de) * 2019-12-11 2024-02-07 SMS Group GmbH Warmwalzgerüst für ein warmwalzwerk und zum herstellen eines metallenen flachprodukts, warmwalzwerk sowie verfahren zum betreiben eines warmwalzwerks
EP4019156B1 (en) * 2020-04-07 2023-12-13 Primetals Technologies Japan, Ltd. Rolling mill, method for manufacturing rolling mill, and method for modifying rolling mill
US20220118492A1 (en) * 2020-10-21 2022-04-21 Digi Drives Private Limited Cold rolling mill
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EP2572808A1 (en) 2013-03-27
WO2013042204A1 (ja) 2013-03-28
KR20130054965A (ko) 2013-05-27
JPWO2013042204A1 (ja) 2015-03-26
BR112012027654B1 (pt) 2018-03-13
JP4928653B1 (ja) 2012-05-09
CN103118813A (zh) 2013-05-22
CN103118813B (zh) 2016-01-20
BR112012027654A2 (pt) 2016-08-16
KR101424375B1 (ko) 2014-07-31

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