EP2277638B1 - Laminoir et laminoir tandem le comprenant - Google Patents

Laminoir et laminoir tandem le comprenant Download PDF

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Publication number
EP2277638B1
EP2277638B1 EP20100007223 EP10007223A EP2277638B1 EP 2277638 B1 EP2277638 B1 EP 2277638B1 EP 20100007223 EP20100007223 EP 20100007223 EP 10007223 A EP10007223 A EP 10007223A EP 2277638 B1 EP2277638 B1 EP 2277638B1
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EP
European Patent Office
Prior art keywords
roll
rolls
rolling mill
work
work rolls
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Not-in-force
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EP20100007223
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German (de)
English (en)
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EP2277638A1 (fr
Inventor
Takashi Norikura
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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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • 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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • B21B2031/025—Shifting the stand in or against the rolling direction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
    • B21B2203/02—Backlash elimination
    • 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
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • B21B31/028—Prestressing of rolls or roll mountings in stand frames
    • 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
    • B21B31/07—Adaptation of roll neck bearings
    • 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
    • B21B31/22—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal
    • B21B31/30—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal by wedges or their equivalent
    • 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

  • 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.
  • DE 103 56 591 A1 discloses a four-high rolling mill with the feature in the pre-characterizing portion of claim 2.
  • a six-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 rolls, 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.
  • 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 present invention provides a six-high rolling mill and a four-high rolling mill as defined in claims 1 and 2 further advantageous features are set out in the dependent claims.
  • 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 at least two bearings are provided on each of the operating side and the drive side of each of the paired upper and lower work rolls, and the restraining means for restraining the bearings are provided on the inlet side, or the outlet side, or both of the inlet side and the outlet side, of the bearings to restrain the horizontal displacement of each of the bearings.
  • the diameter of the work roll can be rendered even smaller.
  • 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 a sectional view taken along line III-III in Fig. 2 .
  • Fig. 4 is an explanation drawing of a taper wedge liner.
  • 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 7a, 7b via 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 6a, 6b.
  • Bearing housings 13a to 13d and 13e to 13h are mounted on roll neck portions of the paired upper and lower work rolls 2 via bearings (not shown). These bearing housings 13a to 13h are pressed against projection blocks 19a, 19c on their outlet side by backlash elimination cylinders 18a to 18d and 18e to 18h provided on projection blocks 19b, 19d on the inlet side of the bearing housings 13a to 13h, whereby the horizontal displacement of each of the bearings is restrained.
  • the projection blocks 19a, 19b, 19c, 19d are equipped with bending cylinders 14a to 14d and 14e to 14h for imparting roll bending.
  • roll bending is imparted to the work rolls 2 to make the modification of the strip shape possible.
  • the backlash elimination cylinders 18a to 18d and 18e to 18h are provided on the inlet side, but may be provided on the outlet side or on both of the inlet side and the outlet side.
  • the backlash elimination cylinders 18a to 18d and 18e to 18h are shown, but worm jacks or taper wedge lines for operating taper wedges by hydraulic cylinders, etc. may be used.
  • the motions of the taper wedge liner will be described by reference to Fig. 4 .
  • a taper wedge 21 is pushed in horizontally leftwardly in the drawing by a hydraulic cylinder 20
  • a taper liner 22 slides over the wedge portion, because its horizontal movement is restrained by a stopper 23.
  • the taper liner 22 moves vertically.
  • the bearing housings 13a to 13d and 13e to 13h can be restrained.
  • rolling load is imparted by the hydraulic cylinders 6a, 6b, and rolling torque is transmitted to the work rolls 2 by spindles (not shown).
  • 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 plate width of the strip 1.
  • rolling torque is transmitted to the work rolls 2 by the spindles (not shown) via the intermediate rolls 3.
  • 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.
  • two of the bearing housings, 13a to 13d and 13e to 13h are mounted on each of the roll neck portions of the paired upper and lower work rolls 2.
  • These bearing housings 13a to 13h are pressed against the outlet-side projection blocks 19a, 19c by the inlet-side backlash elimination cylinders 18a to 18h, whereby the horizontal displacement of each of the bearings is restrained.
  • deflection of the work roll 2 which occurs under the tangential force of the intermediate roll drive or the inlet side-outlet side differential tension of the work roll drive, can be suppressed.
  • the diameter of the work roll can be rendered small.
  • the work rolls 2 of a smaller diameter can be rendered usable for the purpose of rolling a hard material.
  • edge drops can be reduced, surface gloss can be improved, and the strip 1 with high productivity and of high product quality can be obtained.
  • the present embodiment is characterized in that a material having a high modulus of longitudinal elasticity is used for the paired upper and lower work rolls 2 in the above-described Embodiment 1.
  • a material having a 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.
  • two of the bearing housings, 13a to 13h are mounted on each of the roll neck portions of the paired upper and lower work rolls 2.
  • the respective two of the bearing housings 13a to 13h are restrained by the backlash elimination cylinders 18a to 18h from being displaced in the horizontal direction.
  • the work roll 2 of the material having a high modulus of longitudinal elasticity such as a cemented carbide or a ceramic material, is used.
  • the diameter of the work roll can be rendered further smaller, and the strip 1 with high productivity and of high product quality can be obtained in the rolling of a hard material.
  • Embodiment 1 two of the bearing housings, 13a to 13h, are mounted on each of the roll neck portions of the paired upper and lower work rolls.
  • the respective two of the bearing housings 13a to 13h are restrained by the backlash elimination cylinders 18a to 18h from being displaced in the horizontal direction.
  • Deflection ⁇ f in the horizontal direction of the work roll in this case is expressed by the following equation (3), where Df represents the diameter of the work roll of Embodiment 1, and If represents the second moment of area of the diameter of the work roll of Embodiment 1.
  • Patent Document 2 describes a method of pressing only one each of the bearings on the operating side and the drive side by pressing cylinders. According to this method, only the one bearing is pressed. Thus, the supporting conditions for fixed support for the roll ends, shown in Fig. 7B , are not established. The supporting conditions for simple support for the roll ends, shown in Fig. 7A , apply.
  • the minimum roll diameter of the work roll is intermediate between the minimum diameter upper limit Dmax1 and the minimum diameter lower limit Dmin1, which are expressed by the following equations based on the above equation (4):
  • Minimum diameter upper limit Dmax ⁇ 1 D ⁇ 4 ⁇ max ⁇ B / 5 1 / 4
  • D4max is a minimum diameter upper limit of a conventional work roll with a strip width of 1,300 mm: 380 mm
  • B is a plate width (mm)/1,300 mm.
  • the minimum diameter upper limit Dmax1 per strip width in Embodiment 1 is shown in Fig. 8 .
  • Minimum diameter lower limit Dmin ⁇ 1 D ⁇ 4 ⁇ min ⁇ B / 5 1 / 4
  • D4min is a minimum diameter lower limit of the conventional work roll with the strip width of 1,300 mm: 180 mm.
  • the minimum diameter lower limit Dmin1 per strip width in Embodiment 1 is shown in Fig. 9 .
  • Embodiment 2 two of the bearing housings, 13a to 13h, are mounted on each of the roll neck portions of the paired upper and lower work rolls.
  • the respective two of the bearing housings 13a to 13h are restrained by the backlash elimination cylinders 18a to 18h from being displaced in the horizontal direction.
  • the supporting conditions for fixed support shown in Fig. 7B apply.
  • the material having the 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 or a ceramic.
  • Deflection ⁇ fr in the horizontal direction of the work roll 2 in this case is expressed by the following equation (7), where Dfr represents the diameter of the work roll 2 of Embodiment 2, Ifr represents the second moment of area of the diameter of the work roll of Embodiment 2, and Er represents the modulus of longitudinal elasticity of the material for the work roll of Embodiment 2.
  • ⁇ fr F ⁇ L 4 / 384 ⁇ Er ⁇ Ifr
  • Ifr ⁇ ⁇ Dfr 4 /64
  • Dfr Dc / ( 5 ⁇ K ⁇ ) 1 / 4
  • the minimum roll diameter of the work roll is intermediate between the minimum diameter upper limit Dmax2 and the minimum diameter lower limit Dmin2, which are expressed by the following equations:
  • Minimum diameter upper limit Dmax ⁇ 2 D ⁇ 4 ⁇ max ⁇ B / 5 ⁇ K 1 / 4
  • D4max is a minimum diameter upper limit of a conventional work roll with a strip width of 1,300 mm: 380 mm
  • B is a strip width (mm)/1,300 mm
  • K is a ratio of the high longitudinal modulus material to a conventional material (modulus of longitudinal elasticity of the high longitudinal modulus material/modulus of longitudinal elasticity of the conventional material (21,000 kg/mm 2 ))
  • the minimum diameter upper limit Dmax2 per strip width in Embodiment 2 is shown in Fig.
  • K 2.5, provided that the material for the work roll was a cemented carbide.
  • Minimum diameter lower limit Dmin ⁇ 2 D ⁇ 4 ⁇ min ⁇ B / 5 ⁇ K 1 / 4 where D4min is a minimum diameter lower limit of the conventional work roll with the strip width of 1,300 mm: 180 mm
  • the minimum diameter lower limit Dmin2 per strip width in Embodiment 2 is shown in Fig. 9 .
  • K 2.5, provided that the material for the work roll was the cemented carbide.
  • the work rolls 2 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. 11A ).
  • 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. 12A ).
  • 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 do not show a structure for shift 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 3.
  • the paired upper and lower work rolls 2 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.
  • the roll neck portions of the paired upper and lower work rolls 2 are mounted with two bearings each (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. 13 describes the mill of Fig. 1 as a representative, but the mill with the variably offset work rolls in Figs. 11A, 11B or the mill with the variably offset intermediate rolls in Figs. 12A, 12B may be used.
  • Embodiments 1 and 2 show 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 at shape control is lower than in the six-high mill having the roll shoulders 3a, but is higher than in the four-high mill.
  • the aforementioned work roll shift shown in Fig. 13 may be applied to this mill.
  • Fig. 14 is a front sectional view of a four-high mill showing Embodiment 3 of the present invention.
  • Fig. 15 is a sectional view taken along line XV-XV in Fig. 14 .
  • Fig. 16 is an explanation drawing of a work roll shift of a four-high mill showing an applied example of Embodiment 3.
  • 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 Embodiments 1 and 2, as shown in Figs. 14 and 15 .
  • the strip 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 the 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 at shape control is higher than in the four-high mill shown in Fig. 16 .
  • 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. 17 , 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. 17 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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  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
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Claims (6)

  1. Laminoir sexto comprenant des cylindres de travail (2) supérieur et inférieur en tant que paire pour laminer une bande de métal (1), des cylindres intermédiaires (3) supérieur et inférieur en tant que paire pour supporter les cylindres de travail, et des cylindres d'appui (4) supérieur et inférieur en tant que paire pour supporter les cylindres intermédiaires supérieur et inférieur, le laminoir sexto n'ayant pas de cylindres de support, qui supportent une force horizontale exercée sur les cylindres de travail, à l'intérieur d'une largeur de bande de laminage des cylindres de travail, dans lequel
    au moins deux paliers (13a, 13e, 13b, 13f, 13c, 13g, 13d, 13h) sont prévus sur chacun d'un côté de fonctionnement et d'un côté d'entraînement de chacun des cylindres de travail supérieur et inférieur appariés, et
    une pluralité de moyens de retenue (18a, 18e, 18b, 18f, 18c, 18g, 18d, 18h), chacun pour retenir un palier correspondant parmi les paliers, sont prévus d'un côté d'entrée, ou d'un côté de sortie, ou à la fois du côté d'entrée et du côté de sortie, des paliers pour empêcher un déplacement horizontal de chaque palier correspondant.
  2. Laminoir quarto comprenant des cylindres de travail (2) supérieur et inférieur en tant que paire pour laminer une bande de métal (1), et des cylindres d'appui (4) supérieur et inférieur en tant que paire pour supporter les cylindres de travail, le laminoir quarto n'ayant pas de cylindres de support, qui supportent une force horizontale exercée sur les cylindres de travail, à l'intérieur d'une largeur de bande de laminage des cylindres de travail, dans lequel
    au moins deux paliers (13a, 13e, 13b, 13f, 13c, 13g, 13d, 13h) sont prévus sur chacun d'un côté de fonctionnement et d'un côté d'entraînement de chacun des cylindres de travail supérieur et inférieur appariés, et
    caractérisé en ce que
    une pluralité de moyens de retenue (18a, 18e, 18b, 18f, 18c, 18g, 18d, 18h), chacun pour retenir un palier correspondant parmi les paliers, sont prévus d'un côté d'entrée, ou d'un côté de sortie, ou à la fois du côté d'entrée et du côté de sortie, des paliers pour empêcher un déplacement horizontal de chaque palier correspondant.
  3. Laminoir selon la revendication 1 ou 2, dans lequel
    un diamètre de cylindre minimum du cylindre de travail est compris entre une limite supérieure de diamètre minimum Dmax1 et une limite inférieure de diamètre minimum Dmin1, qui sont exprimées par les équations suivantes : Dmin ⁢ 1 = D ⁢ 4 ⁢ min x B / 5 1 / 4 ,
    Figure imgb0025
    où D4max est égal à 380 mm et B est une largeur de bande en mm/1300 mm ; Dmin ⁢ 1 = D ⁢ 4 ⁢ min x B / 5 1 / 4 ,
    Figure imgb0026
    où D4min est égal à 180 mm.
  4. Laminoir selon la revendication 1 ou 2, dans lequel
    un matériau ayant un module élevé d'élasticité longitudinale est utilisé pour le cylindre de travail, et
    un diamètre de cylindre minimum du cylindre de travail est compris entre une limite supérieure de diamètre minimum Dmax2 et une limite inférieure de diamètre minimum Dmin2, qui sont exprimées par les équations suivantes : Dmax ⁢ 2 = D ⁢ 4 ⁢ max x B / 5 x K 1 / 4 ,
    Figure imgb0027
    où D4max est égal à 380 mm et B est une largeur de bande en mm/1300 mm, et K est un rapport entre le matériau à module longitudinal élevé et un matériau classique, c'est-à-dire le rapport entre le module d'élasticité longitudinale du matériau à module longitudinal élevé et le module d'élasticité longitudinale du matériau classique de 21000 kg/mm2 ; Dmin ⁢ 2 = D ⁢ 4 ⁢ min x B / 5 x K 1 / 4 ,
    Figure imgb0028
    où D4min est égal à 180 mm.
  5. Laminoir selon la revendication 4, dans lequel
    le rapport entre le matériau à module longitudinal élevé et le matériau classique, c'est-à-dire le rapport des modules longitudinaux, K, est de 1,2 à 3,0.
  6. Laminoir tandem comprenant une pluralité de cages de laminoir agencées dans celui-ci, dans lequel
    le laminoir selon l'une quelconque des revendications 1 à 5 est prévu en tant que l'une des cages.
EP20100007223 2009-07-22 2010-07-13 Laminoir et laminoir tandem le comprenant Not-in-force EP2277638B1 (fr)

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JP2009170816A JP5491090B2 (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

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EP2277638B1 true EP2277638B1 (fr) 2013-03-20

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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
JP4928653B1 (ja) * 2011-09-20 2012-05-09 三菱日立製鉄機械株式会社 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
ITMI20131078A1 (it) * 2013-06-27 2014-12-28 Sms Innse Spa Dispositivo di bilanciamento per un laminatoio
CN104384198B (zh) * 2014-10-14 2016-10-05 江苏甬金金属科技有限公司 一种二十辊中间辊推辊装置
DE102017205325A1 (de) * 2017-03-29 2018-10-04 Robert Bosch Gmbh Verfahren und Steuereinheit zum Betrieb eines Partikelfilters
WO2019230850A1 (fr) * 2018-05-29 2019-12-05 日本製鉄株式会社 Laminoir et procédé pour le réglage d'un laminoir
JP6992032B2 (ja) * 2019-10-25 2022-01-13 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機
JP2023510090A (ja) * 2019-12-11 2023-03-13 エス・エム・エス・グループ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 熱間圧延機のため、および、金属の平板製品の製造のための熱間圧延スタンド、熱間圧延機、並びに、熱間圧延機の作動のための方法
EP4094857A1 (fr) 2021-05-28 2022-11-30 Primetals Technologies Austria GmbH Stabilisation des rouleaux de travail et d'appui d'une cage de laminoir lors du laminage à chaud d'un produit laminé en une bande dans la cage de laminoir

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CN101961728A (zh) 2011-02-02
EP2277638A1 (fr) 2011-01-26

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