EP2277637B1 - Rolling mill and tandem rolling mill having the same - Google Patents
Rolling mill and tandem rolling mill having the same Download PDFInfo
- Publication number
- EP2277637B1 EP2277637B1 EP10007529A EP10007529A EP2277637B1 EP 2277637 B1 EP2277637 B1 EP 2277637B1 EP 10007529 A EP10007529 A EP 10007529A EP 10007529 A EP10007529 A EP 10007529A EP 2277637 B1 EP2277637 B1 EP 2277637B1
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- EP
- European Patent Office
- Prior art keywords
- rolling mill
- roll
- rolls
- work
- work rolls
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- 238000005096 rolling process Methods 0.000 title claims description 69
- 239000000463 material Substances 0.000 claims description 52
- 229910052751 metal Inorganic materials 0.000 claims description 3
- 239000002184 metal Substances 0.000 claims description 3
- 230000003247 decreasing effect Effects 0.000 description 10
- 238000013000 roll bending Methods 0.000 description 6
- 229910000831 Steel Inorganic materials 0.000 description 4
- 238000005452 bending Methods 0.000 description 4
- 239000002131 composite material Substances 0.000 description 4
- 239000010959 steel Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 239000010410 layer Substances 0.000 description 3
- 239000002344 surface layer Substances 0.000 description 3
- 230000003292 diminished effect Effects 0.000 description 2
- 206010041662 Splinter Diseases 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 238000005097 cold rolling Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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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 present invention provides a rolling mill as defined in claim 1.
- 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.
- a still further example 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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Description
- 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.
- In a conventional so-called intermediate roll-drive six-high rolling mill (hereinafter referred to as a six-high 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. According to Non-Patent
Document 1, for example, this value is 180 mm to 380 mm in the case of a 4-feet width material upon the intermediate roll drive. - With work 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. Within the range of the permissible strength of the drive system, therefore, 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. With 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. -
- [Patent Document 1]
JP-A-5-50109 - [Patent Document 2]
JP-A-60-238021 - [Non-Patent Literature]
- [Non-Patent Document 1] "Industrial Machinery", May Issue, 1991 (pp. 56-60)
- To meet a recent demand, an attempt has been made to roll a special steel, such as a harder stainless steel, by a six-high mill or four-high mill having no support rolls inside the rollable strip width of the work rolls. This attempt has posed a problem such that the aforementioned work roll diameter is too large and imposes a heavy load, thus failing to ensure a necessary reduction in thickness by rolling, and a problem such as poor gloss.
- On the other hand, 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.
-
DE 102 08 389 A1 discloses a rolling mill with the features of the preamble ofpresent claim 1. - To solve the above-mentioned problems, the present invention provides a rolling mill as defined in
claim 1. An example provides a six-high rolling mill including upper and lower work rolls as a pair for rolling a metal strip, upper and lower intermediate rolls as a pair for supporting the work rolls, and upper and lower back-up rolls as a pair for supporting the upper and lower intermediate rolls as the pair, the six-high rolling mill having no supporting rolls inside and outside a rollable strip width of the work rolls, characterized in that
the work rolls are driven,
a material having a high modulus of longitudinal elasticity is used for the work roll, and
a minimum roll diameter of the work roll is intermediate between a minimum diameter upper limit Dmax1 and a minimum diameter lower limit Dmin1, and these parameters are expressed by the following equations:
where 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, and
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/mm2))
where D4min is a minimum diameter lower limit of the conventional work roll with the strip width of 1,300 mm: 180 mm. - Another example provides a four-high rolling mill including upper and lower work rolls as a pair for rolling a metal strip, and upper and lower back-up rolls as a pair for supporting the work rolls, the four-high rolling mill having no supporting rolls inside and outside a rollable strip width of the work rolls, characterized in that
the work rolls are driven,
a material having a high modulus of longitudinal elasticity is used for the work roll, and
a minimum roll diameter of the work roll is intermediate between a minimum diameter upper limit Dmax1 and a minimum diameter lower limit Dmin1, and these parameters are expressed by the following equations:
where 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, and
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/mm2))
where D4min is a minimum diameter lower limit of the conventional work roll with the strip width of 1,300 mm: 180 mm. - 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.
- A still further example 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.
- According to the features of the present invention, the high longitudinal modulus material is used for the work roll. By so doing, 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. Furthermore, 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] Fig. 1 is a front sectional view of a six-highmill showing Embodiment 1 of the present invention. - [
Fig. 2] Fig. 2 is a sectional view taken along line II-II inFig. 1 . - [
Fig. 3] Fig. 3 is an explanation drawing of a composite roll. - [
Fig. 4] Fig. 4 is an explanation drawing of inlet side-outlet side differential tension. - [
Fig. 5] Fig. 5 is an explanation drawing of the deflection of a work roll. - [
Fig. 6] Fig. 6 is a graph showing a comparison between the work roll minimum diameter upper limits Dmax' s inEmbodiment 1 and a conventional example. - [
Fig. 7] Fig. 7 is a graph showing a comparison between the work roll minimum diameter lower limits Dmin's in them. - [
Fig. 8A] Fig. 8A is an explanation drawing of a work roll offset showing an applied example ofEmbodiment 1. - [
Fig. 8B] Fig. 8B is an explanation drawing of load imposed on the work roll in the applied example. - [
Fig. 9A] Fig. 9A is an explanation drawing of an intermediate roll offset showing another applied example ofEmbodiment 1. - [
Fig. 9B] Fig. 9B is an explanation drawing of load imposed on the work roll in the another applied example. - [
Fig. 10] Fig. 10 is an explanation drawing of a work roll shift of a six-high mill showing still another applied example ofEmbodiment 1. - [
Fig. 11] Fig. 11 is a front sectional view of a four-highmill showing Embodiment 2 of the present invention. - [
Fig. 12] Fig. 12 is a sectional view taken along line XII-XII inFig. 11 . - [
Fig. 13] Fig. 13 is an explanation drawing of a work roll shift of a four-high mill showing an applied example ofEmbodiment 2. - [
Fig. 14] Fig. 14 is an explanation drawing of the application of the present invention to a tandem rolling mill. - A rolling mill and a tandem rolling mill equipped therewith, according to the present invention, will be described in detail by the following embodiments using drawings.
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Fig. 1 is a front sectional view of a six-highmill showing Embodiment 1 of the present invention.Fig. 2 is a sectional view taken along line II-II inFig. 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 inEmbodiment 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. 8A is an explanation drawing of a work roll offset showing an applied example ofEmbodiment 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 ofEmbodiment 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 ofEmbodiment 1. - As shown in
Figs. 1 and2 , astrip 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 lowerintermediate rolls 3 as a pair. These paired upper and lowerintermediate rolls 3 are in contact with, and supported by, upper and lower back-uprolls 4 as a pair. - The upper back-up
roll 4 is supported by bearinghousings housings line adjusting devices line adjusting devices - The lower back-up
roll 4 is supported by bearinghousings housings housings - 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/mm2), or a ceramic (modulus of longitudinal elasticity: 31,000 kg/mm2). Special forged steel (modulus of longitudinal elasticity: 21,000 kg/mm2) or the like has been used as a conventional material.
- It is preferred that the ratio of the high longitudinal modulus material to the conventional material (longitudinal modulus ratio), K, be set at 1.2 to 3.0.
- As shown in
Fig. 3 , moreover, a roll composite material using a high longitudinal modulus material as a rollsurface layer material 2A and a conventional material as a rollinternal 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. - The equivalent modulus of longitudinal elasticity, Ee, is expressed by the following equation (1)
where d2 is the outer diameter of the rollsurface layer material 2A, E2 is the modulus of longitudinal elasticity of the rollsurface layer material 2A, d1 is the outer diameter of the rollinternal layer material 2B, and E1 is the modulus of longitudinal elasticity of the rollinternal layer material 2B. - Further, 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 bearinghousings 13a to 13d are furnished with bendingcylinders 14a to 14d for imparting roll bending. By so doing, roll bending is imparted to the work rolls 2. - Here, rolling load is imparted by the
hydraulic cylinders intermediate rolls 3 haveroll 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 thestrip 1. - The paired upper and lower
intermediate rolls 3 are supported by bearinghousings 15a to 15d via bearings (not shown). The paired upper and lowerintermediate rolls 3 are axially movable by shifting devices (not shown) via the drive-side bearing housings housings 15a to 15d are furnished with bendingcylinders 16a to 16d for imparting roll bending. By so doing, roll bending is imparted to the intermediate rolls 3. - Deflection of the work roll by the rolling mill inlet side-outlet side differential tension will be described using
Fig. 4 and Fig. 5 . - As shown in
Fig. 4 , if the inlet-side tension of the rolling mill is designated as Tb, and the outlet-side tension of the rolling mill is designated as Tf, differential tension which is the difference between Tb and Tf is exerted on the work rolls 2. Since the number of the bearings for the work roll is one each on the operating side and on the drive side, the supporting conditions for simple support shown inFig. 5 apply. Horizontal deflection δ s of the work roll in this case is expressed by the following equation (2), where F represents the differential tension per unit length, L represents the support spacing, Dc represents the diameter of theconventional work roll 2, Ic represents the second moment of area of the conventional work roll diameter, and Ec represents the modulus of longitudinal elasticity (21,000 kg/mm2) of the material (special forged steel) for the conventional work roll:
where - A material with a high modulus of longitudinal elasticity is used for the paired upper and lower work rolls 2. Deflection δ r in the horizontal direction of the
work roll 2 in this case is expressed by the following equation (3), where Dr represents the diameter of thework roll 2 ofEmbodiment 1, Ir represents the second moment of area of the diameter of the work roll ofEmbodiment 1, and Er represents the modulus of longitudinal elasticity of the material for the work roll ofEmbodiment 1.
where Ir = π ×Dr4/64
Assuming that δr = δs, Dr is expressed by the following equation (4): - On the other hand, 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):
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/mm2))
The minimum diameter upper limit Dmax1 per strip width inEmbodiment 1 is shown inFig. 6 . K=2.5, provided that the material for the work roll was a cemented carbide.
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 inFig. 7 . K=2.5, provided that the material for the work roll was the cemented carbide. - In the present embodiment, as describe above, 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. Thus, 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, thestrip 1 of high product quality can be obtained with high productivity by the rolling of a hard material. - As shown in
Figs. 8A and 8B , 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 α inFig. 8A ). By so doing, 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 thework roll 2 is decreased. InFig. 8B , Fb represents the offset vertical component force of the rolling load Q. - As a result, the advantage that the deflection of the
work roll 2 can be further diminished is produced.
The total force Fw in the horizontal direction exerted on thework roll 2 is expressed by the following equation (7):
where Dw represents the diameter of the work roll, and DI represents the diameter of the intermediate roll. - As shown in
Figs. 9A and 9B , theintermediate 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 β inFig. 9A ). By so doing, 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 thework roll 2 of the high longitudinal modulus material is decreased. InFig. 9B , Fb represents the offset vertical component force of the rolling load Q. - As a result, the advantage is produced that the deflection of the
work roll 2 can be further diminished.
The total force Fw in the horizontal direction exerted on thework roll 2 is expressed by the following equation (8):
where Dw represents the diameter of the work roll, and DI represents the diameter of the intermediate roll. - In the present embodiment, the paired upper and lower work rolls 2 are not structured to be shifted in the axial direction. As will be described below, however, 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 inPatent Document 2. - As shown in
Fig. 10 , the upper and lower work rolls 2 as a pair haveroll 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 thestrip 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). - Next, an explanation will be offered for a method of decreasing edge drops by the shift of the
work roll 2 having the taperedroll shoulder 2a. The work rolls 2 are provided with the taperedroll shoulders 2a in vertical point symmetry, and the distances from the positions of the roll shoulders to the plate ends are designated as δw and δd. 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. - If the strip thickness at the one point or the plurality of points in the vicinity of the strip edge portion, which has been measured on the operating side, is smaller than a predetermined strip thickness, the
upper work roll 2 is shifted in the direction of the roll shaft width narrowing. That is, theupper work roll 2 is shifted in a direction in which δ 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, theupper work roll 2 is shifted in the direction of the roll shaft width broadening. That is, theupper work roll 2 is shifted in a direction in which δw is decreased. - If the strip thickness at the one point or the plurality of points in the vicinity of the strip edge portion, which has been measured on the drive side, is different from the predetermined strip thickness, the
lower work roll 2 is similarly shifted so that the above strip thickness equals the predetermined strip thickness. Essentially, the work roll diameter can be rendered small by applying thework roll 2 of the high longitudinal modulus material. Thus, 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. - The combined use of the small-diameter work roll and the work roll shift mentioned above can minimize the tapered
roll shoulder 2a or minimize the shift distance δw or δd. This technology is preferred, in particular, for rolling of a brittle material, such as an electromagnetic steel sheet, which is susceptible to these values and is apt to splinter.Fig. 10 describes the mill ofFig. 1 as a representative, but the mill with the variably offset work rolls inFigs. 8A, 8B or the mill with the variably offset intermediate rolls inFigs. 9A, 9B may be used. - The present embodiment shows an example in which the paired upper and lower
intermediate rolls 3 have theroll 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 thestrip 1. However, the paired upper and lowerintermediate 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 thestrip 1, and to be shifted in the axial direction, as shown inNon-Patent Document 1. In this case, the ability to control shape is lower than in the six-high mill having theroll shoulder 3a, but is higher than in the four-high mill. Moreover, the aforementioned work roll shift shown inFig. 10 may be applied to this mill. -
Fig. 11 is a front sectional view of a four-highmill showing Embodiment 2 of the present invention.Fig. 12 is a sectional view taken along line XII-XII inFig. 11 .Fig. 13 is an explanation drawing of a work roll shift of a four-high mill showing an applied example ofEmbodiment 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 bearinghousings 15a to 15d, and thebending cylinders 16a to 16d from the six-high rolling mill which representsEmbodiment 1, as shown inFigs. 11 and12 . In this case, the plate shape control ability declines greatly, but the structure is further simplified. - In the present embodiment, the paired upper and lower work rolls 2 do not show a structure for shift in the axial direction. As shown in
Fig. 13 , however, the work rolls 2 may be structured to haveroll 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 thestrip 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 thestrip 1, and are shiftable in the axial direction. However, 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 thestrip 1, and to be shifted in the axial direction, as shown inNon-Patent Document 1. In this case, the ability to control shape is higher than in the four-high mill shown inFig. 13 . - If 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. When it is applied to the final stand, i.e., No. 4 stand in the drawing, a thinner strip can be rolled by the small-diameter work rolls of the high longitudinal modulus material. It goes without saying that 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. -
- 1
- Strip
- 2
- Work roll
- 3
- Intermediate roll
- 4
- Back-up roll
- 5a, 5b
- Pass line adjusting device
- 6a, 6b
- Hydraulic cylinder
- 7a, 7b
- Housing
- 13a to 13d
- Work roll bearing housing
- 15a to 15d
- Intermediate roll bearing housing
- 17a to 17d
- Back-up roll bearing housing
- 14a to 14d
- Work roll bending cylinder
- 16a to 16d
- Intermediate roll bending cylinder
Claims (4)
- A rolling mill including upper and lower work rolls (2) as a pair for rolling a metal strip (1), the rolling mill having no supporting rolls inside and outside a rollable strip width of the work rolls (2) which exert a horizontal force on the work rolls (2), wherein
the work rolls (2) are driven,
a material having a high modulus of longitudinal elasticity is used for the work rolls (2), and
a minimum roll diameter of the work rolls (2) is intermediate between a minimum diameter upper limit Dmax1 and a minimum diameter lower limit Dmin1,
characterised in that Dmax1 and Dmin1 are expressed by the following equations:
where D4max is 180 mm,
B is a strip width in mm/1,300 mm, and
K is a ratio of the high modulus of longitudinal elasticity to the modulus of longitudinal elasticity of a conventional material of 21,000 kg/mm2 and is set to be from 1.2 to 3.0,
where D4min is 180 mm. - The rolling mill of claim 1, wherein the rolling mill is a six-high rolling mill further including
upper and lower intermediate rolls (3) as a pair for supporting the work rolls (2), and
upper and lower back-up rolls (4) as a pair for supporting the upper and lower intermediate rolls (3) as the pair. - The rolling mill of claim 1, wherein the rolling mill is a four-high rolling mill further including upper and lower back-up rolls (4) as a pair for supporting the work rolls (2).
- A tandem rolling mill including a plurality of rolling mill stands arranged therein, wherein the rolling mill of any preceding claim is provided as at least one of the stands.
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JP2009170815A JP5568261B2 (en) | 2009-07-22 | 2009-07-22 | Rolling mill and tandem rolling mill equipped with the rolling mill |
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EP2277637B1 true EP2277637B1 (en) | 2013-03-27 |
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JP5683082B2 (en) * | 2009-07-29 | 2015-03-11 | 三菱日立製鉄機械株式会社 | Rolling mill with work roll shift function |
CN104209325A (en) * | 2014-09-10 | 2014-12-17 | 中冶南方工程技术有限公司 | Large roll, small roll and bent roll system suitable for double-stand flattening and double cold reduction unit |
JP6470134B2 (en) * | 2015-07-08 | 2019-02-13 | Primetals Technologies Japan株式会社 | Rolling mill and rolling method |
CN111318569B (en) * | 2020-03-24 | 2021-08-24 | 河北东海特钢集团有限公司 | Steel plate cold rolling equipment |
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JPS60238021A (en) | 1984-05-10 | 1985-11-26 | Ishikawajima Harima Heavy Ind Co Ltd | Rolling mill |
JP2972401B2 (en) * | 1991-08-26 | 1999-11-08 | 株式会社日立製作所 | Rolling mill and rolling method |
JP3209705B2 (en) * | 1997-03-25 | 2001-09-17 | 川崎製鉄株式会社 | Composite roll for cold rolling |
TW401326B (en) * | 1998-03-23 | 2000-08-11 | Kawasaki Steel Co | Method of manufacturing metal foil |
JP2002066608A (en) * | 2000-08-30 | 2002-03-05 | Hitachi Ltd | Cold rolling mill and rolling method |
DE10046426A1 (en) * | 2000-09-20 | 2002-03-28 | Sms Demag Ag | Four high rolling stand, used in rolling mill for rolling hot and cold strips, comprises two working rollers and supporting rollers driven by drive spindles with one supporting roller detachably connected to motor |
DE10208389B4 (en) * | 2001-07-11 | 2004-11-04 | Hitachi, Ltd. | Roll stand, rolling mill and rolling process |
JP2003275803A (en) * | 2002-03-20 | 2003-09-30 | Jfe Steel Kk | Method for cold-rolling metallic sheet having excellent gloss |
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JP2011025253A (en) | 2011-02-10 |
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