US3762202A - Rolling mill for flat-rolled products - Google Patents

Rolling mill for flat-rolled products Download PDF

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Publication number
US3762202A
US3762202A US00189900A US3762202DA US3762202A US 3762202 A US3762202 A US 3762202A US 00189900 A US00189900 A US 00189900A US 3762202D A US3762202D A US 3762202DA US 3762202 A US3762202 A US 3762202A
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roll
bearing
work roll
crossbeam
bearing support
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US00189900A
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English (en)
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W Sherwood
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    • 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

Definitions

  • the invention is a rolling mill for flat-rolled products 22 Fil d; Oct 1 1971 designed in a manner to substantially eliminate bending of the rolls under load with associated convexity of the [21] Appl. No.: 189,900
  • the rolling mill employs the partial cylindrical surface of the roll barrel itself in [51] 1321 31 32 contact with a corresponding work roll bearing pad, [58] Field of Search 72/245, 246, 241, rather than roll neck end bearings, as the main load 72 199 bearing mill bearings, and supports this bearing against a transversely elongated hydrostatic cushion which dis- [56] References Cited tributes the reaction to the roll force uniformly along UNITED STATES PATENTS the length of the work roll. Pressure equalizing cylinders at the roll ends are also used to compensate for 2 5x 2?
  • the invention relates to the mechanical working of metals such as steel, copper and aluminum and, more particularly, to an improved rolling mill for flat-rolled products such as plate, sheet and strip.
  • Another object is to provide an expedient for simple and continuous control and adjustment of the roll gap and therefore the thickness of the material being rolled.
  • Another object is to reduce the power requirements and energy required for rolling.
  • a further object is to reduce the capital cost of a rolling mill for flat rolled products, in particular, mills for hot and cold rolled products in the steel industry.
  • a further object is to eliminate the need for high reaction, concentrated load roll end bearings, backup rolls, and complex mechanical screwdowns.
  • Still another object of the invention is to provide a rolling mill stand particularly suited for installation in tandem for reduction of continuously cast steel slabs in a continuing sequence following their exit from the continuous casting machine, usually with an intermediate temperature equalizing heating step.
  • the invention is a rolling mill for flat-rolled products in which the work roll is mounted for rotation with the working surface of the roll barrel, on the diametrically opposite side to the bar, in contact with and supported by an elongated work roll bearing pad incorporated into a backup bearing assembly, whereby the rolling force is borne by this assembly, rather than by roll neck bearings at the ends of either backup or work rolls as in the usual rolling mill practice.
  • the backup bearing assembly includes a partial cylindrical sleeve bearing or equivalent low-friction contact with the roll surface, and is supported along the length of the roll barrel against a hydrostatic cushion containing fluid under a pressure corresponding to the roll force, with the pressure distributed along the roll similarly to the rolling load.
  • the hydrostatic cushion in turn, is supported against a backup crossbeam connecting between the mill end housings.
  • a backup crossbeam connecting between the mill end housings.
  • an equal and opposite force to the rolling force is exerted, but rather than being concentrated at the roll ends, the force is distributed all along the roll length, thus effectively eliminating large bending forces and roll deflections such as are normally encountered in the conventional two-high and four-high mill having rolls supported by roll neck bearings only at the roll ends.
  • the roll gap can be adjusted at one end of the rolls in relation to the other end, thereby controlling bar thickness as between the roll ends and therefore the two bar edges and thus reduce the occurrence of wedge-shaped transverse profiles of the rolled bar.
  • hydraulic equalizing cylinders are also included between top and bottom backup bearing assemblies at the roll ends for exerting controlled supplementary separating forces between top and bottom backup bearing assemblies. As bar width decreases, increased balancing forces can be exerted by these cylinders to maintain a substantially flat and uniform roll gap at various bar widths.
  • FIG. 1 is a side view of a rolling mill stand according to this invention
  • FIG. 2 is a front elevation of the rolling mill stand of FIG. 1;
  • FIG. 3 is a sectional view taken along line A-A of FIG. 1;
  • FIG. 4 is a representation of forces in the rolling mill stand of FIGS. 1-3, for the case where bar width is equal to working length of the roll barrel;
  • FIG. 5 is a representation of forces in the rolling mill stand of FIGS. l-3 for the case where the bar width is significantly narrower than the working length of the roll barrel.
  • top work roll 1, and bottom work roll 2 are mounted for rotation by a suitable rolling mill drive, for example, by a motor, gear reducer, coupling, pinion stand and spindles to top roll Wobbler drive connection 24, and bottom roll Wobbler drive connection 25.
  • a suitable rolling mill drive for example, by a motor, gear reducer, coupling, pinion stand and spindles to top roll Wobbler drive connection 24, and bottom roll Wobbler drive connection 25.
  • the rolling force is transmitted from the work roll barrel to bearing inserts 3 which form partial cylindrical bearing surfaces in contact with the working length of the work roll barrels l, 2.
  • the bearing inserts 3 are mounted within work roll bearing pads 6, which transmit the rolling force by way of pressure contact surface 7 to work roll bearing support crossbeam 9.
  • the hydrostatic roll pressure distribution cushions l0, 1 1, 26 and 27 then transmit this pressure to the backup crossbeam l2, l3, l4 and bottom roll backup crossbeam l6, l7 and 18 which are supported at their ends within mill stand end housings 15.
  • porous iron offers high strength at low cost for low speed operation.
  • Babbit base materials, reinforced Teflon and various other materials can also be considered, the selection depending upon the force and speed conditions of the particular rolling application.
  • the roll cooling water provides a natural lubricant.
  • the bearing surface may also be pressure fed with water or lubricant emulsion by way of an appropriate groove system in the insert, according to known practice for sliding bearings. Since roll scale and dirt on the roll surface tend to accelerate scoring and wear of the bearing, a rotary roll cleaning brush can also be incorporated into the mill stand design.
  • the work rolls 1, 2, bearing support pads 6, bearing insert 3 and end collars 4 are made up as an integral unit assembly.
  • the end collars also serve to hold the work rolls in position when the mill is not loaded.
  • the entire assembly is slid along the guide slot between positioning track 8 and pressure contact surface 7 of hearing support pad 6.
  • the work roll bearing support crossbeam 9 is mounted for adjustable vertical movement within the sets of centering guide rolls 21 attached to support brackets 22 of end housings 15 on both entry and exit sides of the mill stands. in this manner, the work roll and backup assembly may be maintained in correct vertical alignment within the work roll housing at all times.
  • the roll pressure distribution cushions are confined in a bellows type enclosure consisting of flanges 11, 11A, one or more expansion corrugations l and internal guide sleeve 27, connecting between appropriate flanges on work roll bearing support crossbeams on the work roll side and top and bottom backup crossbeams l2, l3, l4, and l6, l7, 18 on the backup side.
  • the cushion shown is ofa design equivalent to a Zallea Hyptor (high pressure toroid) or equivalent expansion joint.
  • the pressure of hydraulic fluid 26 is transmitted equally in all directions.
  • An equal and opposite force to the rolling force therefore is transmitted against the work roll bearing support crossbeam 9, which is distributed along the beam in proportion to the vertically projected area of the hydrostatic cushion.
  • the rolling force may cause a very substantial deflection of the backup crossbeams 12, 13, 14 and 16, 17, 18 this deflection does not affect the pressure distribution within the hydrostatic cushion, and therefore does not influence the roll cambers under load of the work rolls. This is a key advantage over mills employing backup rolls to enhance mill stiffness under load.
  • the cushion has been divided into two parts 10, 11 on one side of centre line of the roll barrel and 10A, 11A on the other side.
  • hydraulic pressure equalizing cylinders 23 are provided which will be seen to serve an additional service of compensating for differences between strip width and length of the hydrostatic backup cushions.
  • FIG. 4 illustrates schematically the effect of the cushion on transverse profile of the roll gap under load for the condition that strip width is equivalent to the cushion length, with cushion area uniform along the entire roll length. lt may be seen the fluid pressure within the cushion creates an equal and opposite reaction force to the rolling force which is similarly distributed along the roll length, thereby creating a condition of bending moment and deflection equal to zero all along the roll length. With balancing cylinders 23 exerting no significant force, and employing straight cylindrical rolls, the resulting roll camber and transverse bar profile could be expected to be substantially flat (ignoring bar edge effects).
  • FIG. 5 illustrates the case where bar width is substantially narrower than hydrostatic cushion length. As width of the rolled bar 28 decreases, the compensating force applied to the hydraulic balancing cylinders 23 is progressively increased. A substantially flat profile of the roll gap thus can be maintained over a wide range of conditions and sizes of stock being rolled.
  • a backup bearing assembly including work roll bearing support crossbeam and partial cylindrical roll support bearing elements extending along the working length of said work roll against which the barrel of said work roll rotates under load; a backup crossbeam spanning the roll length connecting between mill end housings and adapted to accommodate the total rolling force; a hydrostatic roll pressure distribution cushion extending along the length and between said work roll bearing support crossbeam and said backup crossbeam, said hydrostatic cushion containing an essentially noncompressible hydraulic fluid and being enclosed on one side by said backup crossbeam, on the other side by said bearing support crossbeam, and enclosed around the cushion edges by an expandable retractable sealed expansion joint, wherein said hydraulic fluid is adapted to effectively resist and counteract the rolling force with an equal and opposite reaction force to the rolling force, said reaction force being distributed along the length
  • a rolling mill for flat-rolled products which also includes separating force equalizing cylinders acting upon the work roll bearing support crossbeam near the crossbeam ends, adapted for applying a controlled separating force to the ends of the work roll bearing support crossbeam, thereby compensating for bending forces and deflection of said work roll bearing support crossbeam caused by differences in the distribution of forces on either side of the bearing support crossbeam, particularly those forces resulting from differences between the width of the bar being rolled and the length of said hydrostatic roll pressure distribution cushion as bars of different widths are rolled.
  • a rolling mill for flat-rolled products according to claim 1 in which said hydrostatic roll pressure distribution cushion is made up in two separate hydraulic chambers, one on each side of the centre of the roll barrel, including means for independently controlling the amount of hydraulic fluid as between each of said chambers, said hydraulic chambers threby being adapted to adjust the size of the roll gap at either end of the work rolls as required to maintain the desired bar profile and thickness during rolling.
  • a rolling mill for flat-rolled products in which said cushion edges comprise a packless expansion joint in the form of a flexible bellows incorporating at least one e'xpansible corrugation disposed longitudinally along the cushion edges.
  • said backup bearing assembly includes a removable bearing support pad integral with said work roll bearing support crossbeam, comprising an elongated body member with end bearing collars for retention of the roll necks at either end of the rolls, and a partial cylindrical contact surface forming a partial bearing along the roll length between said bearing pad and the roll barrel working surface, said support pad being adapted for insertion within guide tracks integral with said work roll bearing support crossbeam, whereby the opposite side of said support pad to said partial cylindrical contract surface makes a pressure contact with said work roll bearing support crossbeam by way of which contact the rolling force is transmitted between said work roll, and said work roll bearing support crossbeam, and in turn to said hydrostatic roll pressure distribution cushion.
  • a rolling mill for flat-rolled products which includes a partial cylindrical bearing insert attached to said bearing pad along the roll length to form said partial cylindrical bearing surface.
  • a rolling mill for flat-rolled products in which the rolling force is substantially borne by back-up supports bearing against the work roll barrel rather than by end neck bearings at the work roll ends, comprising, in combination, an elongated rotating work roll, a backup bearing assembly including work roll bearing support crossbeam and partial cylindrical roll support bearing elements extending along the working length of said work roll against which the barrel of said work roll rotates under load; a backup crossbeam spanning the roll length connecting between mill end housings and adapted to accommodate the total rolling force; a hydrostatic roll pressure distribution cushion made up in two separate hydraulic chambers, one on each side of the centre of the roll barrel and extending along the length and between said work roll bearing support crossbeam and said backup crossbeam, said hydraulic chambers containing an essentially non-compressible hydraulic fluid, and said chambers being enclosed on one side by said backup crossbeam, on the other side by said bearing support crossbeam, and enclosed around the cushion edges by an expandable retractable sealed expansion joint, wherein said hydraulic fluid is adapted to effectively resist and counter
  • said backup bearing assembly includes a removable bearing support pad integral with said work roll bearing support crossbeam, comprising an elongated body member with end bearing collars for retention of the roll necks at either end of the rolls, and a partial cylindrical contact surface forming a partial bearing along the roll length between said bearing pad and the roll barrel working surface, said support pad being adapted for insertion within guide tracks integral with said work roll bearing support crossbeam, whereby the opposite side of said support pad to said partial cylindrical contact surface makes a pressure contact with said work roll bearing support crossbeam by way of which contact the rolling force is transmitted between said work roll, and said work roll bearing support crossbeam, and in turn to said hydrostatic roll pressure distribution cushion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
US00189900A 1971-10-18 1971-10-18 Rolling mill for flat-rolled products Expired - Lifetime US3762202A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US18990071A 1971-10-18 1971-10-18

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US3762202A true US3762202A (en) 1973-10-02

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US (1) US3762202A (de)
JP (1) JPS5618284B2 (de)
AU (1) AU4781572A (de)
CA (1) CA959311A (de)
DE (1) DE2250948A1 (de)
ES (1) ES407739A1 (de)
GB (1) GB1413517A (de)
IT (1) IT975274B (de)
ZA (1) ZA727407B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4603569A (en) * 1984-07-20 1986-08-05 Tadeusz Sendzimir Pressure controlled plate mill
US4768366A (en) * 1987-04-30 1988-09-06 Tadeusz Sendzimir Wide strip mill using pressure elements
WO1999011396A1 (fr) * 1997-09-04 1999-03-11 Hongzhuan Zheng Laminoir pour feuillards ou produits plats
US20110027057A1 (en) * 2008-03-27 2011-02-03 Numalliance Sas Supply station
US20140331730A1 (en) * 2011-11-19 2014-11-13 Jilin University Rolling device and the method thereof
CN104858236A (zh) * 2015-06-15 2015-08-26 中冶赛迪工程技术股份有限公司 一种轧辊辅助支撑装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61190783U (de) * 1985-05-21 1986-11-27
JPS6322291U (de) * 1986-07-29 1988-02-13

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1519657A (en) * 1922-06-10 1924-12-16 United Eng Foundry Co Mill
US2573353A (en) * 1945-10-04 1951-10-30 Bethlehem Steel Corp Rolling mill
US3031872A (en) * 1958-09-16 1962-05-01 Textilmaschinen Eduard Kusters Fluid pressure roll
US3355924A (en) * 1963-07-10 1967-12-05 Sendzimir Inc T Control of deflection in rolling mills and the like
US3429166A (en) * 1965-03-09 1969-02-25 Aluminium Lab Ltd Rolling mill
US3561241A (en) * 1968-03-13 1971-02-09 Siderurgie Fse Inst Rech Rolling mill for thin strips
US3572079A (en) * 1966-08-31 1971-03-23 Davy & United Eng Co Ltd Rolling mills
US3592036A (en) * 1968-07-23 1971-07-13 Siderurgie Fse Inst Rech Method and apparatus for pressing a rotating roll against a surface
US3651675A (en) * 1968-10-21 1972-03-28 United Eng Foundry Co Automatic gauge control of strip in rolling mill employing backup roll bending

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1519657A (en) * 1922-06-10 1924-12-16 United Eng Foundry Co Mill
US2573353A (en) * 1945-10-04 1951-10-30 Bethlehem Steel Corp Rolling mill
US3031872A (en) * 1958-09-16 1962-05-01 Textilmaschinen Eduard Kusters Fluid pressure roll
US3355924A (en) * 1963-07-10 1967-12-05 Sendzimir Inc T Control of deflection in rolling mills and the like
US3429166A (en) * 1965-03-09 1969-02-25 Aluminium Lab Ltd Rolling mill
US3572079A (en) * 1966-08-31 1971-03-23 Davy & United Eng Co Ltd Rolling mills
US3561241A (en) * 1968-03-13 1971-02-09 Siderurgie Fse Inst Rech Rolling mill for thin strips
US3592036A (en) * 1968-07-23 1971-07-13 Siderurgie Fse Inst Rech Method and apparatus for pressing a rotating roll against a surface
US3651675A (en) * 1968-10-21 1972-03-28 United Eng Foundry Co Automatic gauge control of strip in rolling mill employing backup roll bending

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4603569A (en) * 1984-07-20 1986-08-05 Tadeusz Sendzimir Pressure controlled plate mill
US4768366A (en) * 1987-04-30 1988-09-06 Tadeusz Sendzimir Wide strip mill using pressure elements
WO1999011396A1 (fr) * 1997-09-04 1999-03-11 Hongzhuan Zheng Laminoir pour feuillards ou produits plats
KR100504356B1 (ko) * 1997-09-04 2005-07-28 홍주안 젱 판 또는 스트립 압연용 압연기
US20110027057A1 (en) * 2008-03-27 2011-02-03 Numalliance Sas Supply station
US8783084B2 (en) * 2008-03-27 2014-07-22 Numalliance Sas Supply station
US20140331730A1 (en) * 2011-11-19 2014-11-13 Jilin University Rolling device and the method thereof
CN104858236A (zh) * 2015-06-15 2015-08-26 中冶赛迪工程技术股份有限公司 一种轧辊辅助支撑装置

Also Published As

Publication number Publication date
IT975274B (it) 1974-07-20
CA959311A (en) 1974-12-17
AU4781572A (en) 1974-04-26
GB1413517A (en) 1975-11-12
JPS5618284B2 (de) 1981-04-28
ES407739A1 (es) 1975-10-16
DE2250948A1 (de) 1973-04-26
ZA727407B (en) 1973-08-29
JPS4849655A (de) 1973-07-13

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