GB2199276A

GB2199276A - Cold-rolling mill

Info

Publication number: GB2199276A
Application number: GB08727416A
Authority: GB
Inventors: Erhard Witting
Original assignee: Andritz AG
Current assignee: Andritz AG
Priority date: 1986-11-24
Filing date: 1987-11-23
Publication date: 1988-07-06
Anticipated expiration: 2007-11-23
Also published as: ATA313386A; SE8704635L; FR2607034A1; GB2199276B; GB8727416D0; SE8704635D0; AT390574B; DE3738034A1

Description

219 9 270' ROLLING MILL, IN PARTICULAR COLD-ROLLING MILL The invention

relates to a rolling-mill, in particular a cold-rolling mill, preferably for metallic material, mainly steel and non-ferrous metals, convenientiy for rolling, roughing (blooming) or skin-passing (rerolling) of strip or sheets, having at least two, conveniently four to ten, mainly essentially superimposed rolls, with an hydraulic medium, in particular at least one, conveniently at least two, hydrostatic bearin element(s) and/or hydraulic cylinders preferably acting on conveniently hydrostatic bearing elements acting directly on the outer jackets of the rolls barrels, namely on each roll barrel.

In cold-rolling mills, the transmission of forces required for rolling sheets and Strip to the roll barrels is normally effected via the roll necks. The result are negatively curved elastic bending lines; these bending lines are detrimental because in spite-of a limited effected due to ground-down roll camber, they result in camber and sharpened edges of the rolling stock cross section which thus deviates from the desired rectangular form.

This disadvantage is largely eliminated according to the invention in that hydraulic lifting cylinder or hydraulic traction cylinders (differential cylinders) actuable for controlling the elas-tic bending line(s) of the series of rolls, in particular the topmost back-up roll, by signals emitted by a surface evenness measuring device act directly on the roll bearings or on the roll bearing necks at least of the topmost roll, in particular the topmost back-up roll, in addition to th hydraulic medium directly acting on the Outer jacket of the roll barrel or the hydrostatic bearing element(s) acting thereon.

This control of the elastic bending line(s) is particularly effective because the initially mentioned measure of a direct action of an hydraulic medium, in particular of at least two hydrostatic bearing elements and of hydraulic cylinders acting on these, on roll barrels, namely on each roll barrel, can,be combined therewith. As a result, the roll necks are pulled up, on the one hand, and the main rolling forces act in the area of the roll barrels, on the other hand, whereby the elastic bending lines of the series of rolls can be particularly favorably influenced.

A control combination of this type in relation to the elastic bending line(s) of the series of rolls has not been known. This also applies to the embodiment according to DE-OS 31 45 526.While according to the invention, an hydraulic medium or hydraulic bearing elements act directly on the outer jacket of the roll barrels, the state of the art relates to deflection adjustment rolls in which thus the supporting elements act on interior surfaces of the roll in question. In addition, the cylinders in the known devices act on stationary supports and not on rotating roll bearing necks. Moreover, known device are provided with bending devices acting on the ends of the work rolls, but not on the ends of the back-up rolls or of the topmost roll. The embodiment according to DE-OS 21 38 894 does not anticipate the object of the invention, either. This already applies to the type of rolling mill according to the invention, because bending pressure rolls instead of an hydraulic medium or hydrostatic bearing elements act on the back-up roll barrels. Tilis makes control more difficult if not virtually impossible. Tho lifting devices according to this DE-OS do not act directly on the roll bearings or roll necks, but instead on special neck extensions. This results not only in greater construction length of the rolling mill, but also in a negative influence o'n the control of the elastic bending line(s) of the series of rolls.

The favourable influence on the elastic bending lines of the series of rolls according to the invention is highly intensified according to a further development of the invention in that in addition to the lifting cylinder control acting on the roll bearings or roll bearing necks, a control of the elastic bending lineOof the series of rolls, in particular the roll(s) arranged above the roll gap, preferably the topmost back-up roll, is effected by shifting force lines of the 10-rolling forces, in particular of the pressure forces acting on the roll. in particular the topmost'. back-up roll, in particular completely, from the area of the bearings of the roll necks to the area of the roll barrels, and that the hydraulic medium directly acting on the outer jacket of the roll barrels is controlled as a function of parameters depending on the state of the rolling mill parts effective in respect of the material deformation and the material treated, signal transmitter.

integrated in a surface evenness measuring device and/or thickness measuring device and/or the particularly upper hydraulic cylinder(s) acting on the hydrostatic bearing element(s) and/or on one each, conveniently at least two, hydraulic cylinders acting on conveniently hydrostatic bearing elements arranged above the topmost and optionally underneath the lowermost back-up roll in the area of their roll barrels, a computer control being connected to the signal transmitters, the computer comparing the input set values for the rolling stock to the actual values of the signal transmitters or the incoming signals, on the one hand, and to the hydraulic cylinders or their pressure medium supply or actuators for these cylinders and optiO-l1d11,11,in particular indirectly, to the hydrostatic bearing elements, on the other hand.

encing of the This means a particularly favourable control or influl elastic bending line(s) of the series of rolls based on, and made possible by, the basic combination according to the invention. Computercontrolled hydrauliccylinders are arranged immediately above or underneath the back-up roll barrels, whereby the rolling forces in their force lines or lines of application can be applied via the cylinder piston ends and the hydrostatic roll bearings disposed above or underneath them within the width of the rolling stock. The hydrostatic bearing elements themselves are conveniently operated by means of roll oil or roll oil emulsion. The roll neck bearings of prior art with their elaborate rolling bearing systems can be eliminated. More- over, the use of the arrangement according to the invention permits a reduction of bending stresses and of back-up roll diameters. Moreover, a series of rolls according to the invention can be of reduced height, which results in a shorter roll housing height and a more rigid stand construction.By the extensive and direct influencing and change of conventional elastic bending lines according to the invention, the strip shape over the strip width is essentially improved By the relief of the strip edges thus obtainable, the hazard of strip breakage during the rolling operation is also reduced. Intermediary processes such as strip edge trimming are reduced in number, which permits an increase in production and a reduction of cost. In order to optimize the strip shape to precise parallelism, the hydrostatic roll bearings arranged underneath or above the upper roll. barrel are as already mentioned - also concertedly adjustable. This allows an additional quality increase by strip shape improvement. Roll stands of reduced height extension improve the stand module and contribute proportionally to quality increase by tolerance improvement.

According to a further variant of the invention, a special combinatory effect in the direction of an especially convenient embodiment of the rolling mill stand can be achieved if the, in particular vertical, plane of symmetry of the roll supporting structu, or roll stand or roll housing, in particular their main supporting structure, made up of two supporting frames arranged on either side of the rolls parallel to their axes and provided with a window at leas in the area of the roll barrels or the roll gap, wholly or at least essentially coincides, with the in particular vertical plane of 1.5 symmetry of the roll system or the roll arrangement, the supporting frames arranged immediately at both sides of the roll systems and parallel to their roll axes and provided with a window conveniently being connected above and/or below the rolls by means of con_n,ections extending transversely to their axes, in particular very largely rigidly. The embodiment of the main supporting structure of- the rolling mill can be further improved if the roll supporting structure consists of frame-like roll housings arranged laterally of the roll jackets or roll barrels and mad., of hot-rolled, appropriately cut steel slabs cut out. for forming the window, at least the upper, horizontal cross beams of these frame-like steel slabs being largely rigidly connected-by means of spacers.

Neither the AT-PS 339 854 nor the DE-OS 31 32 339 describe a roll supporting structure of the type previously disclosed. According to the AT-PS, the stands are placed conventionally transversely to the plane of symmetry of the roll system; it is evident from this publication that 5 the stands are merely connected by cross beams in The frame-like roll housings provided with a window the plane of symmetry are placed transversely to the plane of symmetry or the roll axes, however. Moreover, the DE-OS 31 32 339 does not describe a rolling mill within the meaning of the present invention, and not even a frame-like roll supporting 10structure; as a result, it does not show connecting slabs for two supporting frames provided on the top and bottom; all that is visible are solid flange walls slotted from one side. The variants according to the invention last described assure a practice-related stable embodiment of the rolling mill stand and high rigidity at compara- 15tively low expenditure. The measuring precision and - what is particularly important in this case - the control possibilities can be considerably improved if a thickness measuring device conveniently having a signal transmitter for adjusting the roll gap height, in paricular for adjusting the hydrostatic bearing elements and/or the hydrauli.- cylinders, is provided on the discharge side of the rolled stock from the roll supporting structure immediately or virtually immediately at it, conveniently at a maximum. distance of 125 to 150 percent of the diameter of the largest roll of the roll systen, from its axis of symmetry, or close to the roll gap within the area of the said rolling stock discharge. Basically, the advantages described result above all from the said rotation of the plane ol symmetry as compared to the state of the art, so that by moving the measuring device par ticularly close to the roll gap, the control can be optimized. This -- 7 supports this variant of the invention, as well, considering that the US-PS 3_517 531 again shows transversely placed housing frames and as a consequence permits the placing of a measuring device only outside of the-compact, thus thick, transversely placed frame, thus far removed from the roll gap.

A particularly effective further improvement of the control or variations thereof of the elastic bending line(s) of the series of rolls can be achieved by providing a wedge adjustment underneath of, advantageously at least two, in particular hydrostatic bearing elements acting on the roll barrel(s) of the lower or lowermost roll(s), a.o. conveniently also for compensating the wear of the lowermost series of rolls-or the lowermost roll, which wedge adjustment is subject to the- action of an hydraulic actuating cylinder, whicb-cylinder or its actuator or its pressure medium supply is 1-5 actuable. for controlling the elastic bending line(s) of the lower roll(s) by means of signal transmitters, in particular indirectly, mainly via a computer control, the computer comparing the input set values for the rolling stock to the actual values of the signal transmitters or the incoming signals, which signal transmitters are inte- grated in the previously mentioned bearing elements and/or arranged in the-surface evenness measuring device, a control by means of hydraulic lifting cylinders possibly being provided in addition. The plant operates particularly economically if the present or supplied refrigerating medium roll oil or roll emulsion is provided for the construction of the hydrostatic supporting oil gaps and/or the bearin elements for the upper or topmost and/or the lower or lowermost roll in particular back-up rolls, and/or for optionally hydrostatically supported thin rolls.

A construction of the plant particularly favourable in practice can be obtained by providing hydraulic traction cylinders conveniently pivotally above the roll neck bearings, conveniently simple journal bearings, advantageously spherical roller bearings, of the upper or uppermost roll(s), in particular the upper back-up roll, in the upper lateral area of the roll supporting structure, preferably on either side of the upper spacer in the free space between the steel slabs essentially forming the main supporting structure, the piston rods of the cylinders being positively connected to the said roll necks or their housings via traction elements extending to the bearings or bearing necks of the upper or topmost roll(s), in particular via a pivoting bearing which is conveniently provided on an upwardly directed projection of the journal bearing housing.

The invention is explained in the following by means of exemplary embodiments under reference to the accompanying drawing.

Fig. I to 4 show a ten-high cold-rolling stand of compact construction according to the invention, Fig. 1 showing a sectional view along line CC of Fig. 3, Fig. 2 a partial representation of the sectional view along line B-B in Fig. 1, Fig. 3 a front view and Fig. 4 a partial view of a sectional view along line A-A in Fig. 3, Fig. 5 to 8 show a four-high cold-rolling stand of compact construction according to the invention with corresponding sectional views as for the previously mentioned roll stand and Fig. 9, 9a and 10, 10a represent Lqrhigh cold-rolling stands of compact construction. 25 Fig. 11 shows a block diagram. The ten-high rolling mill according to Fig. 1 to 4 shows thin work rolls 1,2, lateral back-up rolls 3 to 6, interm?diate rolls 7 and 8 and back-up rolls 9 and 10. The lateral back-up rolls 3 to 6 - 9 are supported in a manner known per se by means of hydrostatic supporting elements. The large back-up rolls 9 and 10 are supported in this case by four hydrostatic bearing elements 11 to 14 in the zone of their barrels 15,16. The hydrostatic supporting oil gaps of these bearingelements and for the hydrostatically supported thin rolls 1, 2 and their draw-pull are conveniently formed by means of the available cooling medium rolling oil or rolling emulsion. The bearing elements 11, 12 are subject to the action of computer-controlled hydraulic cylinders 17, 18 located on the spacer 19 whic h connects the steel slabs 21, 22 to one another together with a second spacer 20 and thus forms the main supporting structure of the rolling mill. The conveniei-. ly computer-controlled hydraulic cylinders 17, 18 and the bearing elements 11, 12 are adjustable by signals generated by signalling means integ rated into a surface. evenness measuring device and thickness measuring device 24 placed close to the roll gap 23 in this case or integrated into the hydraulic cylinders 17,18. The computer used for the control compares the desired set values of thickness or surface evenness of the rolling tock to the actual values of the signals it receives from the various signal transmitters and then controls the supply of pressure medium or the actuators for the va rious hydraulic cylinders.

By changing the arrangement of the hydrostatic bearing elements 11, 12 or the hydraulic cylinders 17, 18 acting on the roll barrel from the conventional area of the bearing necks of the rolls to the area of-the axes 25, 26 of the hydrostatic bearing elements 11, 12 or the hydraulic cylinders 17, 18, the lines of application are also displaced towards the axes 25, 26 or transferred into these. This fac, - 10 and the previously mentioned, in particular indirect connection of the computer-controlled hydraulic cylinders with the previously mentioned signal transmitters permits a particularly convenient control of the elastic bending line(s) of the set of rolls, in particular of the back-up roll 9.

It is evident that the in particular vertical plane of symmetry S of the roll supporting structure or roll stand or roll housing, in particular their main supporting structure 19 to 22, of frame-like shape and provided with a window at least in the zone of the roll barrels or the roll gap, wholly or at least essentially coincides with the in particular vertical plane of symmetry S of the roll system 1 to 10 or the roll structure.

The previously mentioned computer control is connected to the signal transmitters, on the one hand, and the hydraulic cylinders 17, 18 and their hydraulic control means and optionally to the hydrostatic bearing elements, on the-other hand.

In this case, the roll bearing necks and their bearings 27, 28 of the upper back-up roll 9 are additionally subjected to the action of hydraulic lifting or traction cylinders (differential cylinders) 29, 31 which are actuated by signals emitted by the surface evenness measurin device for the control of the elastic bending line(s) of the set of ro in particular of the topmost!Dac!,-up roll 9. These cylinders 29, 30 ar( arranged conveniently pivotally above the roll necks or bearings, conveniently simple journal bearings, advantageously sperhical roller bearings 27, 28, of the upper or topmost roll(s), in particular the up, back-up roll 9, in the upper lateral area of the roll supporting struc ture, preferably on both sides of the upper spacer 19, in the free spa between the steel slabs 21, 22 essentially forming the main supporting structure, the piston rods 33, 34 of the cylinders being pc)sitively - 11 connected to the previously mentioned roll necks or their housings via tension elements 35, 36 extending to the bearing necks or the uppe, or topmost roll(s) (9), in particular via a pivoting bearing convenie, ly located on an upwardly projecting extensi'on 35a, 36a of the journ 5 bearing housing 27, 28.

Moreover, a wedge adjustment 31 known per se is provided_. This wedg adjustment is arranged underneath the two hydrostatic bearing element13, 14 of the lowermost back-up roll 10 a.o. also for compensating the wear of the lower set of rolls 2,8,10 or the lowermost roll 10.

-10 This wedge adjustment is subject to the action of a hydraulic actuatir. cylinder or'lifting and lowering cylinder 32 which is actuable for thE control of the elastic bending line(s) of the lower roll(s) 2,8, 10 by signal transmitters, in particular indirectly via the previously mentioned computer control or actuators actuated thereby which are arranged in the previously mentioned surface evenness measuring devi( A control of the hydraulic differential cylinders 29, 30 can be combined therewith.

The wedge adjustment 31 is provided with wedge plates 37, 38 approximately extending in longitudinal direction of the rolls, the plane contacting wedge faces-39, 40 of the plates 37, 38 forming an angle with the horizontal. The above-mentioned actuating cylinder 32 is arranged centrally in relation to the said wedge-plates and under neath and laterally of the series of rolls. The piston rod 41 of thi cylinder is connected, in particular articulated, to -aL wedge base of the displaceable, in particular upper wedge plate 38, the other wedge plate 37 being rigidly connected on the lower spacer 20 eith( directly or indirectly on theportion of the roll supporting structur. on the foundation side, conveniently on its structure of two steel slabs 21, 22 and the spacers 19, 20 connecting these.

Fig. 5 to 8 show a further exemplary embodiment of the invention in the form of a four-high cold-rolling stand of compact construction, Fig. 9 show_ing a sectional view along line C-C in Fig. 7, Fig. 6 a partial representation of a sectional view along line B-B in Fig.

5, Fig. 7 a front view and Fig. 8 a partial view of a sectional viev: along line A-A in Fig. 7. The four rolls of the rolling mill bear the reference numbers 43 to 46, the barrels of the upper and lower backup rolls 45, 46 bear the reference numbers 47, 48. The remaining part of this rolling mill are formed and constructed like those shown in the exemplary embodiment according to Fig. 1 to 4. Their function is also corresponding, so that reference can be made to Fig. 1 to 4.

Similarly, Fig. 9, 9a and 10, 10a refer to a two-high cold-rolling stand of compact construction. Again, Fig. 9 shows a section a 1 view along line C-C in Fig. 10, Fig. 9a shows a partial representation of a sectional view along line B-B in Fig. 9 and Fig. 10 a front view of this rolling mill and Fig. 10a a partial view of a section view along line A-A of Fig. 10. Only two rolls 49, 50 with barrels 51, 52 are provided. For a supplementary description of the remaining parts, reference is made to the first exemplary embodiment.

Fig. 11 shows a block diagram of the previously mentioned control of the hydraulic medium or the hydraulic cylinders 17, 18, 29, 30, 32 which act particularly on the hydrostatic bearing elements 11, 12 of the back-up rolls, mainly in the area of their barrels. The actual values determined in the thickness measuring device 24 and the surfact evenness measuring device 65 and/or the hydraulic cylinders 17, 18 ai transmitted to the computer 64 by signal transmitters. The computer compares these values to the predetermined set values indicated by tl operating panel 66 ---------------------------------------------------- 13 and, by means of signals emitted via hydraulic control means or pilot (relay) valves 67, actuates the various hydraulic cylinders 17, 18, 29, 30 and 32. The remaining parts of the rolling mill as represented bear the same reference numbers as those shown in the previously described exemplary embodiments.

Cl aims: 1. A rolling mill, in particular a cold-rolling mill, preferably for metallic materials, mainly steel and non-ferrous metals, conveniently for rolling, roughing (blooming) or skin-passing (rerolling) of strip or sheets, with at least two, conveniently four to ten, mainly essentially superimposed rolls, with an hydraulic medium, in particular at least one, conveniently at least two, hydrostatic bearing elements and/or hydraulic cylinders preferably acting on conveniently hydrostatic bearing elements acting directly on the outer jacket of the rolls barrels, namely on each roll barrel, characterized in that in addition to the hydraulic medium acting directly on the outer jacket of the roll barrels or the hydrostatic bearing element(s) acting on them, the roll bearings (27, 28) or the roll bearing necks of at least the topmost roll, in particular the topmost back-up roll (9), are directly subjected to the action of hydraulic lifting cylinders or hydraulic traction cylinders or differential cylinders (29, 30) actuable by signalsemitted by a surface evenness measuring device foy the control of the elastic bending line(s) of the series of rolls, in particular the topmost back-up roll (9).

2. The rolling mill according to claim 1, wherein in addition to the lifting cylinder control acting on the roll bearings or roll necks (27, 28), a control of the elastic bending line(s) of the series of rolls, in particular the roll(s) arranged above the roll gap, prefer- ably the topmost back-up roll, is effected by shifting force lines of the rolling forces, in particular of the pressure forces acting on the rolls, in particular the topmost back-up roll, in particular completely from the area of the bearings of the roll necks to the area - of the roll barrels and wherein the hydraulic medium directly acting on the outer jacket of the roll barrels is controlled as a function of the parameters depending on the state of the rolling mill parts effective in respect of material deformation and the material treated, signal transmitters integrated in a surface evenness measuring device and/or thickness measuring device and/or in the, in particular upper hydraulic cylinder,. acting in particular on the hydrostatic bearing element(s) and/or one each, conveniently at least two, advantageously conveniently hydrostatic bearing elements and arranged above the topmost back-up roll and optionally underneath the lowermost back-up roll in the area of its roll barrel, a computer control advantageously being connected to the signal transmitters, the computer comparing the set values for the rolling stock to be treated to the actual values of the signal trans- mitters or the incoming signals, on the one hand, and to the hydraulic cylinders (17, 18) or their pressure medium supply or actuators for said cylinders and optionally, in particular indirectly, to the hydrostatic bearing elements (11, 12), on the other hand.

3. The rolling mill according to claim 1 or 2, wherein the, in particular vertical, plane of symmetry (S) of the roll supporting structure or rolling mill stand or roll housing, in particular their main supporting structure (19 to 22), made up of two supporting frames (21, 22) arranged on either side of the rolls parallel to their axes and provided with a window at least in the area of the roll barrels or the roll gap, wholly or at least essentially coincides with the in particular vertical plane of symmetry (S) of the-roll system (1 to 10) or the roll arrangement, the supporting frames (21, - 16 22) arranged immediately at both sides of the roll systems and parallel to their roll axes and provided with a window conveniently being connected above and/or below the rolls by means of connection, (19, 20) e-tanding transversely to their axes, in particular very largely rigidly.

4. The rolling mill according to claim 3, wherein the roll supporting structure consists of frame-like roll housings arranged laterally of the roll jackets or roll barrels (15, 16) and made up of hot-rolled apprppriately cut steel slabs (21, 22) cut our for forming the window, at least the upper, horizonal cross beams of these frame-like steel slabs being very largely ridigly connected by means of spacers (19,20) 5. The rolling mill according to any one of the claims 1 to 4, wherein a thickness measuring device (24) conveniently having a signa transmitter for adjusting the roll pressure force, in particular for adjusting the hydrostatic bearing elements (11 to 14) and/or the hydraulic cylinders (17, 18), is provided on the discharge side of the rolled stock from the roll supporting structure immediately or virtual immediately to it, conveniently at a maximum distance of 125 to 150 percent of the diameter of the largest roll of the roll system from its axis of symmetry or close to the roll gap (23) in the area of the said rolling stock discharge.

6. The rolling mill according to any one of the claims I to 5, wherein a wedge adjustment (31) is provided underneath of, conveniently at least two, in particular hydrostatic bearing elements (13, 14) actina on the roll barrel(s) of the lower or lowermost roll(s) 17 (10), a.o. conveniently also for compensating the wear of the lowermost series of rolls (2, 8, 10) or the lowermost roll (10), which wedge adjustment is subject to the action of an hydraulic actuating cylinder (32), which cylinder or its actuator or its pressure medium supply is actuable for controlling the elast, ic bending line(s) of the lower roll(s) (2,8,10) by means of signal transmitters, in particular indirectly, mainly via a computer control, with the computer comparing the input set values for the rolling stock to be treated to the actual values of the signal transmitters or the incoming signals, which signal transmitters are integrated into the previously men_tioned bearing elements. (13, 14) and/or arranged in the surface evenness measuring device, an additional control by means of hydraulic lifting, traction or differential cylinders (29, 30) possibly being combined therewith.

15.7. The rolling mill according to any one of the claims 3 to 6, wherein hydraulic traction or differential cylinders (29, 30) are arranged conveniently pivotally above the roll necks or bearings, convenientlysimple journal bearings, advantag eously spherical roller bearings (27, 28) of the upper or topmost rool(s), in particular the upper back-up roll (9), in the upper lateral area of the roll supporting structure, preferably on either side of the upper spacer (19) in the free space between the steel slabs (21, 22) essentially forming the main supporting structure,-the piston rods (33, 34) of the cylinders being positively connected to the said roll necks or their housings via traction elements (35,36) extending directly to the bear or bearing necks of the upper or topmost roll(s) (9), in particular vi, - 18 a pivoting bearing which is conveniently provided on an upwardly directed projection 35a, 36a of the journal bearing housing (27,28).

8. The rolling mill according to any one of the claims 1 to 7, wherein the present or supplied refrigerating medium roll oil or roll emulsion is provided for the construction of the hydrostatic supporting oil gapsof the bearing elements for the upper or topmost or the lower or lowermost rolls, in particular back-up rolls, and/or for optionally hydrostatically supported thin rolls.

9. A rolling mill substantially as hereinbefore described under reference to the accompanying drawing.

10. A rolling mill having at least two superimposed rolls with hydraulic medium acting directly on the outer jacket of the topmost roll in the area of the roll barrel and in addition two hydraulic cylinders acting on each side of the topmost roll on its roll bearings or roll bearing necks thereby to control the elastic bending line of the rolls.

zo 11. A rolling mill according to claim 10 comprising means for measuring the surface evenness of the material being treated by the rolling mill and emitting signals in dependence - on the measurements and means for receiving these signals and controlling the elastic bending line of the topmost roll in response to such signals.

19 12. A rolling mill according to claim 10 comprising means for -measuring the strip thickness of the material being treated by the rolling mill and emitting signals in dependendence on the measurements and means for receiving these signals and controlling the elastic bending line of th e topmost roll in response to such signals.

13. A rolling mill according to any one of claims 8 to 11 wherein there is train of rolls above the material and another train of rolls below the material to be rolled, said topmost roll on which the hydraulic medium and hydraulic act being a back-up roll.

Amendments to the claims have been filed as follows

Claims

Claims:

1. A rolling mill, in particular a cold-rolling mill, preferably for metallic materials, mainly steel and non-ferrous metals, conveniently for rolling, roughing (blooming) or skin-passing (rerolling) of strip or sheets, wi th at least two, conveniently four to ten, mainly essentially superimposed rolls, with an hydraulic medium acting from without directly on the outer jacket of the individual roll barrels, characterized in that on each roll barrel in addition to the hydraulic O medium acting from without direc,.ly on at least two locations of the outer jacket of the roll barrels and consisting of at least two hydrostatic bearing elements and/or hydraulic cylinders preferably acting on conveniently hydrostatic bearing elements acting from without directly on the outer jacket of the individual roll barrels, preferably of the topmost roll, the roll bearings (27,28) or the roll bearing necks of at least the topmost roll, in particular the topmost back-up roll (9), are directly subjected to the action of hydraulic lifting cylinders or hydraulic traction cylinders or differential cylinders (29,30) actuable by signals emitted by a surface evenness measuring device for the control of the elastic bending line(s) of the series of rolls, in particular the topmost back-up roll (9).

2.The rolling mill according to claim 1, wherein in addition to the lifting cylinder control acting on the roll bearings or roll necks (27,28), a control of the elastic bending line(s) of the series of rolls, in particular the roll(s) arranged above the roll gap, preferably the topmost back-up roll, is effected by shifting force lines of the rolling forces, in particular of the compression forces acting from without on the rolls, in particular the topmost back-up roll, in particular completely from the area of the bearings of the roll necks to the area of the roll barrels-and wherein the hydraulic medium directly acting on at least two locations of the outer jacket of the roll barrels of each roll is controlled as a function of the parameters depending on 0 the state of the rolling mill parts effective in respect of material deformation and the material treated, signal transmitters integrated in a surface evenness measuri ng device and/or thickness measuring device and/or in the, in particular upper., hydraulic cylinder, and acting on the hydrostatic bearing element(s) and/or on the conveniently hydrostatic bearing elements.

1

3. The rolling mill according to claim 2, wherein a computer_ control is connected to the signal transmitters, the computer comparing the set values for the rolling stock to be treated to the actual values o of the signal transmitters or the incoming signals, on the one hand, and to the hydraulic cylinders (17,18) or their pressure medium supply or actuators for said cylinders and optionally, in particular indirectly, to the hydrostatic bearing elements (11, 12), on the other hand.

4. The rolling mill according to any one of the claims 1 to 3, wherein the, in particular perpendicular plane of symmetry (S)of t he roll supporting structure or rolling mill stand or roll housing in particular their main supporting structure (19 to 22), made up of two supporting frames (21, 22) arranged on either side of the rolls parallel to their axes and provided with a window at least in the area of the roll barrels or the roll gap, wholly or at least essentially coincides with the in particular perpendicular plane of symmetry (5) of the roll system (1 to 10) or the roll arrangement.

D

5. The rolling mill according to claim 4, wherein the supporting frames (21, 22) are arranged immediately at both sides of the roll systems and parallel to their roll axes and provided with a window are conveniently connected above and/or below the rolls by means of connections (19,20) extending transversely to their axes, in particular very largely rigidly.

6. The rolling mill according to claim 4 or 5, wherein the roll supporting structure consists of frame-like roll housings arranged laterally of the rol 1 jackets or roll barrels (15, 16) and made up of hot-rolled appropriately cut steel slabs (21, 22) cut out for forming the window, at least the upper, horizontal cross beams of these frame- 0 like steel slabs being very largely rigidly connected by means of spacers (19,20).

7. The rolling mill according to any one of the claims 4 to 6, wherein a thickness measuring device (24) conveniently having a signal transmitter for adjusting the roll pressure force, in particular for adjusting the hydrostatic bearing elements (11 to 14) and/or the hydraulic cylinders (17,18), is provided on the discharge side of the rolled stock from the roll supporting structure immediately or virtual Immediately to it, conveniently at a maximum distance of 125 to 1 percent of the diameter of the largest roll of the roll system fr,, its axis of symmetry or close to the roll gap (23) In the- area of tl said rolling stock discharge.-

8. The rolling mill according to.any one of the claims 1 to 7, where a wedge adjustment (31) is provided underneath of, conveniently least two, in particular hydrostatic bearing elements (13_,14) acti 10 on the roll barrel(s) of the lower or lowermost roll(s) (1), a. conveniently also for compensating for the wear of the lowermost seri of rolls (2,8, 10) Or the lowermost roll (19),which wedge adjustme is Subject to the action of an hydraulic actuating cylinder (32), whi cylinder or its actuator or its pressure medium supply is actuable f controlling the elastic bending line(s) of the lower roll(s) (2,8,1 by means of signal transmitters, in particular indirectly, which sign transmitters are integrated into the aforementioned bearing elemen (13, 14) and/or arranged in the surface evenness measuring devic an additional control by means of hydraulic lifting, traction differential cylinders (29,30) being combined therewith.

9. The rolling mill according to claim 8, wherein the cylinders actuated via a computer co ntrol, with the computer comparing the inp set values for the rolling stock to be treated to the actual valu 2S of the signal transmitters or the incoming signals.

10. The rolling mill according to any one of the claims 4 to 9, where hydraulic traction or differential cylinders (29,30) are arranged conveniently pivotally above the roll necks or bearings, conveniently simple journal bearings, advantageously spherical roller bearings (27,28) of the upper or topmost roll(s), in particular the upper back-up roll (9), in the upper lateral area of the roll supporting structure, preferably on either side of the upper spacer (19) in the free space between the steel slabs (21, 22) essentially forming the main supporting structure, the piston rods (33, 34) of the cylinders being positively connected to the aforementioned roll necks or the housings via traction elements (35, 36) extending directly to the bearings or bearing necks of the upper or topmost roll(s) (9).

11. The rolling mill according to claim 10, wherein the piston rods (33, 34)of the cylinders are positively connected to the aforementioned roll necks or their housings via traction elements (35, 36) extending directly to the bearings or bearing necks of the upper or topmost roll(s) (9) via a pivoting bearing which is conveniently provided on an upwardly directed projection 35a, 36a of the Journal bearing housing (27,28).

12. The rolling mill according to any one of the claims 1 to 11, wherein the present or supplied refrigerating medium rolling oil or rolling emulsion is provided for the construction of the hydrostatic supporting oil gaps of the bearing elements for the upper or topmost or lower or lowermost rolls, in particular back-up rolls, and/or for optionally hydrostatically supported thin rolls.

13. A rolling mill having at least to superimposed rolls with hydraulic medium acting directly on at least two locations of the outer Jacket of the topmost roll in the area of the roll barrel and in addition two hydraulic cylinders acting on each side of the topmost roll on its roll bearings or roll bearings necks thereby to control the elastic bending line of the rolls.

14. A rolling mill according to claim 13 comprising means for measuring the surface evenness of the material being treated by the rolling mill and emitting signals in dependence on the measurements and means for receiving these signals and controlling the elastic bending line of the topmost roll in response to such signals.

15. A rolling mill according to claim 13 comprising means for measurinQ the strip thickness of the material being treated by the rolling mill and emitting signals in dependence on the measurements and means for receiving these signals and controlling the elastic bending]in( of the topmost roll in response to such signals.

16. A rolling mill according to any one of the claims 12 to 15 whereii there is train of rolls above the material and another train of roll, below the ma-terial to be rolled, said topmost roll on which the hydrauli medium and hydraulic act being a back-up roll.

17. A rolling mil 1 substantially as hereinbefore described unde reference to the accompanying drawing.