A ROLLING MILL

Abstract: A rolling mill provided with a pair of rolls (₁0,10) rotatable in a roll housing (14) and drivably connected to respective drive gears (20,20) of a main frame and gearbox (17), the drive gears meshing with respective pinions which mesh together. So that rolls (10,10) of widely varying diameters can be driven at appropriate speeds, the main frame and gearbox is capable of being located in either one of two positions angularly spaced at 180 degrees, and the drive gears (20,20) and pinions (26,26) are capable of being re-adjusted in position whereby the drive gears (20,20) can be brought into mutually meshing positions and the pinions (26,26) can be moved apart to become the gears with which the rolls (10,10) are drivably connected.

Description: The invention relates to the rolling of metal. It is a particular problem to design a rolling mill which can be fitted with either relatively small rolls or relatively large rolls to suit the particular metal sections being worked and to drive the selected rolls at appropriate speeds and/or with sufficient torque. It is also a problem in the design of rolling mills that, because of the need to roll at the highest possible rates of production, coupled with the fact that rolling loads within the roll stands are increasing, the driving of the rolls by means of universally jointed shafts is very often a limiting factor. This is because, although such shafts are capable of transmitting high torque when the driving shafts and rolls which they connect are in line, their torque transmitting capacity rapidly falls off when the rolls are moved out of alignment with the gearbox driving shafts, as of course they must often be when the roll gap is varied and even more so if the rolls are to be changed for different diameter rolls. Consequently, to reduce angularity, the universally jointed shafts in some cases need to be unduly long which results in a cumbersome (i.e. space consuming) arrangement and one which is not torsionally stiff. Various attempts have been made to solve this problem. For example, in GB-A-1281404 there is provided a rolling mill having a pair of rolls; a pair of shafts coaxial with the rolls; a first pair of gears coaxial with the shafts; and a second pair of gears in mesh with each other and each in mesh with one of the gears of the first pair. The shafts are mounted in bearings in arms pivoted coaxially with the respective second gears, adjustment means consisting of combined right-hand and left-hand screws being provided for effecting swinging of said arms for adjusting the roll gap with a constant feed centreline. The use of universally jointed shafts for driving the rolls is therefore avoided. However, in this previously known arrangement there is no provision for the fitment of widely varying sizes of rolls with means for driving such rolls at appropriate speeds and with appropriate torque according to their diameters. The rolling mill therefore is not versatile. Rolling mills have been known in which a gear housing has been located in either one of two positions angularly spaced at 180 degrees. For example, in SU-A-1088824 such an arrangement is provided. However, in this arrangement also the mill is not versatile because there is no provision for the fitment of widely varying sizes of rolls with means for driving such rolls at appropriate speeds and with appropriate torque according to their diameters. EP-A0126059 discloses a rolling mill arrangement in which different diameters of rolls can be connected to a gear housing, the rolls being driven either directly from main drive gears or through an auxiliary gear train to provide a roll drive at speeds appropriate to the diameters of said rolls. However, in this case the rolling mill is not versatile because the roll gap adjustment in either mode of operation is strictly limited. The respective gears by which the rolls are driven are at a fixed spacing and any misalignment between the rolls and their respective drive gears is allowed by means of slide couplings. The invention as claimed is intended to provide a better remedy to the problems referred to. It solves the problem of how to design a rolling mill which can be fitted with either relatively small rolls or relatively large rolls to suit the particular metal sections to be worked and the problem of how rolls of such widely varying diameters can be driven at appropriate speeds and/or with sufficient torque. The advantages offered by the invention are, mainly, that since the rolling mill can be fitted with widely varying sizes of rolls and the rolls can be driven at appropriate speeds according to their diameters the rolling mill is extremely versatile. In addition, since the invention provides a rolling mill which does not require the use of universally jointed shafts to enable the roll spacing to be varied, the mill is of relatively compact size and is torsionally stiff. One way of carrying out the invention is described in detail below with reference to drawings which illustrate, by way of example, one specific embodiment, in which:- Figure 1 is a perspective and purely diagrammatic view of rolling mill apparatus embodying the invention, Figure 2 is a part sectional view of an actual installation, looking in the direction of arrow 2 in Figure 1, Figure 3 is a sectional view on the line 3-3 in Figure 1, Figure 4 is a view of the actual installation looking in the direction of arrow 4 in Figure 1, Figure 5 is a view of screwdown mechanism for effecting adjustments of the roll gap, Figure 6 is a diagrammatic illustration of how roll gap adjustments are effected, Figure 7 is a diagrammatic view looking in the direction of arrow 7 in Figure 1, Figure 8 is a similar view to Figure 7 when a roll change has been effected, and Figures 9 and 10 are views showing apparatus embodying the invention installed in a rolling mill. Referring now to Figure 1 of the drawings, the rolling mill apparatus there illustrated includes a pair of rolls 10,10 located in respective pairs of bearings 12,12 carried in a roll housing generally indicated 14, the latter being represented in Figure 1 as two substantial rectangular plates 16,16 with pairs of bores 18,18 for the reception of roll mounting and adjustment means. The roll housing is capable of compensating adjustment, for a purpose and in a manner which will presently be described, along guides indicated 15, on an end face of a main frame and gear housing generally indicated 17. It will be observed that both end faces of the main frame and gear housing are provided with guides 15 for a purpose which will also be described presently. The roll mounting and adjustment means referred to are constituted by pairs of eccentric sleeves 50,52 which extend through the pairs of bores 18,18 in the plates 16,16. The pairs of sleeves are formed integrally with kidney shaped elements 54,56 (not shown in Figure 1) which, in addition to connecting the pairs of sleeves together for simultaneous rotation when roll centre adjustments are being made, act as spacers between the plates 16,16 of the roll housing as best seen in Figure 2. The plates 16,16 are bolted together, with the kidney shaped elements 54,56 between them, by a pair of bolts 58,58. Said bolts extend through respective arcuate slots 60 in the kidney shaped elements (see Figure 4) so that rotational adjustments of the pairs of eccentric sleeves can be effected to vary the roll gap when the bolts have been slackened. Screwdown mechanism which is provided for effecting adjustments of the roll gap is illustrated in Figure 5. This includes a pair of gears 51,53 which mesh together and with respective gears 61 and 63 to enable the pair of eccentric sleeves to be rotated with equal and opposite movement. As shown in Figure 2, the gears 61 and 63 are formed on extensions of the respective eccentric sleeves 52,52. The gear 51 is drivably connected to worm and wormwheel mechanism 55,57 the worm of which can be rotated manually by means of an extraneous handle (not shown) which can be connected to a spindle with a square end 59. As the rolling mill is set up in Figures 1 to 4 and Figure 7, the rolls 10,10 are driven by respective drive gears 20,20 housed within the main frame, said drive gears being mounted in respective pairs of bearings 22,24 and located in constant alignment with said rolls as will presently be described. They are therefore able to be connected to the respective rolls by splined connections 35 (see Figures 2 and 3) with a very high torque transmitting capacity. The drive gears 20,20 are in constant mesh with respective pinions 26,26, the latter being mounted in bearings 28,30 (see Figure 3) and being in constant mesh with each other as shown diagrammatically in Figure 1. The manner in which the drive gears 20,20 are adjustable, which will be described in detail presently, allows said gears to move orbitally around their respective pinions as roll gap adjustments are made, this being shown diagrammatically in chain-dotted lines in Figure 1. The drive gears thus remain in constant and complete mesh with their respective pinions at all times. Referring now in particular to Figures 2 and 3, it will be seen that at the end of the main frame and gear housing remote from the roll housing, there is bolted an input drive gearbox generally indicated 25. This includes an input drive shaft 27, a main drive gear 29 and a main drive pinion 31 drivably connected to one of the pinions 26 by means of a splined connection 33. As previously explained, roll gap adjustments are effected by rotational adjustments of the pairs of eccentric sleeves 50,52 with equal and opposite movement. It will be apparent that since the drive gears 20,20 are maintained in axial alignment with the respective rolls at all times, and that each drive gear moves along a much larger radius as it makes a simultaneous positional adjustment about its respective pinion 26 with which it is in constant mesh, this can only take place if roll gap adjustment is accompanied by a compensating adjustment of the roll housing 14 along the guides 15 on the end face of the main frame. Thus it will be understood that before roll gap adjustments are made, the bolts 58,58 which clamp the roll housing in position on the main frame will be slackened and rotational adjustments of the pairs of eccentric sleeves will then effect the required roll gap adjustment and simultaneously bring about the required compensating adjustment of the roll housing along the guides 15. In other words, by virtue of the fact that the drive gears are located in axial alignment with the rolls by the splined connections 35, the drive gears 20,20 take up their required positions about the respective gears 26,26 according to the spacing of the rolls, and the roll housing takes up a resultant position along the guides 15 according to the positioning of the drive gears and according to the particular orientation of the eccentric sleeves. (This is true irrespective of the "throw" of the eccentric sleeves. Thus it is a simple matter to mount a different roll housing in position if required, the replacement housing having different diameter rolls and/or different roll spacing outside the range of roll spacing available with the original roll housing). This is illustrated diagrammatically in Figure 6 the dimensions of which have been modified somewhat for the sake of clarity but which it is thought illustrate the movements of the various elements of the apparatus more clearly. It will be seen that as the eccentric sleeves are rotated with equal and opposite movement, as indicated by the arrows, to bring the centres of rotation of the bearings 12,12 from the positions P1, P1 to the positions P2,P2, the drive gears 20,20 can only move about the axes of the respective pinions 26,26 from the positions P1,P1 to the positions P3,P3. Consequently, to ensure that the positions P2 and P3 always coincide it is necessary for the roll housing, represented by the two substantial metal plates 16,16, to make the compensating movement indicated by the chain-dotted line, this being equal to the misalignment between the points P2 and P3 which would otherwise take place. (It will be understood that this is a notional misalignment only, for purposes of illustration. In other words it is a misalignment which never in fact occurs because the rolls and their associated drive gears are maintained in constant alignment at all times by the splined connections 35). Referring now in particular to Figure 3, it will be seen that the bearings 22,24 in which the drive gears 20,20 are mounted, and the bearings 28,30 in which the respective pinions 26,26 are mounted, are located in pairs of carrier plates 32,32. Said carrier plates together with respective connecting casing members 34 form extremely robust cage members 37 (which as the mechanism is set up as shown in Figures 1 to 4 and Figure 7 locate the drive gears for constant mesh orbital adjustment about their respective pinions 26,26 as adjustments of the roll centres takes place). As shown, the pairs of carrier plates are provided with sleeve portions 36,38 which, as the mechanism is set up in Figures 1 to 4 and Figure 7 locate the cage members in the main frame and gear housing, said sleeve portions being concentric with the respective pinions 26. In addition, the sleeve portion 36 shown in Figure 3, being relatively long, serves to guide the shaft of the input pinion as the input drive gearbox 25 is being fitted in position, the respective casing sleeve of said input drive gearbox locating on the outer periphery of said sleeve portion 36 as shown in Figure 3. Further sleeve portions 40 and 42 are provided on the pairs of carrier plates. The sleeve portions 42 are relatively long and facilitate the drive gears 20,20 being brought into line with spline connections 35 of the rolls as a roll housing 14 is being mounted in position on the end face of the main frame and gear housing 17. The further sleeve portions 40 and 42 are concentric with the respective drive gears 20 but, as the mechanism is set up in Figures 1 to 4 and Figure 7, these sleeve portions at this time play no part in locating the cage members in the main frame and gear housing. Referring now to Figures 7 and 8, these illustrate the fact that the extremely robust cage members generally indicated 37,37 formed by the pairs of carrier plates 32,32 and casing members 34 are pivotally mounted within the main frame and gearbox 17 for movement about alternative pairs of pivots. In other words they can move about the axes of the respective drive gears or of the respective pinions. The arrangement is such that, instead of the pinions 26,26 being in constant mesh with each other as previously described, and providing a speed increase to the rolls as shown in Figure 7, the drive gears 20,20 can be brought into mesh with each other as the pinions 26,26 are moved apart as shown in Figure 8. Moreover, since the main frame and gearbox is capable of being turned around end to end as will presently be described, and Figure 8 is a view of the apparatus when this has been effected, the pinions 26,26 can then become the gears connected by splined connections to the respective rolls and one of the drive gears will be the gear receiving drive from the main drive pinion 31. There is therefore obtained a substantial gearing down in the drive to said rolls. (It will of course be understood that there will at this same time be fitted a replacement set of rolls of larger diameter than before, for which the gearing down and consequent greater torque is appropriate, conveniently by the replacement of the entire roll housing as a unit by a roll housing of the same basic design as that described and illustrated, and this is why the main frame and gear housing in Figure 1 is shown to have guides 15 at its opposite ends. The guides 15 in Figures 2 and 3 are shown to be provided in respective adaptor plates 100 and 102 at the opposite ends of the main frame and gear housing 17. The splined connections of the new roll shafts will match the splined shafts of the pinions 26. The splined connections of one of the drive gears 20,20 will be suitably adapted for connection to the main drive pinion 31 of the replacement input gearbox 25 which will also be fitted at this time, the replacement gearbox 25 being designed both to cater for the variation which will be apparent between the centre heights of the gear 20 and pinion 26 receiving drive from the input gearbox and to make any appropriate variation in the input drive speed). During the geared down mode of operation, adjustments of the roll centres towards or away from each other results in the pinions 26,26 performing orbital adjustments around the respective drive gears 20 as indicated in chain-dotted lines in Figure 8, the roll housing being able to make compensating adjustments along the guides 15 as previously explained. As shown in Figures 7 and 8, the means whereby either the pinions 26,26 or the drive gears 20,20 can be maintained in mesh include respective pairs of clamping plates 64,64 (see also Figure 2) pivotally movable about respective pivots 62,62. The clamping plates are provided with part circular apertures 66 and 68 which can clamp the sleeve portions 36,38 or 40,42, selectively, in respective part circular seatings 69 and 71 formed within the main frame and gearbox. The part circular seatings are formed, as shown, in inclined surfaces of internal frame parts, these surfaces each having abutment areas 104 and 106 against the one or the other of which the respective clamping plate is tightly clamped to locate the selected sleeve portions firmly but rotationally adjustable in their respective seatings. The abutment areas 104 and 106 of each of the inclined surfaces are provided with upstanding key pieces 65 and 67 (see Figures 3 and 7) engageable with slots in the areas of the clamping plates which are brought alternately into clamping engagement with said abutment areas. The clamping plates are movable between their alternate positions by mechanism including a rotatable shaft 73 with oppositely handed screwthreaded portions engaging respective nuts 75,77 trunnion mounted between lever portions 79 of the respective pairs of clamping plates. The shaft 73 is capable of being rotated by an extraneous tommy bar (shown in chain-dotted lines in Figure 7) by way of a universally jointed connecting shaft 81. It will be understood that the clamping plates are not clearly visible in Figure 3 because of the section taken, but the key pieces 65 and 67 and the respective pivots 62,62 can be seen in that view. Referring now to Figure 9, this illustrates the manner in which the arrangement just described can be arranged in a rolling mill. The main frame and gearbox 17 is shown to be mounted on a base 82 with the input drive gearbox 25 and roll housing 14 mounted on opposite faces as described above. The input drive gearbox is shown to be connected to a motor 84 by means of an in-line drive shaft 86, the latter incorporating a quick release coupling 88 which is manually operable by means of a lever 90. The base 82 contains a hydraulically operated rotary actuator generally indicated 92 and the arrangement is such that when the quick release coupling has been disconnected by moving the lever 90 to the position shown in chain-dotted lines, the main frame and gearbox can be rotated through 180 degrees about a vertical axis. The input drive gearbox and roll housing can thus be transposed (but it will of course be understood that the roll housing, or more conveniently a replacement roll housing, will then have different diameter rolls to suit the speed increase or gear down obtained by the reversal of drive through the main gearbox). In Figure 10 there is illustrated a very similar arrangement to that just described except that the roll housing is located on an upper face of the main frame and gearbox 17 and with its rolls vertically arranged. Consequently, the main frame and gearbox 17 is trunnion mounted for rotation about a horizontal axis 94 (again by means of a rotary actuator not shown in this view). In this arrangement, the input drive gearbox 25 incorporates bevel gears 96 and 98. However, the installation can be operated in almost exactly the same way as that described with reference to Figure 9. When the lever 90 of the quick release coupling 88 has been moved to the position shown in chain-dotted lines, the main frame and gearbox can be inverted. The input drive gearbox and roll housing can thus be transposed relative to the main frame and gearbox so that there can be obtained either a speed increase of a gearing down in the drive to the rolls as previously described. In all these arrangements described, the roll housings and input drive gearboxes will not pose any problem of handling to enable them to be transposed as required. However, special handling apparatus could quite well be provided for effecting this in the most convenient manner. Thus there is provided rolling mill apparatus which, by virtue of the fact that it does not incorporate universally jointed shafts, and the fact that all drive gears are in constant full mesh, will be capable of being driven at high speed and with high torque. In addition, the construction of the roll housing, and the means for adjusting the roll gap by eccentric sleeves, results in an extremely rigid arrangement capable of withstanding relatively heavy rolling forces. Since the roll housing is relatively simple and small, roll changing will be quick and simple and will not require complicated roll changing equipment. It will in fact be understood that, especially in the way in which roll changing can quickly and easily be effected, apparatus embodying the invention has many of the advantages of a so-called cantilever stand. It is, however, much more robust than a cantilever stand because of the fact that its rolls are simply supported, that is to say because of the fact that each roll has bearings at its opposite ends. In either mode of operation, a relatively wide range of roll diameters can be accommodated and a similarly wide range of roll speeds to suit a wide range of roll diameters can be brought about by fitting different input drive gearboxes. However, by virtue of the fact that the mechanism can be adjusted in such a way that the pinions 26,26 can be either the driving or driven gears and the gears 20,20 the driven or driving gears there is obtained a speed up or gearing down with a roughly corresponding increase in torque transmitting capacity, the roll housing being inherently capable of withstanding the consequent high stresses imposed on it throughout its extremely wide range of use by virtue of its construction and the manner in which the rolls are mounted for adjustment in the eccentric sleeves. Various modifications may be made. For example, the rolling mill need not necessarily incorporate an input drive gearbox. The drive from the drive shaft 86 could, in the installation illustrated in Figure 9, be transmitted by way of suitable driving adaptors directly to the appropriate one of the pinions 26 or to the appropriate one of the drive gears 20, depending on the mode of operation being employed. A universally jointed shaft instead of the in-line drive shaft 86 could in fact be used at this location. This would then cater for the height variation which occurs when one of the gears 20 is to receive input drive instead of one of the pinions 26. It will also be understood that although it is obviously desirable for the main frame and gearbox to be rotatably mounted for convenient positional adjustment into the selected one of its two angularly spaced positions, this is not essential. It could be re-positioned from time to time using a crane and some convenient means for clamping it in its required position. The roll housing need not necessarily be mounted in guides on an end face of the main frame and gearbox. Indeed, if the rolls are made relatively wide and of a relatively large diameter the roll housing may become too large to be mounted solely in such guides and it may need to be mounted on its own bed frame. It can however still be slidably adjustable in a direction perpendicular to a plane containing the axes of the rolls.

Claims: A rolling mill comprising a roll housing (14); a pair of work rolls rotatable in said roll housing; a main frame and gear housing (17); respective drive gears (20,20)located within said main frame and gear housing and in a first mode of operation of the mill drivably connected to said work rolls; respective pinions (26,26) located within said main frame and gear housing and in constant mesh with the respective drive gears (20,20); means in said first mode of operation of the mill, for causing the pinions (26,26) to mesh together and for accommodating orbital adjustment of the respective drive gears (20,20) towards or away from each other around the respective pinions (26,26) to thereby suit the spacing of the rolls (10,10) in the roll housing (14); means for locating the main frame and gear housing (17) in either one of two positions angularly spaced at 180 degrees; and first adjustment means for adjusting the drive gears (20,20) and pinions (26,26) within the main frame and gear housing (17) between said first mode of operation of the mill and a second mode of operation of the mill at which the drive gears (20,20) are in mutually meshing positions and the pinions (26,26) are spaced apart and orbitally adjustable towards or away from each other about their respective drive gears (20,20) to thereby suit a different spacing of the rolls (10,10) in the roll housing (14) so that, depending upon the orientation of the main frame and gear housing (17) and the adjustment of the gearing, there is obtained either a speed increase or a gearing down, this providing a speed differential between the different roll drives obtained so that rolls of widely varying diameters can be driven at appropriate speeds. A rolling mill as claimed in claim 1, in which the drive gears (20,20) and respective pinions (26,26) with which they are in constant mesh are located in respective cage members (37,37) and means are provided for mounting said cage members for pivotal adjustment about the axes of the respective drive gears (20,20) or of the respective pinions (26,26) selectively. A rolling mill as claimed in either one of the preceding claims, in which means whereby either the pair of drive gears (20,20) or the pair of pinions (26,26) can be maintained in mesh, and the respective cage members (37,37) secured for pivotal adjustment about the axes of the respective drive gears or of the respective pinions, selectively, include pairs of clamping plates (64,64) pivotally movable about respective pivots (62,62) and capable of being secured in alternative positions in which respective pairs of part-circular apertures (66,66 or 68,68) selectively locate sleeve portions (40,42 or 36,38) concentric with the drive gears (20,20) and pinions (26,26) respectively in respective part-circular seatings (69,69 or 71,71) formed within the main frame and gearbox. A rolling mill as claimed in claim 3, in which the pairs of clamping plates (64,64) are movable about the respective pivots (62,62) and secured in their alternative positions by means of a rotatable screw mechanism including a rotatable shaft (73) with oppositely handed screwthreaded portions engaging respective nuts (75,77) trunnion mounted between lever portions (79) of the respective pairs of clamping plates, the shaft being adapted for rotation by an extraneous tommy-bar. A rolling mill as claimed in any one of the preceding claims, in which means for effecting adjustments of the roll centres towards or away from each other include pairs of eccentric sleeves (50,52) located in bores (18,18) in the roll housing (14), and compensating adjustment of the rolls (10,10) to retain their axial alignment with the drive gears (20,20) or with the pinions (26,26) as the case may be, is effected by re-adjustment of the roll housing (14) in guides (15,15) extending perpendicular to a plane containing the axes of the rolls. A rolling mill as claimed in any one of the preceding claims, in which the main frame and gear housing (17) has on its opposite end faces mounting means either one of which can receive the roll housing (14). A rolling mill as claimed in any one of the preceding claims, in which the main frame and gear housing (17) is rotatably mounted for convenient positional adjustment into the selected one of its two angularly spaced positions. A rolling mill as claimed in claim 7, in which a hydraulically operated rotary actuator (92) is provided to rotate the main frame and gear housing (17) into the selected one of its two angularly spaced positions. A rolling mill as claimed in either one of claims 7 and 8, in which the main frame and gear housing (17) is rotatable about a vertical axis for positional adjustment into the selected one of its two angularly spaced positions, the rolls (10,10) of the roll housing (14) being mounted for rotation about horizontal axes and being located at one end of the main frame and gear housing (17). A rolling mill as claimed in either one of claims 7 and 8, in which the main frame and gear housing (17) is rotatable about a horizontal axis for positional adjustment into the selected one of its two angularly spaced positions, the rolls (10,10) of the roll housing (14) being mounted for rotation about vertical axes and being located above the main frame and gear housing (17).

Inventors: WILSON, ALEXANDER IAN
Applicants: IAN WILSON TECHNOLOGY LIMITED
Application year: 1988
Main classification: B21B35
IPC codes: B21B31, B21B35, B21B13