WO1997003768A1 - Commande de profil variable pour cylindres - Google Patents

Commande de profil variable pour cylindres Download PDF

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Publication number
WO1997003768A1
WO1997003768A1 PCT/US1996/011339 US9611339W WO9703768A1 WO 1997003768 A1 WO1997003768 A1 WO 1997003768A1 US 9611339 W US9611339 W US 9611339W WO 9703768 A1 WO9703768 A1 WO 9703768A1
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WO
WIPO (PCT)
Prior art keywords
roll
shell
wedge
bars
shaft
Prior art date
Application number
PCT/US1996/011339
Other languages
English (en)
Inventor
Curt Braun
Original Assignee
Fata Hunter, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fata Hunter, Inc. filed Critical Fata Hunter, Inc.
Priority to AU64533/96A priority Critical patent/AU6453396A/en
Publication of WO1997003768A1 publication Critical patent/WO1997003768A1/fr

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Classifications

    • 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
    • B21B27/03—Sleeved rolls
    • B21B27/05—Sleeved rolls with deflectable sleeves

Definitions

  • This invention relates to variable crown rolls for rolling mills, strip levelers, coating apparatus and the like.
  • Strip rolling mills, plate rolling mills, and levelers have been used to fabricate, for example, sheet metal.
  • the process involves taking a thick plate or strip of metal, which may be hot or cold, and rolling the metal between two or more rolls.
  • the gap between the rolls is smaller than the thickness of the metal, so that after the metal passes between the rolls, it has a reduced thickness.
  • the metal may then be passed to a leveler to "level" the metal.
  • the leveler has many rolls arranged into two rows with horizontally offset centers. The metal is passed through the rolls whereby it is flexed up and down. The rolls are positioned so that the amount of flexing decreases as the metal travels to the end of the leveler.
  • undesirable variations in thickness of the metal can occur, for example, because the rolling loads applied to the longitudinal center of the roll flex or bend the roll between the supports. This rolling or flexing, unless compensated for by a crown on the roll, will produce a product having undesirable variations in thickness across its width.
  • a rolling mill may be used for metals of different widths, thicknesses, and properties.
  • a fixed crown ground into the roll may not properly compensate for bending for the various products rolled and flat products when desirable may not be uniformly obtained.
  • the rolls used in the rolling mills can be provided with a means to adjust the crown of the roll.
  • the function of the crown control on the roll is to shape the outer crown of the roll so that the metal passing through the mill is produced with a flat surface or constant profile and a uniformly reduced thickness. It is ideal for the crown to adjust continuously during the rolling process; so that the process is not stopped to adjust the crown, and the crown can be adjusted nearly instantaneously based on profile data collected from the metal just rolled. If the crown is not adequately controlled, the metal will not have a flat surface or uniform profile, and it must be melted down for reuse.
  • One apparatus providing a roll with a variable profile utilizes a plurality of rings or "wedges" inte ⁇ osed between a roll core and a sleeve.
  • the rings are angled so that they mate against an angled surface of the sleeve.
  • the angled surfaces interact to either push the sleeve radially outward or allow the sleeve to contract radially inward, thereby varying the profile of the sleeve.
  • the angle on the movable rings is constant along the length of the roll. Thus, to obtain a larger crown in the center of the roll, there must be independently movable rings at the center of the roll.
  • the rings at the center of the roll can then be displaced a greater distance than the outer rings to provide a larger crown in the center of the roll. This is somewhat disadvantageous because of the additional parts required and because high stress concentrations occur at the single point contacts at the edges of the rings.
  • variable crown rolls utilizing rings or wedges which move longitudinally along the axis of the roll, it is desirable to provide a simplified means for varying the crown of the roll by larger amounts at different locations on the roll more uniformly. It is further desirable to more efficiently move the rings between the roll shaft and the sleeve.
  • the roll comprises a generally cylindrical roll shaft surrounded by a hollow cylindrical shell with a pair of opposing mating surfaces in between the roll shaft and shell.
  • the opposing mating surfaces have contours with camming angles that vary continuously along the length of the roll.
  • the means for translating one of the surfaces relative to one of the other opposing surfaces comprises in one embodiment fluid chambers acting on a flange of a wedge interposed between the roll shaft and the shell.
  • An inner fluid chamber acts on the wedge flange to move the wedge flange longitudinally outwardly
  • an outer fluid chamber acts on the wedge flange to move the wedge flange longitudinally centrally, that is, toward the center of the roll.
  • a single wedge is interposed between the shell and the roll core.
  • One fluid chamber acts on the right side of the wedge to move the wedge to the right.
  • the other fluid chamber acts on the left side of the wedge to move the wedge to the left.
  • a novel crown control mechamsm to control the crown on a leveler.
  • the mechanism comprises a plurality of angled surfaces mating with opposing angled surfaces. At least two of the angled surfaces having different magnitude.
  • a means for translating one of either the angled surfaces or the opposing angled surfaces is also provided.
  • FIG. 1 is a schematic elevational view of a rolling mill
  • FIG. 2 A is a partial cross-sectional view of a roll core and shell with mating opposing surfaces; the proportions of which are exaggerated for purposes of illustration;
  • FIG. 2B is an enlarged view of the area designated by the circle 2B in FIG. 2A;
  • FIG. 3 is a partial cross-sectional view of an alternate embodiment of the roll in FIG. 2A utilizing a split roll core;
  • FIG. 4 is a partial cross-sectional view of an alternate embodiment of the roll of FIG. 2A utilizing a fixed wedge
  • FIG. 5 is a fragmentary cr ⁇ ss-sectional view of a roll with a single wedge and a fluid chamber disposed on each end of the roll to translate the wedge;
  • FIG. 6 is a fragmentary cross-sectional view of a roll with a single wedge and two fluid chambers on the same end of the roll to translate the wedge;
  • FIG. 7 is a fragmentary cross-sectional view of a roll with two wedges and two fluid chambers disposed on each end of the roll to translate the wedge;
  • FIG. 8 is a fragmentary cross-sectional view of an alternate embodiment of the roll in FIG. 7 utilizing wedges, each with a continuously curved surface facing the roll core;
  • FIG. 9 is a perspective view of two wedges illustrating how the wedges mesh together.
  • FIG. 10 is a fragmentary cross-sectional view of a roll having an external actuator for translating the wedges
  • FIG. 11 is a perspective view of the roll neck of the roll in FIG. 10;
  • FIG. 12 is a cross-sectional view of an alternate external actuator for the wedges for the roll of FIG. 10;
  • FIG. 13 is a schematic illustration of the rolls of a coating apparatus;
  • FIG. 14 is a perspective view of an alternate embodiment of the roll neck of FIG. 10;
  • FIG. 15 is an end view of a further alternate embodiment of the roll neck of FIG. 10;
  • FIG. 16 is a fragmentary cross-sectional view of a roll utilizing the roll neck of FIG. 14;
  • FIG. 17 is a fragmentary partial cross-sectional schematic view of a crown control mechamsm for a leveler
  • FIG. 18 is a fragmentary partial cross-sectional schematic view of an alternate crown control mechanism for a leveler
  • FIG. 19 is a cross-sectional plan view of a roll with a single wedge without flanges
  • FIG. 20 is a fragmentary partial cross-sectional schematic view of a roll with two wedges utilizing left and right hand threads on the roll and wedges;
  • FIG. 21 is a schematic illustration in partial cross-section of a roll utilizing an oil film.
  • FIG. 1 shows a rolling mill having a supporting structural frame 20, a plurality of rolls, generally designated 22, supported in the support strucmre with bearings and chocks 24 commonly referred to in the art as bearing-chock assemblies.
  • the exemplary mill shown has four rolls. There are two work rolls 26 which operatively interact to reduce the thickness of a strip of material 28 passing in between the work rolls. The two larger rolls are backup rolls 30 which operatively interact with the adjacent work roll to support and stiffen the work roll.
  • the rolls are rotated on the roll chocks about their central axis by a conventional drive mechanism (not shown) or by frictional engagement with another roll or the workpiece, and the strip of material 28 is passed between the rotating rolls to reduce the thickness of the strip of material.
  • the bearing-chock assemblies shown in greater detail in FIG. 2A include a bearing with an inner race 32 which fits tightly around a roll shaft, generally designated 34, and an outer race 35 capable of rotation relative to the inner race and which engages the supporting backup roll chocks 37.
  • the bearing chock assemblies are shown schematically and further, they are shown smaller than their actual size relative to the rolls. To obtain a strip of material with a flat surface or a uniform reduced profile, it is desirable to vary the outer crown of one or both of the work rolls in the mill.
  • the roll 22 shown in Figure 2 A can be employed as any one of the rolls 22 utilized in the rolling mill. Generally, there are two such rolls in a mill, one above the workpiece and the other below the workpiece, i.e., on each side of the workpiece.
  • the adjustable rolls may be either the work rolls or backup rolls. In other types of mills, the adjustable roll can be an intermediate roll. It should be recognized that features shown in FIG. 2A and other of the drawings are exaggerated for purposes of illustration. For example, the actual curvature between a roll core and shell with respect to the roll axis is only a very few degrees or fraction of degrees instead of the sweeping curve illustrated.
  • the roll comprises the roll shaft 34 having a centrally located large diameter roll core 36 and stepped down diameters at the ends forming roll necks 38.
  • the size of the step down is also exaggerated in the Figures, except for FIGs. 19 and 20, for the sake of clarity.
  • the bearing chock assemblies fit around the roll necks to support the roll in the strucmral frame.
  • a hollow cylindrical shell 40 surrounds the roll core and a portion of the roll necks for some embodiments.
  • a safety guard 42 extends radially inward from the shell and engages the roll neck. The safety guard is attached to the shell with conventional fasteners (not shown).
  • the internal circumferential surface 44 of the roll shell is continuously curved along the length of the roll, so that it has increased thickness at one end. It will be recognized that when stating that a surface of the roll is continuously curved, reference is made to the shape of the surface in a longimdinal cross section. Essentially all parts of the roll surfaces are curved if viewed in a transverse cross section.
  • the outer circumferential surface 46 of the roll core opposing the inner surface of the shell is also continuously curved to mate with the inner surface of the shell.
  • an external actuator not illustrated in FIG. 2A
  • the complementary curved surfaces engage and force the shell to elastically expand radially outward and create or enlarge a crown on the shell.
  • the shell is allowed to contract radially inward. The hoop strength of the shell and the rolling forces cause the shell to elastically contract radially inward.
  • the roll core and shell are rotated about the center line by a conventional drive mechamsm (not shown).
  • the crown of the shell is varied by moving the roll core axially within the shell.
  • the curved surfaces of the roll core and shell interact to vary the crown of the shell and thereby control the thickness and flatness of the workpiece material.
  • FIGs. 2A, 2B, 3-8, 10, 12, 16, 19, and 20 are provided with a pair of mating opposing surfaces according to the present invention as described in the following discussion of FIG. 2B.
  • the complementary surfaces are continuously curved so that the camming angle o- c of the surfaces at the center of the roll is larger than the camming angle af located toward each end of the roll. Because the central camming angles have a greater magnitude than the outer camming angles, the crown at the center of the roll is increased more than the crown at the ends of the roll for a given longimdinal movement of the core.
  • the camming angles of the surfaces are defined by a first line A through a point of interest X on the surface and which is parallel to the centerline B (see FIG. 2A) of the roll and the portion of a second line C which is tangential to the point X on the surface.
  • all of the camming angles a in the embodiment shown in FIG. 2A open toward an end of the roll.
  • the overall contour of the surfaces is determined by finding the camming angle at a finite number of points on the surface.
  • the camming angle at a specific point on the surface is found by taking the desired maximum change in roll radius ⁇ R at that point and dividing it by the maximum distance £ by which the roll core is moved longimdinally in the axial direction.
  • tan ⁇ R/ .
  • ⁇ R indicates the variation in shell crown
  • i. indicates the lateral(axial) stroke between the opposing curved surfaces.
  • This provides a result that is essential an average of the angles over the stroke £.
  • the continuously varying curvature of the surfaces of the core and shell can be considered to resemble half of a cycle of a very long period sine wave.
  • the ends of the curvature are near adjacent positive and negative peaks of the wave where the slope is slight.
  • the center portion of the roll has the greatest slope, i.e. largest camming angle.
  • deflection of the shell can be greatest in the center where the slope is largest.
  • the curvature is typically not a sine function.
  • the outside of the shell may be ground in the shape of a parabola.
  • the desired change in radius of the outside of the shell at each location along the length to achieve a desired crown is determined empirically as described hereinafter. The result is a curvature that may not be readily expressed mathematically.
  • the desired angle over a length of the curved surfaces is related to the maximum deflection of the shell desired at that location and the length of stroke of the core. Some numerical values will be of assistance.
  • Half of the length of an exemplary roll body is 900 mm.
  • the longimdinal stroke of the curved surfaces relative to each other is 50 mm.
  • the maximum radial deflection in the center of the roll is in the order of 0.5 mm.
  • a preferred manufacmring technique is to assemble a roll core and shell with the shell positioned in the middle of its intended longimdinal average stroke. The outside of the shell is then ground to the desired contour. By shifting the core in one direction the deflection of the center of the roll increases and by shifting in the opposite direction, the center radius decreases.
  • a middle, neutral position for the core relative to the shell is desirable in some mills since it may be desirable to have a negative "crown" for some products where a distinct crown is desired on the workpiece.
  • the stroke of the core relative to the shell may be about 50 mm in each direction from the neutral position.
  • the camming angle will be somewhat less since less deflection is required.
  • the average tan ⁇ from an end of the roll to its center is about half of the maximum camming angle or about 0.29° .
  • the camming angle near the end of the roll may be vanishingly small or zero, whereas the camming angle near the center of the roll is appreciably larger since that is the location where the maximum change in crown is desired.
  • FIG. 3 illustrates a split shaft alternative embodiment of the roll of FIG. 2A.
  • the shell 48 is curved so that it has increased thickness at the center.
  • the roll core is split into two halves: a shaft receiving roll core 50 and a shaft roll core 52.
  • the shaft receiving roll core has a connecting shaft receiving bore 54, shown in dashed lines, for receiving a connecting shaft 56 extending internally from the shaft roll core.
  • the shaft 56 slidably fits into the bore 54 to connect the two halves of the roll core.
  • the camming angles open away from the longimdinal center of the roll.
  • an annular wedge 60 extending along the length of the roll core is interposed between a roll core 62 and shell 64 of a roll.
  • the shell has a flange 65 at each end which extends radially inward to fix the wedge relative to the shell.
  • the flanges on the wedges and shell of this and other embodiments can be integral with the wedge or shell or they can be separately attached by conventional fasteners (not shown in most embodiments, but see FIG. 15).
  • the choice of how the flange is attached is largely governed by the assembly constraints of the roll. Another consideration is that the shell must be centered relative to the center line of the mill for most embodiments.
  • the mating opposing surface 68 is the outer circumferential surface of the roll core.
  • the shell 64 has a substantially constant thickness, and the wedge has an increased thickness at one end.
  • the camming angles in this embodiment open toward an end of the roll.
  • the mating surfaces engage and force the wedge and shell to elastically expand radially outward to create or enlarge a crown on the roll.
  • the shell and wedge are allowed to contract radially inward.
  • the hoop strengths of the shell and wedge cause the shell and wedge to contract radially inward.
  • the wedge is fabricated from steel and coated with polytetrafluoroethylene or the like to lubricate the wedge and facilitate the sliding of the wedge between the roll core and shell.
  • the magnitude of the camming angle a again increases toward the longimdinal center of the roll, so that a larger crown variation is produced at the center of the roll.
  • all of the camming angles open toward an end of the roll. Because of the curved surface, the shell increases in thickness toward an end.
  • the wedge is translated longimdinally in the axial direction toward the thicker end of the shell. Translating the wedge away from the thicker end reduces the crown. Means for translating the wedge are discussed below.
  • the embodiment shown in FIG. 6 has a wedge 80 inte ⁇ osed between a shell 82 and a roll core 84.
  • the opposing complementary surfaces of this embodiment comprise the inner circumferential surface 86 of the wedge and the outer circumferential surface 88 of the roll core.
  • the camming angles open toward an end of the roll.
  • This embodiment like the embodiment of FIG. 4, provides a further advantage because the shell, which wears out and must be replaced, is more easily and inexpensively fabricated due to it having a constant thickness.
  • the fabrication of the roll core is made more costly by making l the outer circumferential surface curved, but that cost increase is offset by the reduction in cost from fabricating the shells with a constant thickness.
  • an actual roll with a roll neck 400 of only slightly less diameter than the roll core 402 has an annular wedge 404, without flanges, inte ⁇ osed between the roll
  • the opposing curved surfaces 408 between the wedge and shell represent an actual curve. Because it is frequently undesirable to have any change in crown at the ends of the roll, the curve of the opposing surfaces may be flat at the ends so that there is no camming angle.
  • Annular fluid chambers 410,412 are inte ⁇ osed between the ends 414 of the wedge and the shell flanges 416. The flat portion of the curve preferably
  • Fluid passages 418 extend axially through the roll neck and roll core until they are positioned radially inward from the outer edges of the fluid chambers which are defined by the shell flanges. The fluid passages then extend radially outward to the surface of the roll core and the fluid chambers.
  • Static seals 420 are provided between the roll core and the shell flange, and dynamic seals 422 with
  • the roll neck shown is not tapered; however, for steel mills the roll necks are preferably tapered, and the roll necks of the embodiments in FIGs 5, 6, and 19, for example, may be cylindrical or tapered where the roll necks are engaged by bearings. 0 When a single wedge traversing the length of the roll core is used, it is apparent that there is some asymmetry in the roll. The asymmetry can be compensated for in two ways. An equal and oppositely asymmetrical roll can be used as the other work roll or backup roll to counterbalance the effects of the asymmetry, or the effects of asymmetry can be calculated and the shape of the curved surfaces determined to minimize asymmetrical deformation.
  • FIG. 7 illustrates such an embodiment where a roll utilizes two wedges and is symmetrical for any given shift of the wedges.
  • FIG. 7 further illustrates an embodiment where opposing continuously curve mating surfaces, generally designated 90, according to the present invention are provided on the outer circumferential surface 85 of two wedges 92,
  • an alternative embodiment of the roll of FIG. 7 achieves the same reduction-in-cost advantage as FIG. 6 by locating the opposing mating surfaces 90 on the outer surface 89 of the roll core 87 and inner surface 91 of the wedges 93 to reduce the cost of fabricating replacement shells 95.
  • Both of the embodiments of FIGs. 7 and 8 utilize
  • an alternate embodiment of the wedges 98 is crenelated with protrusions 100 and apertures 102 as shown in FIG. 9. Even when the wedges are in the position where there is no enhanced crown, the protrusions 100A of wedge 98A extend into the apertures 102B of wedge 98B, and the protrusions 100B extend into the apertures 102A. Thus, the protrusions mesh together to provide spaced central support for the shell where there would otherwise be none, and therefore prevents adverse crowning on the roll.
  • the single wedge rolls shown in FIG. 5 and 6 provide this advantage over the two wedge rolls. There is no gap at the center of the roll.
  • FIG. 5 there is one continuous wedge 70 covering the length of the roll core 74.
  • the wedge has flanges 150 extending radially inward and sealably engaging the cylindrical roll neck 152.
  • the portions of the roll neck engaged by the bearings may be cylindrical or tapered.
  • the wedge flanges 150 are sealed against the roll neck with an O-ring 154 or other conventional means.
  • the inner circumferential surface of the wedge is sealed with an O-ring 156 against the outer circumferential surface of the roll core at the ends of the roll core.
  • fluid chambers 160, 162 defined radially between the outer circumferential surfaces 158 of the roll necks and the inner circumferential surface 164 of the wedge.
  • the chambers are defined axially by the flanges of the wedge and the radially extending surfaces 166 at the junctions between the roll necks and the roll core.
  • Individual fluid passages 168, 169 through the roll shaft connect each fluid chamber to a fluid source, and end drain lines 170 through the roll shaft connect open cavities 172 between the flanges and roll shell to the atmosphere.
  • the drain lines prevent pressure from building in the cavities, thereby avoiding unwanted axial movement of the wedge and unwanted variation of the roll crown.
  • a central drain line 174 shown partially, runs through the roll shaft to the gap between the wedge and roll core at a location between the two fluid chambers. This fluid drain line prevents fluid pressure from building up between the wedge and roll core which could alter the roll crown if oil were to leak through the seals 156.
  • the roll could be provided with seals, so that fluid is introduced into the outside cavities 172. Fluid in the outside cavities provides additional hydraulic pressure to move the wedge.
  • the crown of the shell is varied by moving the wedges axially in between the shell and roll core.
  • the curved surfaces of the wedge and shell interact to vary the crown of the shell and thereby control the profile of the workpiece material.
  • the longimdinal movement of the wedge is actuated by changing the oil pressure in the fluid chambers 160, 162.
  • fluid is forced through the fluid passage 169 and into the fluid chamber 162 on the same end of the roll as the thicker end of the shell.
  • the increased pressure pushes on the wedge flange 150 which is a boundary of the fluid chamber 162.
  • the wedge is moved toward the thicker end of the shell.
  • Splines may be provided between the roll core and the wedges, or between the shell and the wedges, depending on the embodiment, to restrict rotational motion therebetween. If the opposing curved surfaces are between the wedges and shell, then the splines would be between the wedges and core, and if the opposing surfaces are between the core and wedges, the splines would be between the wedges and the shell.
  • fluid is forced through the fluid passage 168 and into the fluid chamber 160 on the opposite end of the roll as the thicker end of the shell.
  • the increased pressure pushes on the wedge flange 150 wliich is a boundary the fluid chamber 160. Because only the wedge flange is free to move and only longimdinally in the axial direction, the wedge is moved away from the thicker end of the shell. Therefore, adjustment of the fluid pressure in the fluid chambers controls the translation of the wedge in opposite directions. If the cavities 172 are used as fluid chambers, the fluid pressure in the cavities would be adjusted inversely to the adjacent fluid chambers 160, 162.
  • FIG. 6 illustrates another embodiment in which fluid chambers are used to actuate translation of the wedge 80.
  • the shell 82 has a flange 178 at one end extending radially inward toward and sealably engaging the roll neck 184 by means of an O-ring 186.
  • the roll neck may be cylindrical or tapered where the bearings engage the roll neck.
  • the generally cylindrical wedge 80 extends along the full length of the roll core.
  • the wedge On the same end of the roll as the shell flange 178, the wedge has a flange 182 extending radially inward toward and sealably engaging the roll neck 184 by and O-ring 188.
  • the outer circumferential surface of the roll core is sealed against the inner circumferential surface of the wedge by an O-ring 190, and the outer circumferential surface of the wedge is sealed against the inner surface of the shell by an O-ring 192.
  • the seal rings are located such that neither fluid chamber extends an appreciable length along the wedge.
  • there are two fluid chambers one fluid chamber 194 inward from the wedge flange and one fluid chamber 196 outward from the wedge flange.
  • the outer fluid chamber 196 is defined radially by the outer circumferential surface
  • the outer fluid chamber is defined axially by the shell flange and the wedge flange.
  • the inner fluid chamber is radially defined by the outer circumferential surface 198 of the roll neck and inner
  • the inner chamber is axially defmed by the wedge flange and the radially extending surface 204 at the junction between the roll neck and the roll core.
  • Two passages 206, 208 are fluid lines that connect the fluid chambers to an oil reservoir (not
  • the third passage 210 is a drain line which prevents unwanted fluid pressure from occurring in the cavity 212 at the other end of the roll.
  • the unwanted fluid pressure can lead to undesirable variations in the roll crown caused by movement of the wedge or by the pressure acting directly on the shell.
  • the roll has an annular curved wedge 92 at each end of the roll, leaving a gap 99 in the middle of the roll between the two wedges, roll core, and shell.
  • Each wedge has a flange 5 218 extending radially inward toward and sealably engaging the roll neck 220 with a seal 222.
  • the outer surface of each wedge is sealed against the inner surface of the shell at the outer end of each wedge by a seal 224, and the inner surface of each wedge is sealed against the surface of the roll core at the ends of the roll core by a seal 226.
  • the shell has flanges 219 on both ends of the roll extending radially inward toward the roll neck. Each shell flange is sealed 228 against the roll neck.
  • Two chambers are located on each end of the roll.
  • the outer fluid chambers are defined axially by the flanges of the shell and the flanges of the wedges.
  • the inner fluid chambers are radially defined by the outer circumferential surface 232 of the roll necks and inner circumferential surface 242 of the wedges.
  • the inner chambers are axially defined by the flanges of the wedges and the radially extending surfaces 244 at the junctions between the roll necks and the roll core.
  • passages There are five passages formed in the roll shaft. Four of the passages are fluid lines that connect the four fluid chambers to oil reservoirs, and the fifth passage is a drain line 246 that vents the middle of the roll core to atmosphere. The drain line prevents pressure build up at the center of the roll which could cause unwanted variations of the roll crown.
  • the crown of the shell is varied by moving the wedges axially in between the shell and roll core.
  • the curves of the wedges and shell (FIG. 7) or the wedges and roll core (FIG. 8) interact to vary the crown of the shell and thereby control the profile ofthe workpiece material.
  • the axial movement ofthe wedges is actuated by changing the oil pressure in the fluid chambers.
  • the amount of axial movement and the position of the wedges is monitored by proximity gauges 247 or the like suitably placed in the fluid chambers.
  • the spaces 99 between the wedges can be bifurcated, sealed, and used as a centrally located fluid chambers.
  • Fluid chambers would also be formed at the outer ends of the wedges between the ends of the wedges and the shell flanges (see fluid chamber 410 in FIG. 19). If the pressure is increased in the central fluid chambers and decreased in the outer fluid chambers, the wedges would be moved outwardly. If the pressure is decreased in the central fluid chambers and increased in the outer fluid chambers, the wedges would be translated inwardly.
  • internal fluid chambers have been described as the means for translating the wedges, external acmators such as rotating hydraulic cylinders can also be used, as illustrated in FIG. 10. The roll of FIG.
  • splines 260 extending radially outward.
  • a hollow cylindrical shell 262 surrounds the roll core and the portion of each roll neck which is closest to the roll core. The inside of the shell is curved, so that it has increased thickness at its center.
  • An annular generally cylindrical wedge 264 is inte ⁇ osed between the shell and the roll core at each end of the roll, leaving a gap 266 in the middle between the wedges, roll core, and shell. Because the two ends of the roll are identical, the roll is described by reference to a single end.
  • the wedge has a flange 268 extending radially inward toward the roll neck.
  • the flange engages a plurality of bars or keys 270 which form a cage fitting between the splines and extend longimdinally outward beyond the roll neck.
  • the bars are preferably fabricated from bronze because of how bronze interacts with the steel roll shaft. For example, there is no galling between steel and bronze.
  • the outward ends 272 of the bars are attached to a circular plate 274, and the circular plate is engaged by a hydraulic cylinder 276 for actuating the longimdinal movement of the wedge.
  • a shaft connector 284 is provided to facilitate the engagement of the circular plate by the shaft 286 of the hydraulic cylinder.
  • a pair of circumferential roll chocks 278, 280 support the bearings 282 and in mrn the roll necks.
  • the inner race of the bearing fits around the roll neck splines allowing no relative movement between the inner race of the bearings on the roll neck and provides a clearance of about 1/4 mm between the bearing and the bars, thus allowing the roll shaft to rotate with the bearing and the bars to translate in the axial direction between the splines.
  • An alternate solution provides splines between the wedge and the roll core or between the wedge and the shell with a solid wedge sleeve surrounding the roll neck (replacing the bars) extending from the wedge flange to the actuator.
  • the roll shaft, shell, and wedges are rotated about the centerline by a drive mechanism (not shown) or frictional engagement with other rolls or the workpiece.
  • the external actuator can rotate with the roll or it can remain rotationally fixed if an appropriate thrust bearing is provided.
  • the crown of the shell is varied by moving the wedges axially in between the shell and roll core.
  • the curves of the wedge and shell interact to vary the crown of the shell and thereby control the profile of the workpiece material.
  • the longimdinal movement of the wedge is acmated by an external operator, namely the hydraulic cylinder. Because the shear forces at the connection between the wedge flange and the bars are high, especially when the wedge is being forced inward, the bars have protrusions 288 which engage annular recesses 289 in the wedge flanges.
  • the hydraulic cylinder can be replaced by another external acmator shown enlarged in FIG. 12.
  • the strucmre of the roll is substantially the same as FIG. 10, so the strucmre of the roll is described only as it becomes necessary to the explanation of the acmator, and again, this embodiment is intended for relatively low force applications.
  • the mechanical acmator generally designated 290, comprises a reversible motor 292 (hydraulic or electric), an annular internally threaded member 294, an annular externally threaded member 296, a motor gear 298, and a transfer gear 300.
  • the internally threaded member 294 is attached to any surface that is fixed relative to the roll shaft 304.
  • the roll chock 302 is fixed relative to the roll shaft and is conveniently located close to the roll shaft, so the internally threaded member is attached to the roll chock.
  • the motor is fixed to the internally threaded member. Therefore, the roll rotates independently from the acmator.
  • a motor shaft 306 extends from the motor and terminates in the motor gear 298.
  • the teeth of the motor gear engage the teeth of the transfer gear 300.
  • the transfer gear is annular and has the same internal diameter as the internal diameter of the externally threaded member 296 to which it is attached.
  • the internal diameter of the internally threaded member is substantially the same as the external diameter of the externally threaded member, so that, the externally threaded member is threaded into the internally threaded member.
  • the outer edge 307 of a circular plate 308 fits between the opposing surfaces of the transfer gear and externally threaded member, and is engaged between the surfaces by an outer friction bearing surface 310 and an inner bearing surface 316 which allow the circular plate and the roll to rotate relative to the transfer gear and externally threaded member.
  • a shim 312 is provided between the externally threaded member and the transfer gear to assure the proper spacing between the opposing surfaces to receive the circular plate.
  • a guard 314 surrounds the mechanical acmator for safety
  • the motor When decreased crown is required, the motor is rotated in a second direction opposite to the first direction so that the externally threaded member is threaded out of the internally threaded member. As the externally threaded member threads out, the inner friction bearing surface of the externally threaded member pushes outwardly on the circular plate. Because the circular plate is connected to the wedge 218, the wedge is moved outwardly on the roll, thereby decreasing the roll crown.
  • the roll neck 350 has a solid outer surface with an annular recess 352 between the roll neck and the roll core 354.
  • a plurality of apertures 356 extended through the roll neck at a uniform radial depth in the roll neck, so that they open into the recess 352.
  • the apertures can be circular as shown in FIG. 14, or the apertures can have other shapes such as the trapezoidal apertures 358 as shown in the roll neck 360 of FIG. 15.
  • bars 362 extend through the apertures 356 and engage an annular flange 364 of the annular wedge 366 or the bars could engage the wedge directly if an increased diameter of the roll neck is required.
  • the outer end of the bars engage an annular ring 368 or a circular plate.
  • One or a plurality of acmators 370 translates the assembly comprising the ring, bars, flange, and wedge relative to the roll core 354 and roll shell 372.
  • the acmators may rotate with the annular ring relative to the roll chock 374, or the piston 376 of the acmator can slide against the annular ring.
  • conventional proximity and location sensors 247 such as LVDTs or the like, can be provided for sensing the position of the wedges, and conventional beta or X-ray gauges or the like can be utilized to determine the uniformity of thickness and flatness of the workpiece material.
  • the preferred placement for a position sensor is between the wedge and roll shaft.
  • the thickness data can be evaluated by an appropriate computer program to determine how much and which way to move a wedge if an undesired profile variation in the rolled material is detected by the gauges.
  • Figure 20 illustrates an alternate embodiment for axially translating two wedges 430, 432 relative to shell 434 thereby varying the crown of the roll.
  • the roll core 436 has right hand threads, generally designated 438, on one half of the roll core and left hand threads, generally designated 440, on the other half of the roll core.
  • One of the wedges 432 is threaded to mate with the right hand threads, and the other wedge 430 is threaded to mate with the left hand threads.
  • the wedges move axially in opposite directions.
  • the wedges are fixed rotationally relative to the shell by key ways 442 or splines.
  • the key ways allow the wedges to slide axially relative to the shell but prevent rotation between the shell and wedge, so that the roll core can have a relative rotational speed to the shell and wedges.
  • the entire roll assembly shown, excluding the chock 446 is rotating during operation.
  • the wedges thread in or out depending on the direction of the relative rotation, and slide axially relative to the shell.
  • a means for imparting relative rotation to the roll shaft is provided.
  • the relative rotation means preferably comprises a reversible motor 448 attached to the rotating portion of the bearing 450, so that the motor rotates with the assembly.
  • a gear 452 meshes with the roll neck 454, so that the motor, when activated, imparts rotation to the roll core. Because the motor is fixed to the rotating bearing, rotation imparted to the roll core by the motor causes the roll core to rotate relative to the wedges. Several motors may be spaced around the circumference of the roll and at both ends of the roll to provide the torque required to rotate the roll core.
  • the strip 120 passes between a backup roll 121 and an applicator roll 122 which applies paint to one side of the strip.
  • the applicator roll is adjacent to a pickup roll 123 which dips into a pan 124 which contains a coating material 125 applied to the strip.
  • an intermediate metering or transfer roll 130 is employed between the pickup roll and the applicator roll for transferring coating material between the rolls and assisting in determining the thickness of coating material applied to the strip.
  • the bottom applicator roll When coating the "bottom" face of the strip, there is an applicator roll 126 on only the bottom face of the strip.
  • the bottom applicator roll is adjacent to a pickup roll 127 which dips into a pan 128 which contains a coating material 129 for application to the bottom face of the strip.
  • a transfer roll may be used between the pickup and bottom applicator rolls. The axes of the rolls may be in a line to the backup roll or offset as shown in FIG. 13.
  • a roll with adjustable crown may be used for either of these applicator rolls, for a paint transfer roll, or possibly for the backup roll.
  • An exemplary strip coating apparams is described and illustrated in U.S. Patent No. 5,413,806, the subject matter of which is hereby inco ⁇ orated by reference.
  • a backup roll 500 supports the work roll 502.
  • the backup roll comprises annular grooves 504 to receive bearings 506.
  • the backup roll sections 514 separating the bearing grooves and located at the ends of the backup roll have a larger diameter than the bearings and contact the work roll.
  • the crown control mechanism, generally designated 508, comprises a substantially unbendable fixed bar 510, first and second plurality of opposing angled surfaces 516, 518 on bearing bars 512 and intermediate threaded bars 520 respectively, a continuous threaded shaft 522, and threaded backing bars 530, 532. The backing bars slide over and extend transversely from the fixed bar.
  • the backing bars would be attached to a sliding member which slides against the fixed bar.
  • the backing bars For the mechanism to function, it is only necessary for the backing bars to interact with the fixed bar, so that the backing bars cannot move away from the backup roll.
  • half of the backing bars 530 On the ends opposite the fixed bar, half of the backing bars 530 have right hand threads 528 engaging the right hand threaded half 526 of the shaft.
  • the other half of the backing bars 532 have left hand threads 534 to engage the left hand threaded half 524 of the shaft.
  • the intermediate threaded bars 520A, 520B, and 520C have left hand threads 536 to engage the left hand threaded shaft
  • the threaded shaft is inte ⁇ osed between the threads of the threaded backing bars and the threads of the intermediate threaded bars.
  • the angled surfaces 518 engage and mate with the angled surfaces 516 of the bearing bars.
  • the bearing bars engage the bearings.
  • the angles of the opposing surfaces change over the length of the mechamsm to simulate the curved opposing surfaces described in the previous embodiments.
  • at least two of the sets of mating angles are angles of different magnitude.
  • the outermost camming angles ⁇ of bars 520A and 520F are the smallest because the smallest deflection is desired at the ends of the roll.
  • the camming angles a of the bars 520B and 520E adjacent to and inward from the outermost angles ⁇ are a little larger than the angles ⁇ .
  • the middle bars 520C and 520D have the largest camming angles e to obtain the greatest deflection.
  • the angles have the relationship ⁇ ⁇ a ⁇ e.
  • Other bars could be added to the mechanism with opposing angles intermediate in magnitude and location to ⁇ and e. In this embodiment, all the angles open toward the center of the roll.
  • the shaft is rotated in the direction of arrow 540, which is clockwise when the shaft is viewed from the right.
  • the means for translating one plurality of angled surfaces relative to the other plurality of angled surfaces includes a means for rotating the threaded shaft.
  • the clockwise rotation of the shaft moves the backing bars and threaded bars outwardly, so that the opposing angled surfaces engage and push the bearing bars away from the shaft thereby bending the backup roll and varying the crown of the work roll to control the profile of the workpiece.
  • the substantially unbendable bar prevents the backing bars from translating away from the rolls, so that the bearing bars are forced to translate toward the rolls thereby bending the rolls.
  • the shaft is rotated counter clockwise when viewed from the right end of the roll. If the angles open outwardly toward the ends of the roll, the shaft would be rotated in the opposite directions described to vary the crown as desired.
  • the camming angles ⁇ , , and e of the opposing surfaces 542, 544 all open to one end of the roll.
  • the crown of the work roll 550 is varied similarly to the previous embodiment of FIG. 17.
  • the backing bars 552, instead of being threaded, are fixed to a sliding member or sliding shaft 554 which is prevented from bending by a substantially unbendable fixed bar 556. Further, the backing bars terminate with the opposing surfaces 544.
  • Bearing bars 558 engage bearings 560 located in bearing grooves 562 of the backup roll 564. Larger diameter sections 566 of the backup roll located between the bearing grooves engage the work roll.
  • the roll crown is decreased because the opposing surfaces disengage.
  • the sliding shaft is translated to the left, opposite the direction of arrow 568, the opposing surfaces are brought further into engagement, the backup bar is bent, and the crown of the work roll is increased.
  • a roll for use in a rolling mill, coating apparams, or sheet leveler and a crown control mechamsm for a sheet leveler which utilize a pair of opposing complementary curved or angled surfaces to more effectively obtain the desired roll crown.
  • effective apparatuses are disclosed for actuating movement of wedges inte ⁇ osed between a roll core and shell. Both the adjustable roll and the actuating apparatuses can be used in strip rolling mills, plate rolling mills, strip levelers, coating apparams, and other apparatuses requiring crown control on a roll.
  • An advantage of the roll with adjustment wedges between a roll core and shell is that it can be readily employed in conventional rolling mills, coating machines and the like with only a rather small amount of modification.
  • an existing mill or the like can be retrofitted with a variable crown roll or rolls without incurring the cost of an entirely new mill with other means for controlling workpiece profile.
  • an oil film is forced in between the members of the roll which move past each other.
  • the roll core 600 is translated relative to the shell 602, and an oil film 604 is forced in between the shell and roll core through a plurality of oil passages 606.
  • the oil pressure in the passages is on the order of 10,000 psi.
  • the number of oil passages depends on the length of the roll and the pressure required. If high roll pressures are required, it is necessary, for some embodiments, to place partitions or seals between the oil passages, so that fluid is not forced out of any one area of the roll. In this embodiment, separate supply oil lines 608 would also be provided. Thus, the smaller the space required between partitions, the more passages required. In this embodiment, the roll does not rotate.
  • the roll only translates side to side as shown by arrow 610 to adjust the crown.
  • the shell which is powered by frictional engagement with another roll or the workpiece or by a drive mechanism (not shown), rotates around the core.
  • Seals 612 are provided at the edges of the roll core to keep the oil between the shell and the core. If the roll core is shifted by external means then outer passages 614 act as drain lines. If the cavities 616 are utilized as fluid chambers to move the roll core, the outer passages 614 would be oil lines, and additional seals 618 would be provided between the shell bearings 620 and the roll neck 622.
  • This embodiment is adaptable to use with wedges which are inte ⁇ osed between the shell and roll core. The wedges may rotate with the shell or remain rotationally fixed with the core.

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  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

Cylindre (26) avec commande de profil variable pour laminoirs à chaud et à froid, niveleuses, appareils de revêtement ou similaires pour métaux, ferreux et non ferreux, utilisant au moins une paire de surfaces de contact opposées (404, 406) avec des angles de came qui se modifient continûment sur la longueur du cylindre. Selon l'un des modes de réalisations, l'angle de came se modifiant continûment s'obtient par l'utilisation de surfaces courbes continues pour les surfaces de contact opposées. L'une des surfaces de contact opposées peut se situer sur le corps du cylindre (402). Selon une variante, une surépaisseur (404) constituant l'une des surfaces de contact opposées est intercalée entre une coque (406) et un corps de cylindre (402). L'autre surface de contact opposée peut être constituée par la coque (406) ou le corps (402) de cylindre. Pour réguler le bombé du cylindre, soit le corps de cylindre (402), soit la surépaisseur (404) opèrent une translation longitudinale.
PCT/US1996/011339 1995-07-20 1996-06-27 Commande de profil variable pour cylindres WO1997003768A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU64533/96A AU6453396A (en) 1995-07-20 1996-06-27 Variable profile control for rolls

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US131095P 1995-07-20 1995-07-20
US60/001,310 1995-07-20
US65531396A 1996-05-23 1996-05-23
US08/655,313 1996-05-23

Publications (1)

Publication Number Publication Date
WO1997003768A1 true WO1997003768A1 (fr) 1997-02-06

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WO (1) WO1997003768A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0943377A1 (fr) * 1998-03-20 1999-09-22 Sms Schloemann-Siemag Aktiengesellschaft Cylindre pour une cage de laminoir
CN101687233B (zh) * 2007-06-14 2011-10-05 Sms西马格股份公司 多部件式轧辊
US10501264B2 (en) 2008-11-07 2019-12-10 Advanced Custom Engineered Systems & Equipment Co. Method and apparatus for monitoring waste removal and administration
US10585964B2 (en) 2007-02-21 2020-03-10 Advanced Custom Engineered Systems & Equipment Co. System for monitoring a container
US10635864B2 (en) 2013-05-15 2020-04-28 Advanced Custom Engineered Systems & Equipment Company Method for deploying large numbers of waste containers in a waste collection system
US11074557B2 (en) 2016-03-31 2021-07-27 Advanced Custom Engineered Systems & Equipment Co. Systems and method for interrogating, publishing and analyzing information related to a waste hauling vehicle

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US4423541A (en) * 1980-11-11 1984-01-03 Davy-Loewy Limited Rolling mill roll
US4528830A (en) * 1982-06-30 1985-07-16 Sumitomo Metal Industries, Ltd. Method for changing widthwise distribution of thickness of metal strip
US4599770A (en) * 1984-04-06 1986-07-15 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Roll for rolling mill
US4837906A (en) * 1987-05-21 1989-06-13 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Rolling roll with variable profile and of the tapered piston type
US5413806A (en) * 1993-02-01 1995-05-09 Hunter Engineering Company, Inc. Strip coating machine with thickness control

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4423541A (en) * 1980-11-11 1984-01-03 Davy-Loewy Limited Rolling mill roll
US4528830A (en) * 1982-06-30 1985-07-16 Sumitomo Metal Industries, Ltd. Method for changing widthwise distribution of thickness of metal strip
US4599770A (en) * 1984-04-06 1986-07-15 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Roll for rolling mill
US4837906A (en) * 1987-05-21 1989-06-13 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Rolling roll with variable profile and of the tapered piston type
US5413806A (en) * 1993-02-01 1995-05-09 Hunter Engineering Company, Inc. Strip coating machine with thickness control

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6216519B1 (en) 1998-03-20 2001-04-17 Sms Schloemann-Siemag Aktiengesellschaft Roll for a roll stand
AU757666B2 (en) * 1998-03-20 2003-02-27 Sms Schloemann-Siemag Aktiengesellschaft Roll for a roll stand
EP0943377A1 (fr) * 1998-03-20 1999-09-22 Sms Schloemann-Siemag Aktiengesellschaft Cylindre pour une cage de laminoir
US11461424B2 (en) 2007-02-21 2022-10-04 Advanced Custom Engineered Systems & Equipment Co. Waste container monitoring system
US10585964B2 (en) 2007-02-21 2020-03-10 Advanced Custom Engineered Systems & Equipment Co. System for monitoring a container
US11907318B2 (en) 2007-02-21 2024-02-20 Advanced Custom Engineered Systems & Equipment Co. Waste container monitoring system
US11017049B2 (en) 2007-02-21 2021-05-25 Advanced Custom Engineered Systems & Equipment Co. Waste container monitoring system
CN101687233B (zh) * 2007-06-14 2011-10-05 Sms西马格股份公司 多部件式轧辊
US10501264B2 (en) 2008-11-07 2019-12-10 Advanced Custom Engineered Systems & Equipment Co. Method and apparatus for monitoring waste removal and administration
US11767164B2 (en) 2008-11-07 2023-09-26 Advanced Custom Engineered Systems & Equipment Co. Method and apparatus for monitoring waste removal and administration
US11267646B2 (en) 2008-11-07 2022-03-08 Advanced Custom Engineered Systems & Equipment Co. Method and apparatus for monitoring waste removal and administration
US11640575B2 (en) 2013-05-15 2023-05-02 Advanced Custom Engineered Systems & Equipment Co. Method for deploying large numbers of waste containers in a waste collection system
US11144736B2 (en) 2013-05-15 2021-10-12 Advanced Custom Engineered Systems & Equipment Co. Method for deploying large numbers of waste containers in a waste collection system
US10635864B2 (en) 2013-05-15 2020-04-28 Advanced Custom Engineered Systems & Equipment Company Method for deploying large numbers of waste containers in a waste collection system
US11727363B2 (en) 2016-03-31 2023-08-15 Advanced Custom Engineered Systems & Equipment Company Systems and method for interrogating, publishing and analyzing information related to a waste hauling vehicle
US11074557B2 (en) 2016-03-31 2021-07-27 Advanced Custom Engineered Systems & Equipment Co. Systems and method for interrogating, publishing and analyzing information related to a waste hauling vehicle

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