Variable-crown roll

Abstract: A variable-crown roll is disclosed, which comprises a curved arbor (1), a plurality of antifriction bearings (21, 22) which are mounted on said arbor, said bearings being symmetrically disposed with respect to the lengthwise center of said arbor, said bearings on one side of the lengthwise center of said arbor being symmetric with respect to said bearings on the other side of the lengthwise center, a cylindrical sleeve (90) which loosely fits over said bearings, and means (51, 52) for fixing and releasing said sleeve with respect to said arbor, said means being positioned on each end portion of said sleeve.

Description: The present invention relates to a variable-crown roll for use in multi-roll rolling mill. In the rolling of plates, it is important that the plate profile (the thickness distribution in the widthwise direction) be rectangular, that the plate thickness be always constant, and it is particularly important that good shape control be carried out, i.e., that the flatness of the rolled plate be constant. Various new types of rolling mills have been developed in order to meet these requirements. In order to improve the flatness and profile of a plate, it is necessary to compensate the deflection of the work roll, and for this purpose, the work roll bending method, the back-up roll bending method, the double chock bending method, the roll skew method, the roll shift method, the variable-crown roll method (sometimes referred to as the VC roll method), and the like have been developed. Of these methods, the variable-crown roll method is particularly economical because a conventional rolling mill can be adapted so as to perform variable-crown rolling merely by replacing a conventional roll of the rolling mill with a variable-crown roll. Variable-crown rolls have been effectively employed in combination with existing roll benders for improving the flatness and profile of rolled plates. Publication EP-A 0 338172 discloses a variable-crown roll as defined in the non-characterizing part of claim 1 and explains the advantages of such a roll with respect to previous conventional variable-crown rolls. In an actual production line, it is sometimes necessary to carry out grinding of the roll in order to remove a roughened surface layer and to recover the original roll profile. For Example, in a production line for cold rolling of steel sheet, the back-up rolls must be ground every 5 - 7 days each to a depth of 1.5 - 2.0 mm. In addition, since the roundness of a roll has a substantial effect on the accuracy with which the thickness of the rolled sheet can be controlled, the tolerances on the roundness must be at most 5 µm for the whole length of the roll. For conventional solid rolls and VC rolls, grinding has been carried out while the rolls are fixed by their journal portions. It is an object of the present invention to provide a variable-crown roll for which grinding of the roll can be carried out easily. The present invention is a variable-crown roll as defined in claim 1. The bearing may be mounted directly or through a bushing on an outer peripheral straight or sloped surface of the arbor. The outer peripheral surface of the bushing may be sloped with respect to the outer peripheral surface of the arbor. At least one spacer having parallel or sloping sides may also be disposed between adjacent bearings or bushings. The antifriction bearing used in the present invention is not restricted to a specific one, but it is preferable, especially when spacers having sloping sides are inserted between adjacent bearings, to use at least one bearing which has an outer race which is wider than an inner race so as to decrease the gap between the outer races of the adjacent bearings. Furthermore, sealed bearings are employed, so the maintenance of the bearings can be greatly simplified. An oil supply passageway may be formed within the arbor, and lubricating oil is supplied to the bearings through the oil supply passageway. Alternatively, an oil supply hole for supplying an oil mist to the space between the inner race and the outer race of the antifriction bearings and an oil supply hole for recovering the oil mist can be formed in the arbor. In addition, an oil supply hole for supplying oil to the space between the cylindrical sleeve and the outer race of the antifriction bearings can also be formed in the arbor. Seals are provided on the ends of the arbor so as to seal the lubricating oil inside the arbor. As a result, the wear and seizure of the bearings for the sleeve can be prevented, even under severe rolling conditions when the rotational speed or the rolling load is high. In a preferred embodiment the means for fixing and releasing the sleeve comprises movable expanding means provided under the inner peripheral surface of the sleeve. Figures 1 through 6 are longitudinal cross-sectional views of various embodiments of variable-crown rolls used in the present invention; Figure 7 is a schematic view of an oil supply pathway of an embodiment of a variable-crown roll used in the present invention; Figure 8 is a front view of an embodiment of a variable-crown roll used in the present invention which is equipped with an arbor angle adjusting mechanism; Figure 9 is a side view of an arbor angle adjusting mechanism for a variable-crown roll used in the present invention; Figures 10 through 12 are cross sectional views of a supporting mechanism which is disposed at the both end of the sleeve and which comprises means for fixing the sleeve with respect to the arbor when the sleeve is prepared for grinding; Figure 13 is a graph showing the results of rolling of a working example; Figures 14(a), 14(b) and 14(c) are longitudinal cross-sectional views of a bushing with parallel, eccentric walls, and a bushing with sloping walls, and Figures 14(d) and 14(e) are respectively cross-sectional views and a front view of a spacer with sloping sides for a variable-crown roll in accordance with the present invention; and Figure 15 is an enlarged schematic perspective view of a bushing having sloping inner walls. Next, the present invention will be described in greater detail while referring to the accompanying drawings. The means for fixing and releasing the sleeve with respect to the arbor is illustrated in Figures 10 - 12, and the means is ommited in Figures 1 - 6 merely for simplifying the drawings. The basic structure of a variable-crown roll used in the present invention is illustrated in Figure 1. As shown in this figure, two thin, large-diameter bearings 21 and 22 are mounted on a curved arbor 1. The bearings 21 and 22 have inner races 24 and 25 and outer races 26 and 27, respectively. The inner and outer surfaces of the inner races 24 and 25 are sloped with respect to the axis of the arbor by angle . The inner races 24 and 25 are secured to the outer surface of the curved arbor 1 by shrink fitting, expansion fitting, interference fitting, keys, or other suitable means. The outer races 26 and 27 of the bearings 21 and 22 are able to freely rotate with respect to the curved arbor 1. When rolling is being carried out, only the outer races of the bearings rotate. The slopes of the outer surfaces of the outer races are symmetric with respect to the lengthwise center of the curved arbor 1. If the angle of slope of the surface of an arbor, i.e., the slope of the inner races 24 and 25 is and the length of each bearing is α, then the crown δ = α x ℓ . If a work roll is disposed beneath the roll of Figure 1, then a convex crown of magnitude is obtained, and if the curved arbor 1 is rotated 180 o from this position, a crown of magnitude -δ is obtained. Accordingly, by adjusting the angle of rotation of the arbor 1, it is possible to adjust the magnitude of the crown by an amount 2 between +δ and -δ. This roll has a cylindrical sleeve 90 which is loosely fit over the outer races of bearings 21 and 22 like those illustrated in Figure 1. Both ends of the cylindrical sleeve 90 are supported by thrust bearings 51 which are mounted on flanges 52. In a variable-crown roll having the structure shown in Figure 1, when a rolling load is transmitted from a work roll, the portion of the cylindrical sleeve 90 which contacts the work roll undergoes elastic bending and contacts the outer races 26 and 27 of the bearings, and the cylindrical sleeve 90 rotates together with the outer races. At this time, the cylindrical sleeve 90 contacts the work roll around its entire periphery, so there is no irregularity in the luster or amount of wear of the work roll. As a result, it is possible to perform rolling of soft materials or products requiring a high-quality finish. In the embodiment of Figure 1, two bearings 21 and 22 are mounted on the curved arbor 1, but it is also possible to employ three, four, or a larger number of bearings. In another embodiment, the radial center of the inner peripheral surface of the inner race of each bearing may be eccentric with respect to the radial center of the outer peripheral surface of the inner race of the same bearing at the ends of the inner races. Furthermore, a thin wall portion at one end of each of the bearings lies on a longitudinal extension of a thick wall portion of the other end. More precisely, the maximum thickness at one end lies on a longitudinal extension of a portion of the other end which is thinner than the maximum thickness at the first end. Figure 2 is a cross-sectional view of another embodiment of a variable-crown roll used in the present invention in which a straight arbor is used and sloped bushings 71 whose outer surfaces slope upwards top the right and left from the lengthwise center of the arbor 1 are mounted on the outer surface of the arbor 1. Bearings 21 and 22 are fit over the outer surfaces of the bushings 71. The radial center of the inner periphery of each bushing 71 is eccentric with respect to the radial center of the outer periphery of the same bushing 71 at the ends of the bushing 71. It is not essential that the portion of miminum thickness at one end of the bushing 71 lie on a longitudinal extension of the portion of maximum thickness at the other end of the bushing 71. It is sufficient that the maximum thickness at one end lies on a longitudinal extension of a portion of the other end which is thinner than the portion of maximum thickness at the first end. Figures 14(a), (b) and (c) show bushings with parallel, eccentric walls, and a bushing with sloping walls. Figure 15 is a schematic perspective view of a sloped bushing 71. The bushing 71 has a cylindrical bore at its center. The axis of the cylindrical bore is not parallel to the axis of the outer surface. The bushings 71 can be secured to the arbor 1 by means of a shrink fit, an expansion fit, an interference fit, keys, or the like. A cylindrical sleeve 90 is loosely fit on the outside of the bearings 21 and 22. In the embodiment of Figure 2, the space between the straight arbor 1 and the cylindrical sleeve 90 is airtight, and an oil supply passageway 62 is formed in the center of the curved arbor 1, one end thereof opening onto the outer peripheral surface of the center of the arbor 1. Lubricating oil can be supplied to the airtight space through the oil supply passageway 62. Seals 85 are provided between the cylindrical sleeve 90 and thrust bearings 51 which bear the thrust from the cylindrical sleeve 90. One end of the oil supply passageway 62 opens onto an oil supply port 8 formed on one end surface of the arbor 1 and is connected to an unillustrated oil supply by a rotating joint 10. In this manner, lubricating oil can be supplied to the bearings 21 and 22 through the oil supply passageway 62, whereby the life span of the bearings can be lengthened and the load which can be applied to the roll can be increased. Figure 3 is a partially cross-sectional front view of another embodiment used in the present invention. In this embodiment, two sloped bushings 71 are secured to the outside of a straight arbor 1, and a cylindrical bushing 72 with parallel walls is secured to the outside of the arbor 1 between the sloped bushings 71. Three separate bearings 21, 22 and 23 are mounted on the bushings 71 and 72. The left and right bushings 71 are symmetrically disposed with respect to the lengthwise center of the roll. Similarly, the right and left bearings 21 and 22 which are mounted on bushings 71 are identical to the corresponding bearings 21 and 22 of the previous embodiment. The radial centers of the inner and outer peripheral surfaces of the cylindrical bushing 72 disposed at the center of the arbor 1 are eccentric with respect to one another, but both surfaces are each parallel to the outer surface of the arbor 1. The radial center of the outer periphery of the outer race of the central bearing is eccentric with respect to the axis of the arbor 1, but the outer peripheral surface thereof is parallel to the outer peripheral surface of the arbor 1. Figure 4 is a partially cross-sectional front view of another embodiment used in the present invention. In this embodiment, two sloped bearings 21 and 22 are secured to the outside of a curved arbor 1, and a cylindrical bearing 23 with parallel walls is secured to the outside of the arbor 1 between the two sloped bearings 21 and 22. The curved surface of the arbor 1 comprises a flat central portion and curved outer portions symmmetrically disposed with respect to the central one. In Figure 4 the left and right bearings 21 and 22 are identical to each other and are symmetrically disposed with respect to the lengthwise center of the roll. In Figures 3 and 4, the sleeve is omitted merely for the purpose of simplifying the drawings. Figure 5 shows another embodiment of the variable-crown roll used in the present invention, in which a plurality of bearings 21, 22, 23', 24 and 25 are installed symmetrically with respect to the lengthwise center of the arbor 1. In this case, central bearing 23' also has a curved inner surface, and the arbor 1 does not have a flat surface portion. Figure 6 is a partially cross-sectional front view of the right lengthwise half of another embodiment of a roll in accordance with the present invention. In this embodiment, three sloped bearings 21 are mounted on a sloped bushing 71 on the right side of a straight arbor 1, three unillustrated sloped bearings 22 are mounted on an illustrated bushing 71 on the left side of the arbor 1, and an eccentric bearing 23 is mounted on a parallel-walled bushing 72 at the center of the arbor 1. A total of 7 bearings are disposed in the embodiment of Figure 5. All of the bearings are sealed bearings. The roll is symmetric about its lengthwise center. The bushings 71 and 72 and the bearings 21, 22 and 23 are positioned on the straight arbor 1 by means of spacers 81 and 82 having sloping sides. The bushings 71 and 72 and the arbor 1 are secured by shrink fitting, expansion fitting, interference fitting, keys, or the like. It is not necessary that the spacers 81 and 82 are fixed directly to the arbor 1, but they may be fixed at position only by a laterally pressing force from sides of the bearings. Alternatively, the spacers may be fixed by shrink fitting, expansion fitting, interference fitting, keys, or the like. The spacers 81, 82 may be in a shape shown in Figures 14(c), 14(d) and 14(e). The outer surfaces of the bushings 71 and 72 are secured to the inner races of the bearings 21, 22 , and 23 in a like manner. A cylindrical sleeve 90 loosely fits over the bearings 21, 22, and 23. Thrust loads from the cylindrical sleeve 90 are transmitted through flanges 52 at opposite ends of the arbor 1 to bearings 51. The outer race of each bearing 51 is secured to the corresponding flange 52. As shown in Figure 6, an oil supply passageway 62 is formed in the center of the arbor 1 and extends to the outer end thereof in the same manner as in the embodiment of Figure 3. However, it is not mandatory that the oil supply passageway 62 be at the center of the arbor 1, and it can be radially displaced from the center. In addition, there may be a plurality of inlets and discharge ports for lubricating oil. Figure 7 is a cross-sectional view of a portion of another embodiment which is equipped with an oil mist supply passageway 62. An oil supply port 8 is formed in the end of the arbor 1, and oil mist which enters the oil supply port 8 is supplied through the oil mist supply passageway 62, from where it spreads to the antifriction bearings 21 and 22. The oil mist is then discharged through an oil recovery passageway 63. Figure 8 is a front view of a variable-crown roll used in the present invention which is equipped with an arbor angle adjusting mechanism 70 at one end of the arbor 1, and Figure 9 is a side view of the arbor angle adjusting mechanism 70. By means of this mechanism 70, the arbor rotational angle and therefore the roll crown can be freely adjusted. As shown in Figure 9, a worm wheel 31 is secured to the end of an arbor 1 by a key, and the worm wheel 31 meshes with a worm 32 which is secured to one end of a shaft. An adjusting wheel 33 for rotating the shaft is mounted on the other end thereof. When the adjusting wheel 33 is rotated, the worm 32 rotates therewith, and the rotation of the worm 32 causes the worm wheel 31 and the arbor 1 to rotate together about the axis of the arbor 1. Therefore, the arbor 1 can be rotated to any desired angle by turning the adjusting wheel 33. It is possible to adjust the arbor rotational angle of a variable-crown roll according to the present invention while rolling is being performed. Normally, however, a simpler control method is employed; namely, the arbor rotational angle is set in advance at a suitable value based on the dimensions and material characteristics of the item being rolled, the rolling temperature, and the like, and during rolling, control is performed mainly by adjusting the force applied by the roll bender. Nevertheless, when correcting shape irregularities of sheets caused by complex shape defect during cold rolling, it is desirable to perform shape control by simultaneously adjusting both the bending force of the roll bender and the roll crown of the back-up roll. In this case, in order to allow the rapid adjustment of the arbor rotational angle during high-speed rolling, it is desirable that the arbor angle adjusting mechanism 70 be powered by an electric motor or a hydraulic apparatus, whereby changes in the arbor rotational angle can be made quickly and with high precision. However, since in most cases the arbor rotational angle is set prior to rolling and remains the same throughout rolling, an inexpensive, mechanically-operated apparatus like that illustrated in Figure 9 is normally adequate. In a variable crown roll used in the present invention which comprises a straight or curved arbor 1 and sleeve 90, the arbor and sleeve are not fixed but are rotatably connected with each other through bearings 21. Therefore, whenever grinding is performed, the sleeve 90 has to be removed. It takes much time and labor to remove and then remount the sleeves. Furthermore, a conventional grinding machine cannot be employed, and it is necessary to use a specially designed grinding machine, which increases manufacturing costs. Thus, according to the present invention the variable crown roll includes means for fixing and releasing the sleeve with respect to the arbor, the sleeve being rotatably supported by the arbor via bearings during rolling and being fixed with respect to the arbor during grinding. The variable crown roll may further comprise means for sealing the sleeve from the inside thereof. The means for fixing and releasing the sleeve comprises a supporting mechanism to be provided on both ends of the roll. The supporting mechanism includes a movable expanding mechanism. In Figure 10, a supporting mechanism 104 supports sleeve 90 from the inside thereof at both ends of a roll. When the sleeve 90 is prepared for grinding, the supporting mechanism 104 prevents the rotation of the sleeve 90 with respect to the arbor 1. When the roll is performing rolling, the supporting mechanism 104 releases the sleeve 90 so that it can freely rotate with respect to the arbor 1. In this case the arbor 1 may be either a curved one or a straight one covered with sloped bushings or the like. The supporting mechanism 104 includes thrust bearings 105, thrust-receiving flanges 106, a movable expanding mechanism 107, sealing bodies 108, 109, a lateral stoper 110, a cover 111, and a spacer 112. An inner ring 105a of the thrust bearing 105 is fixed between spacer 112 and the lateral stopper 110 which is also fixed to the arbor with a screw 110a. The thrust-receiving flange 106 is inserted into the outer ring 105b of the thrust bearing 105. The movable expanding mechanism 107 is inserted into a space formed between the outer periphery of the thrust-receiving flange 106 and the inner periphery of the sleeve 90. The movable expanding mechanism 107 includes an outer ring 107a, a pair of wedge shape bodies 107b, and a drive bolt 107c which moves back and forth. A plurality of similar movable expanding mechanisms 107 are provided around the periphery of the thrust-receiving flange 106. Sealing members 108a and 109a are respectively disposed between sealing body 108 and the lateral stopper 110 and between sealing body 109 and the sleeve 90. Sealing body 108 is secured to the thrust-receiving flange 106 by a bolt 113. If necessary, another bolt 114 may be provided to secure the sealing body 108 and the lateral stopper 110 to one another. The cover 111 is secured to both sealing bodies 108, 109 by a bolt 115. During the operation of a production line, the movable expanding mechanism 107 of the supporting mechanism is in an idle state and does not contact the inner surface of the sleeve 90. The bolt 114 is removed so that sealing body 108 and the lateral stopper 110 are disconnected. Therefore, the sleeve 90, the movable expanding mechanism 107, the thrust-receiving flange 106, the sealing bodies 108, 109, and outer ring 105b of the thrust bearing 105, and the cover 111 are all caused to rotate when a rolling load is applied to the sleeve 90. When grinding is to be performed on the sleeve 90, first bolt 114 is replaced to secure the lateral stopper 110 to the sealing body 108, so that the entire supporting mechanism 104, including the above-described elements which were movable during rolling, is fixed with respect to the arbor 1. Bolt 115 is then removed and the cover 111 is removed. After pulling out the sealing body 109, the drive bolt 107c is tightened to a given torque to move the left wedge body 107b towards the right wedge body 107b as shown by the arrows. The movement of the left wedge body 107b causes the outer ring 107a to expand outwardly to bring the sleeve 90 and arbor 1 into a position in which they are disposed concentrically and are firmly in contact with each other. In this position, grinding can be performed on the sleeve. The thrust bearing 105 and movable expanding mechanism 107 which are installed within the supporting mechanism 104 are sealed by the sealing members 108a and 109a to completely prevent cooling water, rolling oil, dust, scale, and the like from coming into the apparatus. Figure 11 shows another embodiment of the present invention in which the movable expanding mechanism 107 comprises a tapered ring 116 and a sleeve 90 has a tapered edge. A drive bolt 118 with a seat can move the tapered ring 116 back and forth. According to this embodiment, during rolling a pin 114 is removed and the tapered ring 116 is moved leftwards in the drawing so that the tapered ring 116 does not contact the inner surface of the sleeve 90. The sleeve 90, the movable expanding mechanism 107, the thrust-receiving flange 106, the sealing body 109, the outer ring 105b of the thrust bearing 105, and a cover 111 which is secured to a sealing member by a bolt 115 rotate when a rolling load is applied to the sleeve 90. The lateral stopper 110, the inner ring 105a of the thrust bearing 105 and the spacer 112 do not rotate. When grinding is to be performed on the sleeve 90, the pin 114 is replaced. All the elements which constitute the supporting mechanism 104 are interconnected with each other and are fixed with respect to the arbor 1. Then bolt 118 is tightened to move the tapered ring 116 rightwards in the drawing until its tapered inner surface is pressed against the sleeve 90. In this state, the sleeve 90 is coaxially secured to the arbor 1 and is prevented from rotation. Figure 12 shows a still another embodiment of this invention. In this embodiment, a tapered ring 116 is employed to prevent the rotation of a sleeve with untapered edges. The operation of this embodiment is essentially the same as that of the previous embodiment. When bolt 118 is loosened, tapered ring 116 is moved to the left in the drawing, and the sleeve 90 is free to rotate with respect to the arbor 1. When bolt 118 is tightened, tapered ring 116 is moved to the right in the drawing, and a wedge 117 is pushed outwards against the sleeve 90. This secures the sleeve 90 to the arbor 1 and enables grinding to be performed on the sleeve 90. Thus according to the above-described embodiments, the sleeves can either be rotatably supported by the arbor through bearing, or they can be secured to the arbor by their inner surfaces whenever it is necessary to carry out grinding. The grinding of the sleeve can be carried out without removing the sleeve from the roll, resulting in a marked decrease in maintenance costs. Next, the present invention will be described in further detail by means of a working example. Example A small, 4-high rolling mill was employed which used a variable-crown roll like that shown in Figure 1 as a back-up roll on one side. The work rolls measured 80 mm in diameter and had a barrel length of 400 mm, while the back-up rolls measured 240 mm in diameter and had a barrel length of 400 mm. Roller bearings 21 and 22 (outer diameter = 240 mm, inner diameter = 170 mm, length = 175 mm) were fit directly over a curved arbor 1 having an outer diameter of 170 mm and were secured thereto by keys. The bending angle α of the curved arbor was 0.2 o . Accordingly, by rotating the arbor 1, the roll crown could be varied from a concave crown to a convex crown having the following magnitude: δ = α · ℓ = 3.14 x 0.2/180 x 175 = 0.6 mm. A cylindrical sleeve 90 having an inner diameter of 250 mm and a wall thickness of 4 mm was fit loosely over the outer races of the bearings. Thrust loads from the sleeve 90 were received by supporting plates which supported both ends of the sleeve 90. An arbor angle adjusting mechanism 70 like that shown in Figures 8 and 9 was installed on one end of the arbor 1. The ability of this rolling mill to control the deflection of the work rolls was investigated. An aluminum plate measuring 4 mm thick and 350 mm wide was compressed between the work rolls with a force of 20 tons, and the distribution of dents in the aluminum plate was observed as an indication of variations in the roll deflection. During the rolling, the arbor rotational angle was varied from 0 o to 180 o , and the roll crown was varied in 5 steps from δ to -δ. When the arbor rotational angle was 0 o , the roll crown was . The results of measurements are shown in Figure 13. The abscissa indicates the distance from the widthwise center of the plate, and the ordinate indicates the deviation in mm of the thickness of the plate from the thickness at the widthwise center. Each curve is for a different value of the arbor rotational angle. The maximum convex roll crown was obtained with an arbor rotational angle of 0 o , and in this case, the plate thickness decreased towards the widthwise center thereof. The maximum concave roll crown was obtained with an arbor rotational angle of 180 o , and in this case, the plate thickness increased towards its widthwise center. It can be seen that the profile of a plate can be freely adjusted by setting the arbor rotational angle. The magnitude of the roll crown which can be obtained is 5 - 10 times that possible using a conventional variable-crown roll. The dashed lines in Figure 13 show the results when an already-installed roll bender was employed together with an arbor rotational angle of 0 o , 90 o , and 180 o . At an angle of 0 o , the plate crown was increased, whereas with an angle of 90 o or 180 o , the plate crown was decreased. Thus, the effects of the roll bender are superimposed on the effects of the variable-crown roll of the present invention, but the effects of the bender are far less than those of the variable-crown roll. Furthermore, as it is possible to regrind the peripheral surface of the sleeve without removing it from the roll when it undergoes wear and roughening of the surface, a variable-crown roll of the present invention which is equipped with the means for fixing and releasing the sleeve with respect to the arbor is very much advantageous from a practical viewpoint. A variable-crown roll in accordance with the present invention can also be employed as a work roll. However, in this case, the requirements as to the sleeve thickness, the material constituting the sleeve, the sleeve hardness, and the like are stricter than when the roll is used as a back-up roll.

Claims: A variable-crown roll comprising: an arbor (1); a plurality of antifriction bearings comprising first bearings (21,22; 24,25) which are mounted on said arbor, each of said first bearings having a cylindrical outer surface which is sloped with respect to the outer surface of said arbor, said first bearings being symmetrically disposed with respect to the lengthwise center of said arbor, the slopes of the outer surfaces of said first bearings on one side of the lengthwise center of said arbor being symmetric with respect to the slopes of the outer surfaces of said first bearings on the other side of the lengthwise center; a cylindrical sleeve (90) which loosely fits over said antifriction bearings; means for transmitting thrusts from said cylindrical sleeve to said arbor; characterized in that the variable-crown roll comprises fixing means (104) for releasably fixing said sleeve with respect to said arbor to prevent rotation of said sleeve with respect to said arbor whenever grinding is to be performed, said fixing means being positioned on each end portion of said sleeve. A variable-crown roll as claimed in claim 1, wherein: said arbor is a straight arbor (1), and wherein said antifriction bearings further comprise a second antifriction bearing (23;23') which is mounted on the center of said arbor between said first bearings, said second bearing having a cylindrical outer surface which is parallel to but eccentric with respect to the outer surface of said arbor (1). A variable-crown roll as claimed in claim 1, wherein: said arbor is a curved arbor (1). A variable-crown roll as claimed in claim 1, wherein: said arbor comprises a straight central portion and opposite curved portions symmetrically positioned with respect to said central portion and wherein said antifriction bearings comprise a second antifriction bearing (23;23') which is mounted on the center portion of said arbor between said first bearings (21,22;24,25). A variable-crown roll as claimed in any one of claims 1 - 4 wherein said fixing means (104) comprises means for fixing the sleeve by applying frictional force to an inner peripheral surface of the sleeve. A variable-crown roll as claimed in claim 5 wherein said fixing means (104) comprises an expandable ring (107a) disposed between the sleeve and the arbor and means (107) for expanding the ring from a state in which the expandable ring is separated from the inner peripheral surface of the sleeve (90) to an expanded state in which the ring contacts the inner peripheral surface of the sleeve. A variable-crown roll as claimed in claim 6 wherein the expandable ring (107a) has a sloping surface and the means for expanding the ring comprises a wedge shaped body having a sloping surface and means for moving the wedge shaped body to exert a force on the sloping surface to expand the expandable ring. A variable-crown roll as claimed in claim 5 wherein: the inner peripheral surface of the sleeve has a slope formed therein ; and said fixing means (104) comprises a tapered ring (116) having a tapered outer peripheral surface and means (118) for moving the tapered ring along a path to move the tapered surface of the tapered ring into and out of contact with the slope in the sleeve. A variable-crown roll as claimed in claim 5 wherein said fixing means (104) comprises: a tapered ring (116) having a tapered outer peripheral surface disposed between the sleeve (90) and the arbor (1); a wedge (117) disposed between the tapered ring and the sleeve and having an outer surface opposing the inner peripheral surface of the sleeve and a sloping surface opposing the tapered surface of the tapered ring; and means (118) for moving the tapered ring along a path to press the tapered surface of the tapered ring against the sloping surface of the wedge.

Inventors: INOUE SUSUMU, MASUI TAKESHI, TOMIZAWA ATSUSHI, INOUE, SUSUMU, MASUI, TAKESHI, TOMIZAWA, ATSUSHI
Applicants: SUMITOMO METAL IND, SUMITOMO METAL INDUSTRIES, LTD.
Application year: 1990
Main classification: B21B27
IPC codes: B21B27