US3172314A - Roll adjustment means - Google Patents

Description

March 1965 M. MORGAN ETAL 3,172,314

ROLL ADJUSTMENT mums Filed Sept. 24, 1962 7 Sheets-Sheet l l'aweiziom: Myles Mozig 02308 208 :11 by W, aux-Q4 y ffwd.

fliioflifiqya March 9, 1965 M. MORGAN ETAL ROLL ADJUSTMENT MEANS Filed Sept. 24, 1962 7 Sheets-Sheet 2 1208374303 Mazes Mar am, WM d1. ,Jz by W, 64% #f/wmfi fli'i'orflqys Q0 mm March 9, 1965 M. MORGAN ETAL 3,172,314

ROLL ADJUSTMENT mums Filed Sept. 24. 1962 '7 Sheets-$heet 3 M. MORGAN ETAL ROLL ADJUSTMENT MEANS March 9, 1965 7 Sheets-Sheet 4 Filed Sept. 24, 1962 301 530 no Euzw dwa Iawerai'oas: Myles Morgana CWZQQ' /1.Rici= ,Je! by M, W 1 W fliovizeys I an QT NM |-l-l Ilia}! l-l.l wm B Q a l km mm 3. mm 5 m March 9, 1965 M. MORGAN ETAL ROLL ADJUSTMENT MEANS 7 Sheets-Sheet 5 Filed Sept. 24, 1962 12201223202.- M92. Mozigw,

, Gama/ -r W flavflneya March 9, 1965 M. MORGAN ETAL ROLL ADJUSTMENT MEANS 7 Sheets-Sheet 6 Filed Sept. 24, 1962 Z H n 1 mm m o I d 9 ll v 4 z i M a I 3 a 4 4 w m %mm a 0 5 I Un ited States Patent 3,172,314 ROLL ADJUSTMENT MEANS Myles Morgan and Charles A. Rich, Jr., Worcester, Mass, assignors to Morgan Construction Company, Worcester, Mass, a corporation of Massachusetts Filed Sept. 24, 1962, Ser. No. 225,818 8 Claims. ((31. 80-56) This invention relates to metal working machinery and is particularly concerned with rolling mills and the means for controlling and adjusting the spacing between the rolls.

In the rolling of metals, whether they be sheet, skelp, rods, bars or otherwise, it is essential that the spacing between the rolls be subject to accurate adjustment and control. In current practice, adjust-intent is achieved through the use of screwdown devices which in the case of horizontal rolls control the distance of separation between the upper and lower rolls. When adjustment of the spacing between the rolls is made, in some cases only the upper roll is moved, or alternatively only the lower roll is moved; the other roll in either case remains unchanged. This results in vertical displacement of the pass line; that is, the pass line will shift upwardly when either the upper or lower roll is adjusted upwardly and downwardly when either roll is adjusted downwardly. Shifting the vertical position of the pass line necessitates corresponding adjustments of the pass guide that direct the leading end or edge of the next oncoming bar or strip to a central position between the rolls.

In all constructions of the prior art, the separating forces applied to the rolls by the metal passing therebetween is resisted by the frame of the roll housing in which the roll chocks are mounted. However, elongation of the frame under this separating force is of suflicient magnitude to limit the accuracy of adjustment. To overcome this deficiency, a new type of roll mounting has recently been developed as shown in United States Patent No. 3,055,242 to A. 1. Wilson. In this construction, the lower roll bearings are hung from the upper roll bearings by four short heavy links. Because of their dimensions, the links are subject to negligible elongation under the separating forces exerted by metal passing between the rolls. In the Wilson patent just referred to, eccentric means are disclosed for shifting the vertical position of the links with respect to the upper rolls, thereby varying the distance between the rolls by vertically displacing the lower roll. This means of adjustment has been found entirely satisfactory both as to accuracy of control and ease of operation. It suflers, however, from the same disability found in the prior art in that the vertical position of the pass line changes as the lower roll is moved up and down with respect to the upper roll.

Accordingly, the present invention is directed toward providing a new and novel mechanism which may be utilized with the link structure of Wilson Patent No. 3,055,242 to produce equal and opposite movement of the rolls during adjustment, thereby enabling the pass line to remain at a constant level. More specifically, eccentric mechanisms are provided to act in conjunction with the links carrying the lower roll and the upper roll supporting trunnions, whereby as the eccentrics are rotated to cause the required adjustment, the upper roll will be raised or lowered with respect to the roll housing or frame and the links will be lowered or raised with respect to the upper roll through a distance which is twice the distance the upper roll is raised or lowered. This results in equal displacement of both rolls in opposite directions toward or away from the pass line.

A second aspect of the present invention is the inclusion of two additional eccentrics positioned within the roll adjusting eccentrics in such manner that, upon rotation of the inner eccentrics, coarse adjustment of the rolls may be quickly made to provide for the major adjustment in roll spacing necessitated when roll changes are made in which the new rolls are of greater or lesser diameter than the replaced rolls. Since the upper and lower rolls are always of equal diameter, although possibly of diameters different from the rolls previously used, adjustments made according to the present invention will cause the pass line to remain at a constant level. Hence it is unnecessary to make any adjustment of the pass guides when roll changes are undertaken. It is to be appreciated, however, that the coarse adjustment eccentrics may be omitted in those cases where any required adjustment of the rolls will fall within the scope of the fine adjustment eccentrics. Thus it will be understood that the fine adjustment eccentrics may be used either with or without the inclusion of the coarse adjustment eccentrics.

While the coarse adjustment eccentrics are utilized to impart quick coarse adjustment to the rolls, they operate on the same principle as that of the fine adjustment eccentrics; namely, the upper roll is moved up or down one unit with respect to the supporting housing or frame while the links that carry the lower roll are simultaneously lowered or raised two units in an opposite direction.

Accordingly, a major object of the present invention is to provide means for imparting precise and known adjustments to rolls supported by the frame and links structure of Wilson Patent No. 3,055,242 while maintaining the pass line at a constant level.

A further object of the invention is to provide an arrangement of eccentrics such that one unit of angular rotation of the fine adjustment eccentrics will result in one unit of linear separation or closing of the rolls over the full extent of adjustment required.

A further object of the invention is to provide novel means for actuating the adjusting eccentrics whereby the upper and lower chocks at the work and drive sides of the housing may be adjusted independently. In this way, the parallelism of the rolls may be controlled at will but without changing the vertical level of the pass line.

These and other objects of the invention will be more particularly understood as the description proceeds with the aid of the accompanying drawings in which:

FIG. 1 is a side elevation partly in vertical section of a pair of horizontal rolls and related housing taken along line 11 of FIG. 3 and illustrating the principal embodiments of the invention herein chosen for purposes of disclosure;

FIG. 2 is a plan view of FIG. 1 with the top cover removed;

FIG. 3 is a vertical sectional view in end elevation taken along lines 3-3 of FIG. 1 with the eccentrics in a position corresponding to that shown in FIG. 5;

FIG. 4 is a side-by-side arrangement of two sectional views taken on the lines 4-4 and 4A4A of FIG. 3 illustrating the roll adjusting mechanism disclosed in the principal embodiments of the invention wherein the connected and rotatable first and second eccentrics have been shown in the position in which their largest radial dimensions are upwardly disposed;

FIG. 5 is a view similar to FIG. 4 wherein both eccentrics have been rotated through an angle of FIG. 6 is a view similar to FIGS. 4 and 5 wherein both eccentrics have been rotated through an angle of FIG. 7 illustrates the relationship between the displacement of the upper and lower rolls with respect to the pass line as the first and second eccentrics are rotated through an angle of 180 starting from the position of FIG. 4 and ending with the position of FIG. 6;

FIG. 8 is a sectional view in end elevation similar to FIG. 3 with the first and second eccentrics in the position of FIG. 5 but illustrating an alternate embodiment of the invention wherein connected and rotatable third and fourth eccentrics have been positioned within the first and second eccentrics with their largest radial dimensions upwardly disposed;

FIG. 9 is a view similar to FIG. 8 showing the relative displacement of the upper and lower rolls as the third and fourth eccentrics are rotated 90 while the first and second eccentrics remain as in FIG. 8; 7

FIG. 10 is a view similar to FIGS. 8 and 9 showing the relative displacement of the upper and lower rolls as the third and fourth eccentrics are rotated through a further angle of 90; FIG. 11 is a side-by-side arrangement of two sectional views taken on lines 11-11 and 11A-11A of FIG. 8 illustrating the roll adjusting mechanism disclosed in the alternate embodiment of the invention wherein the third and fourth eccentrics have been shown with their largest radial dimension upwardly disposed and the first and second eccentrics shown in the intermediate rotational position similar to FIG. with the adjusting arm in'normal vertical position;

FIG. 12 is a view similar to FIG. 11 wherein the third and fourth eccentrics have been rotated through an angle of 90 with the first and second eccentrics remaining as shown in FIG. 11;

FIG. 13 is a view similar to FIG. 11 wherein the third and fourth eccentrics have been rotated through an angle of 180 with the first and second eccentrics remaining as in FIGS. 11 and 12; and

FIG. 14 illustrates how the fine adjustment between the rolls achieved by the firs-t and second eccentrics may be utilized over a wide range of roll spacings made possible by the use of the third and fourth rough adjustment eccentries.

The principal embodiment of the invention which is concerned with fine adjustment of the rolls while in operation or stationary is illustrated in FIGS. I7 and generally consists of means for accomplishing the simultane ous vertical displacement in opposite directions of both upper and lower rolls 2 and 4 which are mounted horizontally between members 6 and 8 of an open-ended roll housing or supporting frame generally referred to at 10.

In order to facilitate the description of the invention, only the supporting and adjusting mechanisms of the chocks at one end of the rolls will be referred to in detail. However, it will be understood that both the 'work side A and drive side B of the rolls are provided with identical supporting and adjusting mechanisms. Consequently, the description of the mechanisms at the work side will apply equally to the drive side.

Referring to FIGS. 1, 2 and 3, the roll neck of upper roll 2 at the work side A is rotatably contained within upper chock 12. Upper axially aligned trunnions 16 and 18 (see FIG. 3) extend laterally from chock 12 normal to the vertical plane passing through the longitudinal axes of the rolls 2 and 4. The outer ends of trunnions 16 and 18 are rotatably contained within first eccentrics 20 and 22 which are in turn rotatably contained within supporting means in the form of collars 24 and 26. These collars rest on portions 21 and 23 of the frame in such manner that when the roll 2 is adjusted axially by adjusting means 27 (see FIG. 1) the collars may move correspondingly. Eccentric adjusting arms 28 and 30 and the associated second eccentrics 32 and 34 are also rotatably mounted on upper trunnions 16 and 18. The second eccentrics 32 and 34 are positioned between first eccentrics and 22 and the sides of chock 12 (see FIG. 3). For convenience, eccentrics 20 and 32 and 22 and 34 may be made as a single unit or, if preferred, may be made separately and pinned together. Depending links 36 and 38 rotatably carried by eccentrics 32 and 34 are positioned between adjusting arms 28 and and chock 12.

Again referring to FIGS.- 1 and 3, the roll neck of lower roll 4 on the work side A is rotatably mounted with in lower chock 40 having lower axially aligned trunnions 44 and 46 laterally extending therefrom. All trunnions have their axes parallel to the pass line. The lower trunnions are rotatably mounted in bearings 48 and 50 positioned within circular apertures 52 and 54 at the lower ends of depending links 36 and 38. The faces of bearings 48 and 50 are in slidable engagement with frame 10.

As best seen in FIG. 3, eccentrics 20, 32 and 22, 34 are rotated together on their respective trunnions 16 and 18 by arms 28 and 30 and are so angularly related that the points of largest radial dimension of each eccentric are radially aligned. Thus in FIGS. 4, 5 and 6' the points of largest dimension indicated at L and L in eccentrics 32 and 20 are in radial agreement.

Rotation of adjusting arms 28 and 30 about upper trunnions 16 and 18 will cause corresponding rotation of both pairs of connected eccentrics on their respective trunnions. For reasons that will appear hereinafter, however, it should be noted that rotation of these eccentrics is conducted only through a limited angular range.

Since first eccentrics 20 and 22 are rotatably contained within collars 24 and 26 which reside. at a fixed vertical level, their rotation will result in vertical displacement of the upper trunnions 16 and 18. This in turn will cause the vertical displacement of the upper chock 12 which rotatably supports the work side of upper roll 2. At the.

same time, rotation of second eccentrics 32- and-34 will cause simultaneous and opposite vertical displacement of depending links 36 and 38 with respect to the upper trunnions 16 and 18. This in turn will cause a corresponding vertical displacement of lower chock 40 which rotatably supports the work side of lower roll 4.

FIGS. 4-6 are side-by-side sectional views on lines 44 and 4A-4A of FIG. 3 illustrating the resulting vertical displacements of the various members comprising the adjusting mechanism as the first and second eccentrics are rotated through an angle of 180. For purposes of illustration, upper trunnion 16 has been sectioned in two places to show the simultaneous rotation of first eccentric 20 and second eccentric 32. However, it will be understood that FIGS. 4-6 are also illustrative of the simultaneous operation of eccentrics 22 and 34 mounted on trunnion 18. In actual operation, the eccentrics 32 and 20 are moved through an angle of not more than 27,

13 /2 in each direction from the position shown in FIG. 5. However, for an understanding of the behavior of the parts, it is believed it will be clear if the explanation is given on the assumption that rotation of the eccentrics will be through an angle of 180. Accordingly, in FIGS. 4-6, the two eccentrics 32 and 20 are simultaneously rotated counterclockwise from the position of FIG. 4 through to the position of FIG. 5 and then 90 more to the position of FIG. 6. In so doing, there is caused upward displacement of upper trunnion 16 with respect to collar 24 and frame 10. Simultaneously the link 36 mounted on eccentric 32 descends with respect to trunnion 16. If the pass line PL is to be kept at the same level, trunnion 16 must rise one unit of distance with respect to the frame 10 while link 36 and its associated lower trunnion 44 must descend two units of distance. This result is accomplished by properly dimensioning eccentrics 20 and 32.

As can be seen in FIGS. 4-6, the difierence between the maximum and minimum radial dimensions 25 and 27 of second eccentric 32 is twice the difference between the maximum and minimum radial dimensions 29 and 31 of first eccentric 20. Consequently rotation of first eccentrics 20 and 22 and second eccentrics 32 and 34 through movement of adjusting arms 28 and 30 will cause links 36 and 38 to be vertically displaced downwardly through twice the distance of the vertical upward displacement of upper trunnions 16 and 18 or vice versa. The result is equal separation of upper and lower rolls 2 and 4 at the work side A with respect to the constant level pass line PL throughany degree of angular rotation of the eccentrics.

Hereinafter, the eccentrics 32 and 34 that affect the displacement of the links 36 and 38 may be referred to as double throw eccentrics and eccentrics 20 and 22 may be referred to as single throw eccentrics.

As previously stated, the drive side B of the roll housing is also provided with similar roll adjusting eccentric mechanism operated through rotation of a second set of adjusting arms 64 and 66 (see FIGS. 1 and 2).

The means for angularly moving adjusting arms 28 and 30 and 64 and 66 about upper trunnions 16 and 18 will now be described. Bracket 68 is mounted at the upper end of frame at the work side A and supports bearings 70 and 72 containing internally threaded hollow rotatable spindles 74 and 76 which can be separately operated by hand wheels 78 and 80. Rods 82 and 84 having screw threads at one end threaded within rotatable spindles 74 and 76 are pivotally secured by pins 85 and 87 at their opposite ends to brackets 86 and 88 (see FIGS. 2 and 3) which are in turn secured to crosswise extending brackets 90 and 92. Brackets 90 and 92 are rigidly secured to and between adjusting arms 28 and 30 and arms 64 and 66 by bolts 95 at the work and drive sides respectively.

In this manner, rotation of either hand wheel 78 or 80 will cause a corresponding horizontal displacement of either rod 82 or 84 and result in angular movement of the adjusting arms at either the work side A or drive side B of the housing. This in turn will actuate the work or drive side roll adjusting eccentrics and related mechanisms previously described and result in opposite vertical displacement of the rolls without any variance in the vertical position of the pass line.

As can be seen from the graphical illustration of FIG. 7, curves 94 and 96 are representative of the relationship between the vertical displacement of the upper and lower rolls 2 and 4 with respect to the pass line as the first and 'second eccentrics are rotated through an angle of 180".

.T his is not a straight line curve, but it is apparent that when the eccentrics are in the position of FIG. 5 with their thick and thin portions lying in a horizontal plane equal degrees of eccentric rotation in either direction from the 90 position will yield corresponding constant units of vertical roll displacement. The practical limits of such adjusting arm movement is from 76 /2 to 103 /2 Through this angular range of 27, the curves 94 and 96 are substantially straight lines as indicated at S. If the adjusting arms are operated outside this range, a unit of angular displacement will yield varying units of vertical roll displacement. By calibrating wheels 78 and 80, the

. extent of movement of the rolls 2 and 4 over the 27 range of eccentric movement may be accurately known and controlled.

Where all roll adjustments can be performed within an adjusting arm angular displacement range of 27 with the eccentrics in the position of FIG. 5, the above-mentioned mechanism is perfectly satisfactory. However, under certain conditions, it is not possible to accomplish the desired roll adjustments using only first and second eccentrics without exceeding this permissible range of angular -rotation. For example, when roll changes are made in which the new rolls are of greater or lesser diameter than the old rolls, substantial roll adjustments are sometimes necessitated. Furthermore, the performance of substantial roll adjustments through the use of hand wheels 78 and 80 would require considerable time. Hence means for quickly performing these large adjustments is highly desirable.

Accordingly, an alternate embodiment of the invention is disclosed in FIGS. 8 through 14 wherein coarse adjustment third eccentrics 98 and 100 and fourth eccentrics 102 and 104 have been rotatably mounted on upper trunnions 16 and 18 and positioned within the fine adjustment first and second eccentrics respectively. The third and fourth eccentrics are secured together and constitute single units 106 and 108 with a cylindrical bore which fits closely and, rotatably on their respective trunnions 16 and 18. Their rotation about trunnions 16 and 18 is accomplishedby rotation of circular end plates 110 and 112 attached the same angular extent.

6 to the units 106 and 108. The end"plates and 112 may be locked in position by pins 114 and 116 which reside in radial slots in the plates and extend into the fixed cover plates 115 and 117.

As can be seen in FIG. 8, third eccentrics 98 and 100 are rotatably positioned between upper trunnions 16 and 18 and first eccentrics 20 and 22. Similarly fourth eccentrics 102 and 104 have been rotatably positioned between upper trunnions 16 and 18 and second eccentrics 32 and 34. It should be noted at this time that rotation of the inner coarse adjustment third and fourth eccentrics by manual or mechanical rotation of end plates 110 and 112 does not cause or require rotation of the fine adjustment first and second eccentrics. Instead, it is intended that units 106 and 108 rotate independently of the first and second eccentrics. FIGS. 9 and 10 illustrate the effects resulting from rotation of the third and fourth eccentrics of unit 106 about upper trunnion 16 through angles of 90 and 180. As can be seen from a comparison of FIGS. 8, 9 and 10, rotation of third eccentric 98 results in an upward displacement of upper trunnion 16 with respect to frame portion 21, and rotation of fourth eccentric 102 results in a downward displacement of depending link 36 with respect to trunnion 16.

FIGS. 11, 12 and 13 are side-by-side sectional views taken on the line 1111 and 11A11A of FIG. 8 illus trating the changing vertical displacement of the trunnions and links as the third and fourth eccentrics 98 and 102 are rotated through angles of 90 and 180 while the first and second eccentrics 20 and 32 remain undisturbed in the position of FIG. 5.

Again, it should be noted that the difference between the maximum and minimum radial dimensions 116 and 118 of fourth eccentric 102 is twice the difference between the maximum and minimum radial dimensions 120 and 122 of third eccentric 98. In this manner, rotation of both units 106 and 108 carrying the third and fourth eccentrics will result in links 36 and 38 being vertically displaced through twice the distance of the vertical displacement of upper trunnion 16 and in the opposite direction. Consequently, the upper and lower rolls 2 and 4 will be equally displaced in opposite directions without disturbing the vertical position of the pass line PL.

In this alternative construction the first and second eccentrics do not have a common bore and must, therefore, be separate so that they may shift laterally of each other as the units 106 and 108 bearing the third and fourth eccentrics are rotated therewithin. However, means have been provided so that when the eccentric 32 is rotated by arm 28, eccentric 20 will also rotate to As can be seen in FIG. 8, eccentrics 32 and 20 have aligned radial keyways 123 and 125 out in adjacent surfaces at the position of maximum radial dimension. A snugly fitting key 127 in the form of a cylindrical button is placed in the keyways. This permits the eccentrics to shift laterally with respect to each other but compels simultaneous and equal rotation under the movement of arm 28. v

FIG. 14 is a graphic illustration showing the range of roll adjustments made possible through the combined use of first, second, third and fourth eccentrics. Curves 94 and 96 again illustrate the relationship between the angular rotation of first and second eccentrics 20 and .32 and the vertical displacement of the upper and lower rolls 2 and 4. Curves 124 and 126 represent the maximum opening of the rolls and 120 and 130 the minimum opening obtainable through rotation of the third and fourth eccentrics. It should be noted that the third and fourth eccentrics can be efficiently utilized throughout an entire of rotation about the upper trunnions by radially sub-dividing adjusting end plates 110 and 112 as at 130 into units of varying degrees in order that any one unit of angular rotation will produce a constant unit of vertical roll displacement. In this manner, a wide range of roll adjustments can be accomplished by operating personnel without any resulting confusion. In addition, large adjustments can be quickly performed by the use of a third and fourth eccentric, and fine adjustments can be completed by the use of the first and second eccentrics moved from the position of FIG. through a 27 range.

The coarse adjustments utilizing the single and double throw eccentrics 98, 160 and 102, 104 are normally made while the rolls are not in operation or when they are out of the housing by manual rotation of plates 110 and 112. On the other hand, the fine adjustments accomplished by movement of arms 23 and 30 are made when the rolls are in the housing, stationary or operatmg.

While the invention has been described with particular reference to a horizontal rolling mill, it is obvious that it is equally applicable to a vertical mill. That is to say, since the trunnions, the eccentrics and the links all engage each other in a no-clearance manner, it is believed apparent that if the disclosed rolls, chocks and adjusting means were shifted from the horizontal to the vertical in conventional rolling position the adjustment means would be equally effective in maintaining the pass line in a constant transverse position. The links would, of course, be horizontal rather than vertical and would bear the separating forces.

Therefore, in the claims when reference is made to the upper roll, it is to be understood as meaning the upper roll in a horizontal mill and that roll in a vertical mill whose chocks carry the eccentrics. When the links are described as depending from the upper chocks, it is to be understood that in a vertical mill the links would extend horizontally to the other roll chocks, which in the claims are called the lower chocks.

It is our intention to cover all changes and modifications of the example of the invention herein chosen for purposes of disclosure which do not constitute departures from the spirit and scope of the invention.

We claim:

1. In a rolling mill, a frame, an upper roll, upper chocks rotatably supporting the ends of said upper roll, upper trunnions extending from opposite sides of each of said upper chocks, intermediate means including a first eccentric between each said upper trunnion and said frame for supporting said upper chocks, a link supported by each said upper trunnion depending below said upper chocks, a lower roll, lower chocks rotatably supporting the ends of said lower roll, lower trunnions extending from opposite sides of each said lower chock and connected to the lower ends of said links, a second eccentric intermediate said link and upper trunnion, said first and second eccentrics comprising means for simultaneously accomplishing equal and opposite displacement of said upper and lower rolls toward or away from a fixed pass line.

2. In a rolling mill, a frame, an upper roll, upper chocks rotatably supporting the ends of said upper roll, upper trunnions extending from opposite sides of each of said upper chocks, means intermediate each said upper trunnion and said frame for supporting said upper chocks, a link on each said upper trunnion depending below said upper chocks, a lower roll, lower chocks rotatably supporting the ends of said lower roll, lower trunnions extending from opposite sides of each of said lower chocks and connected to the lower ends of said links, first eccentrics between each said intermediate means and each of said upper trunnions, second eccentrics between each of said links and each said upper trunnion, means for causing simultaneous rotation of said first and second eccentrics about said upper trunnions and within their respective intermediate means and links, the dimensions of said first and second eccentrics being such that p or closing movement of said upper and lower rolls is equal and opposite with respect to a fixed pass line.

3. In a rolling mill, a frame, an upper roll rotatably supported by upper chocks, upper trunnions extending from opposite sides of said upper chocks and supported through intermediate means by said frame, a link depending from each said upper trunnion below said upper chocks, a lower roll rotatably supported by lower chocks having lower trunnions extending from opposite sides thereof and connected to the lower ends of said links, means for accomplishing coarse roll adjustments of substantial magnitude at each end of said rolls, said means acting to move said rolls simultaneously toward or away from each other equal distances from a fixed pass line, and other means acting in cooperation with said coarse adjusting means for accomplishing similar but precise roll adjustments of smaller magnitude without changing the position of said fixed pass line.

4. A rolling mill as described in claim 3, said last mentioned means and other means comprising for each upper trunnion, first, second, third and fourth eccentrics, said third and fourth eccentrics rotatably positioned on said upper trunnion, said first eccentrics rotatably positioned on said third eccentrics and supported through said intermediate means by said frame, said second eccentrics rotatably positioned on said fourth eccentrics and contained for rotation within each said depending link, said first and second eccentrics operatively connected for simultaneous rotation about said third and fourth eccentrics, said third and fourth eccentrics comprising an integral unit each adapted for rotation about its said upper trunnion, said third and fourth eccentrics capable of being rotated independently of said first and second eccentrics, the dimensions of said first and second eccentrics being such that when rotated displacement of said upper trunnion with respect to said frame is one-half the displacement of said links with respect to said upper trunnions and in the opposite direction, whereby said first and second eccentrics can be utilized through a limited angular rotation to accomplish fine adjustments of limited magnitude, the dimensions of said third and fourth eccentrics being such that when rotated the displacement of said upper trunnion with respect to said frame is one-half the displacement of said links with respect to said upper trunnion and in the opposite direction, whereby said third and fourth eccentrics can be rotated through a large angle to perform large adjustments.

5. Means for adjustably connecting upper and lower roll chocks and the rolls carried thereby, said means comprising parallel trunnions extending from said chocks with their axes parallel to the pass line of the rolls, a coarse adjustment eccentric unit positioned on the upper trunnion, said unit comprising two side-by-side eccentrics in which the eccentric adjacent the chock has double the throw of the eccentric remote from the chock, said coarse adjustment unit rotatable on said trunnion through an angle greater than two fine adjustment eccentrics positioned on said coarse adjustment eccentrics, one of said fine adjustment eccentrics having double the throw of the other and coacting with the corresponding coarse adjustment double throw eccentric, a link mounted on the fine adjustment double throw eccentric and rotatably connected to the lower trunnion, the fine adjustment single throw eccentric rotatably mounted on the single throw coarse adjustment eccentric and carried by a supporting member, the wide and narrow portions of said fine adjustment eccentrics being normally positioned in a horizontal plane, means for simultaneously moving said fine adjustment eccentrics in either direction from said normal POSI- tion through a relatively small angular range, whereby upon rotation of said fine adjustment eccentrics through said small angle there will be corresponding equal and opposite movements of said chocks and a unit of angular motion throughout the said angular range will produce a unit of linear motion of said chocks and whereby rotation of said coarse adjustment eccentrics through any angle Within said fine adjustment eccentrics and about said upper trunnion will produce additional equal and opposite movements of said chocks toward and away from each other.

6. Means for simultaneously moving the chocks at one end of adjacent rolls in a rolling mill toward and away from each other an equal amount, said means comprising parallel trunnions extending laterally from said chocks with their axes parallel to the pass line, two pairs of double throw eccentrics in which each pair has one eccentric mounted within the other with the inner eccentric rotatably mounted on one of the trunnions of one chock, links carried by the outer eccentrics of said double throw eccentrics and having their other ends rotatably connected to the trunnions of the other chock, two pairs of single throw eccentrics in which each pair has one eccentric positioned within the other with the inner of said two single throw eccentrics rotatably mounted on said trunnion, the outer of said single throw eccentrics rotatably positioned within supporting means, means for causing simultaneous rotation of the two inner single and double throw eccentrics and means for causing simultaneous rotation through a limited angle of the two outer single and double throw eccentrics, whereby independent or collective rotation of the two inner eccentrics and/or the two outer eccentrics will cause equal and opposite movements of the chocks with respect to the supporting means.

7. Means for causing equal and opposite movements of a pair of rolls and their supporting chocks with respect to the pass line, said means comprising trunnions extending laterally from said chocks and having their axes parallel to the said pass line, two side-by-side inner eccentrics positioned on each trunnion of one chock for producing coarse adjustment of said chocks, one of the said inner eccentrics having double the throw of the other inner eccentric, another pair of side-by-side outer eccentrics encompassing the first two inner eccentrics for producing fine adjustment, the outer eccentric that encompasses the inner double throw eccentric having double the throw of the other outer eccentric which encompasses the inner single throw eccentric, a link carried by the outer of the two double throw eccentrics and rotatably engaging the trunnions of the other chock, supporting means rotatably carrying the outer eccentric of each pair of single throw eccentrics, means for simultaneously rotating the inner coarse adjustment eccentrics through a substantial angle,

whereby equal and opposite movements of said chocks may be caused, means for securing said inner coarse adjustment eccentrics in any selected angular position with respect to said supporting means, said outer fine adjustment eccentrics normally positioned with their wide and narrow sections in a horizontal plane, and means for simultaneously rotating the outer eccentrics through a limited angle, said angle being such that for one unit of angular rotation through the entire angular range of movement there will be a corresponding unit of movement of said chocks toward or away from each other.

8. Means forrefiecting fine adjustment of the rolls of a rolling mill whereby the pass line will remain in a constant position, said means comprising adjacent chocks on the ends of said rolls, trunnions extending laterally from said chocks with their axes parallel to the said pass line, pairs of adjacent eccentrics mounted for rotation about the trunnions of one chock, one of said eccentrics having double the throw of the other, a link having one end surrounding said double throw eccentric and the other end pivotally mounted on the corresponding trunnion of the other adjacent chock, a support, the other eccentric rotat ably mounted within said support, an adjusting arm operatively connected to the eccentrics whereby movement of said arm will cause corresponding rotative movement of said eccentrics about said trunnion, said eccentrics being normally positioned so that the wide and narrow parts thereof are generally in a horizontal plane whereby rotation of said eccentrics through a limited angular range in either direction from normal position will produce movement in one direction of the eccentric carrying trunnions of one of said chocks with respect to the support and movement in the opposite direction of the links with respect to the trunnions in the ratio of one to two and whereby the roll carried by the chock having the associated trunnions and eccentrics will move equally and oppositely from the roll carried by the other chock.

References Cited in the file of this patent UNITED STATES PATENTS 285,567 Carter Sept. 25, 1883 2,774,263 Leufven Dec. 18, 1956 3,055,242 Wilson Sept. 25, 1962 FOREIGN PATENTS 502,916 Belgium May 15, 1951

Claims (1)

1. IN A ROLLING MILL, A FRAME, AN UPPER ROLL, UPPER CHOCKS ROTATABLY SUPPORTING THE ENDS OF SAID UPPER ROLL, UPPER TRUNNIONS EXTENDING FROM OPPOSITE SIDES OF EACH OF SAID UPPER CHOCKS, INTERMEDIATE MEANS INCLUDING A FIRST ECCENTRIC BETWEEN EACH SAID UPPER TRUNNION AND SAID FRAME FOR SUPPORTING SAID UPPER CHOCKS, A LINK SUPPORTED BY EACH SAID UPPER TRUNNION DEPENDING BELOW SAID UPPER CHOCKS, A LOWER ROLL, LOWER CHOCKS ROTATABLY SUPPORTING THE ENDS OF SAID LOWER ROLL, LOWER TRUNNIONS EXTENDING FROM OPPOSITE SIDES OF EACH SAID LOWER CHOCK AND CONNECTED TO THE LOWER ENDS OF SAID LINKS, A SECOND ECCENTRIC INTERMEDIATE SAID LINK AND UPPER TRUNNION, SAID FIRST AND SECOND ECCENTRICS COMPRISING MEANS FOR SIMULTANEOUSLY ACCOMPLISHING EQUAL AND OPPOSITE DISPLACEMENT OF SAID

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