Apparatus for bias rolling of strip metal

A process and apparatus for bias rolling of strip metal is provided wherein the strip stock is formed cylindrically and passed through a rolling station wherein roll passes formed by small diameter rolls traverse the stock on the bias along helical paths which successively overlap so that a uniform and flat rolled surface is formed.

FIELD OF THE INVENTION 
This invention relates to the reduction of strip metal by rolling. It 
applies to both hot and cold rolling. More particularly it relates to 
methods and apparatus for rolling strip metal on an angle or on the bias. 
BACKGROUND OF THE INVENTION 
Strip metal has been conventionally reduced by rolling it along the 
longitudinal axis of the strip in succeeding roll stands the passes of 
which are on transversely extending lines. In one instance, however, 
rollers have been arranged to rotate in an orbital path and come down 
abruptly onto the strip, (see German Pat. No. 2622606). These latter 
devices have various disadvantages including severe treatment of the 
bearings, and causing dimples or waves on the surface of the strip. 
A general object of this invention is to provide an improved strip rolling 
process and apparatus in which a multiplicity of small diameter rolls can 
be used with the concomitant increase in the efficiency thereof, but 
without at the same time sacrificing flatness and uniformity of surface of 
the strip. Another object is to provide a strip rolling process and 
apparatus in which the strip can be readily equalized and interchanged 
between concave or convex cross-section. 
BRIEF DESCRIPTION OF THE INVENTION 
In the accomplishment of these and other objects of the invention in a 
preferred embodiment, the strip is fed through a roll stand in which a 
multiplicity of work rolls arranged in radially aligned pairs define roll 
passes which are supported respectively on an inner central shaft and an 
outer planetary ring so as to orbit around the central axis as the strip 
stock in the form of a cylinder comes through. In this way the rolling 
action takes place on the bias, i.e. at an angle across the stock and the 
roll pressure paths follow parallel helical lines. It is a feature of the 
invention that the pressure paths of succeeding rolls overlap so that the 
entire surface of the strip is uniformly and flatly rolled. Another 
feature is that when the overlap is at least 50% rolling, efficiency is 
improved because each roll is then acting at least 50% on stock which has 
previously been rolled only shortly before. Still another feature is that 
a multiplicity of small work rolls can be employed with the concomitant 
efficiency advantages thereof. The process and apparatus are especially 
useful for the hot rolling of steel strip, but can also be used 
advantageously for cold or warm rolling as well as for copper, aluminum 
and other metals including continuously cast stock. 
A feature of one embodiment is that the strip can be fed to the rolling 
station in the form of an elongated portion of the surface of a segment of 
a cylinder and reduced by the action of roll passes orbiting in a plane 
normal to the axis of the strip. In another embodiment two or more strips 
can be fed in barber pole fashion around the surface of a rotating 
mandrel. In this latter embodiment, the orbital motion of the roll passes 
is on a plane set at an angle to the motion of the stock, but the bias 
rolling principal and the overlap of the pressure paths of the respective 
roll passes is the same. A feature, however, of latter embodiment is that 
the cylindrical form of the stock takes the shape of a helix rather than 
extending longitudinally of the stock.

DETAILED DESCRIPTION OF THE INVENTION 
The illustrative embodiment therein shown of a mill for rolling strip metal 
on the bias is mounted on a base frame 3 having side supports 1, 2. Chocks 
11, 12 are mounted respectively on side supports 1, 2 and serve as a base 
for shaft housings 7, 8 in which journals 5, 6 are mounted for 
longitudinal but not rotational movement and held in place by springs 9, 
10 in key ways. The journals 5, 6 support a central shaft 4, on which is 
mounted a tapered (truncated conical) member 13 having eight symetrically, 
circumferentially disposed grooves 14 in each of which is slidably mounted 
a work roll supporting shoe 15 on which a work roll 17 is mounted. 
A hydraulic ram comprising cylinder 18 and piston 19 is mounted coaxially 
at the end of shaft housing 7 for the purpose of moving the journals 5, 6 
together with the central shaft 4 longitudinally so as to move the shoes 
15 in grooves 14 and thereby to control the radial distance of all eight 
work rolls 17 from the axis of shaft 4 simultaneously. Hydraulic fluid is 
supplied to cylinder 18 by a double rotary valve 21 which also serves to 
supply regulated fluid in series to hydraulic motors 20 each of which 
drives each of the work rolls 17. Central shaft 4 is driven by a 
gear-actuated shaft 22 which communicates through housing 8 with shaft 4. 
Each work roll 17 acts against a corresponding external work roll 23 
mounted in a planetary ring 24 coaxially with shaft 4, on roller bearings 
25 supported by an outer housing 26. 
In order to adjust housing 26 horizontally relative to central shaft 4, the 
lower side portion of housing 26 is mounted on a bolt 26 (see FIG. 3) with 
a bracket 28 arranged with an eccentric drive 29 to move housing 26 
horizontally. Vertical adjustment of housing 26 is achieved by means of a 
wedge 30 acting under the control of a hydraulic ram 31 on the opposite 
side of housing 26 to raise and lower the housing 26. 
A motor 34 is mounted on side plate 2 arranged to drive a shaft 33 which in 
turn drives a branching gear 32, to turn shaft 22 (and hence central shaft 
4) through stationary housing 8. A further, motor 36 is mounted above 
motor 34 and serves to drive planetary ring 24 around the axis of central 
shaft 4 by means of a shaft 35 acting through intermediate shaft 38 and a 
pinion 39 mounted in housing 26 and meshing with gear teeth 40 in the 
external surface of the planetary ring 24. These drives are locked in 
synchronism so that the inner work rolls 17 and outer work rolls 23 are 
maintained precisely in tandem to form a rolling nip or bite therebetween 
in the plane of the stock. 
In the embodiment shown in FIG. 1 the outer work rolls 23 rotate merely 
under the influence of friction. They can, however, be driven by mechanism 
shown in FIG. 3. This is done by providing each outer work roll-23 with a 
drive shaft 47 having a helical gear 46 at its end which is in turn driven 
by gear teeth on an internal planetary gear ring 45 coaxial with center 
shaft 4. Ring gear 45 is driven by a pinion 44 on shaft 43 which is in 
turn driven by motor 41 mounted on side support 1 on a bracket 42. 
The rolling operation is diagramatically illustrated in FIG. 4 in which 
only inner work rolls 17 are shown. It will be understood outer work rolls 
23 will act against work rolls 17 so as to form a rolling nip or bite 
therebetween bearing against the stock. It will also be understood that 
the strip stock advances axially in a cylindrical path as designated at 48 
and that the work rolls 17 traverse the stock along helical lines as 
designated at a to k. An important feature is that the contact paths 
between the respectively consecutive work rolls 17 and the stock, extend 
transversely of the stock at an angle .alpha. to a plane normal to the 
axis of shaft 4. This angle is referred to herein as the bias angle of 
rolling. 
Since the stock is in the form of a longitudinal section of a cylinder and 
the work rolls 17, 23 are set at the bias angle of rolling, the nip is not 
a straight line but is curved slightly depending on the bias angle and the 
radius of the stock cylinder. Therefore, ideal contact between work rolls 
17, 23 and the stock requires work rolls 17 to be commensurately convex 
and work rolls 23 to be complementarily concave. To be precise, the curve 
is a segment of an ellipse. 
The relationship between the bias angle, the rotational rate of work rolls 
17, 23, and the rotational rate of shaft 4, are gauged so that, as the 
work rolls traverse the stock, the stock is advanced axially of cylinder 
48. Also it is important that the width (axial length) of work rolls 17, 
23 in relation to the spacing between successive pairs, and the ratio of 
axial advance to rotational rate, are such that the successive contact 
paths overlap. In this way, a complete and gapless rolling coverage of the 
strip surface is accomplished. 
In one embodiment, the successive paths are gauged so that each path 
overlaps the proceeding one by at least 50%. In this way, each roll pass 
acts 50% on fresh stock to start plastic deformation and thereby to exceed 
its elastic limit, and 50% on stock which has very shortly beforehand been 
rendered plastic by the next ahead roll pass. This makes for more 
efficient rolling in that more forward slip in the stock is accomplished 
in the second 50% or more in the axial direction of the stock for the same 
expenditure of energy. This feature applies especially to hot rolling but 
is advantageous in warm rolling (400.degree. C. to 550.degree. C.) and 
even in cold rolling. 
It is not necessary, however, to have this exact double overlap to gain 
material advantages of the invention as long as there is sufficient 
overlap to roll all parts of the stock and thereby to provide a resulting 
product which is uniformly thick and flat. While the overlap is achieved 
in the embodiments shown by the use of a single set of work rolls arranged 
on a single plane transverse to the axis of shaft 4, it will be understood 
that the overlap can be achieved by using one or more sets of work rolls 
arranged on planes axially removed upstream or downstream of the work 
rolls herein shown, without departing from the spirit of the invention. 
The bias angle of the work rolls in a suceeding plane or planes will, of 
course, have to be adjusted to account for the forward slip of the 
proceeding roll passes. 
Another way to increase the overlap is to reduce the diameter of the work 
rolls 17, 23 and employ more of them as diagramatically illustrated in 
FIGS. 5 and 6. This has the advantages of increasing the angle of bite, 
and reducing the rolling angle, the contact area, and the friction, which 
combine to give more forward slip for a given expenditure of energy. 
A way to obtain even smaller work roll diameter is shown diagramatically in 
FIGS. 7 and 8, in which backup rolls 53, 54 are employed to support small 
work rolls 52. Similar but complementary supports for work rolls to form a 
roll pass with rolls 52 are assumed and need not be described. 
FIG. 9 shows a device for bending the strip stock 49 to form the desired 
cylindrical shape. It employs a pay-off reel 55 from which the stock is 
fed through a bender comprising an upper convex roll 57 acting against a 
pair of spaced concave roll sections 59. From there the stock passes 
through the bias rolling mill and thence through a second convex, concave 
pair of rolls 58, 60 identical to rolls 57, 59, and out to a take up reel 
56. The two pairs of convex-concave rolls hold the stock in the desired 
cylindrical shape while it passes through the bias rolling mill so as to 
correspond to the orbital paths of work rolls 17, 23. 
A further embodiment of the invention is shown in FIGS. 10 and 11 in which 
two strips are fed simultaneously through the bias rolling mill. This is 
done by supporting the inner work rolls 17 on a long central shaft 63 
mounted in bearings on end supports 61, 62. A branching gear 64 is 
provided at support 61 to drive both the shaft 63 and, through a shaft 66 
and pinion 67, a planetary ring 65 carrying outer work rolls 23. In this 
case neither inner work rolls 17 nor outer work rolls 23 are driven, 
although it will be understood that a drive for them can be provided if 
desired. 
Cylindrical mandrels 69, 68, coaxial with shaft 63, are provided 
respectively to guide the strip from pay-off reels up to the bias rolling 
mill and from there to take-up reels. Mandrels 69, 68 are respectively 
driven in rotation by gears 74 and 73 acting in response to motors 72, 71. 
In order to facilitate longitudinal motion of the respective stock strips 
along mandrels 69, 68, closely spaced roller bearings 75 are distributed 
around the surfaces of both mandrels. 
As is illustrated diagramatically in FIG. 11, strips 78, 29 are fed from 
pay off reels 82, 81 around the mandrel 69 through the bias rolling mill, 
over mandrel 68 and out to take-up reels 78, 79 respectively. In this way 
the bias rolling mill acts respectively equally on the two strips 
simultaneously on opposite sides of the mill. Additional strips an be 
added in a star configuration if desired. 
Mandrel 69 is driven by motor 72 and gear 74 at a rate fixed in relation to 
the rotational rate of shaft 63 and the bias angle of work rolls 17, 23 is 
selected to provide the least friction between the strip stock and work 
rolls 17, 23. The rotational rate of mandrel 68 is, of course, faster due 
to the forward slip of the stock, and is gauged only to maintain tension. 
Since the line of the bite between work rolls 17, 23 follows a curve 
determined by the radius of mandrel 68 and the bias angle, it is 
preferable, as above indicated, to make work rolls 17 correspondingly 
convex and work rolls 23 concave, although flat rolls can be used 
especially if a large number of them is employed as in FIG. 8. 
In another embodiment shown in FIGS. 12 and 13, the external work rolls 23 
are replaced by a multipart concave backing roll 84-88, the face of which 
corresponds to the contour of the stock. The backing roll 84-88 includes 
freely pivoting roll sections 87, 88 on journals 86. The backing roll 
84-88 is supported on roller bearings mounted on base members 90 which are 
movable horizontally by means of bolt 91 and eccentric drive 94. Vertical 
adjustment is attained by means of wedge 95 driven by hydraulic ram 96 
acting to lift on the opposite side of support 90. In this way the concave 
backing roller 84-88 can be adjusted relative to the orbit of work rolls 
17 to provide the desired rolling stock profile. Backing roller 84-88 is 
supported from below by a support roller 97 which bears only against 
central portion 84 of the roller 84-88. 
A further embodiment is shown in FIG. 14 in which the stock is held under 
tension and is bent downwardly around concave roller 84-88. In this 
instance work rolls 17 are provided with correspondingly concave faces 
(depending on the respective radii and bias angles). Whereby a particular 
flat rolled strip is attained. 
In view of the various embodiments described numerous other variants will 
now be apparent to those skilled in the art. Therefore, it is not intended 
to confine the invention to the precise forms herein shown but rather to 
limit it to the terms only of the appended claims.