US 3910090 A
A metal working machine having a two-high rolling mill in which two horizontally spaced frames support shafts for eccentrically mounting the roll housings. The roll housings are journalled in the frames. The shafts protrude through the frames and at a common end each shaft receives a lever which in turn is connected with articulation to a linkage system which can alter the distance between the roll housings and also respond to a piston drive to provide roll overload relief.
Claims available in
Description (OCR text may contain errors)
United States Patent [191 Lorenz May 15, 1974 TWO-HIGH ROLL STAND WITH ROLL ADJUSTING AND OVERLOAD PREVENTION MECHANISM  Inventor: Horst Lorenz, Solingen, Germany  Assignee: TH. Kieserling & Albrecht,
Solingen, Germany 22 Filed: May 15, 1974 21 Appl. No.: 469,970
 Foreign Application Priority Data May 23, 1973 Germany 2326140  US. Cl 72/245; 72/248  Int. Cl. B21B 31/26; B21B 31/24  Field of Search 72/245, 244, 237, 248,
 References Cited UNITED STATES PATENTS 3,172,314 3/1965 Morgan et a1. 72/237 Wilson et a1 72/235 Bergstrom et a1. 72/246 Primary Examiner-Milton S. Mehr Attorney, Agent, or FirmEdward E. Sachs  ABSTRACT A metal working'machine having a two-high rolling mill in which two horizontally spaced frames support shafts for eccentrically mounting the roll housings. The roll housings are journalled in the frames. The shafts protrude through the frames and at a common end each shaft receives a lever which in turn is connected with articulation to a linkage system which can alter the distance between the roll housings and also respond to a piston drive to provide roll overload relief.
7 Claims, 4 Drawing Figures US. Patent Oct. 7,1975 Sheet 1 of 2 3,910,090
US. Patent Oct. 7,1975 Sheet 2 of2 3,910,090
ll nwlllrl l ll IL FIG.3
TWO-HIGH ROLL STAND WITH ROLL ADJUSTING AND OVERLOAD PREVENTION MECHANISM The invention relates generally to a metal working machine and, more particularly, to a two-high rolling mill or stand having a mechanism for radially adjusting the the distance between the rolls and for preventing an overload thereof.
In the prior art a two-high rolling mill or stand is already known in which the bearings for each roll shaft are arranged in eccentrically designed housings mounted rotatably in the frames of the stand. The housings are provided externally with meshing gears with the gears of one roll engaging two pinions mounted on a shaft, so that when the shaft is rotated the rolls can be radially adjusted. For instance see German Technical Journal Stahl und Eisen, Vol. 7, of Mar. 30, 1972.
This type of construction has a number of disadvantages. It does, for instance, make roll changing fairly difficult. Also, it prevents the rolls from yielding in the event of an overload, since the eccentricity of the housings must be near the top or bottom dead centers; otherwise the rolls would automatically rise under the force of rolling.
Another disadvantage resides in that due to sliding friction considerable adjusting forces are necessary to adjust the rolls radially under load.
It is therefore the primary object of the present invention to provide a metal working machine which includes a two-high roll stand in which the permissible rolling force can be very accurately adjusted.
It is a further object of the present invention to provide a two-high roll stand in which all major elements thereof are securely protected against overload.
It is a still further object of the invention to provide a two-high roll stand or mill in which the position of the rolls can also be readily adjusted when under load.
An aspect of the present invention resides in providing a two-high rolling mill or stand having horizontally spaced roll stand frames with vertically spaced shafts interposed therebetween for linking the frames. Eccentric journal means are formed on each of the shafts with a lever secured at one common end to each shaft. The lever is constructed and arranged to establish a longitudinal axis whose location coincides with the main axis of the corresponding eccentric journal means. These axes define a substantially right angle with an imaginary line defined by the axis of rotation of each shaft. Articulately connected to each lever is a piston drive arrangement which includes a movable piston responsive to predetermined overload conditions.
A further aspect of the present invention resides in providing a metal working machine having an apparatus for radially adjusting the rolls of a two-high roll stand and for precluding an overload thereof in which the eccentric journals are arranged on the shafts connecting the frame members of the roll stand. The shafts receive at their free ends levers whose longitudinal axis coincides with the main axis of the eccentric members, whereby these axes and an imaginary line connecting the axes of rotation of the shafts define a substantially right angle. The levers are articulated to a threaded shaft constructed as a piston drive, the piston thereof being adapted to move, in the event of an overload,
against the action of an adjustable force such as fluid pressure means or suitable springs.
Another advantage of the construction and arrangement in which the housings carry the roll shafts resides in that it facilitates the use of a rapid roll changing device, for example as described in my co-pending U.S. patent application, Ser. No. 467,632, filed May 7, 1974, (based on a priority application in Germany, Ser. No. P 23 23 768.).
Another aspect of the present invention resides in providing a metal working machine having an apparatus of the character aforedescribed and in which, in order to adjust the rolls radially, the two portions of the threaded shaft are provided with clockwise and counter-clockwise threads, each of which engage a collar pivotably secured to the levers. One of these threaded portions is provided with a shoulder bearing on each axial face against a stationary abutment. The housings are retained in a vertical position by means of journals formed thereon and mounted within one of the frames. The rolls may thus be radially adjusted by rotating the threaded shaft clockwise or counter-clockwise. Any oscillation of the housings about the eccentrics is prevented.
For a better understanding of the present invention, together with other and further objects thereof, refer ence is had to the following description taken in connection with the accompanying drawings, and its scope will be pointed out in the appended claims.
In the drawings:
FIG. 1 is a side elevational view of the roll-stand shown partly in section;
FIG. 2 is a sectional view taken along line II-II of FIG. 1, showing the threaded shaft connecting the levers and providing a piston drive;
FIG. 3 is a sectional view taken along line IIIIII of FIG. 2; and
FIG. 4 is a sectional view taken along line IV-IV of FIG. 1, showing additional details of the present invention.
Referring now to the drawings there is shown part of a metal working machine having horizontally spaced side frame members 1 and 2 linked together through rotatably arranged and vertically spaced shafts 3 and 4. Each shaft is provided with two, axially spaced, eccentrically arranged journal surfaces or cams 5 and 6. Mounted about each journal (5,6) is a rolling contact bearing, see 7 and 8, whose outer races are carried in cross member roll housing 9 interposed between frame members 1 and 2, and surrounding roller shaft 3. While not specifically shown, shaft 4 as noted, is similarly provided with journals 5,6 and bearings 7,8 whose outer races are supported in cross-member housing 10 which surrounds shaft 4 and extends also between frames 1 and 2 in parallel to housing 9.
One common end of shafts 3 and 4 extends beyond the housing 9,10 and frames 1,2 and protrudes therethrough to carry or mount levers 11 and 12, respectively, which are secured to the shafts by means of wedges l3 and 14, respectively, see FIG. 2.
The longitudinal axis 15 of each lever 11,12 coincides with the main axis of eccentric journal surfaces 5 and 6. For clarity of illustration the eccentric journal 5 is shown in dotted lines in FIG. 2. Each axis 15 defines a substantially right angle with an imaginary line 15a defined by the axis of rotation of shaft 3(4).
The levers l1 and 12 are linked together by a threaded shaft or spindle which forms a piston drive and includes a shaft-piston 16 and a hollow cylinder 17 which receives one portion of shaft-piston 16. The opposite end of shaft-piston 16 is threaded, see 16a, and protrudes through and is in engagement with internally threaded collar 18. From the cylinder 17 extends a threaded shaft extension 17a which is connected to a cardan shaft 31 and in engagement with the internal threads of block 19. One of the threaded extensions (16a, 1 7a) has a left hand and the other a right hand external thread. In turn, the collars 19,18 are pivotably mounted about lever l1, 12 by means of pins 20,21 respectively. The cylinder 17 is formed with a radial enlargement 17b abutting at each axial face thereof a stationary element 22 which prohibits axial movement of member 17, 17a and 17b. The key-slot arrangement between piston-shaft l6 and the extension of the cylinder 17 permits axial movement of piston-shaft 16 but precludes relative rotation between threaded extensions 16a, l7a which thus always rotate in unison.
When fluid pressure is supplied through bore 23 into cylinder 17, piston portion 16b is in operative position as shown in the drawing. The fluid pressure is supplied by a pump 25 driven by a motor 24, through check valve 26 and line 27a. Connected to line 27a is a hydraulic accumulator 27. The fluid pressure is adjusted by pressure-regulating valve 28 to correspond to maximum allowable rolling forces.
The housings 9,10 are retained in a vertical plane by means of journals 29 mounted in elongated openings 30 provided in frame 2, to prevent oscillation.
The method of operation is as follows: rotation of members 16a,l7a, clockwise or counter-clockwise, by means of cardan shaft 31 and a motor, not shown, pivots levers 11,12 until the rolls have assumed their required operating positions. As long as pressure is applied to piston face 161), shaft-piston 16, lever 12, and therefore bottom roll 32 are held in the position to which they have been adjusted. When the rolling force exceeds its permissible value, pressure-regulating valve 28 opens. This relieves the pressure in cylinder 17, and the fluid pressure can flow back to the tank. This enables shaft 16 to move in the direction of the arrow shown in FIG. 2, and pivots lever 12 in such a manner that the vertical distance between bottom roll 32 and top roll 33 is increased.
As a modification of the invention only one roll is radially adjustable in relation to the other. In this case, for instance, the top roll could be stationary, in which case cardan shaft 31 would be in direct communication with cylinder 17. This eliminates lever 1 l and collar 19.
While there have been described what are at present considered to be the preferred embodiments of this invention, it will be obvious to those skilled in the art that various changes and modifications may be made therein without departing from the invention, and it is aimed, therefore, in the appended claims to cover all such changes and modifications as fall within the true spirit and scope of the invention.
What is claimed is:
1. In a metalworking machine having a two-high roll stand including a mechanism for radially adjusting and for preventing an overload of the rolls, comprising:
horizontally spaced roll stand frames;
two vertically spaced shafts interposed between and linking said frames;
eccentric journal means formed oneach said shafts;
a roll housing eccentrically mounted about each shaft;
a radial roll adjustment linkage system having a lever secured at one common end to each of said shafts, each lever being constructed and arranged to establish a longitudinal axis whose location coincides with the main axis of the corresponding eccentric journal means, said axes defining a substantially right angle with an imaginary line defined by the axis of rotation of said shaft; linkage shaft means articulately connecting to each said lever for moving each lever to alter the radial distance between the roll housings;
hydraulic piston drive means including a piston formed on said linkage shaft means and responsive to predetermined roll overload conditions to act upon part of said linkage system;
and rotary drive means connecting to said lever and linkage system for controlling the rotary movement of said linkage system.
2. In a metal working machine according to claim 1, wherein said linkage shaft means has a threaded extension at two opposite ends;
a collar threadedly mounted about each threaded extension pivotably secured to each lever.
3. In a metal working machine according to claim 2, wherein one of said threaded extensions has a left hand thread and the other a right hand thread.
4. In a metal working machine according to claim 1, wherein said shaft means includes a radial enlargement; and stationary abutment in axial engagement with both axial faces of said radial enlargement.
5. In a metal working machine according to claim 1, and journal means on said housing and mounted in one said frames maintaining said housing in a vertical plane.
6. In a metal working machine according to claim 1, wherein the linkage shaft means of said linkage system comprises two axially relatively movable but rotatably rigidly connected shaft extensions; cylinder means receiving one said shaft extension for axial movement therein; the other said shaft extension being rigidly connected to said cylinder means.
7. In a metal working machine according to claim 6, wherein said other shaft extension is provided with a radial enlargement; and abutment means in engagement with said radial enlargement.