EP2139623B1 - Roller device - Google Patents

Abstract

The invention relates to a roller device (1) comprising at least two rollers, each roller being mounted by means of roll chocks (2) in a roll stand (3), wherein the rollers are provided with axial displacement means (4) for axial displacement in a displacement direction (x), by means of which the rollers may be placed and held in a desired position relative to the roll stand (3), and wherein the rollers are in an operative connection with bending means (5), by means of which a bending momentum may be exerted on said rollers. In order to keep the losses of bending force as a result of the weight of the axial displacement means as low as possible, the invention provides for the axial displacement means (4) to be disposed with a first operative end (6) directly or indirectly on the roll stand (3) by means of an articulated connection (9) on the roll chock (2).

Description

The invention relates to a rolling device with at least two rollers, which are each mounted by means of roll chocks in a rolling mill, wherein the rollers are provided with Axialverschiebemitteln for axial displacement in a displacement direction with which the rollers are brought relative to the rolling mill in a desired position and held there and wherein the rollers are in operative connection with bending means, with which they can be subjected to a bending moment.

A rolling device of this kind is for example from the WO 2005/011884 A1 known, in which two work rolls are located at a defined distance from one another form the rolling gap required for rolling, wherein the work rolls can be supported on support rolls or intermediate rolls. A rolling device formed in this way can therefore be equipped with four or six rollers, wherein the individual rollers can be positioned relative to one another in the vertical direction to produce the desired roll gap.

The work rolls are arranged axially displaceable, whereby it is possible to achieve an influence of the strip profile in strip lines by a variable roll gap profile. Also in Vorstrassen the procedural possibility of axial displacement of the work rolls significance, on the one hand for the purpose of targeted Bandprofilbeeinflussung, on the other hand to extend the roll travel through targeted wear distribution.

Another important embodiment of the rolling device, as in the WO 2005/011884 A1 is described, that means for bending or balancing the work rolls are present. Through this, a bending moment can be introduced into the work rolls, which has procedural advantages.

The work roll bending and shifting systems are housed in stationary blocks in which the adjusting means required for bending and balancing or axial displacement are arranged. These offer the advantage of fixed pressure medium supply lines, which do not have to be separated during the work roll change. To realize the bending and balancing the necessary plunger are either arranged in stationary blocks, which leads disadvantageously to not negligible tilting moments in the axial displacement, or they are designed as with the axial displacement mitverschiebenden cartridges to better control the tilting moments or friction forces to be able to.

Other solutions of this kind as they are used for WO 2005/011884 A1 are similar, are in the EP 0 326 805 B1 , in the DE 24 40 495 A1 , in the DE 36 03 693 A1 , in the WO 98/26883 A1 and in the DE 38 07 628 C2 described.

A disadvantage of all previously known solutions that, when the bending and axial displacement device is used in a mechanically combined unit, wherein the displacement device is designed as a cantilever arm on the guide blocks of the bending device, a torque due to the dead weight of the displacement device occurs, from the perpendicular standing guides of the bending device must be included. This creates a frictional force in the guides of the bending device, which negatively influences the control behavior of the bending device.

The negative influence of this frictional force increases with decreasing height of the vertical guides of the bending device. The height of the guides is directly related to the roll diameter, ie for small roll diameters, the negative influence of the resulting frictional force is greater than for large roll diameters.

The invention is therefore based on the object, a rolling device of the type mentioned in such a way that eliminates the disadvantages mentioned or at least reduced, d. H. in particular that the intrinsic weight-related influences of the axial displacement means are reduced with regard to the frictional forces exerted on the guides of the bending means.

This object is achieved in that the Axialverschiebemittel are arranged with a first operative end on the rolling stand directly or indirectly by means of an articulated connection and are arranged with a second operative end by means of a hinged connection on the roll chock.

The axial displacement means are preferably arranged indirectly via a connecting frame on the rolling stand. They can be arranged with their second operative end in a locking block, which is arranged in the direction of displacement of the Axialverschiebemittel movable in or on the bending means. In this case, a further development provides that an effective in the direction of displacement of the Axialverschiebemittel positive connection between the locking block and roll chock is made by the articulated connection in the form of a locking bolt. In the roll chock, at least one recess congruent with the shape of the locking bolt can be incorporated for this purpose. Furthermore, the locking block may be mounted in or on the bending means at a location spaced from the first operative end by means of a guide. The guide preferably has a link in which a bolt connected to the bending means is arranged. The backdrop, in turn, is advantageously designed as extending in the direction of displacement of Axialverschiebemittel extending groove-shaped recess.

The Axialverschiebemittel preferably have a hydraulic piston-cylinder system.

The first and / or second action end of the axial displacement means may be slidably disposed on the Axialverschiebemitteln and / or on the guide. This makes it possible in a simple manner to be able to adjust the pivot points with additional roll displacement in the horizontal rolling direction.

By virtue of the proposed measure, the generation of a torque in the guides of the bending device is minimized independently of the roll diameter or of the available overall height. As a result, the above adverse consequences are reduced. In particular, the control behavior of the bending device is improved.

So there is a system-related minimization of bending force losses due to internal friction.

Fig. 1

einen Ausschnitt einer Walzvorrichtung in der Draufsicht; und

Fig. 2

den Schnitt A-A gemäß Fig. 1, wobei die Biegemittel nicht dargestellt sind.

In the drawing, an embodiment of the invention is shown.
Show it:

Fig. 1

a section of a rolling device in plan view; and

Fig. 2

the section AA according to Fig. 1 , wherein the bending means are not shown.

In the figures, a rolling device 1 - partially only partially - shown, which is constructed in a conventional manner. In that regard, on the WO 2005/011884 A1 Reference is made, where closer Innformen to such a rolling device are included.

Two work rolls, not shown, are held by roll chocks 2, of which in Fig. 1 one is recognizable. The roll chocks 2 are mounted in a roll stand (or roll stand) 3. In this case, however, provisions are made that the work rolls axially displaced both in a direction of displacement x and applied to a bending moment can be. For this purpose, known Axialverschiebemittel 4 and bending means 5 are provided.

The Axialverschiebemittel 4 have to force a hydraulic piston-cylinder system 16. The Axialverschiebemittel 4 have two effect ends 6 and 8, between which they can generate their displacement force in the direction x. The first operative end 6 located on the right in the figures is fixed by means of an articulated connection 7 in the form of a bolt to a connecting frame 10, which in turn is fastened to the rolling stand 3. At one in the figures further to the left second operative end 8, the Axialverschiebemittel 4 are also hinged articulated, by means of an articulated connection 9 in the form of a locking bolt.

The locking pin 9 is mounted in a locking block 11 so that upon displacement of the Axialverschiebemittel 4, the locking block 11 is moved with. The locking pin 9 passes through the locking block 11 (s. Fig. 1 ) and engages in a recess 12 which is incorporated in the roll chock 2. This has the consequence that upon a displacement of the axial displacement means 4, the movement is transmitted via the locking block 11 to the roll chock 2 and thus to the roll; the roller is then displaced axially in the displacement direction x.

As it is best in Fig. 2 can be seen, a recess 17 is incorporated in the bending means 5, in which the Verriegefungsblock has 11 place and is movable in the displacement direction x. In the recess 17, a guide 13 is accommodated, which is mounted with its one end (left in the figures) by means of a link 14 and a bolt 15 which is fixed in the bending means 5. The scenery 14 is - as in Fig. 2 can be seen - designed as a in the direction of displacement x extending groove. The bolt 15 supports the guide 13 at its one end.

The bending means 5 move in vertical direction V on vertical guides 18 up and down (s. Fig. 1 ), only a partial weight of the Axialverschiebemittel 4 loads on them and only with a relatively short lever arm r (s. Fig. 1 ). The weight of the Axialverschiebemittel 4 can thus cause only a very small torque in the vertical guides 18 of the bending device 5, which is also ensured by the fact that the effective weight is balanced by the bearing in the pivot.

The most important functionalities can thus be summarized as follows: As can be seen, the bending means 5 and the axial displacement means 4 are arranged separately from one another. The bending means remain - compared with previously known solutions - largely unchanged in their function and mechanical design of the components. In extension of the piston-cylinder system 16, the guides 13 are mounted in which the locking block 11 is running. About the locking block 11, the tool chocks 2 are coupled to the Axialverschiebemitteln 4. The guides 13 are based on the running in the gate 14 bolt 15 on the bending means 5 from.

In order to use the device in addition to rolling in the horizontally displaceable rollers, a corresponding displacement of the pivot fulcrums can be provided.

LIST OF REFERENCE NUMBERS

1

rolling device

2

Roll chock

3

Roll stand (roll stand)

4

axial displacement

5

bending means

6

first operative

7

articulated connection

8th

second operative

9

articulated connection (locking bolt)

10

connecting frame

11

locking block

12

recess

13

guide

14

scenery

15

bolt

16

hydraulic piston-cylinder system

17

Recess in the bending means

18

vertical guides

x

displacement direction

V

vertical

r

lever arm

Claims (10)

1. Rolling device (1) comprising at least two rolls, which are each mounted by means of roll chocks (2) in a roll stand (3),
   wherein the rolls are provided with axial displacing means (4) for axial displacement in a displacement direction (x), by which the rolls can be brought into a desired position relative to the roll stand (3) and held there, and
   wherein the rolls are operatively connected with bending means (5) by which they can be subjected to a bending moment,
   characterised in that
   the axial displacing means (4) are arranged by a first functional end (6) at the roll stand (3) directly or indirectly by means of an articulated connection (7) and are arranged at the roll chock (2) by a second functional end (8) by means of an articulated connection (9).
2. Rolling device according to claim 1, characterised in that the axial displacing means (4) are arranged at the roll stand (3) indirectly by way of a connecting frame (10).
3. Rolling device according to claim 1 or 2, characterised in that the axial displacing means (4) are arranged by the second functional end (8) thereof in a locking block (11), which is arranged in or at the bending means (5) to be movable in the displacement direction (x) of the axial displacing means (4).
4. Rolling device according to claim 3, characterised in that a mechanically positive connection, which is effective in displacement direction (x) of the axial displacing means (4), between locking block (11) and roll chock (2) is formed by the articulated connection (9) in the form of a locking pin.
5. Rolling device according to claim 4, characterised in that at least one recess (12) congruent with the shape of the locking pin (9) is formed in the roll chock (2).
6. Rolling device according to any one of claims 3 to 5, characterised in that the locking block (11) is mounted in or at the bending means (5) at a location, which is spaced from the first functional end (6), by means of a guide (13).
7. Rolling device according to claim 6, characterised in that the guide (13) comprises a gate guide (14) in which a pin (15) connecting with the bending means (5) is arranged.
8. Rolling device according to claim 7, characterised in that the gate guide (14) is formed as a groove-shaped recess extending in displacement direction (x) of the axial displacing means (4).
9. Rolling device according to any one of the claims 1 to 8, characterised in that the axial displacing means (4) comprises a hydraulic piston-cylinder system (16).
10. Rolling device according to any one of claims 1 to 9, characterised in that the first and/or second functional end (6, 8) of the axial displacing means (4) is or are arranged at the axial displacing means (4) and/or at the guide (13) to be displaceable.

Images