EP1648626B1 - Rolling device - Google Patents

Abstract

Rolling device with two work rolls supported in a rolling stand by a chock and with at least two additional rolls supported in the rolling stand by an additional chock. At least one of the work rolls and at least one of the additional rolls is adjustable for adjusting a desired roll gap relative to the other work roll or relative to the other additional roll. The work rolls have axial shifting devices for axial shifting and holding the work rolls into a desired axial position relative to the rolling stand. The work rolls are operatively connected with bending devices, by which a bending moment can act on the work rolls. The axial shifting devices are arranged and act between the rolling stand and the work roll locking mechanism. The bending devices are arranged or act between the work roll chock and the chock of the additional roll.

Description

The invention relates to a rolling device with two work rolls, which are mounted in each case by means of work roll chocks in a rolling stand, wherein the work roll chocks in the rolling stand via at least one Arbeitswalzenverriegelung are locked and unlocked, at least two other rollers, in particular two support rollers, each supported by means of roll chocks in the rolling mill are, wherein both at least one of the work rolls and at least one of the other rolls in the roll stand for setting a desired roll gap relative to the other work roll or the other further roll, in particular in the vertical direction, are adjustable, the work rolls with Axialverschiebemitteln for axial displacement are provided, with which the work rolls can be brought relative to the rolling stand in a desired axial position and held there, and wherein the work rolls with bending means in operative connection with which they can be acted upon with a bending moment.

A rolling apparatus of this kind is well known in the art. It is exemplified on the EP 0 256 408 A2 , the EP 0 256 410 A2 , the DE 38 07 628 C2 and the EP 0 340 504 B1 pointed. Rolling devices are known from these documents, in which two work rolls, which are located at a defined distance from one another, form the roll gap required for rolling and are supported on support rolls or intermediate rolls. The thus formed rolling device is thus equipped as a device with four or six rollers, wherein the individual rollers are positioned relative to each other in the vertical direction to produce the desired nip.

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

Another important embodiment of the rolling apparatus is that there are means for bending or balancing the work rolls. Through this, a bending moment can be introduced into the work rolls, which has procedural advantages, as can be seen from the aforementioned literature.

The work roll bending and displacement systems usually have 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 required plunger are either stationary in stationary blocks arranged, which leads disadvantageously to not negligible tilting moments in the axial displacement, or they are designed as with the axial displacement mitverschiebenden cartridges to the tilting moments or friction forces better to master.

The prior art rolling devices reach their limits in terms of process engineering when high roll uprights are required, as required, for example, in sheet metal or pre-lines. The plunger of the bending or Balancierzylinder must be performed over much longer lengths and thus require a lot of space to ensure the lever ratios occurring at long distances, even with fully extended ram.

Larger roller accessions with a combination of work roll bending and axial displacement realize the solutions mentioned only by accepting the mentioned disadvantages.

Short guide lengths of the plunger of the bending or Balancierzylinder be achieved again when the bending or Balancierzylinder with the system Arbeitswalzen- / Stützwalzeneinbaustück ride, so to speak "flying" between in downwardly projecting arms of the support or Zwischenwalzeneinbaustücks and laterally cantilevered tabs of the work roll chock are arranged. Here, the plunger can be arranged either in the support or Zwischenwalzeneinbaustück or in the work roll chock; its arrangement in the support or intermediate roll chock offers the advantage that the Druckmittelzuführleitungen need not be separated when changing work rolls.

Such a solution with "flying" arranged bending or Balanciersystem in combination with an axial displacement is from the DE 101 50 690 A1 known. Here it is provided that the axial displacement of the work roll is realized by a coaxially arranged on the work roll chock displacement cylinder. The displacement cylinder and the work roll set thereby form a structural unit and are installed together in the rolling stand.

In a disadvantageous way, however, it follows that it is necessary for each work roll change set to provide an axial displacement cylinder, which increases the investment costs of the rolling device.

The invention is therefore based on the object to provide a rolling device with bending and Axialverschiebesystem for the work rolls, which on the one hand permits high roll uprights, on the other hand, is characterized by a small space requirement in relation to the stand window height. Furthermore, a good guidance of the plunger of the bending or Balanciermittel should be ensured, while at the same time care should be taken that the number the operating change parts in the case of a work roll change is as low as possible. In addition, the related requirements of the axial Arbeitswalzenverriegelung and the position measurement of Axialverschiebeweges should be met.

This object is achieved in that the Axialverschiebemittel between rolling stand and work roll locking are arranged or act and the bending means between the work roll chock and the other roll chock are arranged or act.

With the combination of these measures is achieved that large roller cradles can be driven with the rolling device. Nevertheless, this results in a very compact machine concept, which requires little space. The leadership of the plunger of the bending means can be done in an optimal manner. Due to the defined design of the rolling device also a work roll change is possible in which does not need to be replaced with the Axialverschiebemittel; Thus, the number of parts to be changed in the event of a work roll change is minimized.

A first further development provides that the further roll chock, that is to say that of the support roll, has a guide in which the work roll chock is arranged so as to be displaceable relative to the further roll chock and fixable.

The axial displacement means are preferably fixedly arranged on the roll stand and have at least one linear guide on which the work roll chock is arranged to be displaceable relative to the axial displacement means in a direction transverse to the axial displacement direction, in particular displaceable in the vertical direction, and fixable.

As a preferred embodiment of the work roll chock, it is provided that this has two webs extending on both sides of the axis of the work roll, which webs can be locked with one axial displacement means each.

It is advantageous with respect to the locking of the work roll chock on the rolling mill provided that the linear guide is fixedly mounted on Axialverschiebemittel and in a direction transverse to Axialverschiebichtung, in particular in the horizontal direction, displaceable, preferably plate-shaped, bar, which together with the linear guide for the end of the web forms a receiving slot. The bolt can be in communication with actuating means, by means of which it is positionable in two layers, namely in a locking position and in an unlocking position. Further, the actuating means per Axialverschiebemittel preferably consists of two hydraulic piston-cylinder systems, which are arranged parallel to each other and can move the bolt, the piston-cylinder systems on the side facing away from the work roll chock side of the bolt attack on this.

The Axialverschiebemittel are equipped according to a development with means for preventing twisting, which prevent rotation of the axial ends of the Axialverschiebemittel.

For work roll bending or balancing is preferably provided that at least one bending means designed as a hydraulic linear actuator is arranged in a cantilever arm of the further roll chock and presses on a laterally projecting tab of the work roll chock. It can be arranged between the bending means and the laterally projecting tab of the work roll chock a sliding surface.

In the drawings, embodiments of the invention are shown.

Fig. 1

in perspektivischer Ansicht den Ausschnitt einer Walzvorrichtung gemäß einer ersten Ausführungsform mit Arbeitswalzeneinbaustück, weiterem Walzeneinbaustück und Axialverschiebemitteln;

Fig. 2

die Vorderansicht der Walzvorrichtung nach Fig. 1 in Walzenachsrichtung betrachtet;

Fig. 3

den Schnitt A-A gemäß Fig. 2;

Fig. 4

die Seitenansicht der Axialverschiebemittel von der rechten Seite gemäß Fig. 2 aus betrachtet;

Fig. 5

die Biegemittel gemäß der Einzelheit "Y" der Fig. 2 im Schnitt;

Fig. 6a

in perspektivischer Ansicht den Ausschnitt einer Walzvorrichtung gemäß einer zweiten Ausführungsform mit Arbeitswalzeneinbaustück, weiterem Walzeneinbaustück und zwei Axialverschiebemitteln, wobei das linke Axialverschiebemittel mit geöffnetem Riegel gezeigt ist (Entriegelungsstellung);

Fig. 6b

eine weitere perspektivischer Ansicht der Walzvorrichtung nach Fig. 6a, wobei das rechte Axialverschiebemittel gemäß Fig. 6a dargestellt ist und wobei dieses Axialverschiebemittel mit geschlossenem Riegel gezeigt ist (Verriegelungsstellung);

Fig. 7

die Vorderansicht der Walzvorrichtung gemäß Fig. 6a/6b in Walzenachsrichtung betrachtet;

Fig. 8

den Schnitt A-A gemäß Fig. 7;

Fig. 9

das Axialverschiebemittel gemäß der Einzelheit "Y" der Fig. 8 im Schnitt;

Fig. 10

den Schnitt B-B gemäß Fig. 9;

Fig. 11

den Schnitt C-C gemäß Fig. 7;

Fig. 12

den Schnitt D-D gemäß Fig. 10;

Fig. 13

den Schnitt E-E gemäß Fig. 7; und

Fig. 14

das Biegemittel gemäß der Einzelheit "Z" der Fig. 7 im Schnitt.

Show it:

Fig. 1

in a perspective view of the section of a rolling device according to a first embodiment with work roll chock, further roll chock and Axialverschiebemitteln;

Fig. 2

the front view of the rolling apparatus of Figure 1 viewed in Walzenachsrichtung.

Fig. 3

the section AA of FIG. 2;

Fig. 4

the side view of the Axialverschiebemittel viewed from the right side of FIG. 2;

Fig. 5

the bending means according to the detail "Y" of Figure 2 in section.

Fig. 6a

in a perspective view the detail of a rolling device according to a second embodiment with work roll chock, further roll chock and two Axialverschiebemitteln, wherein the left Axialverschiebemittel is shown with an open latch (unlocked position);

Fig. 6b

a further perspective view of the rolling device of Figure 6a, wherein the right Axialverschiebemittel is shown in FIG. 6a and wherein said axial displacement means is shown with a closed latch (locking position).

Fig. 7

the front view of the rolling device of Figure 6a / 6b viewed in Walzenachsrichtung.

Fig. 8

the section AA of FIG. 7;

Fig. 9

the Axialverschiebemittel according to the detail "Y" of Figure 8 in section.

Fig. 10

the section BB of FIG. 9;

Fig. 11

the section CC of FIG. 7;

Fig. 12

the section DD of FIG. 10;

Fig. 13

the section EE of FIG. 7; and

Fig. 14

the bending means according to the detail "Z" of Fig. 7 in section.

In Fig. 1, the section of a rolling device 1 according to a first embodiment is shown in perspective. Figures 2 to 5 show views and sections of this embodiment.

The rolling device 1 has work rolls 2, not shown in greater detail, which are mounted in work roll chocks 3, which are arranged in a rolling stand 4, which in turn is sketched only schematically. The work roll chock 3 can be locked or unlocked relative to the rolling stand 4 by means of a work roll lock 5. The work roll 2 is supported by a further roller 6 in the form of a support roller. This further roller 6 is mounted in further roll chocks 7, which are also fixed to the roll stand 4 or can be locked there.

Shown here is only provided above the Walzgutmitte work roll 2 and support roller 6; the same arrangement is symmetrically below the center of the rolling stock. It should also be noted that the rolling device 1 may also comprise further rollers, namely intermediate rollers which are arranged between the work rolls 2 and the support rollers 6.

The work rolls 2, of which in Fig. 1 - as mentioned - only the upper is indicated, should be arranged axially displaceable relative to the roll stand 4. For this Axialverschiebemittel 8 are provided, the structure will be explained later in detail. Depending Axialverschiebemittel 8 is provided on both sides of the center of the work roll 2, these means are fixed with its one axial end 23 fixed to the rolling stand 4. At the other axial end 22 of the Axialverschiebemittels 8 is the work roll latch 5, with the work roll chock 3 can be releasably fixed. The work roll chock 3 has two webs 12 and 13, which extend symmetrically from the axis of the work roll 2 from. The webs 12, 13 are received at their end 15 and 16 in the locked state in a receiving slot 17 which extends in the vertical direction and offers the possibility that the work roll chock 3 and thus the work roll 2 vertically positioned at that level in the rolling stand 4 and can be set, which corresponds to the required roll gap. The receiving slot 17 is limited on the one hand by a linear guide 11, which has the work roll latch 5, on the other hand limits him later described in detail latch 14th

In Fig. 2, the front view of the rolling device 1 - viewed in Walzenachsrichtung - can be seen. The partially sectioned view can be seen that the further roll chock 7 for the support roller 6 in its lower region has a rectangular recess and thus forms a guide 10 for the insertable into the recess work roll chock 3. Ie. the work roll 2 together with its work roll chock 3 can be positioned in the vertical direction relative to the further roll chock 7 or to the support roll 6.

To initiate a bending moment in the work roll 2 bending means 9 are provided in the form of hydraulic linear actuators in a conventional manner, which act between the work roll chock 3 and the further roll chock 7.

The structure of the Axialverschiebemittels 8 is shown in Fig. 3, where the section A-A shown in FIG. 2 can be seen. The Axialverschiebemittel 8 is arranged with its one axial end 23 fixed to the rolling mill 4. At the other axial end 22, the work roll latch 5 is arranged. The Axialverschiebemittel 8 consists of a permanently connected to the roll stand 4 fixed block 27 which projects in a cylindrical shape and forms the bottom of a sliding cylinder. On the outer diameter of this cylindrical projection a sliding sleeve 28 is slidably disposed. The sliding sleeve 28 consists of a sliding tube with guide bushes and a cubically shaped lid 29. With this cover 29 of the displacement piston 30 is coaxially fixed. The sliding tube of the sliding sleeve 28 has laterally projecting guide straps 31 which slide on a T-piece 32 connected to the fixed block 27 (see Fig. 1). Thus, means 21 for preventing twisting of the axial displacement means 8 are provided, i. H. a torsion of one axial end 22 relative to the other axial end 23 of the Axialverschiebemittels 8 is excluded.

Between the base of the T-piece 32 and one of the guide plates 31, a displacement measuring system 33 is arranged. With this it is possible to measure the current axial position of the work rolls 2.

On the outside of the lid 29 of the sliding sleeve 28, the work roll latch 5 is attached. This consists essentially of a base plate 34 (see Fig. 1 and 4), the latch 14 and actuating means 18 for the bolt 14. In the locked state, the work roll latch 5 is positively connected to the webs 12, 13 of the work roll chock 3. The Axialverschiebemittel 8, consisting of fixed block 27, sliding sleeve 28, Wegmesssystem 33 and work roll locking 5 is arranged at the inlet and outlet side substantially mirror-inverted on the roll stand 4.

Alternatively, the work roll latch 5 can be attached to the work roll set 2 by the base plate 34, the actuating means 18 for the bolt 14 and the bolt 14 itself are placed on the bearing cap of the work roll set 2 and corresponding elements for producing the positive connection to the sliding sleeve 28 of Axialverschiebemittel 8 are located.

By operating the Axialverschiebemittels 8 and due to the positive engagement between the work roll latch 5 and work roll chock 3 an axial displacement of the work roll 2 is effected. The work roll chock 3 is slidably guided in downwardly projecting arms of the corresponding further roll chock 7. The Arbeitswalzenverrieglung 5 has an axial offset to - not shown - locking of the other roller 6, so that collisions of these devices are avoided and so large roller passes are guaranteed.

In Fig. 5 can be seen how the bending means 9 are installed in the rolling device 1 in the form of hydraulically actuated linear actuators. The bending means 9 are on the inlet side and outlet side effectively between work roll chock 3 and further roll chock 7 for the support roller 6. For this purpose, the further roll chock 7 has a cantilevered arm 24 which carries the bending means 9. They rest on the work roll chock 3 on a cantilevered tab 25, which is integrally formed on the work roll chock 3. In Fig. 5, only one bending means 9 is shown; From Fig. 3 it can be seen that in the embodiment, two successively arranged bending means 9 are provided. The plunger 35 (movable part) represents a piston coaxially disposed in a corresponding bore of a cylinder 36. The fixed part of the bending means 9 consists essentially of a guide bushing with a corresponding bore, which is incorporated in the downwardly projecting arm 24, as well as a cover and various sealing and stripping elements.

In the exemplary embodiment (see Fig. 3) four bending means 9, each side two, provided, the plunger 35 is supported on the laterally projecting tab 25 of the work roll chock 3. In an axial displacement movement of the work roll 2, the tab 25 slides over the contact surface of the plunger 35. To favor this functionally, a sliding surface 26 is arranged in the contact region of the plunger 35 to the tab 25.

Alternatively, a cylinder 36 may be integrated into the laterally projecting lug 25 of the work roll chock 3. Then the plunger 35 is supported on the cantilevered arm 24 of the further roll chock 7.

FIGS. 6a, 6b to 14 show an alternative embodiment of the rolling device 1 according to the invention. The reference numerals correspond to those of the first embodiment according to FIGS. 1 to 5.

While the general operation of the second embodiment is identical to that of the first, some details are explained in more detail here.

The Axialverschiebemittel 8 are also here above and below the rolling line and on the input and on the outlet side of the operating side stand 4. Solutions for work roll displacement devices above the roll line are problematic at high altitude. Solutions for work roll shifters under the rolling line can be built conventionally or as such for large rises. The devices on the inlet and on the outlet side are substantially identical and symmetrical to each other, so that - as already in the case of the first embodiment - are described here only representative of the rolling line Axialverschiebemittel 8 with high rising.

The configuration of the Axialverschiebemittels 8 also corresponds to that of the embodiment described above. Referring to FIGS. 8 to 12, it can be seen that the lid 29 is fixed to the displacement piston 30 connected is. He stands at least in the direction of the work roll chock 3 against the local outer contour of the sliding sleeve 28 before. Between the cover 29 and arranged on the sliding sleeve 28 plate 37 of the bolt 14 is installed, which surrounds the sliding sleeve 28 and can be moved to close the locking in approximately horizontal direction transverse to the axis of the sliding sleeve 28. Between the plate 37 and the latch 14 is formed by the closing of the bolt 14 of the vertically extending receiving slot 17, in which the laterally projecting web 12, 13 of the work roll chock 3 is guided. For this purpose, a recess is incorporated in the plate 37 or between plate 37 and bolt 14, a spacer is inserted with a comparable recess.

The vertically extending receiving slot 17 receives the axial displacement forces that must be passed through the laterally projecting webs 12, 13 of the work roll chock 3, while allowing large relative movements in the vertical direction. This allows a large roll rise as a result. The contact surfaces of the webs 12, 13 on the plate 37 and the bolt 14 thereby form two abutments for the webs 12, 13 of the work roll chock 3. The vertically extending receiving slot 17 is opened to the work roll removal by the bolt 14 is withdrawn. Then the work roll set can be pulled out to the operating side.

The plate 37 on the sliding sleeve 28 has two main functions. On the one hand, it serves as one of the two abutments for the webs 12, 13. On the other hand, it is part of means 21 for preventing a rotation of the Axialverschiebemittel. 8

For the means 21 for preventing twisting, two embodiments are preferred:

After a possibility, a component is provided, which is mounted outside the central axis, the sliding sleeve 28 fixed to the stand. This sticks out in one Opening of the plate 37 on the sliding sleeve 28 into it, or a component attached to the plate 37 of the sliding sleeve 28 protrudes into a stationary opening. The anti-rotation device must have a guide of sufficient length, so that a rotation between the two axial ends 22 and 23 of the Axialverschiebemittels 8 is prevented for the entire maximum displacement.

Alternatively, the sliding sleeve 28 and the displacement piston 30 may be formed so that they do not slide on each other with cylindrical surfaces, but with such surfaces that prevent rotation to each other.

The fulfillment of the two main functions of the plate 37 on the sliding sleeve 28, namely to be both abutment and part of the rotation, can be achieved by two separate, worked on the sliding sleeve 28 or welded plates. The combination of the two functions by means of the plate is easy to manufacture and therefore advantageous.

The detailed embodiment of the work roll latch 5 by means of the bolt 14 is shown in Figures 10 and 12. The latch 14 may have an O- or U-shaped recess (in Fig. 10, the recess is O-shaped). The latch 14 is not arranged in front of the head 29, but it surrounds the sliding sleeve 28. The recess in the bolt 14 is so large that the bolt for mounting in training in the O-shape axially or when executed in U-shape axially or radially can be pushed onto the sliding sleeve 28. The U-shape is as a closed mold, the stiffer design of the bolt 14. The U-shape has the advantage that the cover 29 can be permanently connected to the sliding sleeve 28 or that the cover 29 and the sliding sleeve 28 may consist of one piece ,

When executed in U-shape, the latch 14 is open on the side of the sliding sleeve 28 which is opposite to the work roll chock 3. Because the latch 14 surrounds the sliding sleeve 28, the web 12, 13 of the Work roll chock 3 - measured from the middle of the work roll bearings - shorter than if the bar 14 were located in front of the head 29. Thus, the lever arm between the work roll bearing and the guide, which is formed by the two abutment bar 14 and plate 37 decreases. A smaller lever arm has the consequence that the frictional forces in the guide exercise only relatively small additional moments on the work roll bearings. The work roll bearing thus has a longer life.

The closing and opening of the receiving slot 17 for the laterally projecting webs 12, 13 of the work roll chock 3 is accomplished by a horizontal or approximately horizontal movement of the bolt 14, the locking stroke. Therefore, the recess in the bolt 14 in the direction of movement (horizontal) at least by the locking stroke is greater than is required for assembly.

The movement of the bolt 14 is effected by actuating means 18. This is z. B. one or more actuators in the form of piston-cylinder systems 19, 20 (hydraulic cylinder with continuous piston rods). The piston-cylinder systems 19, 20 expediently put on the side facing away from the work roll chock 3 of the bolt 14. It is particularly space-saving, if two piston-cylinder systems 19, 20 find space at the top and bottom in recesses of the bolt 14 and on the plate 37 or on the lid 29 are attached. This embodiment is illustrated in FIG. 10; Fig. 12 shows a piston-cylinder system 19, 20 in detail.

For reasons of space, it makes sense to provide in the latch 14 still another recess, namely to let pass elements of the means 21 for preventing twisting and to avoid a collision with these.

The bolt 14 has three recesses in the embodiment of FIG. 10, a large for the sliding sleeve 28, two smaller for the piston-cylinder systems 19, 20 and another to avoid collision with the means 21 for preventing the rotation of the Axialverschiebemittels 8.

The latch 14 is held by the piston-cylinder systems 19, 20 in the open or closed position. But it must also be secured against rotation against an axis parallel or identical to the central axis of the sliding sleeve 28. As can be seen in the embodiment of FIG. 10, for this purpose, above and below the cover of the sliding sleeve 28 or above and below the plate of the sliding sleeve 28 strips 38, 39 are mounted, which prevent such rotation. The strips 38, 39 can also form a common component with the plate 37 or with the plate 37 and the displacement sleeve 28. An alternative embodiment of the rotation is obtained when 29 horizontal grooves are formed in the plate 37 or in the lid, in which raised strips of the bolt 14 are guided. Furthermore, it is possible to mold the grooves in the bar 14 and to attach the raised strips on the plate 37 or on the lid 29. Variants in which the rotation against the plate 37 are mounted, have the advantage that the lid 29 is then not additionally claimed to twist.

The cover 29 of the sliding sleeve 28 is shaped so that two functions can be fulfilled: First, the sliding piston 30 is coaxially fixedly connected to the cover 29 (see Fig. 8), so that the piston above the cover the sliding sleeve 28 including attachments and thus also the vertically extending receiving slot 17 for the work roll chock 3 can move axially. On the other hand, the lid 29 forms an abutment for the bolt 14, especially with its part projecting towards the work roll chock 3. The bolt 14 can be supported there and also above and below the sliding sleeve 28 on the cover 29 or surround the sliding sleeve 28. In addition, the lid 29 may have a recess to allow elements of the rotation to pass and thus to prevent a collision with them. To the To make lid 29 shorter, it is also possible to install an intermediate piece between the lid and latch.

Either in the lid 29 or in this intermediate piece can also be a fuse against rotation of the same on the sliding sleeve 28 are provided. One possibility for this is to provide on the sliding sleeve 28 one or more flat surfaces which do not point in the direction of the axis of the sliding piston 30 and to provide corresponding counter surfaces on the cover 29 or in the above intermediate piece. The lid 29 must then be secured against rotation relative to the sliding sleeve 28 in any case, when the bolt 14 is secured against rotation to the cover 29.

The measurement of the Axialverschiebewegs is made possible by a out of or within the Axialverschiebemittel 8 unit. The arrangement of the transmitter within the printing system is avoided as possible due to risk inclination during maintenance. The displacement measuring system 33 can be formed as an external unit or as an internal unit. In the case of an external unit, protection against harmful environmental influences is required, which can be achieved by a sealed, hydraulic cylinder-like system. A type of piston fixedly mounted on the stator slides through a cylinder tube fixed to the moving parts of the axial displacement. Coaxially with the cylinder tube, the transmitter moves and generates the corresponding path signal. With appropriate sealing and stripping elements a sufficient protection of the system is achieved. In the case of an internal unit, the position sensor is - seen from the end face of the moving parts - inserted into the sliding sleeve. The required encapsulation is produced by the displacement system itself. A suitably sealed housing protects the electronic part of the position sensor.

In the embodiment according to FIG. 9, a position transmitter 40 for controlling the displacement stroke of the displacement sleeve 28 is arranged in the axial displacement means 8.

An arrangement of a position sensor rod 41 inside - but still outside the pressure chamber - is advantageous because this element is then protected without additional encapsulation against environmental influences. The position sensor 40 is mounted on the lid 29, the position sensor rod 41 is passed through a bore in the lid 29 and immersed in a bore in an inner lid 42 a. The inner lid 42 is part of the rolling stand 4 fixed part of the Axialverschiebemittels 8, so that the measurement of the relative displacement of the lid 29 to the roll stand 4 is possible.

In general, it is possible to combine the described axial displacement means 8 with different variants of bending means 9:

As is apparent from Figs. 13 and 14, the bending means 9 are in downwardly projecting arms 24 of the further roll chock 7 of the upper support roll set. The movable plunger 35 is essentially a piston, which is supported on the laterally projecting tab 25 of the work roll chock 3. The design of the bending means 9 thus corresponds substantially to that shown in Fig. 5.

With several plungers 35 it is possible to regulate the pressures in the individual cylinder chambers so that the work roll bearing is loaded as little as possible off-center ("pressure compensator").

Alternatively, the plunger 35 may be housed in the laterally projecting tabs 25 of the work roll chock 3. Here, the plunger 35 would be supported on the downwardly projecting arms 24 of the further roll chock 7. In this case, the work roll bearing would only be loaded centrally.

The lower bending means 9 may be in fixed blocks on the stand. Alternatively, they can also in upwardly projecting arms of the further roll chock of the lower support or intermediate roll set or be housed in laterally projecting tabs of the work roll chock.

With the embodiment according to the invention, a "flying" arrangement of the bending means 9 can thus be achieved, whereby the tilting moments which occur in the case of the axial displacement of the work rolls can be optimally accommodated with the proposed structural design. The design of the rolling device excludes collisions of the various components with each other, even when large roll outruns are driven. Nevertheless, no large space is needed in the rolling stand.

LIST OF REFERENCE NUMBERS

1

rolling device

2

Stripper

3

Work roll chock

4

rolling mill

5

Work roll locking

6

further roller (back-up roller)

7

another roll chock (for back-up roll)

8th

axial displacement

9

bending means

10

guide

11

linear guide

12

web

13

web

14

bars

15

End of the jetty

16

End of the jetty

17

receiving slot

18

Actuation means for the bolt

19

Piston-cylinder system

20

Piston-cylinder system

21

Means for preventing twisting

22

axial end of the axial displacement means

23

axial end of the axial displacement means

24

projecting arm of the further roll chock

25

projecting tab of the work roll chock

26

sliding surface

27

fixed block

28

sliding sleeve

29

cover

30

displacement piston

31

guide tab

32

Tee

33

displacement measuring system

34

baseplate

35

tappet

36

cylinder

37

plate

38

strip

39

strip

40

locator

41

Position sensor rod

42

Innendeckel

Claims (11)

1. Roll device (1) with two working rolls (2) which are each mounted by means of working roll chocks (3) in a roll stand (4), wherein the working roll chocks (3) are lockable and unlockable in the roll stand (4) by way of at least one working roll locking means (5), at least two further rolls (6), particularly two backing rolls, which are each mounted by means of further roll chocks (7) in the roll stand (4), wherein not only at least one of the working rolls (2), but also at least one of the further rolls (6) are adjustable, particularly in vertical direction, for setting a desired rolling gap relative to the other working roll (2) or other further roll (6) in the roll stand (4), wherein the working rolls (2) are provided with axial displacing means (8) for the relative displacement, by which the working rolls (2) are mounted in a desired axial position relative to the roll stand (4) and can be held there and wherein the working rolls (2) are operatively connected with bending means (9) by which they can be acted on by a bending moment, characterised in that the axial displacing means (8) are arranged or act between roll stand (4) and working roll locking means (5) and the bending means (9) are arranged or act between the working roll chock (3) and the further roll chock (7).
2. Roll device according to claim 1, characterised in that the further roll chock (7) has a guide (10) in which the working roll chock (3) is arranged to be displaceable relative to the further roll chock (7) and to be fixable.
3. Roll device according to claim 1 or 2, characterised in that the axial displacing means (8) are fixedly arranged at the roll stand (4) and have at least one linear guide (11), on which the working roll chock (3) is arranged to be displaceable, particularly displaceable in vertical direction, relative to the axial displacing means (8) in a direction transverse to the axial displacement direction and to be fixable.
4. Roll device according to one of claims 1 to 3, characterised in that the working roll chock (3) comprises two webs (12, 13) which extend on either side of the axis of the working roll (2) and are each lockable by a respective axial displacing means (8).
5. Roll device according to claim 3 and 4, characterised in that the linear guide (11) is fixedly arranged at the axial displacing means (8) and comprises a lock (14), which is displaceable in a direction, particularly in horizontal direction, transversely to the axial displacement direction and is preferably of plate-shaped construction and which together with the linear guide (11) forms a receiving slot (17) for the end (15, 16) of the web (12, . 13).
6. Roll device according to claim 5, characterised in that the lock (14) engages around a displacing sleeve (28).
7. Roll device according to claim 5 or 6, characterised in that the lock (14) is connected with actuating means (18) by means of which it is positionable in two positions, namely in a locking position and in an unlocking position.
8. Roll device according to claim 7, characterised in that the actuating means (18) per axial displacing means (8) consists of two hydraulic piston-cylinder systems (19, 20) which are arranged parallel to one another and can move the lock (14), wherein the piston-cylinder systems (19, 20) at the side of the lock (14) remote from the working roll chock (3) engage this.
9. Roll device according to one of claims 1 to 8, characterised in that the axial displacing means (8) are equipped with means (21) for preventing twisting, which means prevent twisting of the axial ends (22, 23) of the axial displacing means (8).
10. Roll device according to one of claims 1 to 9, characterised in that at least one bending means (9), which is constructed as a hydraulic linear actuator, is arranged in a projecting arm (24) of the further roll chock (7) and presses on a laterally projecting strap (25) of the working roll chock (3).
11. Roll device according to claim 10, characterised in that a slide surface (26) is arranged between the bending means (9) and the laterally projecting strap (25) of the working roll chock (3).

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