EP1648626A1

EP1648626A1 - Rolling device

Info

Publication number: EP1648626A1
Application number: EP04763370A
Authority: EP
Inventors: Bernd Zieser; Achim Klein; Florian Lindner; Stefan Wendt
Original assignee: SMS Demag AG
Current assignee: SMS Siemag AG
Priority date: 2003-07-30
Filing date: 2004-07-21
Publication date: 2006-04-26
Anticipated expiration: 2024-07-21
Also published as: RU2346771C2; ZA200509783B; KR101109451B1; AU2004261384B2; JP4564008B2; CA2533693C; EP1648626B1; ES2293315T3; MXPA06001150A; KR20060054205A; RU2006106200A; JP2007500079A; US7299673B2; UA83056C2; AU2004261384A1; CN1832817A; CA2533693A1; TWI314880B; DE502004005516D1; TW200512051A

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

rolling device

The invention relates to a rolling device with two work rolls, each of which is mounted in a roll stand by means of work roll chocks, the work roll chocks in the roll stand being lockable and unlockable via at least one work roll lock, at least two further rolls, in particular two support rolls, each using roll chocks are stored in the roll stand, both at least one of the work rolls and at least one of the further rolls in the roll stand being adjustable for setting a desired roll gap relative to the other work roll or the other further roll, in particular in the vertical direction, the work rolls being provided with axial displacement means are provided for axial displacement, with which the work rolls can be brought into and held in a desired axial position relative to the roll stand, and the work rolls are operatively connected to bending means with which si e can be subjected to a bending moment.

A rolling device of this type is well known in the prior art. Reference is made, for example, to EP 0 256 408 A2, EP 0 256 410 A2, DE 38 07 628 C2 and EP 0 340 504 B1. From these documents, rolling devices are known in which two work rolls 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 rolling device designed in this way is thus equipped as a device with four or six rolls, the individual rolls being able to be positioned relative to one another in the vertical direction to produce the desired roll gap. The work rolls are arranged axially displaceable, which makes it possible to influence the strip profile in strip lines by means of a variable roll gap profile. The process engineering option for axially shifting the work rolls is also becoming more important for roughing lines, on the one hand for the purpose of influencing the strip profile in a targeted manner and on the other hand for extending the roll travel by means of targeted wear distribution.

Another important embodiment of the rolling device is that means are provided for bending or balancing the work rolls. This allows a bending moment to be introduced into the work rolls, which has procedural advantages, as can be seen from the aforementioned literature.

The work roll bending and shifting systems mostly 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 opened when changing the work roll. For the realization of the bending and balancing, the necessary plungers are either arranged in a stationary manner in stationary blocks, which disadvantageously leads to not negligible tilting moments during the axial displacement, or they are designed as cassettes which also move with the axial displacement, in order to improve the tilting moments or frictional forces to be able to master.

The known rolling devices reach their procedural limits when high roller steps have to be run, such as are required in sheet metal or roughing lines. The plungers of the bending or balancing cylinders have to be guided over much greater lengths and therefore require a large amount of space in order to ensure the lever ratios which occur over long distances even when the plunger is fully extended. Larger roll passes with a combination of work roll bending and axial displacement can only implement the solutions mentioned while accepting the disadvantages mentioned.

Short guide lengths of the plungers of the bending or balancing cylinders are only achieved again when the bending or balancing cylinders move with the work roll / backup roll chock system, that is to say "flying" between the downwardly projecting arms of the support or intermediate roll chock and the laterally projecting tabs of the work roll chock. In this case, the tappet can be arranged either in the support or intermediate roll chock or in the work roll chock; its arrangement in the support or intermediate roll chock offers the advantage that the pressure medium supply lines do not have to be separated when changing the work roll.

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

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

The invention is therefore based on the object of providing a rolling device with a bending and axial displacement system for the work rolls, which on the one hand allows high roll heights, but on the other hand is characterized by a small space requirement in relation to the column window height. Furthermore, a good guidance of the plungers of the bending or balancing means should be ensured, while at the same time it should be ensured that the number the change of company parts in the event of a work roll change is as small as possible. In addition, the associated requirements of the axial work roll locking and the position measurement of the axial displacement path should also be met.

This object is achieved according to the invention in that the axial displacement means are arranged or act between the roll stand and work roll lock and the bending means are arranged or act between the work roll chock and the further roll chock.

The combination of these measures ensures that large roller exits can be driven with the rolling device. Nevertheless, there is a very compact machine design that takes up little space. The plungers of the bending means can be guided in an optimal manner. Due to the defined design of the rolling device, a work roll replacement is also possible, in which the axial displacement means do not have to be replaced; this minimizes the number of parts to be changed in the event of a work roll change.

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

The axial displacement means are preferably arranged fixed on the roll stand and have at least one linear guide on which the work roll chock is arranged so that it can be fixed relative to the axial displacement means in a direction transverse to the axial displacement direction, in particular displaceable in the vertical direction. As a preferred embodiment of the work roll chock it is provided that it has two webs which extend on both sides of the axis of the work roll and which can be locked with an axial displacement means.

With regard to the locking of the work roll chock on the roll stand, it is advantageously provided that the linear guide is fixedly arranged on the axial displacement means and has a bolt, preferably plate-shaped, which can be displaced in a direction transverse to the axial displacement direction, in particular in the horizontal direction, which together with the linear guide for the end of the web forms a receiving slot. The bolt can be connected to actuating means by means of which it can be positioned in two positions, namely in a locking position and in an unlocking position. Furthermore, the actuating means per axial displacement means preferably consists of two hydraulic piston-cylinder systems, which are arranged parallel to one another and can move the bolt, the piston-cylinder systems acting on the side of the bolt facing away from the work roll chock.

According to a further development, the axial displacement means are equipped with means for preventing rotation, which prevent rotation of the axial ends of the axial displacement means.

For work roll bending or balancing, it 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. A sliding surface can be arranged between the bending means and the laterally projecting tab of the work roll chock.

Exemplary embodiments of the invention are shown in the drawing. Show it:

1 shows a perspective view of the section of a rolling device according to a first embodiment with work roll chock, further roll chock and axial displacement means;

FIG. 2 shows the front view of the rolling device according to FIG. 1 viewed in the roll axial direction;

Fig. 3 shows the section A-A according to Fig. 2;

FIG. 4 the side view of the axial displacement means viewed from the right side according to FIG. 2;

Figure 5 shows the bending means according to the detail "Y" of Figure 2 in section.

6a shows a perspective view of the detail of a rolling device according to a second embodiment with work roll chock, further roll chock and two axial displacement means, the left axial displacement means being shown with the bolt open (unlocking position);

6b shows a further perspective view of the rolling device according to FIG. 6a, the right axial displacement means being shown in FIG. 6a and this axial displacement means being shown with the bolt closed (locking position);

7 shows the front view of the rolling device according to FIGS. 6a / 6b viewed in the direction of the roll axis;

8 shows the section AA according to FIG. 7; 9 shows the axial displacement means according to the detail "Y" of FIG. 8 in section;

FIG. 10 shows section B-B according to FIG. 9;

FIG. 11 shows the section C-C according to FIG. 7;

FIG. 12 shows the section D-D according to FIG. 10;

13 shows the section E-E according to FIG. 7; and

Fig. 14, the bending means according to the detail "Z" of Fig. 7 in section.

In Fig. 1, the detail 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 more detail, which are mounted in work roll chocks 3, which are in turn arranged in a roll stand 4, which is again only schematically outlined. The work roll chock 3 can be locked or unlocked relative to the roll stand 4 by means of a work roll lock 5. The work roll 2 is supported by a further roll 6 in the form of a backup roll. This further roller 6 is mounted in further roller chocks 7, which are also fixed to the roll stand 4 or can be locked there.

Only the work roll 2 and support roll 6 provided above the center of the rolling stock are shown; the same arrangement is located symmetrically below the center of the rolling stock. Furthermore, it should be noted that the rolling device 1 can also have further rolls, namely intermediate rolls, which are arranged between the work rolls 2 and the support rolls 6. The work rolls 2, of which - as mentioned - only the upper one is indicated in FIG. 1, should be arranged axially displaceable relative to the roll stand 4. For this purpose, axial displacement means 8 are provided, the structure of which will be explained in detail later. One axial displacement means 8 is provided on both sides of the center of the work roll 2, these means being firmly fixed with their one axial end 23 to the roll stand 4. At the other axial end 22 of the axial displacement means 8 is the work roll lock 5, with which the work roll chock 3 can be detachably fixed. The work roll chock 3 has two webs 12 and 13 which extend symmetrically from the axis of the work roll 2. The webs 12, 13 are received at their ends 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 are positioned vertically at that height in the roll stand 4 and can be determined, which corresponds to the required roll gap. The receiving slot 17 is delimited on the one hand by a linear guide 11 which has the work roll lock 5, on the other hand it is delimited by a latch 14 which will be described in detail later.

2 shows the front view of the rolling device 1 - viewed in the direction of the roll axis. The view, shown partially in section, shows that the further roller chock 7 for the support roller 6 has a rectangular recess in its lower region and thus forms a guide 10 for the work roller chock 3 that can be inserted into the recess. I.e. 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 introduce a bending moment into the work roll 2, bending means 9 in the form of hydraulic linear actuators are provided in a manner known per se, which act between the work roll chock 3 and the further roll chock 7. The structure of the axial displacement means 8 can be seen in FIG. 3, where the section AA according to FIG. 2 can be seen. The axial displacement means 8 is fixedly arranged on the roll stand 4 with its one axial end 23. At the other axial end 22, the work roll lock 5 is arranged. The axial displacement means 8 consists of a fixed block 27 which is fixedly connected to the roll stand 4 and which projects in a cylindrical shape and forms the bottom of a displacement cylinder. A sliding sleeve 28 is slidably arranged on the outer diameter of this cylindrical projection. The sliding sleeve 28 consists of a sliding tube with guide bushings and a cubically shaped cover 29. With this cover 29, the sliding piston 30 is firmly connected coaxially. The sliding tube of the sliding sleeve 28 has laterally projecting guide tabs 31 which slide on a T-piece 32 connected to the fixed block 27 (see FIG. 1). This creates means 21 for preventing the axial displacement means 8 from rotating, ie torsion of one axial end 22 relative to the other axial end 23 of the axial displacement means 8 is excluded.

A distance measuring system 33 is arranged between the base part of the T-piece 32 and one of the guide plates 31. With this it is possible to measure the current axial position of the work rolls 2.

The work roll lock 5 is attached to the outside of the cover 29 of the sliding sleeve 28. This essentially consists of a base plate 34 (see FIGS. 1 and 4), the bolt 14 and actuating means 18 for the bolt 14. In the locked state, the work roll lock 5 is positively connected to the webs 12, 13 of the work roll chock 3. The axial displacement means 8, consisting of a fixed block 27, displacement sleeve 28, displacement measuring system 33 and work roll locking device 5, is arranged essentially mirror-inverted on the roll stand 4 on the inlet and outlet side. As an alternative to this, the work roll lock 5 can be attached to the work roll set 2 by the base plate 34, the actuating means 18 for the bar 14 and the bar 14 themselves being placed on the bearing cover of the work roll set 2 and corresponding elements for producing the positive fit on the sliding sleeve 28 Axial displacement means 8.

An actuation of the axial displacement means 8 and due to the positive connection between the work roll lock 5 and the work roll chock 3 causes an axial displacement of the work roll 2. The work roll chock 3 is slidably guided in the downwardly projecting arms of the corresponding further roll chock 7. The work roll lock 5 has an axial offset for locking the further roll 6, not shown, so that collisions of these devices are avoided and large roll runs are thus ensured.

In FIG. 5 it 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 located on the inlet and outlet sides in terms of their effectiveness between the work roll chock 3 and another roll chock 7 for the backup roll 6. For this purpose, the further roll chock 7 has a projecting arm 24 which carries the bending means 9. They rest on the work roll chock 3 on a projecting 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 exemplary embodiment two bending means 9 arranged one behind the other are provided. The plunger 35 (movable part) represents a piston which is arranged coaxially in a corresponding bore in a cylinder 36. The fixed part of the bending means 9 consists essentially of a guide bushing with a corresponding bore, which is machined into the arm 24 projecting downwards, and of an end cover and various sealing and stripping elements. In the exemplary embodiment (see FIG. 3), four bending means 9, two on each side, are provided, the plunger 35 of which is supported on the laterally projecting tab 25 of the work roll chock 3. During an axial displacement movement of the work roll 2, the tab 25 slides over the contact surface of the plunger 35. In order to functionally favor this, a sliding surface 26 is arranged in the contact area of the plunger 35 with the tab 25.

Alternatively, a cylinder 36 can be integrated in the laterally projecting tab 25 of the work roll chock 3. Then the plunger 35 is supported on the projecting arm 24 of the further roller chock 7.

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

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

The axial displacement means 8 are also located above and below the rolling line and on the inlet and on the outlet side of the roll stand 4 on the operator side. Solutions for work roll displacement devices above the roller line are problematic with a large rise. Solutions for work roll shifting devices under the rolling line can be built conventionally or like those for large stairways. The devices on the inlet and on the outlet side are essentially identical and symmetrical to each other, so that - as already in the case of the first exemplary embodiment - only axial displacement means 8 with a high rise lying above the rolling line are described here.

The design of the axial displacement means 8 also corresponds to that of the exemplary embodiment described above. Referring to the figures

8 to 12 it can be seen that the cover 29 is fixed to the displacement piston 30 connected is. It projects at least in the direction of the work roll chock 3 with respect to the local outer contour of the displacement sleeve 28. Between the cover 29 and a plate 37 arranged on the sliding sleeve 28, the bolt 14 is installed, which engages around the sliding sleeve 28 and can be moved transversely to the axis of the sliding sleeve 28 in an approximately horizontal direction to close the lock. Between the plate 37 and the latch 14, the vertically extending receiving slot 17 is formed by closing the latch 14, in which the laterally projecting web 12, 13 of the work roll chock 3 is guided. For this purpose, a recess is worked into the plate 37 or a spacer with a comparable recess is inserted between the plate 37 and the bolt 14.

The vertical receiving slot 17 absorbs the axial displacement forces that have to be passed on via the laterally projecting webs 12, 13 of the work roll chock 3, and at the same time enables large relative movements in the vertical direction. This subsequently enables a large roll emergence. The contact surfaces of the webs 12, 13 on the plate 37 and on the bolt 14 form two abutments for the webs 12, 13 of the work roll chock 3. The vertically extending receiving slot 17 is opened for work roll removal by pulling back the catch 14. 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 the axial displacement means 8 from rotating.

Two embodiments are preferred for the means 21 for preventing twisting:

If possible, a component is provided which is attached to the displacement sleeve 28 outside the central axis and is fixed to the stand. This protrudes into one Opening of the plate 37 on the sliding sleeve 28, or a component fastened to the plate 37 of the sliding sleeve 28 protrudes into an opening which is fixed to the stand. The anti-rotation device must have a guide of sufficient length so that rotation between the two axial ends 22 and 23 of the axial displacement means 8 is prevented for the entire maximum displacement path.

Alternatively, the sliding sleeve 28 and the sliding piston 30 can be shaped in such a way that they do not slide on one another with cylindrical surfaces, but rather with surfaces that prevent rotation relative to one another.

The fulfillment of the two main functions of the plate 37 on the sliding sleeve 28, namely being both an abutment and part of the anti-rotation device, can be achieved by two separate plates which are worked on or welded onto the sliding sleeve 28. The combination of the two functions by means of the plate is technically simple and therefore advantageous.

The detailed design of the work roll lock 5 by means of the bolt 14 is shown in FIGS. 10 and 12. The bolt 14 can have an O-shaped or U-shaped recess (in FIG. 10, the recess is O-shaped). The bolt 14 is not arranged in front of the head of the cover 29, but rather engages around the sliding sleeve 28. The recess in the bolt 14 is so large that the bolt for mounting in an O-shaped configuration or axially or radially in a U-shaped configuration can be pushed onto the sliding sleeve 28. The O-shape as a closed shape is the stiffer version of the latch 14. The U-shape has the advantage that the cover 29 can be non-detachably connected to the sliding sleeve 28 or that the cover 29 and the sliding sleeve 28 can consist of one piece ,

In the case of a U-shaped design, the bolt 14 is open on that side of the sliding sleeve 28 which is opposite the work roll chock 3.

Because the bolt 14 engages around the sliding sleeve 28, the web 12, 13 of the Work roll chock 3 - measured from the center of the work roll bearing - turn out to be shorter than if the bolt 14 were arranged in front of the head of the cover 29. The lever arm between the work roll bearing and the guide, which is formed by the two abutment bars 14 and plate 37, is thus reduced. A lower lever arm means that the frictional forces in the guide only exert comparatively small additional moments on the work roll bearings. As a result, the work roll bearing has a longer service 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) is at least larger by the locking stroke than is required for the assembly.

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

For reasons of space, it makes sense to provide a further recess in the bolt 14, to allow elements of the means 21 to prevent rotation and to prevent a collision with them.

In the exemplary embodiment according to FIG. 10, the bolt 14 has three recesses, one large for the sliding sleeve 28, two smaller ones for the piston-cylinder Systems 19, 20 and another to avoid collision with the means 21 for preventing the axial displacement means 8 from rotating.

The bolt 14 is held in the open or closed position by the piston-cylinder systems 19, 20. However, it must also be secured against rotation against an axis parallel or identical to the central axis of the displacement sleeve 28. As can be seen in the exemplary embodiment according to FIG. 10, strips 38, 39 can be attached above and below the cover of the sliding sleeve 28 or above and below the plate of the sliding sleeve, which prevent such a rotation. The strips 38, 39 can also form a common component with the plate 37 or with the plate 37 and the sliding sleeve 28. An alternative embodiment of the anti-rotation device results if horizontal grooves are formed in the plate 37 or in the cover 29, in which raised strips of the bolt 14 are guided. Furthermore, it is possible to form the grooves in the bar 14 and to attach the raised strips on the plate 37 or on the cover 29. Variants in which the anti-rotation device is attached to the plate 37 have the advantage that the cover 29 is then not additionally subjected to rotation.

The cover 29 of the sliding sleeve 28 is shaped in such a way that two functions can be fulfilled: on the one hand, the sliding piston 30 is firmly connected coaxially to the lid 29 (cf. FIG. 8), so that the piston over the lid, the sliding sleeve 28 together with attachments and thus can also axially shift the vertical receiving slot 17 for the work roll chock 3. On the other hand, the cover 29 forms an abutment for the bolt 14, in particular 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 lid 29 or can grip around the sliding sleeve 28. In addition, the cover 29 can have a recess in order to allow elements of the anti-rotation device to pass through and thus prevent a collision with them. To the To make the cover 29 shorter, it is also possible to install an intermediate piece between the cover and the latch.

Either in the cover 29 or in this intermediate piece, it can also be secured against twisting on the sliding sleeve 28. One possibility for this is to provide one or more flat surfaces on the sliding sleeve 28, 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 intermediate piece above. In any case, the cover 29 must be secured against twisting relative to the sliding sleeve 28 when the latch 14 is secured against twisting against the cover 29.

The measurement of the axial displacement path is made possible by a unit arranged outside or inside the axial displacement means 8. The arrangement of the transducer within the pressure system is avoided as much as possible due to the tendency to risk during maintenance work. The path measuring system 33 can be designed as an external or internal unit. In the case of an external unit, protection against harmful environmental influences is required, which can be achieved by an encapsulated system similar to a hydraulic cylinder. A kind of piston, which is fixed on the upright side, slides through a cylinder tube, which is attached to the moving parts of the axial displacement. The sensor moves coaxially with the cylinder tube and generates the corresponding travel signal. Adequate protection of the system is achieved with appropriate sealing and wiping elements. In the case of an internal unit, the position transmitter - as seen from the end face of the moving parts - is inserted into the sliding sleeve. The necessary encapsulation is produced by the sliding system itself. A suitably sealed housing protects the electronic part of the position transmitter.

In the embodiment according to FIG. 9, a position transmitter 40 is arranged in the axial displacement means 8 to control the displacement stroke of the displacement sleeve 28. An arrangement of a position sensor rod 41 inside - but nevertheless outside the pressure chamber - is advantageous because this element is then protected against environmental influences without additional encapsulation. The position sensor 40 is attached to the cover 29, the position sensor rod 41 is passed through a hole in the cover 29 and dips into a hole in an inner cover 42. The inner cover 42 is part of the part of the axial displacement means 8 which is fixedly arranged on the roll stand 4, so that the measurement of the relative displacement of the cover 29 relative to the roll stand 4 is possible.

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

As can be seen from FIGS. 13 and 14, the bending means 9 are located in arms 24 which project downwards of the further roller chock 7 of the upper support roller 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 conception of the bending means 9 thus essentially corresponds to that shown in FIG. 5.

In the case of a plurality of tappets 35, there is the possibility of regulating the pressures in the individual cylinder spaces in such a way that the work roll bearing is loaded as little as possible off-center ("pressure compensator").

Alternatively, the tappets 35 can be accommodated 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 roller chock 7. In this case, the work roll bearing would only be loaded in the middle.

The lower bending means 9 can be located in fixed blocks on the stand. Alternatively, they can also in the upwardly projecting arms of the further roll chock of the lower support or intermediate roll set or can be accommodated 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, the tilting moments which occur in the event of the work rolls being axially displaced can be optimally absorbed with the proposed design. The design of the rolling device precludes collisions between the various components, even when large roller stacks are being driven. However, no large installation space is required in the roll stand.

LIST OF REFERENCES:

1 rolling device

2 work roll

3 work roll chock

4 roll stand

5 work roll lock 6 additional roll (backup roll)

7 additional roller chock (for backup roller)

8 axial displacement means

9 bending means

10 guide 1 1 linear guide

12 bridge

13 bridge

14 bars

15 end of the web 16 end of the web

17 slot

18 actuating means for the bolt

19 Piston-cylinder system 0 Piston-cylinder system 21 Means to prevent twisting

22 axial end of the axial displacement means

23 axial end of the axial displacement means 4 projecting arm of the further roll chock 5 projecting tab of the work roll chock 6 sliding surface 7 fixed block sliding sleeve

cover

displacement piston

guide tab

Tee

displacement measuring system

baseplate

tappet

cylinder

plate

strip

locator

Position sensor rod

Innendeckel

Claims

claims:

1 . Rolling device (1) with two work rolls (2), each of which is mounted in a roll stand (4) by means of work roll chocks (3), the work roll chocks (3) in the roll stand (4) being lockable and unlockable via at least one work roll lock (5) , at least two further rolls (6), in particular two support rolls, each of which is mounted in the roll stand (4) by means of further roll chocks (7), both at least one of the work rolls (2) and at least one of the further rolls (6) in the roll stand (4) for setting a desired roll gap relative to the other work roll (2) or the other further roll (6), in particular in the vertical direction, can be adjusted, the work rolls (2) having axial displacement means (8) for axial displacement are provided with which the work rolls (2) can be brought and held in a desired axial position relative to the roll stand (4), and wherein the work roll s (2) are operatively connected to bending means (9) with which they can be subjected to a bending moment, characterized in that the axial displacement means (8) are arranged or act between the roll stand (4) and work roll lock (5) and the bending means (9) are arranged or act between the work roll chock (3) and the further roll chock (7) ,

2. Rolling device according to claim 1, characterized in that the further roll chock (7) has a guide (10) in which the work roll chock (3) is arranged relatively displaceable to the further roll chock (7) and fixable.

3. Rolling device according to claim 1 or 2, characterized in that the axial displacement means (8) are fixedly arranged on the roll stand (4) and have at least one linear guide (11) on which the work roll chock (3) is relatively displaceable to the axial displacement means (8) in a direction transverse to the axial displacement direction, in particular displaceable in the vertical direction, and is arranged to be fixable.

4. Rolling device according to one of claims 1 to 3, characterized in that the work roll chock (3) has two webs (12, 13) extending on both sides of the axis of the work roll (2), each of which can be locked with an axial displacement means (8).

5. Rolling device according to claim 3 and 4, characterized in that the linear guide (11) is fixed to the axial displacement means (8) and one in a direction transverse to the axial displacement direction, in particular in the horizontal direction, displaceable, preferably plate-shaped trained, bolt (14), which forms a receiving slot (17) together with the linear guide (11) for the end (15, 16) of the web (12, 13).

6. Rolling device according to claim 5, characterized in that the bolt (14) engages around a sliding sleeve (28).

7. Rolling device according to claim 5 or 6, characterized in that the bolt (14) is connected to actuating means (18) by means of which it can be positioned in two positions, namely in a locking position and in an unlocking position.

8. Rolling device according to claim 7, characterized in that the actuating means (18) per axial displacement means (8) consists of two hydraulic piston-cylinder systems (19, 20) which are arranged parallel to one another and move the bolt (14) can, whereby the piston-cylinder systems (19, 20) act on the side of the bolt (14) facing away from the work roll chock (3).

9. Rolling device according to one of claims 1 to 8, characterized geken nzeic h net that the axial displacement means (8) are equipped with means (21) for preventing rotation, the rotation of the axial ends (22, 23) of the axial displacement means (8 ) prevent.

10. Rolling device according to one of claims 1 to 9, characterized in that at least one bending means (9) designed as a hydraulic linear actuator is in a projecting arm (24) of the further roll insert. construction piece (7) is arranged and presses on a laterally projecting tab (25) of the work roll chock (3).

11. Rolling device according to claim 10, characterized in that a sliding surface (26) is arranged between the bending means (9) and the laterally projecting tab (25) of the work roll chock (3).