EP1648625B1 - Rolling device - Google Patents

Abstract

The invention relates to a rolling device (1) comprising at least two working rolls (2, 3) which are respectively mounted in a roll stand (6) by means of working roll assembly pieces (4, 5). At least one of the working rolls (2, 3) is adjustable relative to the other working roll (2, 3) within the roll stand (6), especially in a vertical direction, so as to adjust a desired rolling gap. At east one working roll (2, 3) is effectively connected to bending means (7), with the aid of which said working roll (2, 3) can be impinged upon by a bending moment. The working roll assembly piece (4, 5) is provided with arms (9, 10) that laterally protrude relative to the axis (8) of the working roll (2, 3) to absorb the force generated by the bending means (7). In order to improve the adjustability of the rolling device to a large ascent, a pressure-transmitting element (12) which can be displaced relative to the roll stand (6), particularly in a vertical direction, is disposed between a pressure-generating element (11) of the bending means (7), especially a piston, and the protruding arm (9, 10) of the working roll assembly piece (4, 5).

Description

The invention relates to a rolling device with at least two work rolls, which are each mounted by means of a work roll chock in a rolling stand, wherein at least one of the work rolls in the rolling stand for setting a desired roll gap relative to the other work roll, in particular in the vertical direction, is adjustable, wherein at least one Working roll is in operative connection with bending means, with which it can be acted upon by a bending moment, and wherein the work roll chock for receiving the force generated by the bending means from the axis of the work roll seen from side cantilevered arms.

A rolling apparatus of this kind is well known in the art. It is for example 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 can thus be 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 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. 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 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 rams.

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 plungers of the balancing cylinders are only achieved again when the bending or balancing cylinders ride with the work roll / backup roll chock, as it were "flying" between downwardly projecting arms of the support or intermediate roll chock and laterally projecting tabs of the work roll chock are arranged. Here, the plunger (piston) 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 "fly" arranged bending or Balanciersystem in combination with an axial displacement is from the DE 101 50 690 A1 known. Here, a coaxially arranged on the work roll chock shift cylinder is provided for the axial displacement of the work roll. 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 from the DE 101 50 690 A1 known rolling device with "flying" arranged bending arrangement - combined with a device for axial displacement of the work rolls in inlet and outlet - is suitable for a high to very high roll rise. However, this presupposes that the tilting moments arising from the axial displacement occurring in these rolling devices are absorbed by a correspondingly rigid design of the back-up roller bearing.

However, there are also compliant back-up roller bearings. During the axial displacement, the upper work roll set is pushed over the balancing pressure applied bending cylinders of the upper backup roll chocks. The frictional forces occurring produce the aforementioned tilting moments and can cause a misalignment of the backup roll chocks. The maximum possible misalignment of the backup roll chocks is doing through the games of the backup roller bearing specified. In a sudden loading of the framework with rolling force following the work roll displacement ("puncture"), therefore, can not be ruled out that it comes to a local edge pressure and thus long term to bearing damage, z. B. damage to the bearing or pin bushing in oil flood storage or overloading individual rows of bearings in bearings.

Therefore, a good guidance of the work roll chocks even at high roll rise is not always guaranteed, and said skew of the backup roll chocks can not always be avoided. This is not ensured when long bending or Balancierzylinder be used. Furthermore, there are disadvantages when an axial displacement of the work rolls should take place and a high or very high roll rise is required.

The invention is therefore an object of the invention to provide a rolling device of the type mentioned, which does not have the disadvantages mentioned. In particular, a rolling device with bending and axial displacement system for the work rolls is to be created, which permits high roll runs.

This object is achieved in that between a compressive force generating element of the bending means, in particular a piston, and the cantilever arm of the work roll chock a relative to the rolling stand, in particular in the vertical direction, displaceable pressure transmitting element is arranged, wherein the pressure force generating element of the bending means and the projecting arm of the work roll chock are positioned so that the center axis of the pressure force generating element intersects the cantilever arm, wherein the bending means are arranged in a fixedly arranged on the rolling mill block and the pressure transmitting element by means of a guide, in particular by means of a vertical guide, is mounted on the block and wherein the pressure transmission element is formed in a horizontal section U-shaped and surrounds the block from three sides at least partially and the pressure transmission element in a perpendicular to the axis of the work roll vertical section L-shaped is formed and at least partially surrounds the block on its upper side.

As a result, such an optimized transmission of the force of the bending means is achieved that the bending can be achieved with simultaneous axial displacement of the work rolls and high roll rise without the above-mentioned disadvantages.

A further development provides that a sliding surface is arranged between the pressure force generating element of the bending means and the pressure transmission element and / or between the pressure transmission element and the cantilever arm of the work roll chock.

The guide is further improved by varying the roller distance, characterized in that the pressure-transmitting element is mounted on the rolling stand by means of a guide, in particular with a vertical guide. It has also been proven that holding means are arranged between the block and the pressure-transmitting element, which hold the pressure-transmitting element immovably in the direction of the work roll on the block.

The work rolls are usually provided with Axialverschiebemitteln for axial displacement, with which the work rolls can be brought relative to the rolling stand in a desired axial position and held there.

A particularly good mode of operation is achieved when the extension of the cantilevered arm of the work roll chock in the direction of the axis of the work roll is large in relation to the dimension measured in the direction of the axis the pressure transmitting element at its part connected to the cantilever arm, preferably at least twice as large.

Alternatively, it can also be provided that the extension of the cantilever arm of the work roll chock in the direction of the axis of the work roll is small in relation to the axis measured in the direction of the extension of the pressure transmitting member at its associated with the cantilever arm part, preferably at most half as large ,

With the proposed embodiment of a rolling device is achieved that a good guidance of the work roll chocks is guaranteed even at high roll emergence and skewing of the backup roll chocks is avoided. For this purpose, the work roll bending device may be equipped with fixed blocks in which although long bending or Balancierzylinder can work, but are relieved of the overturning moments by the said additional measures. The proposed rolling device is suitable for high roller rising and still executable in a compact design.

In the drawings, embodiments of the invention are shown.

Fig. 1

den Ausschnitt einer Walzvorrichtung gemäß einer ersten Ausführungsform mit Biegemitteln in Walzenachsrichtung betrachtet, in der Vorderansicht gemäß dem Schnitt A-A gemäß Fig. 2;

Fig. 2

die Draufsicht auf die Walzvorrichtung im Schnitt B-B gemäß Fig. 1;

Fig. 3

die Biegemittel in der Seitenansicht im Schnitt C-C gemäß Fig. 2;

Fig. 4

eine zu Fig. 2 alternative Ausführungsform;

Fig. 5

die Ansicht X gemäß Fig. 4;

Fig. 6

in perspektivischer Ansicht ein Axialverschiebemittel zur Axialverschiebung der Arbeitswalze;

Fig. 7

dasselbe Axialverschiebemittel in einer etwas anderen perspektivischen Ansicht;

Fig. 8

das Axialverschiebemittel gemäß Fig. 6 bzw. 7 in der Seitenansicht;

Fig. 9

das Axialverschiebemittel in der Seitenansicht gemäß dem Schnitt D-D nach Fig. 10;

Fig. 10

das Axialverschiebemittel in der Draufsicht gemäß dem Schnitt E-E nach Fig. 9;

Fig. 11

das Axialverschiebemittel in der Vorderansicht gemäß dem Schnitt F-F nach Fig. 8;

Fig. 12

einen Ausschnitt des Axialverschiebemittels gemäß dem Schnitt G-G nach Fig. 11;

Fig. 13

die Einzelheit Z gemäß Fig. 11;

Fig. 14

den Schnitt H-H gemäß Fig. 13; und

Fig. 15

eine Explosionszeichnung des Axialverschiebemittels.

Show it:

Fig. 1

considered the detail of a rolling device according to a first embodiment with bending means in Walzenachsrichtung, in the front view according to the section AA of FIG. 2;

Fig. 2

the top view of the rolling device in section BB of FIG. 1;

Fig. 3

the bending means in the side view in section CC of FIG. 2;

Fig. 4

an alternative to Figure 2 embodiment.

Fig. 5

the view X of FIG. 4;

Fig. 6

in perspective view an axial displacement means for axial displacement of the work roll;

Fig. 7

the same Axialverschiebemittel in a slightly different perspective view;

Fig. 8

the Axialverschiebemittel shown in Figure 6 and 7 in the side view.

Fig. 9

the Axialverschiebemittel in the side view according to the section DD of FIG. 10;

Fig. 10

the axial displacement means in the plan view according to the section EE of Fig. 9;

Fig. 11

the axial displacement means in the front view according to the section FF of Fig. 8;

Fig. 12

a section of the Axialverschiebemittels according to the section GG of Fig. 11;

Fig. 13

the detail Z of FIG. 11;

Fig. 14

the section HH of FIG. 13; and

Fig. 15

an exploded view of the Axialverschiebemittels.

In Figures 1 to 3, a rolling device 1 is shown, are arranged in the two cooperating work rolls 2 and 3, which are each mounted in a work roll chock 4 and 5, in a rolling mill 6.

For largely arbitrary setting of a roll gap between the two work rolls 2 and 3, it is provided that the upper work roll chock 4 is made adjustable in the vertical direction; It can therefore be moved in the vertical direction relative to the rolling stand 6.

The work rolls 2, 3 are supported respectively on support rollers 21 and 22, which are each mounted in a support roll chock 23 and 24 respectively. The illustrated rolling device 1 thus has a total of four rollers. It should be noted that it may also comprise further rolls, namely intermediate rolls, which are arranged between the work rolls 2, 3 and the support rolls 21, 22.

To initiate a bending moment in the work rolls 2, 3 bending means 7 are provided. As can be seen in particular from FIG. 2, the bending means 7 are arranged in both axial end regions of the work rolls 2, 3 and, moreover, both on the feed side and on the discharge side on the rolling stand 6. A total of four bending means 7 are provided.

The bending means 7 have a block 16 which is fixedly arranged on the roll stand 6, as can be seen in particular in Fig. 1. The block 16 has cylindrical bores in which compressive force generating elements 11, d. H. Piston, are arranged, which can be acted upon by hydraulic pressure. The pistons 11 have a center axis 13 which extends in the vertical direction.

In Fig. 1 can further be seen that each work roll chock 4, 5 has cantilevered arms 9 and 10, which are arranged laterally of the axis 8 of the work roll 2, 3. The projecting arms 9, 10 extend - from the work roll 2, 3 away - laterally outwards and overlap the piston 11 beyond the center axis 13 out.

Between the bending means 7 and in particular the piston 11 and the cantilevered arms 9, 10 of the work roll chocks 4, 5 is a pressure transmission element 12 arranged. This is equipped with two sliding surfaces 14 and 15, which ensure good sliding conditions between the piston 11 and the pressure transmission element 12 on the one hand and between the pressure transmission element 12 and cantilever arm 9, 10. As will be further seen, the piston 11 and cantilevered arm 9, 10 are positioned so that the center axis 13 of the piston 11 intersects the cantilevered arm 9, 10. As a result, an optimal power transmission from the bending means 7 to the work roll chock 4, 5 is achieved.

The pressure transmission element 12 is arranged via a vertical guide 17 on the block 16 and can thus move in the vertical direction relative to the block 16 and thus to the rolling stand 6. Similarly, a further vertical guide 18 is provided which guides the pressure transmission element 12 in the upper region of the rolling stand 6, namely a crosshead 28 of the pressure transmission element 12th

The pressure transmission element 12 is designed as a "bending hood". That is, it is U-shaped in a horizontal section and at least partially surrounds the block 16 from three sides, as best seen in FIG. From Fig. 1 it is apparent that the pressure transmitting element 12 is formed in a perpendicular to the axis 8 of the work roll 2, 3 vertical section L-shaped and partially surrounds the block 16 on its upper side. With the two legs 26 and 27 (see Fig. 2), the pressure transmitting element 12 is arranged against axial displacement forces vertically sliding but tilt-proof on the sides of the block 16. In addition, it is supported on the working roll 2 facing end face of the block 16 and thus can accommodate large horizontal forces that may be directed in the inlet against and in the outlet with the rolling direction.

As can further be seen, the pressure transmitting member 12 is provided in or against the rolling direction with further sliding surfaces, which are located on the legs 26 and 27, on which a support to the working roll 2 facing side surfaces of the roll stand 6 can be done. So that the pressure transmission element 12 remains in position with the work roll 2, 3 removed and does not fall off the rolling stand 6 or the block 16, holding means 19 are provided (see FIG. prevent the pressure transmitting element 12 is displaceable in the direction R to the roll axis 8.

It can also be seen that axial displacement means 20 for axial adjustment of the work roll 2, 3 are present.

In Fig. 3 it can be seen that in addition to the upward pressure force generating elements 11 (piston) of the bending means 7, which act on the upper work roll chock 4, further force-generating elements 25 are provided which generate a downward force and the lower work roll chock 5 act on a bending force.

A modified rolling device 1 is shown in FIGS. 4 and 5. From Fig. 5 shows that again both work rolls 2, 3 are each provided with Axialverschiebemitteln 20.

Problems with high roll emergence combined with axial displacements of the work rolls occur predominantly in the upper sets of rolls. Therefore, in the exemplary embodiment according to FIG. 1, a "bending hood" is also provided there only. In Fig. 1 it can be seen that the lower pressure force generating elements 25 without "bending hood" (pressure transmission element 12) act on the lower work roll chock 5. It should be noted, however, that a pressure-transmitting element 12 between piston 25 and work roll chock 5 can also be provided here.

The proposed "bending hood" in the form of the pressure transmission element 12 ensures good guidance of the work roll chocks 4, 5, even at high and very high roll emergence. At the same time the frictional forces are absorbed, otherwise in the axial displacement of the work rolls the support roll chocks 23, 24 skewed and would cause additional tilting moments.

To form the contact between the crosshead 28 of the pressure transmission element 12 (see Fig. 1) and the cantilever arm 9, 10, two variants are possible:

The contact surface of the cantilever arm 9, 10 may be formed short in Axialverschieberichtung and are centric to the work roll bearing 29, while the mating surface of the crosshead 28 is formed long. In this case, the work roll bearing 29 is advantageously loaded centric even after the axial displacement. Although this design leads to unequal loading of a plurality of arranged under the crosshead 28 pressure force generating elements 11 - in the embodiment, two pistons 11 per bending means 7 are provided side by side - but this can be compensated by a "pressure compensator", as known in the art is.

As an alternative, the contact surface associated with the crosshead 28 may be made short in the direction of axial displacement and thus only centric to the work roll bearing 29 in the unshifted position. The counter surface under the cantilever arm 9, 10 may be formed long. In the axial displacement of the pressure force generating elements 11 of the bending means 7 are now loaded evenly in an advantageous manner as before, but now the work roll bearing 29 is no longer centrally loaded.

In the exemplary embodiment, the blocks 16 of the upper bending means 7 are enclosed by the pressure transmission elements 12. The nip is set substantially over the upper work roll 2. In this case, the upper work roll 2 is pressed over the upper bending means 7 and the pressure transmission element 12 against the preset by means of mechanical adjustment upper support roller 21.

In the same way, the blocks 16 can also be enclosed in the region of the lower bending means 7 of pressure transmission elements 12 shown in FIGS. 1 and 3.

In addition to the so-called positive work roll bending over the bending means 7, a so-called negative work roll bending can be realized via additional piston-cylinder systems 30, 31 to increase the setting range for the profile influencing (see FIG.

In general, which is advantageous, the described bending system can be combined with different variants of work roll displacement systems. This can z. B. Axialverschiebesysteme be with two separate Axialschiebeeinheiten per work roll set, z. B. with a special, suitable for high roller catch locking and translational locking movement or with a conventional locking and rotary locking movement.

A preferred embodiment of the axial displacement means is shown in Figures 6 to 15.

In FIGS. 6 and 7, the axial displacement means 20 can initially be seen in two different perspectives. The side view of the Axialverschiebemittels 20 is shown in Fig. 8.

The detailed embodiment of the Axialverschiebemittels 20 is apparent from Figures 9 to 15.

The axial displacement means 20 are located above and below the rolling line and on the infeed and outfeed sides of the rolling mill 6. Solutions for work roll shifting devices above the mill line are problematic at high rises. Solutions for work roll shifters under the rolling line can be conventionally built or like those for large rises become. The devices on the inlet and on the outlet side are substantially identical and symmetrical to each other, so that here representatively only lying above the rolling line Axialverschiebemittel 20 are described with high rising.

As can already be seen in FIGS. 2 and 4, an axial displacement means 20 is provided on either side of the center of the work roll 2, 3, said means being firmly fixed to the rolling stand 6 by one axial end 32 thereof. In the region of the section F-F according to FIG. 8 of the axial displacement means 20, there is a work roll lock, with which the work roll chock 4, 5 can be releasably fixed. The work roll chock 4, 5 has two webs 33, 34 (see Fig. 2), which extend symmetrically from the axis 8 of the work roll 2, 3 from. The webs 33, 34 are received at their end in the locked state in a receiving slot in Axialverschiebemittel 20, which extends in the vertical direction and offers the possibility that the work roll chock 4, 5 and thus the work roll 2, 3 vertically in the same height in the rolling stand 6 can be positioned and set, which corresponds to the required roll gap. The receiving slot is on the one hand by a linear guide 54, s. Fig. 15, limited, which has the work roll lock, on the other hand limits him later described in detail latch 35th

The Axialverschiebemittel 20 consists of a fixedly connected to the roll stand 6 flange 36 which protrudes and forms the bottom of a guide tube 37. On the outer diameter of the guide tube 37, a sliding head 38 is slidably disposed.

The sliding head 38 consists of a sliding tube 39 with guide bushes and a cover 40. With this cover 40, a sliding piston 41 is fixedly connected coaxially.

By suitable means, it is ensured that twisting of the axial displacement means 20 in its axial direction is prevented, i. H. a torsion of the one axial end 32 relative to the other axial end of the Axialverschiebemittels 20 is excluded.

For the means for preventing twisting, various embodiments are conceivable. According to one possibility, a component can be provided which is mounted outside the central axis on the displacement tube 39. The anti-rotation device must have a guide of sufficient length, so that a rotation of the Axialverschiebemittels 20 is prevented for the entire maximum displacement.

Furthermore, a displacement measuring system sketched in FIG. 9 is provided, with which it is possible to measure the current axial position of the work rolls 2, 3.

On the Axialverschiebemittel 20, the work roll locking is attached. An essential part of this lock is a coupling 42 with the latch 35; the latter is shown in Fig. 11 cut. The latch 35 is connected to actuating means 43, 44. In the locked state, the work roll lock is positively connected to the webs 33, 34 of the work roll chock 4, 5. The Axialverschiebemittel 20 are inlet and outlet side arranged substantially mirror-inverted on the roll stand 6.

The coupling 42 is designed so that it forms a chamber together with the displacement tube 39, in which the bolt 35 is securely guided. Furthermore, it relies so with their flanks on Verschieberohr 39 that vertical forces and torques are intercepted over the axis of the Verschieberohrs 39 to the flanks. When the latch 35 presses on one flank of the coupling 42, the other flank is supported on a further surface of the displacement tube 39 and vice versa.

By actuation of the Axialverschiebemittels 20 and due to the positive connection between the work roll locking and work roll chock 4, 5 an axial displacement of the work roll 2, 3 is effected.

For locking the bolt 35 is arranged on the coupling 42, which surrounds the Verschieberohr 39 and 39 can be moved to close the locking in approximately horizontal direction transverse to the axis of the Verschieberohrs 39. When moving the bolt 35 in the locking position, a vertically extending receiving slot, in which the laterally projecting webs 33, 34 of the work roll chock 4, 5 are guided.

The vertically extending receiving slot receives the axial displacement forces that must be passed through the laterally projecting webs 33, 34 of the work roll chock 4, 5, while allowing large relative movements in the vertical direction. This creates a large roll rise as a result. The vertically extending receiving slot is opened for work roll removal by the latch 35 is retracted. Then the work roll set can be pulled out to the operating side.

The detailed embodiment of the work roll locking by means of the bolt 35 can be seen from Figures 11 to 14. The latch 35 may have an O- or U-shaped recess (in FIG. 11 the recess is O-shaped). The latch 35 is not arranged in front of the top of the lid 40, but it surrounds the displacement tube 39. The recess in the latch 35 is so large that the bolt for mounting in training in O-shape axially or when executed in U-shape axially or radially can be pushed onto the Verschieberohr 39. The O-shape is a closed form, the stiffer version of the bolt 35th

When executed in U-shape, the latch 35 is open on the side of the displacement tube 39 which is opposite to the work roll chock 4, 5. Because the latch 35 engages the shifting tube 39, the work roll bending arm (measured from the middle work roll bearing 29) may be shorter than if the latch 35 were located in front of the head 40. Thus, advantageously, the lever arm between the work roll bearing 29 and the vertical guide on the displacement head 38 is reduced. A smaller lever arm has the result that the frictional forces in the guide exert only comparatively small additional moments on the work roll bearing 29, which increases the service life of the bearing.

Another advantage of the short design is that the displacement system in front of the rolling mill requires less space for the withdrawn and the newly set sets of rolls, especially when a transverse displacement of the sets of work rolls is provided during the roll change.

Because translational movement of the latch requires less space relative to a rotary latch (as is customary with low-rise rolling mills), it is more suitable for high roller set-up.

The closing and opening of the receiving slot for the laterally projecting webs 33, 34 of the work roll chock 4, 5 is effected by a horizontal or approximately horizontal movement of the bolt 35 with a corresponding locking stroke. Therefore, the recess in the bolt 35 in the direction of movement (horizontal) at least by the locking stroke is greater than is required for assembly.

The movement of the bolt 35 is effected by the actuating means 43, 44. These are, for. B. one or more actuators in the form of piston-cylinder systems (hydraulic cylinder with continuous piston rods) - s. for this purpose the section GG according to FIG. 11 shown in FIG. 12. The piston-cylinder systems are expediently arranged on the side of the bolt 35 facing away from the work roll chock 4, 5. Particularly space-saving, it is when two piston-cylinder systems 43, 44 above and below find in recesses of the bolt 35 place. This embodiment is shown in FIG. 11; Fig. 12 shows a piston-cylinder system 43, 44 in detail.

For reasons of space, it makes sense to provide in the bolt 35 still another recess, in order to allow elements of the means for preventing twisting to happen and to avoid a collision with these.

The latch 35 has in the embodiment of FIG. 11 three recesses, a large one for the Verschieberohr 39, two smaller for the piston-cylinder systems 43, 44 and another to avoid collision with the means for preventing the rotation of the Axialverschiebemittels 20 ,

The recesses for the piston-cylinder systems 43, 44 are closed in an advantageous manner with brackets 45 in the bolt 35, so that the piston-cylinder systems 43, 44 can be expanded to the side without disassembling the clutch 42 or other parts to have to.

The latch 35 is held by the piston-cylinder systems 43, 44 in the open or closed position. But it must also be secured in a suitable manner against rotation against an axis parallel or identical to the central axis of the displacement tube 39. This is accomplished by the flanks 46 and 47 of the coupling 42, which in turn are supported on the displacement tube 39. Advantageously, the rotation is thereby intercepted by a short path.

On the displacement tube 39, one or more flat surfaces 48 can be provided, which clears some space for the locking movement.

The position of the bolt 35 can be checked by two position sensors 49, 50, which are installed in a suitable manner in the coupling 42 and thereby protected against environmental influences by a protective housing 51. The position sensor 49, 50 check the end position of the bolt 35, in the special grooves 52 are incorporated. Reference is made to FIG. 14 and the section HH according to FIG. 13 shown there.

Such a groove 52 has a deep groove in the middle, which is about twice as long as the locking movement, as well as at the two ends of each only shallow furrow. Optionally, one of the position sensors 49, 50 is located above one of the shallow grooves and continues to report the current lock position. The shallow grooves have the particular advantage that theoretically flush mounted position sensors 49, 50 are not sheared off, should they actually survive a bit. If a position sensor 49, 50 is located above one of the deep grooves, it can no longer recognize the latch 35. The corresponding holes and recesses can advantageously be mounted symmetrically above and below, so that the position sensor 49, 50 can be screwed at a suitable location, the empty position z. B. can be closed with a lid 53 (see Fig. 11).

The measurement of the Axialverschiebewegs (see Fig. 9) is made possible by an out of or within the Axialverschiebemittel 20 unit. The arrangement of the transmitter within the printing system is avoided as possible due to hazards during maintenance. The displacement measuring system can be designed 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 an encapsulated system similar to a hydraulic cylinder. 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 or tube. The required encapsulation is provided by the displacement system self made. A suitably sealed housing protects the electronic part of the position sensor.

An arrangement of a position sensor rod inside the Axialverschiebemittels 20 - but still outside the pressure chamber - is advantageous because this element is then protected without additional encapsulation against environmental influences. The position sensor can be mounted on the lid 40, the position sensor rod can be passed through a hole in the lid 40 and immerse in a hole in an inner lid.

With the proposed embodiment, such an arrangement of the bending means and the Axialverschiebemittel can be achieved with the occurring tilting moments in the case of axial displacement of the work rolls can be optimally absorbed. 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

Stripper

4

Work roll chock

5

Work roll chock

6

rolling mill

7

bending means

8th

Axle of the work roll

9

cantilever arm

10

cantilever arm

11

Pressure-generating element of the bending means (piston)

12

Pressure transmission element

13

Center axis of the pressure force generating element

14

sliding surface

15

sliding surface

16

block

17

Guide (vertical guidance)

18

Guide (vertical guidance)

19

holding means

20

axial displacement

21

supporting roll

22

supporting roll

23

Backup roll chock

24

Backup roll chock

25

Pressure-generating element of the bending means (piston)

26

leg

27

leg

28

crosshead

29

Work roll bearings

30

Piston-cylinder system

31

Piston-cylinder system

32

axial end

33

web

34

web

35

bars

36

flange

37

guide tube

38

shifting head

39

shifting tube

40

cover

41

displacement piston

42

clutch

43

actuating means

44

actuating means

45

clip

46

flank

47

flank

48

flat surface

49

locator

50

locator

51

housing

52

groove

53

cover

54

linear guide

R

Direction to the stripper

Claims (7)

1. Roll device (1) with at least two working rolls (2, 3), which are each mounted by means of working roll chocks (4, 5) in a roll stand (6), wherein at least one of the working rolls (2, 3) is adjustable in the roll stand (6), particularly in vertical direction, for setting a desired rolling gap relative to the other working roll (2, 3), wherein at least one working roll (2, 3) is operatively connected with bending means (7) by which this can be acted on by a bending moment and wherein the working roll chock (4, 5) has arms (9, 10) which project laterally as seen from the axis (8) of the working roll (2, 3) for acceptance of the force produced by the bending means (7), characterised in that a pressure transmission element (12) displaceable, particularly in vertical direction, relative to the roll stand (6) is arranged between an element (11), particularly a piston, which produces pressure force and the projecting arm (9, 10) of the working roll chock (4, 5), wherein the element (11), which produces pressure force, of the bending means (7) and the projecting arm (9, 10) of the working roll chock (4, 5) are so positioned that the centre axis (13) of the element (11), which produces pressure force, intersects the projecting arm (9, 10), wherein the bending means (7) are arranged in a block (16), which is fixedly arranged at the roll stand (6), and the pressure transmission element (12) is mounted at the block (16) by means of a guide (17), particularly by means of a vertical guide, and wherein the pressure transmission element (12) is formed to be U-shaped in a horizontal section and surrounds the block (16) at least partly by three sides and the pressure transmission element (12) is formed to be L-shaped in a vertical section perpendicular to the axis (8) of the working roll (2, 3) and at least partly surrounds the block (16) at its upper side.
2. Roll device according to claim 1, characterised in that a slide surface (14, 15) is arranged between the element (11), which produces pressure force, of the bending means (7) and the pressure transmission element (12) and/or between the pressure transmission element (12) and the projecting arm (9, 10) of the working roll chock (4, 5).
3. Roll device according to claim 1 or 2, characterised in that the pressure transmission element (12) is mounted at the roll stand (6) by means of a guide (18), particularly by means of vertical guide.
4. Roll device account to one of claims 1 to 3, characterised in that holding means (19) which hold the pressure transmission element (12) at the block (16) to be immovable in the direction (R) towards the working roll (2, 3) are arranged between block (16) and pressure transmission element (12).
5. Roll device according to one of claims 1 to 4, characterised in that the working rolls (2, 3) are provided with axial displacing means (20) for the axial displacement, by which the working rolls (2, 3) can be mounted in a desired axial position relative to the roll stand (6) and held there.
6. Roll device according to one of claims 1 to 5, characterised in that the length of the projecting arm (9, 10) of the working roll chock (4, 5) in the direction of the axis (8) of the working roll (2, 3) is large in relation to the length, which is measured in the direction of the axis (8), of the force transmission element (12) at its part connected with the projecting arm (9, 12), preferably at least twice as large.
7. Roll device according to one of claims 1 to 5, characterised in that the length of the projecting arm (9, 10) of the working roll chock (4, 5) in the direction of the axis (8) of the working roll (2, 3) is small in relation to the length, which is measured in the direction of the axis (8), of the force transmission element (12) at its part connected with the projecting arm (9, 12), preferably at most half as large.

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