EP0231875A2 - Axial shifting device for the work rolls of a flat material rolling stand - Google Patents

Abstract

In order to reduce the mechanical and control-related effort involved in the opposite axial displacement of work rolls, the push pieces (l5, l7) on the operator side, which engage on the chocks of the work rolls (l, 2), are provided with opposing racks (22) and provided with pinions (22 ) coupled in opposite directions. If the thrust pieces receive roller bending devices, the same counter-rotating gear coupling is also provided on the operating side of the rollers. A drive (25) for axially displacing the work rolls can also be connected to the synchronous pinion (22).

Description

The invention relates to a device for axially displacing the work rolls of a roll stand for rolling flat material, in particular work rolls with a corresponding bottle-shaped contour of the rolled bales, with horizontally guided thrust pieces arranged in stator-fixed blocks at least on the operating side, in pairs via vertical adjustment movements of the work rolls Allow releasable guides to engage positively on the outward projections of each chock, and with stator-mounted power drives on the operating side for axial displacement of the thrust pieces together with chocks and work rolls, the drive-side chocks of which are arranged along with the work rolls. Such a displacement device is described in DE-Al 33 3l 055, the thrust pieces simultaneously receiving the bending device for balancing and bending the work rolls. The power drives for the axial displacement of the thrust pieces together with the rollers can be arranged next to the thrust pieces, but the thrust pieces themselves can also form part of a power drive, for example a cylinder movable relative to a fixed piston rod.

Since the work rolls for strip edge-oriented axial adjustment have to be adjusted in opposite directions, a pair of reversible power drives, which were acted upon in opposite directions, were previously required for each work roll with regard to the axial roll change. This determination is independent of whether the thrust pieces also carry bending devices or not. Bending devices can also not be fixed to the stationary blocks when moving (DE-C3 22 60 256).

The invention has for its object to reduce the mechanical and control effort for the opposite axial displacement of work rolls. In addition to the pairs of power drives required by the operator for each work roll, control and monitoring units are also required in order to axially shift each work roll in accordance with the width of the flat material with a roll bale edge symmetrically to the vertical center plane of the roll stand lying parallel to the rolling direction on both work rolls - in opposite directions. These control and monitoring devices include, for example, position sensors, servo valves and limit switches.

The solution to the problem is according to the invention is that pairs of superimposed thrust pieces of different work rolls are provided with opposing racks and are coupled in opposite directions to one another via stator-mounted, with each pair of racks in engagement. This ensures that power drives and control and monitoring units are only required for one of the two work rolls, since the other work roll follows the displacement movements of the actively displaceable work roll in opposite directions and to the same extent. Neither thrust pieces nor synchronization pinions need to be provided on the drive side, as long as - as stated - accompanying bending devices are not to be considered.

It is also conceivable to bring about the opposite displacement movement of the work rolls via the pinions themselves. For this purpose, the pinions are expediently arranged in a floating manner on each of the stator-mounted pinion shafts with respect to the lateral expansion of the rollers, on which reversible power drives act, for. B. power cylinders or hydraulic motors.

If pairs of thrust pieces for receiving bending devices for balancing and bending the work rolls are assigned to each of the chocks of both work rolls, according to the further invention also the drive-side thrust pieces, which are not positively connected to chocks, are coupled with one another in opposite directions via racks and pinions, the one of the work rolls associated thrust pieces are operatively coupled via linkage parts to the operator-side thrust pieces which can be displaced in the same direction in order to drive the thrust pieces on the drive side in the direction of displacement. The gearing connection from one side of the stand to the other takes account of the fact that, on the drive side of the rolling stand, special power drives and form-fitting connections between thrust pieces and chocks are inappropriate for design reasons. On the other hand, it is possible to connect the pinions on the drive side to one another via a synchronous shaft so that the thrust pieces can be moved without tilting. This advantage can also be obtained in that the drive-side thrust pieces of each work roll are connected to one another via a synchronous crossbar.

Another possibility of gear coupling of push pieces which can be displaced on both sides of the work rolls is, according to a further proposal of the invention, that the four operator-side and drive-side pinions are each rotatably arranged on shafts that extend to the outside of the stand width, which are mounted on the outside of the stand spars and synchronized with one another in parallel via a parallelogram linkage. This solution naturally presupposes that the maximum adjustment angle of the pinion is less than 180 °, ie the maximum displacement path for the work rolls is not too great. This requirement is met if the work rolls have a corresponding, bottle-shaped contour in accordance with DE-Cl 30 38 865, since in such roll stands the maximum displacement path of rolls is less dependent on how large the occurring differences in the width dimensions of the flat material to be rolled are .

With this solution, too, it is advisable to connect the drive-side pinions via a synchronous shaft, just as the operator-side pinion shafts can be reversibly driven by power drives.

Another principle solution to the problem, which also leads to the fact that only one roller power drives and control and control units are provided on the operator side, according to the invention is that the drive-side pairs of thrust pieces of both rollers via stops from the drive-side chocks assigned to them exclusively are displaceable in the same direction of displacement, or vice versa. With this solution, each work roll, the chocks of which are arranged so that they cannot move on the roll neck, takes over the task of the rod parts for a geared connection between the thrust pieces of both roll ends. With regard to the arrangement of synchronization pinions between superimposed thrust pieces on both the operator and the drive side nothing changes with this solution, as will be explained in detail in the drawing description. Only if power drives are provided for each roller on the operator side, which are acted on in pairs in alternating fashion only with a single action, are there no need for the synchronization pinions on the operator side, as will be explained below.

• Fig. l eine teilweise Seitenansicht eines Quarto-­Walzgerüstes von der Bedienungsseite, die Schubstücke geschnitten, wobei die rechte Zeichnungshälfte hinsichtlich der Kraftantrie­be eine andere Lösung zeigt als die linke Zeichnungshälfte,
• Fig. 2 einen waagerechten Schnitt nach der Linie II-II in Fig. l für die rechte Zeichnungs­hälfte, die linke Zeichnungshälfte im waage­rechten Schnitt durch einen Ständerholm mit Draufsicht auf die Verschiebevorrichtung,
• Fig. 3 eine schematische Darstellung eines Quarto-­Walzgerüstes mit Biegeeinrichtungen für die Arbeitswalzen,
• Fig. 4 einen waagerechten Schnitt durch alle vier Ständerholme zur Darstellung von getrieblichen Gestänge-Verbindungen zwischen der Bedienungs- ­und der Antriebsseite des Walzgerüstes, in der oberen Hälfte eine andere Art von getrieblicher Verbindung als in der unteren Zeichnungshälfte,
• Fig. 5 einen waagerechten Schnitt durch alle vier Ständerholme mit Draufsicht auf die obere Arbeitswalze und die Verschiebeeinrichtung in einem weiteren Ausführungsbeispiel mit Biegeeinrichtungen für die Arbeitswalzen, und
• Fig. 6 einen Schnitt nach der Linie VI-VI in Fig. 5.

Several exemplary embodiments of the subject matter of the invention are shown in the drawing, namely:

• 1 is a partial side view of a four-high mill stand from the operating side, the thrust pieces cut, the right half of the drawing showing a different solution with regard to the power drives than the left half of the drawing,
• 2 is a horizontal section along the line II-II in Fig. L for the right half of the drawing, the left half of the drawing in a horizontal section through a stand spar with a plan view of the displacement device,
• 3 shows a schematic representation of a four-high mill stand with bending devices for the work rolls,
• 4 is a horizontal section through all four uprights to show gear linkage connections between the operating and the drive side of the roll stand, in the upper half a different type of gear connection than in the lower half of the drawing,
• Fig. 5 shows a horizontal section through all four uprights with a plan view of the upper work roll and the displacement device in a further embodiment with bending devices for the work rolls, and
• 6 shows a section along the line VI-VI in FIG. 5th

The four-high mill stand according to the various exemplary embodiments has two work rolls 1, 2, two support rolls 3, 4 as well as stand spars 5, 6 on the operator side and stand spars 7, 8 on the drive side (FIGS. 4 and 5). The work rolls 1, 2 are mounted on the operator side in chocks 9, 10 and on the drive side in chocks 11 such that the chocks follow the axial displacement movements of the work rolls. 5 shows a drive spindle l2 with clutch l3 for driving the upper work roll l.

Furthermore, it is common to all the exemplary embodiments that blocks which are fixed to the stand are arranged within the stand window at the level of the work rolls for the horizontal guidance of thrust pieces. According to FIGS. 1 and 2, the right half of the drawing, blocks l4 which are fixed on the operator side are provided, in which an upper pair of thrust pieces l5 are guided horizontally. With regard to the design of the thrust pieces l5 and their dovetail guide l6, there is no difference compared to the embodiment of the left half of the drawing. The same applies to the lower pair of thrust pieces l7. The stationary blocks l4 of the right half of the drawing are formed into cylinders l4a, in which pistons l8 which can be acted upon are guided, the piston rods l9 of which are connected to lateral arms l5a of the thrust pieces l5.

The thrust pieces l5 engage via vertical, releasable guides which permit the adjustment movements of the work rolls to form-fitting projections 9a of the operator-side chock 9 of the upper work roll 1, with controllable bolts 20 as shown in FIG. 1 of DE-Al 33 3l 055 as part of the vertical guidance are provided in order to be able to clear the projections 9a for axial roll removal towards the operating side. The same also applies to the lower thrust pieces l7 for axially displacing the lower work roll 2 together with the chock l0 on the operator side.

The double-acting power drives consisting of the cylinders l4a and piston l8 and piston rod l9 are only assigned to the upper work roll l or its thrust pieces l5. The lower thrust pieces l7 are coupled for the opposite axial displacement of the lower work roll 2 via pinions 2l with the thrust piece l5 lying above them. For this purpose, the thrust pieces l5, l7 of different work rolls lying one above the other in pairs are provided with opposing toothed racks 22, into which the pinions 2l arranged in a fixed manner in bearings 23 engage. The bearing 23 on the right half of the drawing in FIG. 2 cannot be seen.

The exemplary embodiment shown on the left half of the drawing in FIGS. 1 and 2 differs from the previously described exemplary embodiment in that the synchronization pinions 2l are each arranged in a floating manner on a pinion shaft 24 which is mounted on a stand and on which reversible power drives 25, which only act in FIG. l are shown. These power drives consist of power cylinders 25 which are arranged on the stator bars 5 and 6 in an oscillating manner, the piston rods 26 of which are articulated to lever arms 27 fastened to the pinion shafts 24.

For kinematic reasons, this type of power drive 25 allows a reversible rotary adjustment of the pinion 2l only to an extent of less than 180 °. Although the choice of the diameter of the pinion 2l can influence the opposing adjustment paths of the thrust pieces l5 and l7 and thus the work rolls l and 2, these possibilities are limited, so that the extent of the axial adjustment of the work rolls is primarily for is designed such work rolls, which have a corresponding bottle-shaped contour, or for substantially cylindrical work rolls, if the differences between the occurring rolling stock widths are not too great from the rolling program.

In both exemplary embodiments according to FIGS. 1 and 2, only a pair of power drives 14 a, 18, 19 and 25 are required for axially displacing the work rolls 1, 2. No thrust pieces are required on the drive side of the roll stand, not shown, since in the previously described exemplary embodiments the thrust pieces do not also carry the bending devices for the work rolls.

3 shows schematically the case in which the operator-side thrust pieces l5 and l7 are to be provided as thrust pieces 30 and 3l which can be displaced in the same direction, also on the drive side of the roll stand, since all thrust pieces are provided with diametrically acting pressure plungers 32 from bending devices which are attached to them attack, not shown, overlapping claws of the chocks. In addition to the operator-side pinions 2l with toothed racks 22, such synchronization sprockets 33 with toothed racks 22 are also provided on the drive side, which are expediently connected to one another via a synchronous shaft 34.

Provided that either the upper pair of thrust pieces l5 or the lower pair of thrust pieces l7 can be actively displaced by reversible power drives on the operating side, in the exemplary embodiment according to FIG. 3 the lower thrust pieces 3l, which are assigned to the lower work roll 2 on the drive side, Coupled via linkage parts 35 with the operator-side, shiftable push pieces l7. These linkage parts 35 could also be arranged between the upper pairs of thrust pieces 15 and 30. In any case, due to the synchronization pinions 33, an adjustment movement is transmitted in opposite directions to the other pair of thrust pieces 30 on the drive side and thus also to the other work roll 1 via chocks, not shown.

Two other possibilities for a gear coupling between push pieces which can be displaced in the same direction are shown in FIG. 4. Similar to that already described in connection with FIGS. 1 and 2, all four synchronization pinions 2l and 33 are overhung on pinion shafts 24, which are mounted in stator-mounted bearings 23. In the exemplary embodiment according to the upper half of the drawing in FIG. 4, the pinion shafts 24 on the operating side are each coupled to the pinion shafts 24 on the drive side for the same direction of rotation via a parallelogram linkage 36, 37. A geared connection exclusively via rotary shafts is shown in the lower half of FIG. 4, in which the pinion shafts 24 are coupled to one another via bevel gear pairs 38 and a synchronous shaft 39, which also extends outside the stator columns 6 and 8, as does the parallelogram linkage 36, 37 in the upper half of the drawing runs outside of the pillars 5 and 7. In the solution according to FIG. 3, to which the exemplary embodiments according to FIG. 4 belong, the pinions 2l can be driven on the operator side via power drives, for example via schematically illustrated hydraulic motors 40 (FIG. 4).

In connection with the embodiment of FIG. 3 it should be noted that the drive-side pairs of thrust pieces 30, 3l are not provided with positive connections to the associated chocks. The opposite displacement of the drive-side thrust pieces 30, 3l serves only for the purpose that the bending devices with the pressure plungers 32 follow the shifting movements of the work rolls, which are geared from the operating side, so that the bending devices are also "moving" on the drive side.

In the exemplary embodiment according to FIGS. 5 and 6, the operating side on the left does not differ significantly from the exemplary embodiment according to FIG. 2, right half of the drawing, as far as the form-fitting vertical guidance between the operating-side chock 9 of the upper work roll 1 and the push pieces 46 and 47 is concerned. The difference is that the thrust pieces 46 (and also the thrust pieces 47 of the lower work roll 2) do not directly form the vertical guide surfaces for the chocks, but rather the detachable covers 42a of blocks 42 fixed to the stand, in which the thrust pieces 32 provided with bending devices 32 are guided in a piston-like manner. The power drives for actively moving either the upper operator-side chock 9 or the lower chock 10 (FIG. 1) are different from the outside, double-acting power cylinders 43 compared to FIGS. 1 and 2. The decisive factor in the embodiment according to FIGS. 5 and 6 is the fact that the work rolls 1 and 2 with their chocks 9, 10 and 11 (right drive side) firmly seated on the roll neck take over the task of the linkage parts 35 from FIG. 3.

This is due to the fact that the drive-side thrust pieces 44, 45 are provided with inwardly directed stops 44a, 45a, which lie in the adjustment path of stop lugs 11a of the chocks (for both rollers). Thus, when the chock II of the upper work roll 1 is shifted from the operating side to the right, the upper pair of thrust pieces 44 are taken along. Under the synchronizing action of the pinion 33, the lower pair of thrust pieces 45 is adjusted in opposite directions and takes the lower chock 11 with the lower work roll 2 via the stops 45a. When the upper work roll 1 is axially displaced to the left, the synchronization pinions 2l (not shown) on the operating side cause the lower thrust pieces 47 to be moved in opposite directions and, via their form-fitting connection to the chock 10, the lower work roll 2 is displaced to the right. Even then, the lower thrust pieces 45 are taken along from the lower drive-side chock 11 via the stop lugs 11a, the upper thrust pieces 44 following the movement of the upper chock 11 to the left via the drive-side pinions 33, so that the stops 44a and the stop lugs 11a always in Stay in contact, even though the interacting stops are only equivalent to a pressure-resistant connection. Since the work rolls are now virtually clamped on both sides, it is advisable to provide the synchronizing pinion with stressed tooth play due to the length tolerances of the rolls and the thermal expansion occurring during operation.

The operator-side pinions 2l are not required if - with only pressure-resistant stop conditions on the drive side - power drives are provided for each work roller on the operator side that are only single-acting and are acted on in pairs alternately.

This solution brings with it considerable advantages in terms of control, because when the power drives of one roller are acted upon, the power drives of the other roller are mechanically reversed due to the drive-side synchronization pinion 33 and the linkage effect of the rollers. Length tolerances of the rolls and thermal expansion are eliminated by the pressure medium of the power drives.

Returning to the already mentioned chock-side cover 42a of the stand-fixed blocks 42 in the exemplary embodiment according to FIGS. 5 and 6, it should be noted that this enables the configuration of the upper thrust pieces 44 and 46 as shown in FIG. 6, since the cover 42a is removed when the cover 42a is removed their leadership can be installed in the block. As explained with reference to the left-hand side of FIG. 6, the push pieces 46, which are rectangular in cross section, have outwardly directed cutouts 46 a, which are penetrated by webs 42 b of the block 42 fixed to the stand. These webs 42b, which extend transversely and up to the cover 42a, serve to stiffen the block 42 in order to prevent the mobility of the thrust piece 46 from being impaired by jamming its guide.

Claims (11)

1.Device for axially displacing the work rolls of a roll stand for rolling flat material, in particular work rolls with a corresponding bottle-shaped contour of the rolled bales, with horizontally guided thrust pieces (l5, l7) arranged in stator-fixed blocks at least on the operating side, which are arranged in pairs via vertical die Engage detachable guides (l6) that allow the working rollers to move against form-fitting projections (9a) of each chock (9, l0) facing outwards, and with stator-mounted power drives (l8, l9) on the operating side to axially move the thrust pieces and chocks (9, l0) and work rolls (l, 2), the drive-side chocks (ll) of which are arranged along with the work rolls,
characterized in that thrust pieces (l5, l7) of different work rolls lying one above the other are provided with opposing racks (22) and are coupled in opposite directions to one another by means of pinions (2l) which are fixed to the stand and are in engagement with a pair of racks. 2. Apparatus according to claim l, characterized in that the pinions (2l) on a stator-mounted pinion shaft (24) are arranged overhung, on which reversible power drives (25) engage. 3. Device according to claim l or 2, with each of the chocks (9, l0, ll) associated pairs of thrust pieces (l5, l7, 30, 3l, 44, 45, 46, 47) for receiving bending devices (32) for balancing and bending the work rolls (l, 2),
characterized in that the drive-side thrust pieces (30, 3l, 44, 45) connected in pairs and one above the other to chocks (ll) are coupled in opposite directions via racks (22) and pinions (33), and that one of the work rolls assigned thrust pieces are coupled via linkage parts (35) to the operator-side thrust pieces (l7) which can be moved in the same direction (FIGS. 3, 5, 6). 4. The device according to claim 3, characterized in that the drive-side pinions (33) are connected to one another via a synchronous shaft (34). 5. The device according to claim 3, characterized in that the drive-side thrust pieces (30, 3l) of each work roll (l, 2) are connected to one another via a synchronous crossmember. 6. The device according to claim 3, characterized in that the four operator-side and drive-side pinions (3l, 33) are each rotatably arranged on shafts (24) extending to the outside of the stator width, which are mounted on the outer sides of the stator spars (5-8) and are synchronized with one another in parallel in each case via a parallelogram linkage (36, 37) (FIG. 4). 7. The device according to claim 6, characterized in that the drive-side pinion (33) via a synchronous shaft (34) are connected. 8. The device according to claim 7, characterized in that the operator-side pinion shafts (2l) are driven reversibly. 9. The device according to claim 3, characterized in that the drive-side pairs of thrust pieces (44, 45) of both rollers (l, 2) via stops (44a, 45a) from the drive-side chocks (11) assigned to them can be displaced exclusively in the same direction of displacement are, or vice versa (Fig. 5, 6). l0. Apparatus according to claim 9, characterized in that for each roller (1, 2), in pairs, alternating single-acting power drives (43) are provided on the operating side and the synchronization pinions (2l) are omitted on the operating side. 11. Device according to one of the preceding claims, characterized in that the stand-fixed blocks (42) for the lateral installation of the thrust pieces (46) guided therein are open on the chock side and can be closed with a cover (42a), and in that the thrust pieces have outwardly directed cutouts (46a), which are penetrated by webs (42b) of the blocks directed transversely to the cover, which reach up to and support the covers.

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