EP1286793B1 - Multiple-roll rolling mill for strip material - Google Patents

Description

The invention relates to a multi-roll rolling mill for strip material, in particular steel strips, with work rolls which are supported on the stand of the rolling mill via support rollers. In such multi-roll mills, the work rolls are generally supported by intermediate rolls arranged between the support rolls and the respective work roll. The support rollers are usually mounted at regular intervals along the work or intermediate roller on a support axis extending parallel to the axis of rotation of these rollers.

Multi-roll mills of the type mentioned above are usually equipped with adjusting devices for influencing the geometry of the roll gap. The roll gap geometry has a direct influence on the shape of the rolled material.

A roll support device for correcting the roll gap of a multi-roll mill is known for example from DE 41 31 571 A1. In this known device, actuators engage in the free spaces between the support rollers, which are guided in the stand of the rolling mill so as to be displaceable transversely to the longitudinal extent of the support axis. The actuators are divided into two groups of the same number so that the first group is assigned to a length section which is the first half of the The longitudinal extent of the support axis corresponds, while the other group is assigned to the length section corresponding to the second half of the support axis.

The actuators of the two groups are articulated together with one coupling member each. The two coupling links extend essentially parallel to the support axis and are articulated with their end assigned to the end of the support axis on the stand of the rolling mill. At its other end, which is assigned to the center of the supporting axis, the coupling elements are connected to a common actuator which pivots the coupling elements via a hydraulically operating adjusting cylinder which can be moved transversely to the supporting axis and thus causes an adjustment of the actuating elements and, consequently, a bending of the supporting axis. This deflection is transferred to the work roll via the support rollers mounted on the support axle, so that a corresponding shape of the roll gap is established.

The advantage of the device known from DE 41 31 571 A1 is that the desired different position change of the actuators and, accordingly, the setting of the roll gap can be carried out with only a single actuator. In this way, the outlay on equipment and costs for the support device is reduced to a minimum. However, it is disadvantageous that only a roll gap course can be set in which the height of the roll gap changes linearly starting from its outer ends in the direction of the center of the roll gap. Roll gap geometries deviating from the linear course cannot be realized due to the fixed coupling of the movement of the actuators of both groups. This limited Adjustability proves to be a disadvantage, particularly in the case of cold rolling of steel strips, in which, among other things, to compensate for the deformations of the work rolls caused by the rolling forces, a non-linear course of the roll gap opening is required to produce a product with uniform stretching.

In order to allow the roll gap to be freely adjustable, it has been decided to assign a separate actuator to each individual actuator. In this case there is no longer any mechanical coupling between the actuators by means of a coupling member, so that any shape of the roll gap required in practice can be set by a corresponding adjustment of each individual actuator. The disadvantage here is the high cost and control effort that must be applied for the manufacture and operation of the actuators.

On the basis of the prior art explained above, the object of the invention is to provide a multi-roll mill stand in which extensive adjustment of the roll gap is made possible by an inexpensive support device.

This object is achieved by a multi-roll rolling mill for strip material, which is equipped with work rolls, which are supported on support rollers via any intermediate rolls, which are each rotatably mounted on a support axis divided into at least three longitudinal sections, and is equipped with at least one actuating device is assigned to at least one of the support axes and comprises actuators, one of which is one of the longitudinal sections of the Support axis is assigned and, via a group of actuators coupled to one another via a coupling element with regard to their movement relative to the support axis, the respective longitudinal section is subjected to a force directed transversely to the longitudinal direction of the support axis for correcting the roll gap between the work rolls.

In a multi-roll mill stand according to the invention, the supporting axis is divided into at least three longitudinal sections, each of these longitudinal sections being assigned its own actuator. This actuator exerts the force required to influence the roll gap geometry via a group of actuators on the supporting axis. Each of these groups comprises two or more actuators, the movement of which is mechanically coupled to one another transversely to the supporting axis via a coupling element. Since there is no mechanical coupling between the groups at the same time, each group of actuators can be adjusted independently of the other groups by the respective actuator. In this way, depending on the number and distribution of the actuator groups, a large number of different roll gap geometries can be set without the need for separate control of each individual actuator by a separate actuator, as in the prior art.

Thus, the invention makes it possible in the case of rolling mills which are significantly reduced in comparison with conventional, largely free adjustability of the roll gap, and in a variety of setting options which is considerably increased in comparison with rolling mills with a fixed predetermined adjustability of the roll gap a targeted setting of an optimal roll gap geometry for practical operation. It can be seen that the adjustability of the roll gap geometry provided by the invention is sufficient for the vast majority of the requirements that arise in practice.

Since the roll gap geometry required in practical operation usually has a course which is symmetrical in the longitudinal extent, it is advantageous if the support axis is divided into longitudinal sections arranged symmetrically starting from the center of the longitudinal extent of the support axis. In this context, it is advantageous if there is a longitudinal section arranged centrally to the center of the longitudinal extent of the support axis and the actuator assigned to this longitudinal section has the coupling member of the group of actuators assigned to this longitudinal section at a position positioned in alignment with the center of the longitudinal extent with the point generated by the actuator Force applied.

A further embodiment of the invention, which is likewise advantageous for certain applications, is characterized in that, in the case of at least one group of actuators which are coupled to one another, the associated actuator drives the coupling element at a point offset from the center of the longitudinal extent of the length section assigned to the group with the force generated by the actuator applied. This introduction of the actuating forces into the respective coupling element proves to be expedient in particular in those coupling elements via which the respective actuators of the groups connected to the two at the outer ends of the Support axis arranged longitudinal sections are assigned, are connected to each other when these coupling links are each articulated on the stand of the rolling mill. Due to the mounting of the respective coupling member of the groups of actuators arranged at both ends of the supporting axis, a course of the deflection in the relevant length section of the supporting axis automatically arises due to the lever laws, which assumes an always identical starting position at the end of the supporting axis. Starting from this starting position, the degree of change in position of the support axis in the direction of the axis center, which is achieved when the actuators are adjusted, so that a bending curve of the support roller which counteracts the deformation of the work roll during the rolling operation is generated in the edge regions.

As in the prior art, it will also be advantageous in connection with the present invention if the support members are arranged at regular intervals along the support axis. In this way, an equally uniform support of the work roll is achieved.

Fig. 1

eine Walzenstützvorrichtung in einer frontalen Ansicht;

Fig. 2

einen Ausschnitt eines mit der Walzenstützvorrichtung gemäß Fig. 1 ausgestatteten Vielwalzen-Walzwerks im Schnitt entlang der Linie X-X der Fig. 1;

Fig. 3

das Vielwalzen-Walzwerk in einem Schnitt entlang der Linie Y-Y der Fig. 2.

The invention is explained in more detail below on the basis of a drawing illustrating an exemplary embodiment. Show it:

Fig. 1

a roller support device in a frontal view;

Fig. 2

a section of a with the roller support device according to FIG. 1 equipped multi-roll mill on average along the line XX of Fig. 1;

Fig. 3

the multi-roll mill in a section along the line YY of FIG. 2nd

The multi-roll mill W has work rolls 1, 2. Between the work rolls 1, 2, a roll gap 3 is formed, in which, for example, a steel strip S is cold rolled.

The work rolls 1, 2 are each supported on intermediate rolls 4, 5 on support rolls 6, 7, 8, 9, 11, 12, 13, 14, 15, 16a, 16b, of which nine each at regular intervals a on one Support axis 17,18,19,20 are rotatably mounted. In FIG. 2, of the nine support rollers mounted on the support axes 17, 18, 19, 20, only those support rollers 6, 7, 8, 13 are shown which are visible in accordance with the section line XX indicated in FIG. 1, while in FIG. 3 for the support axle 18, all nine support rollers 9 to 16b mounted on this support axle 18 are shown. Of course, other support rollers can be provided, which are supported in the same way on the support axes 17 to 20.

As can be seen from FIGS. 2 and 3, in each of the spaces between the support rollers 9 to 16b, a thrust member 21 engages on the supporting axis 18. The thrust members 21 are mounted on the stand 22 of the rolling mill W so as to be displaceable in the horizontal direction and via a wedge gear 23 coupled with vertically movable rod-shaped actuators 24, 25, 26, 27, 28, 29, 30, 31 guided in the frame 22. About the wedge gears 23, a movement of the actuators 24 to 31 in the vertical direction is converted into a horizontal movement of the thrust member 21 assigned to the respective actuator 24 to 31.

The actuators 24 to 31 are combined in groups G1, G2, G3, with the first three actuators 24, 25, 26, the second group G2, the actuators 27, 28 and the third, starting with one end of the support axis 18 of the first group G1 Group G3 the actuators 29,30,31 are assigned. Each group G1, G2, G3 is in turn assigned a length section L1, L2, L3 of the supporting axis 18. The length sections L1, L2, L3 directly adjoin one another and are oriented symmetrically with respect to the longitudinal extent of the support axis 18 to the center M of the support axis 18, the length of the outer length sections L1, L3 being greater than the length of the length section arranged between these length sections L1, L3 L2.

The actuators 24, 25, 26 belonging to group G1 are articulated with their end facing away from the respective wedge gears 23 with a coupling member 32 which extends essentially axially parallel to the support axis 18 and with an end associated with the end of the support axis 18 in an articulated manner on the frame 22 of the rolling mill is stored. In the same way, the actuators 29, 30, 31 of the group G3 assigned to the other end of the support axle 18 are coupled together with a coupling member 33, which is also articulated on the stand 22 of the rolling mill W with its end assigned to the relevant end of the support axle 18. The actuators 27, 28 of the middle group G2, on the other hand, are together with a coupling member 34 which is not supported on the frame 22.

At the respective end of the coupling members 32, 34 opposite the articulated support on the frame 22, each of these coupling members 32, 34 is articulated to a piston rod of a hydraulically operating actuator 35, 37. The coupling member 33 of the middle group G2 of the two actuators 27, 28, however, is connected to the piston rod of a hydraulic actuator 36. The piston rod of the actuator 36 is arranged centrally to the longitudinal extent of the support axis 18, so that the force generated by the actuator 36 is distributed substantially uniformly among the actuators 27, 28. In contrast, the force generated by the actuators 35, 37 is transmitted non-uniformly to the actuators 24 to 26 or 29 to 31 of the respective group G1 or G3 in accordance with the lever law.

The thrust members 21, the wedge gear 23, the actuators 24 to 31, the coupling members 32, 33, 34 and the actuators 35, 36, 37 are part of the actuating device for adjusting the supporting forces applied by the support rollers 9 to 16b. To adjust the support rollers 6, 7, 8 arranged on the support axles 17, 19, 20, separate actuating devices of the same type, not explained in detail here, can be provided.

When adjusting the geometry of the roll gap 3, the actuators 35, 36, 37 exert separately from one another on the groups G1, G2, G3 of actuators 24 to 31 that are assigned to them. These actuating forces are converted via the wedge gear 23 into bending forces, which in the act substantially transversely to the support axis 18 on this. According to the different distribution of the applied forces, the support shaft 18 deforms. This deformation is transmitted to the upper work roll 1 via the intermediate rolls 4, 5, so that the roll gap geometry is directly influenced by the adjustment of the actuators 35, 36, 37.

LIST OF REFERENCE NUMBERS

1.2

strippers

3

nip

4.5

intermediate rolls

6 to 16b

support rollers

17,18,19,20

axles

21

pusher member

22

Stand of the W rolling mill

23

spline gear

24 to 31

actuators

32,33,34

coupling members

35,36,37

actuators

a

axial distance between two support rollers

G1, G2, G3

Groups of actuators 24 to 30

L1, L2, L3

Length sections of the supporting axis 18

M

Center of the support axis 18

S

steel strip

W

Multi-roll mill

Claims (7)

1. A multiple-roll rolling mill for strip material having work rolls (1, 2), which are supported, via possibly existing intermediate rolls (4, 5), on backup rolls (6, 7, 8, 9 - 16b), which are each rotatably mounted jointly on a support axle (17, 18, 19, 20), divided into at least three longitudinal sections (L1, L2, L3), and having at least one actuating device, which is assigned to at least one of the support axles (18) and includes actuator drives (35, 36, 37), each one of which is assigned to one of the longitudinal sections (L1, L2, L3) of the support axle (18) and has a force directed transversely to the longitudinal direction of the support axle (18) applied to the respective longitudinal section (L1, L2, L3) via a group (G1, G2, G3) of actuators (24, 25, 26; 27, 28; 29, 30, 31), which are coupled to one another via a coupling element (32, 33, 34) in regard to their movement in relation to the support axle (18) to correct the roll gap (3) between the working rolls (1, 2).
2. The multiple-roll rolling mill according to Claim 1, characterized in that the support axle (18) is divided into longitudinal sections (L1, L2, L3), which are symmetrically arranged starting from the middle of the longitudinal extension of the support axle (18).
3. The multiple-roll rolling mill according to Claim 2, characterized in that there is a longitudinal section (L2), which is positioned in alignment to the middle (M) of the longitudinal extension of the support axle (18), and the actuator drive (36) assigned to this longitudinal section (L2) applies the force, generated by the actuator drive (36), to the coupling element (33) of the group (G2) of actuators (27, 28) assigned to this longitudinal section (L2) at a location positioned in alignment to the middle of the longitudinal extension.
4. The multiple-roll rolling mill according to one of the preceding claims, characterized in that, in at least one group (G1, G3) of actuators (24, 25, 27; 29, 30, 31), which are coupled to one another, the assigned actuator drive (35, 37) applies the force, generated by the actuator drive (35, 37), to the coupling element (32, 34) at a location offset in relation to the middle of the longitudinal extension of the longitudinal section (L1, L3) assigned to the group (G1, G3).
5. The multiple-roll rolling mill according to one of the preceding claims, characterized in that at least the coupling elements (32, 34), via which the respective actuators of the groups (G1, G3) which are assigned to the longitudinal sections (L1, L3) positioned at the outer ends of the support axle (18) are connected to one another, are mounted on the stand (22) of the rolling mill (W) in an articulated way.
6. The multiple-roll rolling mill according to one of the preceding claims, characterized in that the backup rolls (6, 7, 8, 9 - 16b) are positioned at regular intervals (a) along the support axle (18).
7. The multiple-roll rolling mill according to one of the preceding claims, characterized in that the actuator drives (33, 34, 35) operate hydraulically.