JPH059165B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention comprises a bending device for an intermediate roll that is axially slidable between a back-up roll and a work roll, the adjustment means for the intermediate roll being horizontally slidable. This invention relates to a six-fold roll stand that is adjustable parallel to the roll axis.

A roll stand of this type already belongs to the known technology from European Patent No. 0 026 903. A similar roll stand has a British patent no.
This is already known from Publication No. 7608285.

By displacing the intermediate roll in the axial direction, it is possible to use the known roll stands for rolling strips with large width variations. In this case, cylindrical polished work rolls are used, and the distance between the rolls is adjusted by means of adjustment means which act as a roll bending device.

In the known roll stand according to European patent no. Built between possible transverse beams. This means that these adjusting means act directly on the chock of the intermediate roll, so that horizontal forces occurring during the rolling operation or during roll changes have an adverse effect on these adjusting means. The arrangement of this known adjustment means also creates problems when replacing the backup roll.

In the case of the roll stand according to British Patent No. 7608285, the adjustment means acting as a roll bending device are provided in a block reinforcing the stand, and the bending of the free end portion of the work roll which projects from the rolled material is provided. It acts on the work roll chock because it has an antagonistic effect on the work roll. In this known roll stand, adjustment means are also provided in the block for the upper intermediate roll, which act on the chock of this intermediate roll. In this case, the adjustment means are provided in such a way that they serve to balance the load on the upper intermediate roll and to enable lifting of the intermediate roll from this work roll if the work roll has to be changed. provided and so configured that it can be used not only as a bending device for the upper intermediate roll in order to achieve additional adjustment between the rolls between both work rolls; There is.

The essential disadvantage of the roll stand according to GB 7,608,285 is that the adjustment means, which can also be used as a bending device for the upper intermediate roll, have on the one hand a fixed relative position to the bracket reinforcing the stand. On the other hand, it acts directly on the chock supporting the intermediate roll. That is, the axial sliding of the intermediate roll between the back-up roll and the work roll, which is carried out in order to achieve adaptation to rolled materials of different widths, is forced by the adjustment means acting as a bending device and the jocks of the intermediate roll. causing a corresponding relative movement between. As a result, the operating conditions of the adjusting means acting as a roll bending device on the chock of the intermediate roll also differ each time the intermediate roll performs a sliding movement in the axial direction. These operating conditions are difficult to control and have a negative effect on the rolling results.

That is, even in the case of the roll stand according to the above-mentioned European Patent No. 0026903 and the roll stand according to the above-mentioned British Patent No. 7608285,
The adjustment means assigned to the intermediate roll as a bending device are in direct contact with the chock of the intermediate roll and are therefore protected against biasing forces occurring during the rolling operation and when changing the rolls. be exposed without any problems.

German Patent Application No. 1289811 discloses, in a roll stand with two back-up rolls and two work rolls, i.e. a quadruple rolling stand, an adjustment means acting as a bending device in the chock of the work rolls. ,
It is already known to provide this adjustment means in such a way that it can work without affecting the roll stand. In this case, the chock of the work roll can be moved horizontally, parallel to the roll axis,
and is engaged with adjustment means forming a bending device. However, this only serves the purpose of guaranteeing a problem-free replacement of the intermediate rolls, and only prevents contradictory sliding in the axial direction of the work rolls for adaptation to different widths of the rolled material. Not.

A quadruple rolling stand, that is, a roll stand equipped with two back-up rolls and two work rolls, is likewise known from German Patent Application Publication No. 2250953. In this case, the chock of the work roll is movably engaged in a horizontal direction parallel to the rolling axis with guide pieces, and these guide pieces are provided in a block reinforcing the stand so as to be movable with respect to each other in a perpendicular direction. There is. Adjustment means as bending devices for the work rolls are provided between each of the two guide pieces which are arranged one above the other. In this configuration as well, the working connection which allows horizontal sliding between the work roll chock and the vertically movable guide piece in the block reinforcing the stand allows each work roll to be moved individually and quickly. It is merely intended to be interchangeable.

Furthermore, Japanese Patent Application No. 128732 (1982)
66307), a rolling mill configured to control the shape of a material to be rolled is known. This rolling mill is provided with a means for moving the intermediate roll in the axial direction and a means for applying roll bending force to the intermediate roll, and these means are configured to interact with each other, and the workpiece is The above configuration is also used for the rolls. The jocks for work rolls mainly have bearings for supporting radial loads, and are equipped with a mechanism that can directly thrust support the work rolls so as to support thrust loads acting on the work rolls.

The object of the invention is to create a roll stand of the type mentioned at the outset, which is suitable for rolling plates with significantly different widths, with the lowest possible Hertzian contact pressure between the work roll and the intermediate roll. The structure is designed so that it is possible to perform rolling operations to accommodate all strip widths that can be rolled under constant working conditions, and to select the optimal diameter of the work roll and intermediate roll. The object of the present invention is to be constructed in such a way that the horizontal lateral forces that occur during the roll change have no influence on the bending device and that a problem-free change of the work roll and the intermediate roll is ensured.

This problem is solved according to the invention by means of two different roll stand configurations.

In this case, the features of the first roll stand are as follows. - the adjustment means are arranged between the housing side parts and the choke side parts which are slidable perpendicularly to each other of the guide pieces of the block reinforcing the stand; - the housing side parts form a block; - in each case one chock side part of the guide piece is provided with a horizontal guide oriented in the horizontal direction for the chuck of the intermediate roll next to the housing side part; - in each case two of the adjusting means the adjustment means are arranged at a distance in the axial direction of the intermediate roll between the chuck side part and the housing side part of the guide piece, and - the position of action of the adjustment means in the guide piece can be changed in the horizontal direction; That is, .

Another feature of the six-layer roll stand according to the present invention is as follows. - the adjustment means are provided between the intermediate member and the choke side member which are held on the housing side member so as to be slidable in the axial direction along the housing side member of the guide piece; the chock-side part is provided with a horizontally oriented horizontal guide for the chock of the intermediate roll; - the housing-side part forms a block; - the chock-side part of the guide piece is provided with a horizontal guide for the chock of the intermediate roll; - the housing side part forms a block; is locked against horizontal sliding with respect to the chock of the roll, and so that the adjustment means, with respect to its operating position, is horizontally with the chock of the intermediate roll and in the axial direction of the intermediate roll on the housing side member of the guide piece; It is possible to change .

The design of the roll stand according to the invention has the advantage, on the one hand, that the wear of the work rolls is low. This is because the work roll is not corrected around the edges of the intermediate roll. On the other hand, however, there is also the advantage that the bending force of the axially movable intermediate roll is constant over the entire width of the sheet to be rolled. Moreover, the sliding conditions for the intermediate rolls are also significantly guaranteed. This is because the adjusting forces that occur in this case have no effect on the adjusting means, which acts completely as a bending device.

Furthermore, it has been found that a high safety against shell cracking is achieved due to the favorable Hertzian contact pressures and high temperature gradients (high material tensions) that can be achieved in the work rolls.

The arrangement according to the invention also avoids mutual interference with the available construction spaces, thus making it possible not only to select an optimal diameter of the work roll and the intermediate roll, but also to ensure effective force transmission for bending-correction forces. There are no restrictions in terms of system configuration. That is,
There are no problems with dimensions.

With the configuration of the first roll stand described above, it is advantageously possible to keep the bending force of the axially movable intermediate roll constant for all rolling conditions. This is because, in this roll stand, the adjustment forces of the two adjusting means, which are arranged one after the other at a distance, can be varied depending on the respective sliding position of the intermediate roll chock. It is.

In the configuration of the first roll stand mentioned above,
It has been found advantageous to integrate the adjusting means forming the bending device in the housing side part of the guide piece and to attach it to the chock side part. This means that the supply of pressurized medium to the regulating means can then be carried out at a particularly low cost.

In both designs of the roll stand according to the invention, the adjusting means forming the bending device consist of hydraulically loadable piston-cylinder units, which are connected to one of the guide pieces. It is built inside the
The other piston rod is attached to the other guide piece.

With respect to the positive or negative bending action of the intermediate roll, the piston-cylinder unit is designed to perform a double-acting action and to act with tension and compression resistance between the parts of the two guide pieces. is important.

The arrangement according to the invention is not only suitable for six-fold roll stands in which all rolls, ie work roll, intermediate roll and back-up roll, are located in a common vertical plane, but also in cases where the work roll is connected to the intermediate roll and the back-up roll. For example, in the German Federal Republic Patent No.
It can also be used in the six-layer roll stand known from Publication No. 2522213.

The guide piece, which is vertically slidably guided in the block reinforcing the stand and is provided with adjustment means forming a bending device, is moved by means of the chock of the intermediate roll and an advantageously horizontal guide piece. They are connected in one piece in the vertical direction, with the horizontal guide strips for the roll changing device being connected parallel to the rolls between the roll stands. In this way an extremely compact guide piece with bending device, which hardly exceeds the dimensions of the chock for the intermediate roll, and thus an optimum diameter selection for the work roll and the intermediate roll, is achieved. A favorable structure is achieved. The smallest diameter of the intermediate roll is limited only by the structural height of its chock and of the guide piece provided between this chock and the stand.

The roll stand according to the invention furthermore makes it possible by simple means to improve the quality of the plate shape and to optimize the contact position between the work roll and the intermediate roll, on the one hand, and the contact position between the intermediate roll and the back-up roll, on the other hand. It is possible to achieve an effective enlargement of the bending-correction area, which allows a strong contact pressure. The advantage of this invention is that the chock of both work rolls is assigned an adjusting means as a bending device which is arranged in the block, which adjusting means is arranged on a guide piece which itself is vertical on the one hand. This is achieved by being held in the block via a horizontal guide piece and, on the other hand, by providing a horizontal guide piece for the chock.

A special advantage of such a configuration is that the quality of the sheet shape is increased due to the simultaneous action of the bending devices installed separately on the intermediate roll and the work roll, and that the contact position between the work roll and the intermediate roll as well as the Separate controllability of the contact pressure at the contact location between the back-up rolls makes it possible to reduce roll wear and in that the stresses on the rolls and the bearing loads on the rolls are reduced.

Moreover, it is important that, on the one hand, the bending of the intermediate rolls induces back-up roll profile modifications and, on the other hand, that the bending of the work rolls can be used for process control.

In order to enable each work roll to bend independently of the other work roll and without dependence on intermediate rolls, another feature of the invention provides that each of the guide pieces is connected between the housing side member and the work roll. and a chock-side part associated with the chock, in which case adjustment means forming a bending device are provided between these two parts.

These housing-side parts of the guide strips are disposed vertically and slidably relative to each other, while the chock of the work roll is slidable horizontally relative to the chock-side parts of the guide strips associated therewith. It is movable.

The adjustment means forming the bending device are integrated in the housing-side part of the guide piece and are provided on the chock-side part of the guide piece. The adjustment means forming the bending device are arranged in the chock-side part of the guide piece and can be arranged in the housing-side part of this guide piece.

According to the invention, the adjusting means associated with the chock of both work rolls can be adjusted by means of a hydraulically loadable iston.
It is also noted that the guide piece consists of a cylinder unit, which piston-cylinder unit is integrated into one housing side part and one choke side part of the guide piece, and whose piston rod is arranged in the other choke part and housing part. This is an important configuration.

These adjustment means are also designed for double action and are tension-resistant and compression-resistant between the two parts of the guide piece. The housing-side parts of the guide pieces for chocking the work rolls are provided with reaction parts in the blocks of the roll stand, via which the housing-side parts of the guide pieces are moved against each other and/or against the blocks. It is possible to determine the relative motion to. In this case, these adjustable reaction forces may consist of piston-cylinder units which are integrated in the housing side of the guide piece.

For the guide piece containing the bending device for the work roll, a very compact construction is achieved which hardly exceeds the dimensions of the work roll chock and is therefore also advantageous for selecting the diameters of the work roll and intermediate roll. It will be done.

Other features and advantages of the invention will be described in detail below with reference to the embodiments illustrated in the accompanying drawings.

The roll stand shown in FIG. 1 has two roll housings 1 which are arranged side by side with a distance in the usual manner. Of these roll housings, only one roll housing is shown in FIG. Inside these roll housings 1 are two work rolls 2, 3, two intermediate rolls 4, 5 and two back-up rolls 6, 7.
is accommodated. A so-called six-layer roll stand is therefore formed. The upper backup roll 6 and the lower backup roll 7 are directly connected to both housings 1 via their jocks 8 and 9.
is held and guided within the housing window 10 of. In this case, a roll stand lowering device 11 is attached to the chuck 8 of the upper backup roll 6.

In the choke area of the work rolls 2 and 3 and the intermediate rolls 4 and 5, blocks 12 are provided in the housing windows 10 of both roll housings 1 to provide strength to the housings. Between these blocks, the chucks 13 and 14 of the two work rolls 2 and 3 are accommodated on the one hand, and the chucks 15 and 16 of the intermediate rolls 4 and 5 on the other hand.

In this case, chock 1 of upper work roll 2
3 is a guide piece 1 that is integrated in the vertical direction, but is slidable in the horizontal direction during the roll recombination process.
It is combined with 7. This guide piece is also vertically slidably guided in a block 12 which provides strength to the housing. The chuck 14 of the lower work roll is likewise connected to a guide piece 18 which is slidably guided vertically in a block 12 which likewise provides strength to the housing.

A guide piece 19 is provided on the chock 15 of the upper intermediate roll 4, and in this case as well, the chock 15
is integrally engaged with the guide piece 19 in the vertical direction but slidably in the horizontal direction. A guide piece 20 of the same construction and operating mode is provided on the chock 16 for the lower intermediate roll 5. In this case, a horizontal guide 21 is provided on the guide pieces 19 and 20 for the chock 15 for the intermediate roll 4 and the chock 16 for the intermediate roll 5, respectively.
This not only makes it possible to change the intermediate rolls 4 and 5 and the work rolls 2 and 3 at the same time, but also to change the intermediate rolls 4 and 5 for the work rolls 2 and 3 for the rolling operation and for the back-up rolls 6 and 7. It is configured to also ensure relative axial sliding movement. This axial sliding movement of intermediate rolls 4 and 5 for the rolling operation is important. This is because it makes it possible to adjust the roll stand to different widths of the sheets to be rolled in each case. This adjustment makes it possible to avoid stronger rolling of the rolled plate in its longitudinal edge region and particularly high loads on the parts of the work rolls acting on this plate edge.

For roll stands used for rolling plates with various widths, constant rolling under the lowest possible Hertzian contact pressure between the work roll and the intermediate roll for all rollable plate widths. The possibility of working with force and the selection of optimal diameters for the work roll and the intermediate roll are important. Special measures are therefore taken in the choke area of the intermediate rolls 4 and 5 in the roll stand. The chuck 15 of the upper intermediate roll 4 and the corresponding chock 16 of the lower intermediate roll 5 are each provided with adjusting means 22 in the form of a piston-cylinder unit which can be hydraulically loaded in the area of the block 12 which gives strength to the housing. It is being The arrangement and configuration of this piston-cylinder unit are shown in Figures 2 and 3.
It is clearly recognized from the figure. The adjusting means or bending devices 22 for the intermediate rolls 4 and 5 are integrated in guide pieces 19 and 20, which belong to the block 12, respectively.

In this case, the right-hand guide piece 19 for the chock 15 of the upper intermediate roll is shown in FIGS. 2 and 3. All guide pieces 19 for the upper intermediate roll 4 and all guide pieces 20 for the lower intermediate roll 5 are also identical in construction. These are housed in the roll housing 1 in mirror image positions relative to each other. That is, the left-hand guide pieces 19 and 20 are mirror images of the right-hand guide pieces 19 and 20, respectively, and the upper guide piece 19 is similar to the lower guide piece 20 in the roll housing 1.
It occupies a mirror-symmetrical position with respect to .

It can be seen from FIG. 2 that each of the guide pieces 19 and 20 consists of a housing side part 23 and a chock side part 24 which belongs to the chock 15, 16 of the intermediate rolls 4, 5.

In this case, adjustment means 22 forming a bending device for the intermediate rolls 4, 5 are integrated in the housing-side part 23. The adjustment means are provided on the choke side member 24 via their piston rods 25. In this case, this working connection is such that a bending force is exerted on the intermediate rolls 4 and 5 via the jocks 15 and 16 at least in a direction towards the back-up rolls 6 and 7.
Piston rod 25 of adjusting means 22 and each guide piece 1
A working connection is made between the choke side members 24 of 9 and 20. Moreover, the operative connection between the piston rod 25 of the adjusting means 22 and the choke-side part 24 of the guide piece 19 ensures that the bending force is also directed towards the back-up rolls 6 and 7 which belong to the intermediate rolls 4 and 5; It is particularly advantageous if it is configured so that it also takes place in a direction away from the roll. For this purpose, on the one hand, the adjustment means 2
It is necessary that the piston rod 25 of this adjusting means is configured to act double-acting, while the piston rod 25 of this adjusting means is provided with tension- and compression-resistant guide pieces 19 and 20.
It must be connected to the choke side member 24 of. Both members 23 and 24 of the guide piece 19 are configured to be slidable vertically relative to each other.

That is, no horizontal sliding movement relative to each other takes place.

From FIG. 3 it can be seen that in each guide piece 19 and 20 there are provided one after the other at a distance in the axial direction of the intermediate rolls 4 and 5, and which together form a bending device for the intermediate rolls 4 and 5. It can be seen that two adjustment means 22 are incorporated in each case. The axial sliding capability of the intermediate rolls 4 and 5 required for the rolling operation is determined by the axial sliding capacity of these intermediate rolls 1.
5 and 16 are connected to each guide piece 19 via the horizontal guide part 21.
and 20 are integrally engaged with the choke side members 24 in the vertical direction.

The purpose of the two adjusting means 22, which are integrated in each guide piece 19 and serve as bending devices for the intermediate rolls 4, 5, is to adjust the bending of the intermediate rolls 4 to the respective possible axial direction. It is to keep it in a constant sliding position.

The two adjustment means 22 are such that they vary relative to the guide piece 19 with respect to the adjustment force exerted by them, depending on the current axial sliding position of the chock 15 and 16 of the two intermediate rolls, respectively. It is configured so that it can be done. In this case, a strong adjusting force is generated by the adjusting means 22' and a weak adjusting force by the adjusting means 22'' in the axial sliding position of the chock 15 of the intermediate roll, which is clear from FIG. If the chock 15 assumes the opposite extreme position in the axial direction, the generation of the adjusting force is the opposite of what has been described above.Furthermore, by varying the adjusting force, a total of four individual forces acting on the intermediate roll are works in contrast to the center of the roll stand in terms of the power it imparts to the back-up roll.

The harmonized adjustment force is achieved by adjusting the intermediate roll
5 depending on its axially central sliding position is achieved by both adjusting means 22', 22''.
The adjusting force generated in each case by the adjusting means 22 is therefore varied in proportion to the rate of axial displacement of the intermediate roll chock 15 relative to the guide piece 19. That is, as a result, the bending due to the bending force on the intermediate roll 4 always acts on the central plane of the chocks 15 and 16 of the intermediate roll, which are present in the direction transverse to the roll axis, and the adjustment forces at both ends of the intermediate roll are summed. The action exists symmetrically with respect to the center of the roll stand.

This mode of operation of the bending device for intermediate rolls is shown schematically in FIG. In this case, the lines of force 26, 27, 28 and 29 indicate the position and action of the four adjusting means 22, which serve as bending devices for the intermediate roll. Double arrows 30 and 31 indicate the center plane of the chock of the intermediate roll, and double arrows 32 and 33 indicate the forces counteracting the bending of the intermediate roll, which forces are generated from the associated back-up roll. On one side of the two-way arrows 30 and 31 are lines of force 26 and 27 or 28 and 2.
9 and, on the other hand, relative to the arrows 32 and 33 correspond to the respective axial sliding position of the chock of the intermediate roll, and thus in contrast to the associated work roll and the associated back-up roll. This corresponds to the respective axial sliding position of the intermediate roll.

The basic structure of the six-layer roll stand shown in FIG. 5 is exactly the same as the basic structure of the roll stand according to FIG. However, the structure and operating mode of the guide strips for the two intermediate rolls 4 and 5 are different here.

FIG. 6 shows the chock 1 of the upper intermediate roll 4.
The right guide piece for 5 is shown enlarged. All guide pieces 1 for the upper intermediate roll 4
9 has the same structure. These differ only in their built-in position within the roll housing 1.

In connection with the upper right-hand guide piece 19 from FIG.
4 and a choke side member 35, and that an intermediate member 36 is additionally provided. Housing side member 34
is immovably housed within the housing 1 as a component of the block 12. This housing side member has a horizontal guide piece 37 running parallel to the roll axis.
It cooperates with the intermediate member 36 via. In this case, the intermediate part 36 is constructed in such a way that it is slidable in the housing side part 34 in the axial direction of the intermediate roll 4 or is supported integrally therein in the vertical direction. A chock side member 35 of the guide piece 19 is vertically slidably engaged in the intermediate member 36 . Therefore, both the intermediate member 36 and the choke side member 35 can perform horizontal sliding movement relative to the housing side member 34. In this case, the orthogonal integral horizontal direction guide between the chock 15 of the intermediate roll 4 and the chock side member 35 of the guide piece 19 is
Useful only when recombining. That is, the chock 15 of the guide piece 19 and the chock side member 35 are locked to each other so as not to make horizontal sliding movement during the rolling operation.

In the case of the guide piece 19 according to FIG. 6, the adjusting means 38 in the form of a hydraulically actuatable piston-cylinder unit forming the bending device for the intermediate roll 4 is located on the choke side of the guide piece 19. 35, whose piston rod 39 cooperates with an intermediate member 36. In this case as well, the adjustment means 38 work in a double-acting piston manner and are provided with their piston rod 39 in a tension-resistant and compression-resistant manner in the intermediate member 36.

In the guide piece 19 according to FIG. 6, only one adjustment means 38 is provided. Moreover, this adjustment means is integrated in such a way that it acts in the central plane of the check 15 running transversely to the longitudinal axis of the intermediate roll 4.

Each time the intermediate roll 4 slides in the axial direction, the chock side part 35, together with the intermediate part 36, carries out a corresponding horizontal movement relative to the housing side part 34. However, in this case the active surface of the adjustment means 38 remains unchanged relative to the chock 15 of the intermediate roll. Therefore, regardless of the axial sliding position of the intermediate roll 4, it remains unchanged against these bending forces.

Compared to the embodiment of the intermediate roll bending device according to FIG. 2, the intermediate roll bending device according to FIG. 6 is simpler in construction in that only one adjusting means 38 serving as a bending device is sufficient. ing. That is, the control mechanism for the bending device shown in FIG. 6 can be easily constructed. This is because only the action of the adjustment forces at the ends of the two intermediate rolls needs to be symmetrical with respect to the center line of the roll stand. However, instead of this, in the embodiment according to FIG. 6 it is necessary to provide an intermediate member 36 as an additional element.
However, this intermediate part is a mechanically simple component and can be installed at low cost.

Both in the embodiment of the intermediate roll bending device according to FIG. 2 and in the embodiment of the intermediate roll bending device according to FIG. Only one built-in space is required, as is required to accommodate the chock 15,16.
This fact presents no obstacles to the selection of optimal diameters for the work roll and intermediate roll. A trouble-free exchange of work rolls and intermediate rolls is easily ensured and the available structural space is not compromised by competing with each other, so that effective forces for the bending-correction forces of the intermediate rolls are ensured. There are no restrictions on the configuration of the transmission system.

The rolling result is improved by the roll bending carried out on the axially movable intermediate rolls 4, 5. This is because the Hertzian contact pressure between the work roll and the intermediate roll is reduced and the resulting temperature gradient on the work roll provides a high degree of security against skin cracking. Work roll wear is also significantly reduced. This is because work roll modifications do not have to be carried out at the periphery of the intermediate roll.

FIG. 7 shows a six-layer roll stand that differs from the roll stands shown in FIGS. 1 and 5 in its basic structure. In the case of the roll stand according to Fig. 1 and Fig. 5, the work roll 2,
3. The intermediate rolls 4, 5 and the back-up rolls 6, 7 are located in a common vertical axial plane,
In the roll stand according to FIG. 7, the essentially common axial plane is offset from the vertical at a constant rate. In this case, in the direction of displacement, the work rolls 2 and 3 are supported with their curved circumferential surfaces by central rollers 42 and 43 and/or support rollers 44, 45, which are supported on support bridges 40 and 41. In this case too, the chucks 15, 16 of the intermediate rolls 4 and 5 are provided with an intermediate roll-bending device of the construction shown in FIGS. 2 and 6, so that the advantages of intermediate roll-bending are optimally achieved. used.

8 and 9, a work roll bending device is shown in addition to an intermediate roll bending device. In this work roll bending device, the guide pieces 117 and 118 for the chucks 13 and 14 of the two work rolls 2 and 3 are essentially the guide pieces 19 for the two intermediate rolls 4 and 5.
and 20 have a similar structure. The relative position of these guide pieces 19 for intermediate rolls 4 and 5 with respect to each other in the roll stand essentially corresponds to the relative position of 20.

It can be seen from FIG. 8 that each of the guide pieces 117 and 118 consists of a housing side member 53 and a member 54 provided on the jocks 13,14. In this case, the housing side part 53 incorporates an adjusting means 55 forming a bending device for the work rolls 2, 3, which adjusting means is constructed as a piston-cylinder unit and via its piston rod 56. and is provided on the choke side member 54. At this time, the adjusting means 5
5 piston rod 56 and each guide piece 117, 11
8 and the chock side member 54 is such that the bending force moves via the guide pieces 117, 118 in the direction of the intermediate rolls 4, 5 to which the work rolls 2, 3 belong. The intermediate rolls act to move them away from each other. For this purpose, on the one hand, the adjusting means 55 is designed to be reciprocating, and on the other hand, its piston rod 5
6 is tensile force resistant and compression resistant guide piece 11
7,118 chock side member 54 is required. Both parts 53, 54 of the guide pieces 117, 118 are assembled in such a way that they are slidable vertically relative to each other. That is, any horizontal sliding movement relative to each other is prevented.

The structure and operation mode are the guide piece 1 of both intermediate rolls.
The housing side parts 53 of the guide pieces 117, 118, which are equal to 9 and 20, are supported on the block 12 and/or on each other via counterforces, the support being provided by the choke side parts 54 of the guide pieces and the work roll. The jocks 13, 14 for 2, 3 are also independently movable by adjusting means 55 forming a bending device.

As shown in FIG. 8, a piston-cylinder unit 57, for example, is provided as the reaction force section. This piston-cylinder unit has work rolls 2 and 3.
The housing-side members of the guide pieces 117, 118 are arranged in such a way as to allow basic adjustment of the distance between the rolls between them and to allow unlimited relative displacement of the guide pieces 117, 118 with respect to the block 12 in a common vertical direction. 53 are held coupled together. Regardless of possible relative displacements of the work rolls 2, 3 in the vertical direction with respect to the block 12, the adjustment means 55 cause the two work rolls 2, 3 to be individually bent in both directions in the vertical plane; This allows desired control over the rolling process.

By combining the bending of the work roll and the intermediate roll when using a slidable intermediate roll, not only can the correction range be expanded, but also
An improvement in the quality of the plate shape is also achieved by the simultaneous action of both correction measures, namely work roll bending and intermediate roll bending.

Furthermore, the contact pressure of the work roll on the intermediate roll on the one hand and the back-up roll of the work roll on the other hand is formed optimally, so that not only a reduction in roll wear is achieved, but also a reduction in rolling stress and rolling load. It is also possible to achieve a reduction. Intermediate roll bending facilitates back-up roll shape correction, while work roll bending at the same time makes it possible to control the rolling process.

The basic structure of the six-layer roll stand shown in FIG. 10 is exactly the same as the basic structure of the roll stand shown in FIG. However, the difference in this case is that, on the one hand, the intermediate rolls - chock 15 and 16;
on the other hand, the structure and mode of operation of the guide strips 19 and 20 for the work roll chock 13 and 14, and on the other hand the structure and mode of operation of the guide strips 117 and 118 for the work roll jocks 13 and 14.

FIG. 11 shows, in addition to the intermediate roll bending section already mentioned in connection with FIG. 117 is shown. In this case too, all guide pieces 117 for the upper work roll 2 as well as the lower work roll 3
All guide pieces 118 (not shown) have the same structure as each other, they differ only in their location in the roll housing.

From FIGS. 10 and 11, the upper right guide piece 1 for the chock 13 of the upper work roll 2
On the side 17, it can be seen that the guide pieces 117 and 118 are likewise provided with a housing side part 58 and a chock side part 59.

Unlike the configuration of the guide pieces 117 and 118 shown in FIGS. 8 and 9, the guide pieces 117 and 118 of the embodiment according to FIGS. 10 and 11 have a bending device for the work rolls 2, 3. The adjusting means 60 forming a hydraulically actuated piston-cylinder unit is provided via the choke side part 59 of the guide pieces 117 and 118, the piston rod 61 of which is connected to the housing side part 5.
Collaborate with 8. In this case as well, the adjusting means 60 performs a double-acting function, and its piston rod 61 also provides tensile force resistance and compression resistance to the housing side member 5.
It is fixed at 8.

As already mentioned in connection with the roll stand according to FIGS. 8 and 9, the guide pieces 117 and 118 for the chock 13 and 14 of the work roll 2 are provided with a reaction force in the block 12 on the housing side, on the one hand. Then, the guide pieces 117 that are located above and below each other.
and 118 on the one hand, and the relative position of these parts with respect to the block 12 on the other hand, and in this case the relative position between the housing side member 58 and the choke side member 59 is determined via the adjusting means 60. There is no need to change it. 10th
In the figure, the chock 13 of the work rolls 2 and 3,
As shown in connection with the left guide pieces 117, 118 for 14, the housing side members 5 of the guide pieces 117 and 118, respectively, are
8 contains piston-cylinder units 62 and 63. The piston rods 64, 65 of these two piston-cylinder units 62 and 63 in this case support each other or can be connected to each other on the one hand, and on the other hand the horizontally oriented support surfaces of these piston rods and of the block 12. come into contact with. At this time, by applying a load to the piston-cylinder unit configured to double-act, the guide pieces 117, 11
The relative positions of the parts 58 on the housing side of 8 are as follows:
On the other hand, it is possible to change the relative position of these parts to the block 12. However, in this case it is not necessary to adjust the adjusting means 60 forming the bending device for the work rolls 2 and 3 in the guide pieces 117, 118 for this purpose.

In the embodiments of the roll stand according to FIGS. 8 and 9 as well as in the embodiments of the roll stand according to FIGS. 10 and 11, an intermediate roll-bending device is provided in the roll stand. actually requires only one installation space, which is divided into intermediate roll chock 15, 16 and work roll chock 1.
This is also necessary for the arrangement of 3 and 14. On this basis, therefore, there is no obstacle to selecting an optimum diameter for the work roll and the intermediate roll, and also a reliable replacement of the work roll and the intermediate roll is easily ensured.
Furthermore, the construction spaces available for the intermediate roll-bending device and the work roll-bending device do not interfere with each other;
Therefore, no restrictions arise in terms of forming an effective force transmission system for the bending-correcting forces of the intermediate roll and the work roll.

Due to the possible roll bending not only on the axially displaceable intermediate rolls 4, 5, but also on the work rolls 2, 3, the rolling results obtained are significantly improved. This is because, on the one hand, the contact force of the work roll to the intermediate roll, and on the other hand, the contact force of the intermediate roll to the back-up roll is optimized, and the quality of the sheet shape is improved by the simultaneous action of both correction means. This is because back-up roll shape modification is possible with intermediate roll bending, while work roll bending serves to control the rolling process.

[Brief explanation of the drawing]

FIG. 1 is a schematic view of a first embodiment of a roll stand according to the invention, shown schematically in a vertical section parallel to the rolling direction, and FIG. Enlarged view of important parts,
3 is a partially sectional plan view of the arrangement according to FIG. 2; FIG. 4 is a force diagram in the area of the axially displaceable intermediate roll with respect to the work roll according to FIG. 1; FIG. is a diagram corresponding to FIG. 1 of another embodiment of the roll stand according to the present invention, and FIG. 6 is a diagram corresponding to FIG. 5.
FIG. 7 is an enlarged view of a subarea of the roll stand according to the invention indicated by the reference numerals in the figure; FIG. 1 and 5, FIG. 8 is a vertical sectional view of another embodiment of the roll stand according to the invention, shown in a simplified manner parallel to the rolling direction, and FIG. 8 is an enlarged view of important subareas according to the invention indicated by the symbols in FIG. 8, FIG. 10 is a view corresponding to FIG.
FIG. 1 is an enlarged view of the important subareas according to the invention indicated by the symbols in FIG. 10; The symbols in the figure are 2, 3... work roll, 4, 5
...Intermediate roll, 12...Block, 15,16
...Chiyotsuku, 19,20...Guidance piece, 22,3
8... Adjustment means.

Claims (1)

[Claims] 1. A bending device is provided for the intermediate rolls 4, 5 which are provided so as to be slidable in the axial direction between the back-up rolls 6, 7 and the work rolls 2, 3. In a six-layer roll stand of the type in which the adjustment means 2, 2 of the intermediate rolls are adjustable in the horizontal direction parallel to the roll axis: - the block 1 by which the adjustment means 22 reinforces the stand;
- the housing side member 23 forms the block 12; - the housing side member 23 forms the block 12; a horizontal guide 21 in which one chock side part 24 of each guide piece 19, 20 is oriented horizontally next to the housing side part 23 for the chock 15; 16 of the intermediate rolls 4, 5;
- each of the two adjusting means 2 of the adjusting means 22;
2';22'' is the chock side member 2 of the guide pieces 19, 20 with an interval in the axial direction of the intermediate rolls 4, 5.
4 and the housing side member 23, and - adjustment means 22, 22' in the guide pieces 19, 20,
A six-layer roll stand characterized in that the operating position of the 22'' can be changed in the horizontal direction. 2. The housing side member 23 and the choke side member of the guide pieces 19, 20 slide relative to each other in the vertical direction. that two adjustment means 22; 22', 22'' are provided one after the other at a distance in the axial direction of the intermediate rolls 4, 5 between these parts 23, 24; The chucks 15, 16 of the intermediate rolls 4, 5 are arranged so as to be slidable in the horizontal direction relative to the chock side members 24 of the guide pieces 19, 20 which belong to them. The six-layer roll stand described in Scope 1. 3 Adjustment means 2 forming a bending device
2 is incorporated into the housing side member 23 of the guide pieces 19, 20, and is provided on the choke side member 24 via a piston rod 25. 6-layer roll stand described in. 4. The two adjusting means 22; 22', 22'' arranged one after the other at a distance vary their adjusting force depending on the respective axial sliding position of the chock 15, 16 of the intermediate roll. 5. A six-layer roll stand according to any one of claims 1 to 3, characterized in that the adjustment means 22 is a piston that can be loaded with reduced pressure. It consists of a cylinder unit, and this piston-cylinder unit is assembled in the housing side member 23 of the guide pieces 19, 20, and the piston rod 25 of this piston-cylinder unit is attached to the choke side member 24. 6. A six-layer roll stand according to any one of claims 1 to 4. 6. The adjusting means 22 is configured to double-act, and has tensile force resistance and Compression resistance guide piece 1
The six-layer roll stand according to any one of claims 1 to 5, characterized in that the roll stand is engaged between the rollers 9 and 20. 7 Chocks 13 and 14 of both work rolls 2 and 3
Also provided as bending devices are adjusting means 55; 60 which are arranged in the block 12 and which are attached to the guide pieces 17; is held in the block 12 via the housing side member 53; 58 and the choke side members 54, 59;
3, 14, comprising a chock side member 59 and a housing side member 53 as horizontal guide pieces for the housing according to any one of claims 1 to 6. 6-layer roll stand. 8 Each guide piece 17; 18 is the housing side member 5
3; 58 and work roll 2; check 13 of 3;
It is noted that adjusting means 55; 60 are provided between the housing side parts 53, 58 and the choke side parts 54, 59, which in this case form a bending device. A six-layer roll stand according to claim 7. 9 Housing side member 53 of guide pieces 17, 18,
58 and the chock side members 54, 59 are relatively slidable in the vertical direction, and the work rolls 2,
The chock 13, 14 of No. 3 is provided so as to be slidable in the horizontal direction relative to the chock side members 54, 59 of the guide pieces 17, 18 belonging thereto. , a six-layer roll stand according to claim 7 or 8. 10 The adjusting means 55 forming the bending device is connected to the housing side member 53 of the guide pieces 17 and 18.
Claims 1 to 9 are characterized in that the piston rod is incorporated in the piston rod and is attached to the choke side member 54 via the piston rod 56.
6-layer roll stand described in any one of the items listed above. 11. Claim 1, characterized in that the adjusting means 60 forming the bending device are integrated in and attached to the choke side parts 54 of the guide pieces 17, 18. The six-layer roll stand according to any one of Items 1 to 10. 12 The adjustment means 55; 60 consist of a hydraulically loadable piston-cylinder unit which is arranged in one of the housing side parts 53 and the choke side part 59 of the guide pieces 17; Piston rod 56;6
1 is provided on the other choke side member 54 and housing side member 58, the six-layer roll according to any one of claims 1 to 11. stand. 13. Claim 1, characterized in that the adjustment means 55 and 60 are configured to double-act and are provided between the guide pieces 17 and 18 to ensure tensile force resistance and compression resistance. The six-layer roll stand described in any one of Items 1 to 12. 14 Housing side member 5 of guide pieces 17, 18
Reaction force parts 57; 62, 63 are provided in the block 12 of the roll housing 1 at 3; 58, and the housing side members 53; A six-layer roll stand according to any one of claims 1 to 13, characterized in that the relative position of the roll stand can be determined. 15. Claims characterized in that the adjustable reaction force part 57; 62, 63 consists of a piston-cylinder unit integrated in the choke-side part of the guide pieces 17, 18 and in the choke-side part 53; 58. The six-layer roll stand according to item 14. 16 A bending device is provided for intermediate rolls 4 and 5 which are provided so as to be slidable in the axial direction between back-up rolls 6 and 7 and work rolls 2 and 3, and adjustment means 3 for the intermediate rolls are provided. , 8 are adjustable in the horizontal direction parallel to the roll axis, - the adjustment means 38 are slidable in the axial direction along the housing side members 34 of the guide pieces 19, 20; an intermediate member 36 held by a housing side member 34;
and the chock side member 35, - a horizontal guide in which the chock side member 35 of the guide pieces 19, 20 is oriented in the horizontal direction for the chock 15, 16 of the intermediate rolls 4, 5; - the housing side member 34 forms the block 12; - the chock side member 35 of the guide pieces 19, 20 slides horizontally on the chock 15, 16 of the intermediate rolls 4, 5; and that the adjusting means 38 is locked against movement, so that the adjusting means 38 is horizontal with respect to its operating position together with the intermediate rolls 4, 5 jocks 15, 16 and in the axial direction of the intermediate rolls 4, 5 with the guide piece 1.
A 6-layer roll stand, characterized in that the housing side members 34 of Nos. 9 and 20 can be changed. 17. The chock side member 35 of the guide pieces 19, 20 is capable of sliding in the horizontal direction with respect to the housing side member 34 together with the intermediate member 36;
The adjusting means 38 built into the chock side members 35 of the intermediate rolls 4 and 20 are respectively provided on the center surfaces of the chock 15 and 16 of the intermediate roll, and the chock side members 35 of the guide pieces 19 and 20 are arranged in the middle rolls 4 and 20 respectively. 17. The six-layer roll stand according to claim 16, wherein the six-layer roll stand is horizontally slidably connected to the chucks 15, 16 of No. 5 and the housing side member 34. 18 The housing side member 34 is connected to the chock side member 35 of the guide pieces 19, 20 via an intermediate member 36, and this intermediate member 36 on the one hand forms a horizontal sliding guide 37 for the housing side member 34.
On the other hand, it is characterized by having a sliding guide part 37' perpendicular to the chock side member 35,
A six-layer roll stand according to claim 16 or 17. 19 The adjusting means 38 is a piston that can be loaded with reduced pressure.
This piston-cylinder unit is housed in the choke-side member 35 of the guide pieces 19, 20, and the piston rod 39 of the piston-cylinder unit is connected to the intermediate member 3.
6. The six-layer roll stand according to any one of claims 16 to 18, characterized in that the six-layer roll stand is provided to cooperate with the six-layer roll stand. 20 The adjusting means 38 is configured to double-act, and the guide piece 1 has tensile force resistance and compression resistance.
It is characterized by being provided between 9 and 20.
A six-layer roll stand according to any one of claims 16 to 19. 21 Chocks 13 and 1 of both work rolls 2 and 3
4 are also provided with adjusting means 55; 60 which are arranged in the block 12 as bending devices, and these adjusting means are connected to the guide pieces 17; 18; 1.
17; 118, and these guide pieces are held in the block 12 via housing side members 53, 58 and choke side members 54, 59 as vertical guide pieces on the one hand, and on the other hand. Any one of claims 16 to 20, characterized in that a chock side member 59 and a housing side member 53 are provided as horizontal guide pieces for the chock 13, 14. 6-layer roll stand described in. 22 Work roll 2;3 check 13;14
Each guide piece 17; 18 belonging to a housing side part 53; 58 and a choke side part 54; 22. The six-layer roll stand according to claim 21, wherein the six-layer roll stand is provided between 54 and 59. 23 Chocks 13, 14 of work rolls 2 and 3
is provided so as to be able to slide horizontally relative to the chock side members 54, 59 of the guide pieces 17, 18 to which it belongs, and the housing side members of the guide pieces 17, 18 23. The six-layer roll stand according to claim 21 or 22, wherein the chock side members 53, 58 and the choke side members 54, 59 are relatively slidable in a vertical direction. 24 The adjusting means 55 forming the venting device for the work rolls 2, 3 are connected to the guide pieces 17,
It is incorporated into the housing side member 53 of No. 18 and is attached to the choke side member 54 via the piston rod 56.
A six-layer roll stand according to any one of claims 16 to 23. 25 The adjusting means 60 forming the venting device for the work rolls 2, 3 are connected to the guide pieces 17,
It is incorporated into the chock side member 54 of 18,
The six-layer roll stand according to claim 23 or 24, characterized in that the stand is attached to the choke side member 54. 26 Adjustment means 5 for work rolls 2, 3
5; 60 consists of a hydraulically loadable piston-cylinder unit which is arranged in one of the housing-side parts 53 and the choke-side part 59 of the guide pieces 17; 18 and whose piston rod 56; 61 is provided on the other choke side member 54 and the housing side member 58, Claim 16
The six-layer roll stand according to any one of Items 25 to 25. 27 Adjustment means 5 for work rolls 2, 3
5; 60 is configured to double-act, and the guide pieces 17, 18 have tensile force resistance and compression resistance.
The six-layer roll stand according to any one of claims 16 to 26, characterized in that the six-layer roll stand is provided between the two roll stands. 28 Work rolls 2 and 3 check 13; 14
Block 1 of roll housing 1 is attached to housing side member 53; 58 of each guide piece 17, 18 belonging to
Reaction force parts 57; 62, 63 are provided in the housing side members 53;
A six-layer roll stand according to any one of claims 16 to 27, characterized in that the relative position with respect to the roll stand can be determined. 29 The adjustable reaction force portion 57; 62, 63 is a piston installed in the chock-side part of each guide piece 17, 18 belonging to the chock 13; 14 of the work rolls 2, 3 and in the chock-side part 53; The six-layer roll stand according to claim 28, characterized in that it consists of a cylinder unit.