EP2450115A2 - Milling system, roller framework and method for changing roller frameworks in a milling system - Google Patents

Abstract

The rolling mill has roll stands (12) that are arranged in rows in a central aperture of scaffold spaces (57) and displaceable along the scaffold. A change carriage (54) is provided with change positions (58,59) for the roll stands at the sides of the row of roll stands. The change positions of the carriage are spaced according to the distance between the scaffold spaces. An independent claim is included for method for changing roll stand.

Description

The invention relates to a rolling mill for rolling elongated material with a plurality of arranged in line, forming a central caliber opening rolling stands, wherein the rolling stands are each arranged in a scaffold and each to at least one change position are displaced and in particular a rolling mill in a compact design for rolling elongate Good , with several arranged in line, a central caliber opening forming, motor-driven rolling stands in a mutually mountable C-stand. Likewise, the invention relates to a rolling stand with at least two driven rollers (2, 3) and with at least two drives and a roll stand with rollers for receiving rolling forces that occur during rolling of elongated material, and a method for changing rolling stands (12) in a rolling mill.

The invention is particularly applicable to stretch-reduction mills (SRW-BCO), sizing mills (MW-BCO) and extension mills (AZW-BCO).

Mills for rolling elongated material are known both with 2-roll stands as well as with 3-roll stands or 4-roll stands, and a setting of the rolls for changing the caliber diameter is also known. In 2-roll stands the offset is 90 °, in the 3-roll stand 60 ° and in the 4-roll stand 45 °.

The invention has for its object to provide a generic rolling mill, a generic rolling stand and a generic method for changing rolling stands in a rolling mill, which allow the most compact possible design a reliable turn of the rolling stands.

To solve this problem, a rolling mill for rolling elongated material is arranged with a plurality of rolling mills arranged in line, forming a central caliber opening, wherein the rolling mills are each arranged in a scaffold and are each displaced to at least one change position and wherein the rolling mill thereby It is characterized by the fact that each scaffolding station has an input clutch and the input clutch having roller stand side coupling part and a drive-side coupling part and the drive-side coupling part is provided axially fixed to the frame site. Thus, for the rolling mill results in a particularly simple dome option, which is used to the very reliable, since the degree of freedom of the two coupling parts of the input clutch are limited by the fixed provision of the drive-side coupling part to the framework site and a successful engagement only from the position of the rolling stand side Coupling parts is affected. If the mill stand is guided without play linearly to the scaffolding station, as can be seen immediately, only one degree of freedom results for the coupling of the input coupling. Consequently, an exact and reliable engagement via a drive or the corresponding input coupling is ensured to a drive motor by the proposed design of the rolling mill.

A rolling mill with a input clutch can also be advantageously configured by two input clutches per rolling stand and each scaffold, the two input clutches each axially to their axes of rotation and the axes of rotation are aligned in parallel and wherein both input clutches are arranged on one side of the line. In this respect, a rolling mill or a rolling mill according to this embodiment just as easy and reliable prepare or put into operation, as if only a single input clutch is provided because the mutually aligned input clutches are handled as a single clutch. Here, the two input clutches, which may have a common or even two individual drives, are coupled in a single assembly step, in particular, only the rolling stand needs to be moved. As a result of the two input clutches, the forces or torques that have to be transmitted from the drive to the rolling stand via a single clutch are correspondingly reduced. As a result, in particular the coupling diameter decrease, whereby the rolling stands can build accordingly narrower.

However, for reliable coupling it is not absolutely necessary that the rolling stand is moved for coupling. It is also a configuration conceivable in which the drive-side coupling part is designed to be axially movable.

In an advantageous embodiment of the rolling mill, a drive with a drive motor can be provided in addition to at least one scaffold place, with a drive Transfer case is connected, which has at least two outputs, wherein the outputs each have a drive-side coupling part of a input clutch. Cumulatively, the drive-side coupling parts can be aligned parallel and in the same direction at the rolling mill. These refinements provide a rolling mill with a roll stand which advantageously has one, two or more input clutches. On the one hand, there is the possibility on the one hand of transferring more torque to the roll stand due to the numerous input clutches or, on the other hand, of driving separate assemblies of the roll stand separately from one another. In suitable embodiments of the rolling stands, these may also be provided with only lower output side coupling parts, if only lower torques are needed, in the areas where further drive-side coupling parts are to be found, structural clearances are left, so that these coupling parts can run freely.

A parallel and co-directional alignment of these drive-side coupling parts also advantageously brings a high degree of flexibility in the selection of the drives. Thus, either a single or multiple drives can be coupled to the rolling stand, in particular, only the rolling stand needs to be moved for engaging, but this does not necessarily have to be provided.

The terms "parallel" and "in the same direction" here refer to the different axes of rotation of the respective coupling parts, with "same direction" an identical direction of rotation is meant. A "transfer case" refers to any transmission that has more outputs than drives, regardless of whether a power split - due to different speeds at the drives - occurs. In this respect, a transfer case can also be a spur gear.

Preferential meadow are, as for example from JP 57-121810 A known, the respective rolling stands are arranged in each case in a scaffold and are each displaced to at least one change position and wherein each scaffold exactly one exchange position is provided and a change position of a first scaffolding site on one side of the line as a change position of a second scaffolding site on the other side the line is provided. The changing positions in relation to the scaffolding places make possible a particularly compact rolling mill, in which a mill stand change takes place correspondingly reliably and quickly can be. In particular, in the rolling direction, ie in the axial direction of a rolling mill arranged on a scaffold place, the overall length of the rolling mill is reduced, since on both sides of the rolling stands space for further modules does not need to be maintained. In particular, at the alternating positions existing on both sides of the lines arise in the axial direction to the change positions free spaces that can be additionally used for assembly, which can increase the reliability especially in a framework change in an advantageous manner, if this space is not used for other units , Another advantage of this arrangement results in the arrangement of drive motors for the rolling mill, which can now optionally also be arranged on both sides of the line and can be designed because of the now available free space approximately up to twice the diameter of the original usable drive motors.

In this way, it is possible in a suitable embodiment, in particular, a powerful rolling mill in compact design for rolling elongated Good, with several arranged in line, a central caliber opening forming, motor-driven rolling stands and a method for easy change of the rolling stands in a confined space to create. In this rolling mill, a variety of rolling mill types can be used with a suitable embodiment. The input clutches of the rolling stands can, as will be explained in detail below, couple independently when inserted into the rolling mill stand. The drives can, as already indicated above, be accommodated to save space. For the method of change car can be kept low with a suitable design of the space requirement.

For a rolling mill, in order to provide a particularly compact and space-efficient rolling mill, the scaffolding places may be numbered along the line, all odd-numbered change positions being on one side of the line and all even-numbered changing positions on the other side of the line. It is immediately apparent that in this embodiment, the scaffolding places can be arranged in a particularly space-saving manner in the rolling direction by the alternating arrangement of the change positions and thus uniform space for assembly and set-up work is provided on both sides of the change positions.

In a further advantageous embodiment, the change positions of the respective rolling stands can be provided on a change carriage in a rolling mill, wherein the change carriage has at least one further change position. This further change position serves to keep ready a rolling mill to be loaded. A roll stand to be removed from the rolling mill after rolling can thus be guided to a first change position, after which the rolling stand provided on the further change position can be returned to the scaffolding spot in immediate connection, and the change carriage is correspondingly displaced. Thus, as can be seen immediately, the set-up times at the rolling mill are reduced to a minimum. The rolling mill can be put into operation again immediately after the change of the rolling stands, wherein the removed rolling stand after commissioning of the rolling mill of its further use, for example, a maintenance, can be supplied.

Furthermore, a rolling mill with a change carriage, which has two change positions, be advantageously designed in such a way that the change carriage has at least four change positions, one change position and another change position for every two scaffold positions, the two change positions corresponding to the distance of the two Scaffolding places and the other two change positions are spaced apart according to the distance of the two scaffolding sites. It can be seen that this advantageously a change of two rolling stands on the two scaffolding places can be done simultaneously. It is also possible, moreover, for the change carriage to have change positions and further change positions for all roll stands available on a rolling mill, which can be loaded simultaneously from one side of the line.

For a rolling mill with a change carriage, which has at least four change positions, it is also advantageous if the change positions and the other change positions are spaced from each other at least by the width of a rolling stand, preferably by the distance of the scaffolding places. By this configuration, it is possible to reduce the travel path of the swap body to a minimum, when the center of the scaffold site or the center of a rolling mill is defined as the starting point for the distance or width measurement. By "center" is meant the axial mean position along the rolling direction.

It is understood that a change carriage with two or more change positions also independent of the other features for a rolling mill for rolling elongated Good arranged with several in line, forming a central caliber opening rolling stands, the rolling stands are each arranged in a scaffolding and each to at least one change position are displaced, is advantageous. This is independent of whether the two change positions are only used for one scaffolding site or for two scaffolding sites. If these are used for only one scaffold place, a fast and reliable scaffolding change takes place in a confined space by a rolling stand, which is held on the change carriage on the first change position, can be quickly positioned by displacing the change carriage, that this to the intended Scaffolding station spent and the operation can be resumed quickly after the replacement scaffold has been moved to the second change position. If these are used for two scaffolding sites, so two exchangeable mills can move simultaneously from its rolling position to its interchangeable position, be transported away from the change car, while another change carriage simultaneously moved two mill stands to their change position and can be moved from there to their rolling position , Further set-up work, such as a removal by crane can then take place from the change car, while the rolling mill is back in operation or is. It is understood that the benefits can be cumulated by multiple change positions on each one change car if necessary.

Preferably, as for example from JP 57-121810 A known, arranged at least one rolling stand on a shuttle shoe and the change shoe on a tilted relative to the horizontal exchange path. The use of a shuttle shoe in conjunction with a change path offers the advantage of positioning the rolling mill easily and reliably within the rolling mill, in particular at the mill site of the rolling mill, even if the rolls of the individual rolling stands are inclined relative to one another in their rolling position. The inclination angle can be specified by the inclination of the exchange path, which may possibly also be adjustable, so that the rolling stands themselves can be constructed simply and preferably even identical or very similar to one another. It can be provided that the positioning of the rolling stand with the flexible shoe advantageously takes place at right angles to the rolling direction of the rolling mill. As a result, the rolling mill, which Contains rollers as rolling tools, aligned to the rolling stock and requires at a play-free displacement of the shuttle shoe on the exchange path no or extremely low adjustments.

The inclination of the exchange path relative to the horizontal already causes a reliable positioning of the displaceable on the exchange mill stand, which is accelerated by its own gravity along the exchange path in the framework place down and in this way readily to a stop, a system, a brake pad or - wedge or can be positioned on similar reliable. A further safeguard against unintentional shifting of the roll stand can, but does not have to, be ensured by further securing means.

In this context, a rolling mill in an advantageous embodiment may have a change path, which has a region inclined relative to the horizontal and a substantially horizontal region. In particular, set-up work can be carried out simply and reliably in the horizontal area. In addition, the energy input for horizontal displacements is minimal, so that in this area can be relocated with a correspondingly low energy expenditure.

Preferably, the substantially horizontal region of the exchange path is provided on a change carriage. This allows in particular a simple construction of the swap body, wherein a roll stand provided on the change carriage can readily be held in position by corresponding detents, such as wedges, brake pads, stops or the like.

According to the above-explained advantages with regard to the locking of a roll stand, it is particularly advantageous if the region of the exchange path inclined relative to the horizontal is provided in the framework stand and inclines downward into the stand. In this way, the corresponding positioning in the rolling position in the scaffold place and can be implemented structurally simple by a fixed stop or the like at the end of the exchange path ending in the framework place.

It is understood that the features of a rolling stand with a change shoe are also advantageous for a rolling mill independently of the other features of the present invention.

An advantageous embodiment of the rolling mill results further, if at least one rolling stand has a drive and the input via an axial input clutch with a drive motor can be coupled, wherein the input clutch has a roll stand side coupling part and a drive-side coupling part and wherein a rotation axis of the input coupling parallel to the exchange path is aligned. This embodiment of the rolling mill, in particular the design of the coupling parallel to the exchange path, allows a particularly simple and above all self-locking coupling possibility of the rolling mill or the input drive to the drive motor or a gear of the drive motor and is independent of the other features of the present invention in a rolling mill for rolling elongated material with a plurality of arranged in line, a central caliber opening forming rolling stands, wherein the rolling stands are each arranged in a scaffold and each along a change path to at least one change position are displaced, correspondingly advantageous to ensure a fast and reliable roll change.

By the above-described orientation of the axis of rotation, with appropriate implementation, an independent closing of the clutch can be ensured because the two coupling parts along the direction of displacement of the rolling stand are positioned to each other exactly and further, in particular manual, coupling activities can be omitted. It is immediately apparent that the set-up time of the rolling mill can be reduced to a minimum by this design.

In addition to the above features, a rolling mill may advantageously comprise at least one mill stand extractor with a hydraulic pull-out cylinder. As can be seen immediately, such a pull-out unit is advantageous for the fast and reliable setup of a rolling mill, as can be dispensed with a manual setup, for example, by manually hooking chains and the like.

Alternatively or cumulatively to the above Markmalen also a rolling mill with at least two driven rollers and at least two drives is proposed accordingly, which is characterized in that each input has a rolling mill side coupling part and the rolling stand side coupling parts are aligned parallel and in the same direction. Advantageously, the rolling stand can be coupled from one side with a drive or with multiple drives structurally simple, space-saving and reliable, in particular, only the rolling mill needs to be moved. However, a movement of the roll stand for coupling does not necessarily have to be provided. Alternatively, for example, a drive for coupling the respective coupling parts may be provided axially to the rolling stand on a rolling mill or on a scaffold place, but this requires further units and therefore a susceptibility to errors and an increased space.

Alternatively or cumulatively to the above features, a rolling stand with at least four driven rollers is proposed to solve the above-mentioned problem, which is characterized in that two rollers are mounted on a common frame part, wherein the two frame parts are in turn mounted on a scaffold body , The object in question is achieved in this case that can absorb and distribute high scaffolding moments and rolling forces through the rolling stand particularly advantageous and reliable.

On a roll stand with four driven rollers, it is particularly advantageous for each frame part to have an input drive and two rollers aligned perpendicular to one another, for example a horizontal and a vertical roller. This allows a compact and simple arrangement, in particular also with regard to the transmission between input drive and rollers. In this case, the rolls can be operatively connected to one another on a roll stand via two meshing bevel wheels, preferably with a cone angle of 45 °. Furthermore, the two meshing bevel gears of a roll stand can be arranged in a cassette. It is immediately apparent that these features of a rolling mill advantageously the forces and moments acting in the roll stand can be particularly evenly distributed by the arrangement of the bevel gears and rollers and absorbed by the rolling mill. A particularly long service life and reliability is thus ensured in a roll stand according to these embodiments.

As an alternative or cumulative to the above features, a roll stand with rolls for receiving rolling forces which occur during rolling of elongated material is proposed, which comprises a framework body having at least two scaffold plates, wherein the scaffold plates are parallel to one another and perpendicular to the rolling forces are arranged, distinguished. The provision of two scaffold plates according to the proposed arrangement causes a very stable design of a rolling stand, which also can be produced with little cost of materials and therefore very inexpensive.

In addition, can be provided on a rolling mill according to the number of rollers elbows, which absorb the rolling forces and transmitted to the scaffold plates. Also, this design of a rolling stand ensures a reliable and long use in rolling, by the rolling forces occurring can be transmitted uniformly to the rolling mill.

In order to solve the object of the present invention, alternatively or cumulatively to the above features, a roll stand for receiving rolling forces which occur during rolling of elongated material is proposed, which is characterized by a hydraulic overload protection. These hydraulic overload safety devices, which can be provided according to the number of rollers on a roll stand, make it possible, on the one hand, to restore the rolling stand to a ready-to-operate state in a simple manner. This can be done after setting up a rolling mill with a rolling mill or even after a shutdown due to an overload by simply built up according to pressure.

If the hydraulic overload cylinders of at least one rolling stand can communicate with one another, they can advantageously, for example in the event of a malfunction, enable simultaneous triggering of all existing overload cylinders.

Also proposed to solve the input task, a method for changing rolling stands in a rolling mill, which is characterized in that at least one rolling stand is displaced along an inclined trajectory. As a result, it is advantageous, as already explained above, for a simple control of the displacement path to be possible in particular even when a clutch is closed on the rolling stand or should be opened. An existing clutch can in this case, by the displacement along an inclined trajectory, automatically close and remain automatically closed.

In particular, it is advantageous if the roll stand is lowered along the inclined exchange path in a rolling position. It will be readily apparent that lowering the mill stand along the inclined change path to a rolling position enables automatic locking or positioning of the mill stand, as self-displacement of the same out of the change path is prevented by the action of gravity, as already explained in detail above.

Likewise, on the one hand alternatively or cumulatively proposed for solving the input standing task, a method for changing rolling stands in a rolling mill, which is characterized in that at least one rolling stand from its rolling position to one side and another rolling mill from its rolling position to another Page be relocated. On the other hand, a method for changing rolling stands in a rolling mill is proposed, which is characterized in that at least two rolling stands are shifted from their rolling position to a common side and to changing positions, which are spaced from each other by at least one rolling stand width. These process steps offer the advantage that free space remains laterally or next to the displaced rolling stands for further assembly or set-up work or else for the interim storage of rolling stands. In particular, a free space can advantageously be made available between two rolling stands, in which a further roll stand can be stored without hindering the other rolling stands for setting.

In this context, it should be emphasized that the "rolling stand width" of the rolling stands is the longitudinal extent of the rolling stands along a rolling axis or the rolling direction. Thus, the rolling stand width extends axially to a main extension direction of the rolling mill.

Preferably, in the latter alternative solution, both rolling stands are displaced together with at least one further roll stand around a roll stand width, before the further roll stand is then shifted to its rolling position. This displacement, which is effected axially along the rolling mill, causes a positioning of the further rolling stand without the first Both rolling stands must be removed. Thus, a very fast change of the rolling stands and it takes this, as well as for the set-up time, only a minimal amount of time to be applied. The entire space required for this process can also be reduced to a minimum.

Alternatively or cumulatively to the above-described method, a method for changing rolling stands in a rolling mill is proposed, which is characterized in that at least one input of a rolling mill is connected via a drive coupling with a drive to a scaffold place by a drive-side coupling part remains stationary and the rolling stand is displaced with the rolling stand side coupling part such that the input clutch closes. Advantageous for this method, but also to solve the problem set out above, the fact that a particularly fast and reliable coupling of the rolling stand can be ensured with its drive, since in itself the two coupling parts of the input coupling only need to be plugged together, without any Perform adjustment or adjustment work, especially when the respective rolling stand is guided on a suitable track. It will be readily apparent that both the set-up times are minimized and the operational safety of such a coupling is maximized due to the simple structure, as has already been explained above.

In particular, in the interaction of the above-mentioned solutions, it is possible to provide 4-roll stands, which allow at a displacement of 45 °, the frameworks to be inserted into the mill stand, that automatically couple the input clutches, compactly builds the drive system and the mill stand change smallest space takes place.

Figur 1

ein Walzwerk in perspektivischer Schemaansicht;

Figur 2

eine Frontansicht auf das erste Walzgerüst des Walzwerks nach Figur 1;

Figur 3

schematisch ein 3-Walzengerüst mit einem Eintrieb und drei angetriebenen Walzen;

Figur 4

schematische ein 4-Walzengerüst mit zwei Eintrieben und zwei angetriebenen Walzen;

Figur 5

schematisch ein 4-Walzengerüst mit zwei Eintrieben und vier angetriebenen Walzen;

Figur 6

eine Detailansicht der Anordnung nach Figur 5, teilweise geschnitten;

Figur 7

eine perspektivische Ansicht der Anordnung nach Figuren 5 und 6 einschließlich Walzengerüst;

Figur 8

die Anordnung nach Figuren 5 bis 7 in ähnlicher Darstellung wie Figur 5 mit dargestellten Überlastzylindern; und

Figur 9

eine Detailansicht der Überlastzylinder.

It is understood that the features of the independent claims can also be cumulated in order to be able to implement the advantages in a cumulative manner. Further advantages, objects and characteristics of the present invention will be explained with reference to the following description of appended drawings. In the drawing show:

FIG. 1

a rolling mill in perspective schematic view;

FIG. 2

a front view of the first mill stand of the rolling mill to FIG. 1 ;

FIG. 3

schematically a 3-roll stand with a drive and three driven rollers;

FIG. 4

schematic a 4-roll stand with two drives and two driven rolls;

FIG. 5

schematically a 4-roll stand with two drives and four driven rollers;

FIG. 6

a detailed view of the arrangement FIG. 5 partially cut;

FIG. 7

a perspective view of the arrangement according to Figures 5 and 6 including roll stand;

FIG. 8

the arrangement after FIGS. 5 to 7 in a similar representation as FIG. 5 with illustrated overload cylinders; and

FIG. 9

a detailed view of the overload cylinders.

According to the embodiment FIGS. 1 and 2 Each scaffolding station 57 is assigned its own controllable drive motor 51 and a transfer case 52, each with two drives, to a respective rolling stand located on the scaffolding station 57 in a rolling position 61. In this case, the drive motors 51 rest on a foundation 50, which also carries the scaffolding places 57. The rolling stands 12, in turn, each comprise four rollers which form a caliber for rolling stock to be rolled. All rolling mills 12 according to this embodiment, apart from the caliber diameters, which in this embodiment taper in a rolling direction from rolling stand 12 to rolling stand 12 and can change their caliber in other embodiments, are identical in construction.

The rolling stands 12 of the even-numbered scaffold places 57 are arranged inclined in this embodiment in the rolling stand within the rolling line by 22.5 ° to a roll axis 17 corresponding to the rolling axis with respect to the horizontal. Correspondingly, the rolling stands 12 of the odd-numbered scaffolding places 57 in the rolling stand are offset within the rolling line by -22.5 ° relative to a rolling axis corresponding to the rolling direction 17 with respect to the horizontal. Accordingly, a roll stand 12 is offset to the next adjacent roll stand 12 in each case by 45 ° about the rolling axis.

The individual stands 12 sit in this embodiment each on a guided change shoe 53 with rollers. This special changing device allows a framework change in a few minutes in a confined space.

The rolling stand change of the even-numbered scaffolding places 57 takes place in the rolling direction 17 from the right side of the rolling line. The rolling stand change the odd-numbered scaffolding places takes place in the rolling direction 17 from the left side of the rolling line. On each side of the rolling mill is an on unnumbered rails, which are supported by the foundation, displaceable changing carriage 54 for receiving both the up to a change in use rolling stands 12 as well as prepared for use rolling stands 12. Also located on each Rolling mill side for each rolling stand 12, a rolling stand extractor 55 with a hydraulic Ausziehzylinder, each mounted on the foundation 50. The change of the individual rolling stands 12 is easily possible with the aid of these rolling stand extraction devices 55.

The rolling stands 21 in use are pulled to change with the cylinder of the rolling stand extractor 55 from the rolling stand or from their framework place 57 on the respective change carriage 54, wherein they describe on a change path 60 an arc and from the inclined position of 22.5 ° or . 22.5 ° in their change position 61 reach their horizontal position on the change carriage 54 in a change position 58. Thereafter, the change carriage 54 moves along the rolling direction 17 by a stand distance. Now, the rolling stands 12 provided for replacement are located in front of the rolling mill stand opening or with their changing position 59 in front of the scaffolding place 57 and can be pushed with the cylinder of the rolling stand pull-out device 55 to the stand space 57 in the rolling position 61 within the rolling stand. When the rolling stands reach an inclined position of 22.5 ° and -22.5 °, respectively, and are brought to the rolling position 61 when moving on the exchange path 60, input clutches 56 for transmitting the drive power of the drive motors 51 to the rolling stands 12 automatically engage.

The automatic coupling of the input clutches is facilitated by the inclined position of the exchange path 60 of 22.5 ° or -22.5 ° in the region of the rolling position 61, since no further forces are required for the dome operation due to gravity. The rolling stand extractor 55 thus requires only a fraction of the drive power for retracting the rolling stands 12 into the rolling positions 57 than for extending the rolling stands 12 after use. Also, the inclined trajectory 60 requires a high level of operational reliability during rolling, since the rolling stands 12 abut against the respective frame place 57 due to their own weight and are positioned in this way. In that respect, if necessary, how In particular, in this embodiment, an additional backup for positioning the rolling stands 12 omitted.

The rolling mills 12 removed from the rolling mill, which are now stored correspondingly displaced on the change carriage 54, can be taken from the change carriage 54 with a crane after resuming the rolling operation, fed to a further use and replaced by new rolling mills 12. Other measures, such as an immediate maintenance or the like may possibly be made there. In this embodiment, the interchangeable shoes 53 preferably remain on the change carriage 54 when the rolling stands 12 are removed from the change carriage 54. It is clear on the basis of the two change positions 58, 59 on the common change carriage 54, that the set-up time and thus the downtime of the rolling mill are reduced to a minimum, since the actual transport of the rolling stands 12 to the rolling mill and decoupled away from the mill away from the actual setup is.

The alternating arrangement of the rolling stands 12 along the rolling line or along the rolling direction 17 offers, as the FIG. 1 can be removed, the other already mentioned advantage that the rolling stands 12 are mutually offset by 45 ° to the rolling axis. As a result, a possibly resulting in rolling burr when passing through the next roll stand 12 is smoothed again, since abutting edges of the rollers 2, 3, 16 used in each stand 12 at each pass of a roll stand 12 at a different position, namely offset by 45 ° , are located.

In the sectional view of the rolling mill to FIG. 2 the arrangement of an even-numbered scaffolding site 57 with an angle of 22.5 ° to the horizontal and the right side to the rolling direction 17 arranged changing device clearly. The mirror-image arrangement applies to the odd-numbered scaffolding places 57, wherein in each case a drive 51 of an even-numbered scaffolding site 57 is arranged below the change-over position 58 of an odd-numbered scaffolding site 57. The alternating arrangement of the drives 51 further allows the use of stronger drives, since now 17 more free space for a single drive remains along the rolling direction and drives with approximately twice the diameter and consequently a higher torque can be used. When using a rolling mill 12 with only a single input clutch can in such an embodiment to a translation or gear reduction or be dispensed with a transfer case entirely, if the drive power of a more powerful drive 51 may be sufficient even at a non-translated or reduced speed.

In addition, in this exemplary embodiment, the changing orientation of the respective exchange paths 60 directly implies that in each case between the rolling stands 12 in the individual change positions 58 there is sufficient space for another rolling stand 12 in one of the change positions 39, since at this height the scaffolding station 57 of FIG the other side is equipped or converted. Thus, by a displacement of the changing carriage 54 about a rolling stand width, a corresponding set of new rolling stands 12 can be provided.

• 3-Walzengerüst mit einem Eintrieb 1 und drei angetriebenen Walzen 2, 3,
• 4-Walzengerüst mit zwei Eintrieben 1 und zwei angetriebenen Walzen 2, oder
• 4-Walzengerüst mit zwei Eintrieben 1 und vier angetriebenen Walzen 2, 3,

wobei ggf. der Neigungswinkel der Wechselbahnen 60 an die jeweiligen Erfordernisse angepasst werden kann.The rolling stands after the FIGS. 1 and 2 For example, rolling mills can be of the following types:

• 3-roll stand with a drive 1 and three driven rollers 2, 3,
• 4-roller stand with two drives 1 and two driven rollers 2, or
• 4-roll stand with two drives 1 and four driven rolls 2, 3,

where appropriate, the inclination angle of the exchange paths 60 can be adapted to the respective requirements.

A 3-roll stand with a drive 1 and three driven rollers 2, 3 has, as in FIG. 3 shown by way of example, for example, two bevel gear pairs, each consisting of two bevel gears 7, 8, which are provided on both sides of a coaxial to the drive driven roller 2 and in turn each drive a driven roller 3. The rollers 2, 3 are hereby set at an angle of 120 ° to each other and arranged in the rolling mill 12. Such a unit can in particular be used both in stretch-reducing mills and in sizing mills or in Ausziehwalzwerken. In this case, such rolling stands 12 may be formed with or without a thru axle 4 and fixed or adjustable.

In the case of a 3-roll stand results, as can be seen immediately, an optimal angle of the exchange path 60 in the inclined portion of 30 ° or -30 ° relative to the horizontal, as between a symmetry axis of a roller 2, 3 and their abutting outer Each edge gives an angular distance of 60 °. With such an offset, as already explained above in connection with a 4-roll stand, a burr emerging in a first roll stand 12 can be smoothed again in the following rolling stand 12.

It is immediately apparent that for any two arranged in the rolling direction 17 stands 12, any other angular offset is possible, however, in the described arrangements with 45 ° or 60 ° offset, the forces acting on a burr rolling forces reach a maximum and thus achieves the best possible rolling result becomes. Possibly. However, it is also possible to provide a rolling surface deviating from the circular shape in that - in the plane of the drawing FIGS. 3 to 6 - At the abutting edges of two rollers 2, 3 is a smaller radius than in the region of the axis of symmetry of a roller, whereby a constant around the circumference of the rolling force can be achieved. Likewise, other arrangements of the rolls in the roll stand 12 and / or a different from 45 ° or 60 ° offset of the rolling stands 12 and the rollers 2, 3 or other or variable inclination angle may be provided for special rolling operations.

The thru axle 4 in a rolling mill 12 after FIG. 3 leads the driven roller 2 and the means of the bevel gears 7, 8 also driven rollers 3 to the input drive 1 supplied to drive power. The roll stand 12 has a roll stand-side coupling part 11 of the input coupling, which is in rotary operative connection with the plug-in axis 4 and which in turn, as explained in the preceding embodiment, cooperates with a drive-side coupling part of the input coupling, wherein the rolling stand 12 through the inclined exchange path selbsttätig causes the coupling of both coupling parts.

The two coupling parts are here, as in the other embodiments explained, always aligned coaxially with one another in the region of the rolling position 61. Thus, the rotational axis 15 of the input clutch coincides both with rotational axes of the two coupling parts and with a rotational axis of the driven roller 2. In addition, the axis of rotation 15 of the input coupling runs parallel to the exchange path 60.

Possibly. The driven rollers 3 may also be designed as drag rollers.

For a 4-roll stand after FIG. 4 with two drives 1 and two driven rollers 2, these are arranged opposite one another and in each case connected to one of the two drives 1. Each offset by 90 ° to the two driven rollers 2, a total of two guide rollers 16 are provided. This arrangement is also preferably held in a roll stand 12 (not shown here) and can be used both in stretch-reducing mills and in sizing mills or in drawing-out mills. In this case, such rolling stands 12 can be formed with or without thru axle 4 and fixed or adjustable.

In a 4-roll stand with two drives, in contrast to the previously explained 3-roll stand, the two guide rollers 16 are decoupled from the driven rollers 2. A rotation of these drag rollers 16 thus takes place only via the movement of the rolling stock along the rolling direction 17, wherein the drag rollers 16 are dragged over a force acting on the rolling contact pressure.

In contrast to the previous embodiment, the driven rollers 2 of the 4-roll stand do not have coaxial axes of rotation to the stub axles 4 and to the drives 1. Between the thru axle 4 and the driven roller 2 and on the side facing away from the plug axis of the driven roller 2 is each provided an eccentric bushing. This eccentric bush 9 makes it possible to adjust the respective roller to the rolling stock to be rolled, with the drag rollers 16 also having corresponding eccentric bushings 9. The contact pressure and the rolling dimension can be adjusted via a force exerted on the eccentric bushing 9 according to the requirements. On the eccentric bush 9 acts in this embodiment, to generate the contact pressure in a FIG. 4 Unillustrated overload cylinder.

The two drives 1 one in the FIGS. 5 to 8 illustrated 4-roll stand with four driven rollers 2, 3, but also the above-explained 4-roll stand with two driven rollers 2, have aligned parallel axes of rotation 15 of their input clutches. This arrangement ensures the automatic closing of the input clutch during setup and lowering of the roll stand 21 on the exchange path 60 in the rolling position 61st

That in the FIGS. 5 to 8 illustrated 4-roll stand with two drives 1 and four driven rollers 2, 3 has in deviation from the 3-roll stand after FIG. 3 to accommodate high scaffolding torques and rolling forces two roller units. In each case one drive 1 two mutually perpendicular rollers 2, 3 are driven via two mutually meshing bevel gears 7, 8, wherein the bevel gear angle is 45 °.

In this case, the respective inner bevel gears 7, 8 are mounted separately in a cassette 6 displaceably guided in the roll stand. Furthermore, the bevel gears 7, 8 sit with a splined profile displaceable at the end of short shaft pieces of a respective associated plug-in axis 4, 5, the other end sits with a Innenvielkeilprofil on the roll shafts. The shaft pieces are mounted by means of rolling bearings in eccentric bushes 9. In an eccentric adjustment of the rollers 2, 3, the cassettes 6 are moved and thus also fixed therein bevel gears 7, 8, which thereby move in the splined profile of the roll ends. The eccentric bushings 9 are provided on both sides with a flattening on the side facing away from the rolling stock. The center of the eccentric is shifted in the rolling direction 17 in the rolling stand. The employment of the rollers 2, 3 and the rotation of the eccentric via threaded bolts in the roll housing which press on one side of the flattening. Brackets with threaded bolts surround the flattening of the eccentric bushing 9. On the threaded bolt sit spur gears which mesh with a ring gear. By turning the ring gear in the circumferential direction and simultaneously the threaded bolts are rotated with the attached spur gears, whereby the radial position of the rollers changes. The roller shafts units designed as stub axles 4, 5 are braced with a threaded rod 10 and a clamp nut 10.

The rolling stand 12 has in the embodiment of the FIGS. 5 to 8 two scaffolding plates 13, which enclose four angle pieces 14. In this respect, take the scaffolding plates 13 to the rolling forces. The angle pieces 14 are processed before joining, preferably before welding, and are in this embodiment with their shoulders firmly in the surrounding them scaffold plate 13. It is understood that instead of such a scaffolding construction and a conventional rolling mill, for example as a cast body, for use can come.

In particular, the cassettes 6 in this case form separate framework parts, so that in the present case two separate framework parts are provided, which each have a drive 1, which is connected to two mutually perpendicularly aligned roller 2, 3. The cassettes 6 or the separate framework parts in turn are in turn mounted on the framework body formed by the framework plates 13. In other embodiments, it is conceivable that in each case two opposing rollers are provided in a frame part. The separate scaffolding parts allow high scaffolding moments and rolling forces to be absorbed.

As overload protection conventional break bolts or other known devices may be used. In the present embodiment, as in particular in FIG. 8 shown, hydraulic overload cylinder 20 is provided, whereby a quickly put back in their operating state overload protection can be realized, which can be done for example simply by providing the appropriate pressure. Also, a corresponding signal can be tapped quickly and reliably and used for further reactions, such as to shut down the entire rolling mill.

The hydraulic overload cylinder 20 exist, as in detail in particular FIG. 9 In a roll stand 12, one of the rolls 2, 3 has two overload cylinders 20 which act on the eccentric bushes 9. A rolling stand 12 of a 4-roll stand therefore has eight separate overload cylinders 20.

Through the cylinder cover 21 performs a retaining pin 23 with an anti-rotation 22. Hereby, a fine adjustment of a gap between a guide piece 27 of the overload cylinder 20 and the underlying eccentric 9. A formed between the piston 25 and the cylinder cover 21 displacement 24 is in this embodiment with subjected under high pressure oil or grease, possibly also other media can be used accordingly. The overload cylinder 20 are connected in this embodiment by means of pipes via pressure ports 28 with each other, which may possibly be waived. However, a common triggering of the overload protection for all rollers 2, 3 at the same time can not be so easily ensured in the absence of communication by means of the pressure port 28 or other means for signal transmission become. The overload cylinders 20 are adjusted via a common valve such that they open at a set release force and the guide piece 27 releases the eccentric bushes 9 with the inner parts. This is done in contrast to the conventional breaking pin, which does not necessarily break all the bolts at the same time, at the same time and in particular reversible.

Such an overload protection, in particular a synchronization with respect to all the rolls of a roll stand, is particularly advantageous for Ausziehwalzwerke.

Reference numerals:

1

input drive

2

driven roller

3

driven roller

4

floating axle

5

floating axle

6

Cassette for bevel gear pair

7

bevel gear

8th

bevel gear

9

eccentric

10

Threaded rod with clamp nut

11

Roller frame side coupling part of the input clutch

12

rolling mill

13

scaffolding sheet

14

elbow

15

Rotation axis of the input clutch

16

idler

17

rolling direction

20

Overload cylinder

21

cylinder cover

22

twist

23

retaining bolt

24

capacity

25

piston

26

cylinder body

27

guide piece

28

pressure connection

50

foundation

51

drive motor

52

Transfer Case

53

exchange Shoe

54

change car

55

Walzgerüstausziehvorrichtung

56

Input drive coupling

57

scaffolding place

58

change position

59

further change position

60

AC train

61

roll position

Claims (18)

Rolling mill for rolling elongated material with a plurality of rolling stands (12) arranged in line, forming a central caliber opening, wherein the rolling stands (12) are each arranged in a framework (57) and can be displaced to at least one change position (58, 59), in particular according to one of the preceding claims, characterized in that each scaffold station (57) has a input clutch and the input clutch a roller stand side coupling part (11) and a drive-side coupling part, wherein the drive-side coupling part axially fixed to the framework place (57) is provided. Rolling mill according to claim 1, characterized by two input clutches per rolling stand (12) and scaffold place (57), wherein the two input clutches each axially to their axes of rotation (15) and the axes of rotation (15) are aligned parallel and both input clutches on one side of the Line are arranged. Rolling mill according to one of the preceding claims, characterized in that a drive with a drive motor (51) is provided on at least one framework site (57), which is connected to a transfer case (52) having at least two outputs, wherein the outputs each Having drive-side coupling part of the input clutch. Rolling mill for rolling elongated material with a plurality of rolling stands (12) arranged in line, forming a central caliber opening, wherein the rolling stands (12) are each arranged in a framework (57) and can be displaced to at least one change position (58, 59), characterized in that the change position (58) is provided on a change carriage (54), wherein the change carriage (54) has at least one further change position (59). Rolling mill according to claim 4, characterized in that the change carriage (54) at least four change positions (58, 59), one change position (58) and a further change position (59) for each two scaffold places (57), wherein the two change positions (58) corresponding to the distance between the two scaffolding places (57) and the other two change positions (59) corresponding to the distance between the two scaffolding sites (57) are spaced from each other. Rolling mill according to claim 5, characterized in that the interchangeable positions (58) and the further interchangeable positions (59) are spaced from each other at least by the width of a rolling stand (12), preferably by the distance of the scaffold places (57). Rolling mill according to one of the preceding claims, characterized by at least one rolling stand extraction device (55) with a hydraulic pull-out cylinder. Roll stand with at least two driven rollers (2, 3) and with at least two drives (1), characterized in that each drive (1) has a roll stand side coupling part (11) and the rolling stand side coupling parts (11) are aligned parallel and in the same direction. Roll stand with at least four driven rollers (2, 3), characterized in that in each case two rollers (2, 3) are mounted on a common frame part, wherein the two frame parts are in turn mounted on a frame body. Roll stand according to claim 9, characterized in that each frame part a drive (1) and two perpendicular to each other aligned rollers (2, 3) is provided. Roll stand according to claim 10, characterized in that the rollers (2, 3) via two mutually meshing bevel gears (8, 9), preferably with a cone angle of 45 °, are operatively connected to each other. Roll stand according to claim 11, characterized in that the two meshing bevel gears (8, 9) are arranged in a cassette (6). Roll stand with rollers for receiving rolling forces which occur during rolling of elongated material, characterized by a framework body having at least two scaffold plates (13), wherein the scaffold plates (13) are arranged parallel to each other and perpendicular to the rolling forces. Roll stand according to claim 13, characterized in that according to the number of rollers (2, 3) angle pieces (14) are provided, which receive the rolling forces and transmitted to the scaffold plates (13). Roll stand for receiving rolling forces that occur during rolling of elongated material, characterized by a hydraulic overload protection. Roll stand according to claim 15, characterized in that according to the number of rollers (2, 3) overload cylinders (20) are provided which communicate with each other. Method for changing rolling stands (12) in a rolling mill, characterized in that at least two rolling stands (12) are displaced from their rolling position (61) to a common side and to changing positions (58, 59) which are spaced from each other by at least one rolling stand width are, wherein both rolling stands (12) are displaced together with at least one further roll stand (12) to a rolling stand width, before the further roll stand (12) is then moved to its rolling position (61). Method for changing rolling stands (12) in a rolling mill, characterized in that at least one input drive (1) of a roll stand (12) is connected via a drive coupling to a drive at a scaffolding station (57) by a stationary drive coupling part remains stationary and the Roll stand (12) with the rolling stand side coupling part (11) is displaced such that the input clutch closes.

Images