EP1018376A2 - Rolling train for rolling bar-shaped rolling stock, e.g. steel bars or wire - Google Patents

Abstract

Roll gaps (s3-s10) of the active roll stands (3-10) are adjusted via hydraulic cylinder units (12) which are controlled by roll gap regulators (13) by whose frame springs of the active roll stands are compensated into fractions. The fractions are separately adjusted for each roll stand. Mill train has active roll stands operating in pairs and being adjustable to roll gaps. The rolled material (11) can be rolled to a final height (h) and a vertical final width (b) by applying rolling forces (F3-F10). Roll gaps (s3-s10) of the active roll stands (3-10) are adjusted via hydraulic cylinder units (12) which are controlled by roll gap regulators (13) by whose frame springs of the active roll stands are compensated into fractions. The fractions are separately adjusted for each roll stand.

Description

The present invention relates to a rolling mill for rolling rod-shaped Rolled material, e.g. B. steel bars or wire, with several adjustable on nips, of the rolling stock passed through one after the other, combined into pairs of rolling stands active rolling stands, by means of which the rolling stock is applied with Rolling forces can be rolled to a final height and a vertical width perpendicular thereto.

Rolling mills of this type are generally known. The individual mill stands one Such rolling mill are alternately as horizontal and as vertical stands trained, the last pass rolling mill always the end profile, z. B. a round, square or hexagonal caliber.

In the prior art, the roll stands are open by means of electric or hydraulic motors Roll gap adjustable. The setting of the roll gap can usually only in load-free state. It is not possible to adjust the nips under load possible. It is only possible to change the speeds of the roll stands during the Operating change. Other interventions such as B. are a roll gap correction not possible.

In the older, unpublished German patent application 198 31 481.7 is a rolling mill for rolling rod-shaped rolling stock is described, the several adjustable from the rolling stock via hydraulic cylinder units on the roll gap has successive active rolling stands, by means of which the rolling stock applying rolling forces to a final height and a vertical one End width is rollable, the hydraulic cylinder units of roll gap controls can be controlled by means of which spring-force-related suspensions of the active roll stands can be compensated for at least to a fraction.

The task is based on the prior art mentioned at the beginning of the present invention therein, a rolling mill for rolling rod-shaped To create rolling stock in which the roll gaps are adjustable under load and above in addition, the rolling behavior of the roll stands can be adapted to the respective rolling stock is.

• daß die Walzspalte der aktiven Walzgerüste über Hydraulikzylindereinheiten einstellbar sind,
• daß die Hydraulikzylindereinheiten von Walzspaltregelungen ansteuerbar sind, mittels derer walzkraftbedingte Auffederungen der aktiven Walzgerüste zumindest zu Bruchteilen kompensierbar sind, und
• daß die Bruchteile für jedes aktive Walzgerüst separat einstellbar sind.

The task is solved by

• that the roll gaps of the active roll stands can be adjusted via hydraulic cylinder units,
• that the hydraulic cylinder units can be controlled by roll gap controls, by means of which spring force-dependent spring-ups of the active roll stands can be compensated for at least to a fraction, and
• that the fractions can be set separately for each active roll stand.

Due to the use of hydraulic cylinder units as adjustment devices an adjustment of the roll gap under load is possible for the roll gap. Because of The compensations of the spring forces caused by the rolling force are automatic Correction of these suspensions. Because in this case a possible rolling error but if it were rolled into full width, the spring-back only becomes too compensated for a fraction. Due to the adjustability of the fractions, the Roll stands can be optimally adapted to their respective task within the rolling mill.

The rolling stands take over in the rolling train depending on the rolling Product, various tasks, namely either an acceptance or a so-called Presizing or a so-called sizing.

The main task of acceptance stands is to make the cross section of the rolling stock possible greatly reduce. For this purpose, the respective roll stand should be as rigid as possible his. In connection with a monitor control, even with these rolling stands the cross section can be optimized.

The main task of presizing scaffolds is the ratio of height to width of the rolling stock in front of the subsequent sizing stands to a defined value adjust. For this, z. B. with a round end profile, the oval frameworks high and the round frameworks have an optimal rigidity. Because by that temperature and cross-sectional disturbances are even on both dimensions distributed.

The main task of sizing stands is to roll the rolling stock to the desired final dimensions to be rolled and at the same time to ensure good ovality of the rolling stock. For this, z. B. with a round end profile, the oval structure relatively high and the round scaffold have a lower, optimal rigidity.

• Die walzkraftbedingte Auffederung des von dem Walzgut später durchlaufenen Sizinggerüsts wird zu einem kleineren Bruchteil kompensiert als die walzkraftbedingte Auffederung des von dem Walzgut vorher durchlaufenen Sizinggerüsts.
• Die walzkraftbedingte Auffederung des von dem Walzgut später durchlaufenen Presizinggerüsts wird zu einem kleineren Bruchteil kompensiert als die walzkraftbedingte Auffederung des von dem Walzgut vorher durchlaufenen Presizinggerüsts.
• Die walzkraftbedingten Auffederungen der Abnahmegerüste werden zumindest im wesentlichen in vollem Umfang kompensiert.

The following settings are optimal:

• The spring force-related spring-back of the sizing stand later passed through by the rolling stock is compensated to a smaller fraction than the spring-force-related spring-back of the sizing stand previously passed through by the rolling stock.
• The spring force-related spring-back of the presizing stand later passed through by the rolling stock is compensated to a smaller fraction than the spring force-related spring-back of the presizing stand previously passed through by the rolling stock.
• The spring force-related spring-ups of the tapping stands are at least substantially fully compensated for.

The last two active roll stands always work in sizing mode. At least a pair of mill stands directly upstream of the sizing stands works in Presizing mode. The remaining mill stands work in acceptance mode. Because of The adjustability of the fractions can now be set which rolling stands work in sizing mode, in presizing mode and in acceptance mode.

The ovality of the end product is particularly good if the rolling force-related Springing of the sizing frames was compensated on average for smaller fractions are called the spring force-related spring-ups of the presizing stands.

Tolerance compliance is even better when the rolling stock is removed from the presizing stands is rolled such that the sizing frames in their most favorable dynamic range operate. This can e.g. B. can be achieved in that the roll gaps of the presizing stands can be determined from the roll gaps of the sizing stands.

The dimensional accuracy of the rolled rolling stock can be increased even further, if a measuring device is added to the sizing stand that is later passed through by the rolling stock is subordinate to the detection of the final height and final width of the rolling stock and the roll gaps of the sizing stands based on the recorded end height and width can be corrected (monitor control).

The rolling stock can be rolled even more precisely, even if the other pairs of stands, preferably even any other roll stand, measuring devices are subordinate to record the height and width of the rolling stock. In this In this case, the roll gaps for these roll stands can be taken directly from the detected heights and widths can be determined.

Between the individual roll stands is usually the one occurring in the rolling stock Train detected and the speeds of the rolling stands adjusted so that the train is constant. In addition, it is possible with the measuring devices Cross-section of the rolling stock between the roll stands. The train and / or Height and width measurements can be used Optimize fractions during rolling.

When a new rolling stock is rolled, the first billet should already be possible have the correct final dimensions in a batch. This can be achieved be that the rolling mill a storage device for storing a Variety of material properties of rolled goods, the final height, the final width, the framework parameters and the framework settings, an input device for entering the material properties, the final height and the final width of a new rolling stock to be rolled and a comparison device for comparing the material properties, the final height and the final width of the rolling stock to be rolled with the material properties, the final height and the final width of the saved Rolled goods and the current stand parameters with the saved Has stand parameters, so that the roll stands at matching Stand parameters when rolling a new rolling stock onto the stand settings for an already rolled rolling stock with corresponding material properties and final dimensions can be preset.

The stand parameters particularly include the roll diameters. The scaffold settings include in particular the roll gaps, the rolling speeds and the fractions. The material properties of the rolling stock include in particular the temperature, the initial dimensions and the quality of the rolling stock.

With such presets, when the new stick is actually the one entered Has material properties, an immediate optimal rolling this Bludgeon possible.

If in the storage device there are also a large number of rolling the rolling stock resulting rolling parameter can be stored and the rolling mill a comparison device to compare yourself when rolling the new rolling stock resulting rolling parameters with those corresponding to the new stand settings Rolling parameters and an output device for outputting a Warning signal when there are significant deviations when rolling the new one Rolling stock resulting from the rolling parameters with the new stand settings Corresponding rolling parameters, it is possible to use the billet to check whether he actually entered the material properties having.

The rolling parameters include in particular the rolling forces and / or the rolling moments.

Figur 1

eine Walzstraße für stabförmiges Walzgut und

Figur 2

eine Hydraulikzylindereinheit mit einer Walzspaltregelung.

Further advantages and details emerge from the following description of an exemplary embodiment. Show in principle

Figure 1

a rolling mill for rod-shaped rolling stock and

Figure 2

a hydraulic cylinder unit with a roll gap control.

According to FIG. 1, a rolling mill has roll stands 1-10, which are in succession are passed through by a rolling stock 11. The rolling stock 11 is in the present Case a rod-shaped rolling stock 11, for. B. steel bars or wire. The roll stand 10 is the first to pass through the roll stand 1 as the last. The mill stands 1 - 10 are alternately designed as horizontal and vertical frames. she have z. B. alternately round and oval calibers. That of the rolling stock 11 last passed through mill stand 1 z. B. a round caliber. Two in a row Roll stands 1 - 10 are combined to form a pair of roll stands.

The rolling stock 11 is subjected to rolling forces by means of the roll stands 1-10 F3 - F10 can be rolled to a final height h and a vertical width b perpendicular to this. The last two roll stands 1 and 2 are according to the embodiment inactive. So you do not roll the rolling stock 11. The rolling stock 11 passes through only the last two roll stands 1, 2. So there are only the roll stands 3 - 10 active. This is possible because the final dimensions h, b according to the embodiment are relatively large. With smaller values for the final dimensions h, b would the last two roll stands 1, 2 are also activated.

If the rolling mill is equipped with roll stands 1 - 10, the quick-change devices have inactive mill stands - in this case the Rolling stands 1 and 2 - extended from the rolling mill and only when necessary entered the rolling mill.

The roll stands 1 - 10 are all constructed in the same way. The following is therefore only the structure of the roll stand 3 described.

According to FIG. 2, a hydraulic cylinder unit 12 is assigned to the roll stand 3, by means of which a roll gap s3 can be set under load. The required rolling force F3 is associated with the hydraulic cylinder unit 12 and the working pressure p3 to whom this is applied. The hydraulic cylinder unit 12 is from controlled a roll gap control 13.

Before the start of rolling, the hydraulic cylinder unit 12 is controlled by the roll gap control 13 first controlled in such a way that the roll gap s3 closed becomes. The working pressure p3 is practically zero. If the roll gap s3 completely has closed, the working pressure p3 increases. Because of the increasing working pressure p3 increases the force F3 exerted on the roll stand 3. The mill stand 3 thereby springs open. The roll gap control 13 is continuously transmitted at which working pressure p3 which adjustment path a3 of the hydraulic cylinder unit 12 is taken. From this curve, the roll gap control 13 can then on the one hand the zero point of the roll gap s3 and the spring constant C3 of the Determine roll stand 3. The spring constant C3 is required to when rolling the spring force-related suspension, which is the product of spring constant C3 and rolling force F3 results.

At the start of rolling, the roll gap control 13 becomes a desired roll gap s3 * and an expected rolling force F3 * is given. Due to the known zero point of the Roll gap s3 and the known spring constant C3 can control the roll gap 13 then position the hydraulic cylinder unit 12 in such a way that the roll stand 3 assumes the target roll gap s3 * after springing open.

Due to various influences, e.g. B. roll eccentricities, cross-sectional fluctuations of the rolling stock 11, temperature fluctuations of the rolling stock 11, etc., the rolling force F3 varies during rolling. As a result, the roll stand 3 springs up more or less in accordance with the variable rolling force F3. Because of the known spring-back behavior of the roll stand 3, the spring-force-related spring-back can be continuously measured by detecting the working pressure p3 and correspondingly correcting the adjustment path a3 C3 · (F3 - F3 *) be compensated. In the case of the rod-shaped rolling stock 11, however, this would lead to the fact that the height h of the rolling stock 11 emerging from the roll stand 3 would be correct, but the entire rolling defect would be rolled into the width b. Preferably, the lamination of the roll stand 3 due to the rolling force is therefore only compensated to a fraction t3. The fraction t3 is given to the roll gap control 13 by a higher-level computer 14 - see FIG. 1.

What has been said above regarding the roll stand 3 also applies accordingly to the others active mill stands 4 - 10. In particular, the remaining active Roll stands 4 - 10 a nominal roll gap s4 * - s10 *, an expected rolling force F4 * - F10 * and a respective fraction t4 - t10 are specified.

The sizing frames 3, 4 only work with optimal dynamics if the cross section of the rolling stock 11 fed to them in a predetermined cross-sectional area Therefore, the rolling stock 11 is from the rolling stands 5, 6, the sizing stands 3, 4 are immediately upstream, always rolled such that the Sizing stands 3, 4 are operated in their most favorable dynamic range. The Roll stands 5, 6 thus work as so-called presizing stands 5, 6.

Further rolling stands 7-10 are immediately upstream of the presizing stands 5, 6. In these, the rolling stock 11 is rolled as much as possible to make it with a minimum total number of stitches to its final dimensions h, b roll can. The rolling stands 7-10 thus work as so-called acceptance stands 7 - 10th

According to the exemplary embodiment, only the roll stands 5, 6 are used as presizing stands 5, 6 operated. In principle, however, the rolling stands of two or even could three pairs of mill stands can be operated as presizing stands.

• Die walzkraftbedingte Auffederung des Sizinggerüsts 3 wird zu einem kleineren Bruchteil t3 kompensiert als die walzkraftbedingte Auffederung des Sizinggerüsts 4.
• Die walzkraftbedingte Auffederung des Presizinggerüsts 5 wird zu einem kleineren Bruchteil t5 kompensiert als die walzkraftbedingte Auffederung des Presizinggerüsts 6.
• Die walzkraftbedingten Auffederungen der Sizinggerüste 3, 4 werden im Mittel zu geringeren Bruchteilen t3, t4 kompensiert als die walzkraftbedingten Auffederungen der Presizinggerüste 5, 6.
• Die walzkraftbedingten Auffederungen der Abnahmegerüste 7 - 10 werden zu 90 % - 100 %, also zumindest im wesentlichen in vollem Umfang, kompensiert.

The fractions t3 - t10, to which the spring force-related spring-back of the roll stands 3 - 10 are compensated, can be set separately. In practice, the following settings have proven to be particularly advantageous:

• The spring force-related suspension of the sizing stand 3 is compensated for by a smaller fraction t3 than the spring force-dependent suspension of the sizing stand 4.
• The spring force-related suspension of the presizing stand 5 is compensated for by a smaller fraction t5 than the roll force-related suspension of the presizing stand 6.
• The spring force-related suspensions of the sizing stands 3, 4 are compensated on average to smaller fractions t3, t4 than the spring force-dependent suspensions of the presizing stands 5, 6.
• The spring force-related spring-ups of the tapping stands 7-10 are compensated for by 90% to 100%, that is to say at least essentially in full.

This compensation of the spring forces caused by the rolling force alone causes a significant increase in the quality of the rolled stock 11. In addition, 1, the two inactive roll stands 1 and 2 a measuring device 15 for detecting the final height h and final width b of the rolling stock 11. The detected end values h, b are transmitted to the higher-level computer 14. This continuously calculates new nominal roll gaps s3 *, s4 * for the sizing stands 3, 4. The roll gaps s3, s4 are thus due to the final height h and the detected final width b can be corrected.

The superordinate computer 14 can on the basis of the transmitted final dimensions h, b and the nominal roll gap s3 *, s4 * of the sizing stands 3, 4 the dimensions determine the rolling stock 11 between the roll stands 4 and 5. Based on these Ascertainable dimensions, the higher-level computer 14 can then also target roll gaps Determine s5 *, s6 * for the presizing stands 5, 6 and their roll gap controls pretend.

Alternatively, it is also possible, in addition to the measuring device 15 behind the Roll stand 1 to provide further measuring devices 16 - 19, which are immediately behind the pair of sizing stands, the pair of presizing stands and the pairs of acceptance stands are arranged. There is preferably even 1 behind each roll stand - 10 a measuring device 15 -19 arranged. Using the higher-level computer 14 is then the respective roll gap regulations of the individual roll stands 3 - 10 can be specified directly which roll gap s3 * - s10 * you should set.

Tension measuring devices are arranged between the roll stands 1-10. The For the sake of clarity, only one of the tension measuring devices is shown in FIG. 1, namely the tension measuring device 20 shown. The measured values of the tension measuring devices 20 are also transmitted to the higher-level computer 14. This can by comparing the train measurements with the positions of the previous one Roll stands 1 - 10 determine whether the fraction t3 - t10 by which the rolling force-related Spring deflections are compensated for, is optimally set. Possibly the respective fraction t3 - t10 can be corrected, so the result during of rolling are optimized.

This correction is of course even easier if the further measuring devices 16 - 19 are available. Then you can directly from the measured heights and widths of the rolling stock 11 behind the roll stands 9, 7, 5 and 3 to the optimum Fractions t3 - t10 can be closed.

For each rolled material 11 that has already been rolled, the parent computer 14 stored a record. The record includes on the one hand the roll diameters of the roll stands 1 - 10 as stand parameters, on the other hand the stand settings s3 - s10, t3 - t10 of the roll stands 1 - 10 and thirdly, the material properties of the rolling stock 11. For each roll stand 1 - 10 are therefore in particular the roll diameters, the roll gaps s3-s10, the rolling speeds and the fractions t3 - t10 are stored. Furthermore, it is saved what temperature, what initial dimensions and what quality has a rolled rolling stock 11. The data set also includes 11 per rolling stock the final height to be rolled h and the final width to be rolled b. Finally includes the data set also includes the rolling parameters resulting from the rolling of the rolling stock 11 F3 - F10, i.e. the rolling forces F3 - F10 and / or the rolling moments.

The temperature of the rolling stock 11 can, for example, by means of a temperature measuring device 22 are determined, which are arranged at the entrance of the rolling mill is. The material properties of the rolling stock 11 can, for example, have a Keyboard 23 serving as an input device in the higher-level computer 14 can be entered.

A large number of such data sets (per rolling stock) are in the storage device 21 11 one data record each) can be saved. If now roll a new rolling stock 11 is, the material properties of the Rolled stock 11 and the final dimensions to be rolled h, b entered. The parent Computer 14 then compares the entered data to be newly rolled Rolled stock 11 with the stored data records. If he finds a record, its material properties and final dimensions h, b with those of new rolling stock 11 to be rolled, he compares the current one Framework parameters with the saved framework parameters. They agree matches, he calls the corresponding settings s3 - s10, t3 - t10 from the storage device 21 and passes this to the roll gap controls 13 of the rolling stands 1 - 10. This makes it possible to get the first stick already a new batch immediately with good tolerances to the desired final dimensions h, b to roll. A slow approach to the right settings s3 - s10, t3 - t10 is not required.

In addition, the parent computer 14 when rolling the new Rolling stock 11 of course also when rolling the new rolling stock 11 resulting rolling parameters F3 - F10 of the roll stands 1 - 10 transmitted. Under the superordinate computer 14, the rolling forces applied F3 - F10 transmitted. The superordinate computer 14 compares these values with the rolling forces F3 - previously stored for an equivalent rolling stock 11 - F10. If there are significant deviations in this comparison, this is a Indication that the new rolling stock 11 is not the previously selected rolling stock 11 corresponds. In this case, an output device 24, for. B. one Monitor 24 issued a warning signal. Because of this warning signal can then an operator corresponding corrections of the settings of the roll stands 1 - 10 and, if necessary, an analysis of the newly rolled Arrange rolling stock 11.

With the rolling mill described above there is unprecedented flexibility achievable when rolling rolled goods 11. In particular, each roll stand is 1 - 10 can be activated individually. You can also set 1-10 for each individual roll stand, which fraction t3 - t10 of its spring force-related spring deflection it compensates for. In addition, it can be specified for each individual scaffold whether it is a monitor control, d. H. a correction of his target roll gap s3 * - s10 * due to the measured heights h and widths b of the measuring devices 15-19 or Not.

As a result, each of the roll stands 1 - 10 can be used as a sizing stand, as a presizing stand or operated as acceptance scaffolding. This is no longer one Question of the construction of the respective mill stand 1 - 10, but only one question the corresponding setting of the roll gap regulations, which is in seconds can be made.

According to the exemplary embodiment, all roll stands 1-10 are of identical design. In particular all roll stands 1 - 10 can be adjusted via hydraulic cylinder units 12. If it is known from the outset that only some of the roll stands 1 - 10 can be considered as sizing and presizing stands, the other rolling stands, e.g. B. the roll stands 9 and 10, but also be made in a different way. At least the presizing and sizing frameworks, at least the last four active roll stands 3 - 6, but should be hydraulically adjustable.

Reference list

1 - 10

Mill stands

11

Rolling stock

12th

Hydraulic cylinder unit

13

Roll gap control

14

parent computer

15-19

Measuring devices

20th

Tension measuring device

21

Storage device

22

Temperature measuring device

23

keyboard

24th

monitor

a3

Adjustment path

b

Final height

C3

Spring constant

F3 - F10

Rolling forces

F3 * - F10 *

expected rolling forces

H

Final width

p3

Working pressure

s3 - s10

Nips

s3 * - s10 *

Target nip

t3 - t10

Fractions

Claims (17)

Rolling mill for rolling rod-shaped rolling stock (11), e.g. B. bar steel or wire, with several adjustable on roll gaps (s3 - s10), from the rolling stock (11) successively, combined into rolling stand pairs active rolling stands (3 - 10), by means of which the rolling stock (11) with application of rolling forces (F3 - F10) can be rolled to a final height (h) and a vertical width (b) perpendicular thereto,
characterized, that the roll gaps (s3 - s10) of the active roll stands (3 - 10) can be adjusted via hydraulic cylinder units (12), that the hydraulic cylinder units (12) can be controlled by roll gap controls (13), by means of which spring force-dependent spring-backs of the active roll stands (3 - 10) can be compensated for at least to a fraction (t3 - t10), and that the fractions (t3 - t10) can be set separately for each active roll stand (3 - 10). Rolling mill according to claim 1,
characterized,
that in the rolling stands (3, 4) (sizing stands) of the pair of rolling stands last passed through, the spring force-related spring-back of the sizing stand (3) later run through by the rolling stock (11) is compensated for to a smaller fraction (t3) than the spring-force-related spring-back of the rolling stock ( 11) Sizing frame (4) previously run through. Rolling mill according to claim 2,
characterized,
that the rolling stock (11) is rolled by the roll stands (5, 6) (presizing stands) of at least one pair of roll stands directly upstream of the sizing stands (3, 4) in such a way that the sizing stands (3, 4) are operated in their most favorable dynamic range. Rolling mill according to claim 3,
characterized,
that the spring force-related spring-back of the presizing stand (5) later passed through by the rolling stock (11) is compensated to a smaller fraction (t5) than the spring-force-related spring-back of the presizing stand (6) previously run through by the rolling stock (11). Rolling mill according to claim 3 or 4,
characterized,
that the spring force-related spring-ups of the sizing stands (3, 4) are compensated for on average to smaller fractions (t3, t4) than the spring-force-dependent springs of the presizing stands (5, 6). Rolling mill according to claim 3, 4 or 5,
characterized,
that the roll gaps (s5, s6) of the presizing stands (5, 6) are determined from the roll gaps (s3, s4) of the sizing stands (3, 4). Rolling mill according to claim 3, 4, 5 or 6,
characterized,
that the presizing stands (5, 6) is immediately upstream of at least one pair of roll stands, in the roll stands (7 - 10) (removal stands) of which the rolling stock (11) is reduced as much as possible in cross section. Rolling mill according to claim 7,
characterized,
that the spring force-related spring-ups of the take-off stands (7-10) are at least substantially fully compensated for. Rolling mill according to one of claims 2 to 8,
characterized,
that a measuring device (15) for detecting the final height (h) and final width (b) of the rolled stock (11) is arranged downstream of the sizing stand (3) that is later passed through and that the roll gaps (s3, s4) of the sizing stands ( 3, 4) can be corrected on the basis of the detected final height (h) and final width (b). Rolling mill according to claim 9,
characterized,
that the other pairs of roll stands, preferably even every other roll stand (4 - 10), are followed by measuring devices (17 - 19) for detecting the height and width of the rolling stock (11). Rolling mill according to one of the above claims,
characterized,
that it has at least one temperature measuring device (22) for measuring the temperature of the rolling stock (11). Rolling mill according to one of the above claims,
characterized,
that the fractions (t3 - t10) can be optimized on the basis of tensile and / or height and width measurements during rolling. Rolling mill according to one of the above claims,
characterized,
that it has a storage device (21) for storing a large number of material properties of rolling stock (11), the final height (h), the final width (b), the stand parameters and the stand settings (s3 - s10, t3 - t10), an input device (23 ) for entering the material properties, the final height (h) and the final width (b) of a new rolling stock (11) and a comparison device (14) for comparing the material properties, the final height (h) and the final width (b) of the new rolling rolling stock (11) with the material properties, the final height (h) and the final width (b) of the stored rolling stock (11) and the current stand parameters with the stored stand parameters, so that the rolling stands (1 - 10) with matching stand parameters during rolling a new rolling stock (11) on the stand settings (s3 - s10, t3 - t10) for an already rolled rolling stock (11) with corresponding material properties and final dimensions (h, b) are ellellbar. Rolling mill according to claim 13,
characterized,
that the stand parameters include the roll diameters and stand settings (s3 - s10, t3 - t10), the roll gaps (s3 - s10), the roll speeds and the fractions (t3 - t10). Rolling mill according to claim 13 or 14,
characterized,
that the material properties of the rolling stock (11) include the temperature, the initial dimensions and the quality of the rolling stock (11). Rolling mill according to claim 13, 14 or 15,
characterized,
that a large number of rolling parameters (F3-F10) resulting from the rolling of the rolling stock (11) can also be stored in the storage device (21) and that the rolling train has a comparison device (14) for comparing the rolling parameters resulting from the rolling of the new rolling stock (11) (F3 - F10) with the rolling parameters (F3 - F10) corresponding to the new stand settings (s3 - s10, t3 - t10) and an output device (24) for outputting a warning signal in the event of significant deviations when the new rolling stock (11) is rolled resulting rolling parameters (F3 - F10) of the rolling parameters (F3 - F10) corresponding to the new stand settings (s3 - s10, t3 - t10). Rolling mill according to claim 16,
characterized,
that the rolling parameters (F3 - F10) include the rolling forces (F3 - F10) and / or the rolling moments.

Images