DE2949043A1 - Continuous rolling of semi-finished prods. or thick steel profiles - in row of horizontal and vertical rolling mills using stands with the same flexure characteristics - Google Patents

Abstract

The rolling mill train consists of a row of horizontal mills used alternately with vertical mills; and all the mills are two- high with grooved rolls. All the mill frames or stands possess the same flexure or spring characteristics; and the rolls in all the stands are adjusted from both sides while being subjected to the rolling force. The rolling pressure is measured by transducers located in tie rods or straps, which transmit the rolling pressure to the chocks carrying the rolls; and the roll gap is pref. adjusted via eccentrics or pistons in hydraulic cylinders. Simplified control of the rolling pressure so fully automatic operation of the rolling mill train is possible with reduced capital- and labour-costs.

Description

Continuous rolling mill for semi-finished products and

Section steels The invention relates to a continuous rolling train for semi-finished products and profile steels with duo-groove roller sets in a 7-zontal vertical arrangement, with one-sided adjustment of the rolls of the horizontal roll stands and both sides Adjustment of the rolls of the vertical roll stands, with a control of the drives of the roll sets of the individual roll stands.

According to the prior art, roll stands are closed Stands used, with one-sided pressure spindle adjustment of the rolls in the horizontal roll stands and two-sided pressure spindle adjustment of the rolls in the vertical roll stands. As a result, the elongation behavior of these roll stands is different. the Spring characteristics of the roll stands are not linear. Due to the friction losses of the pressure spindles, the rollers can only be adjusted under pressure at considerable expense possible. Due to the different and non-linear spring characteristics the roll stands is a pre-setting of the rolls to a specific roll gap, the under load is enough, only empirically or with a considerable amount Standard effort possible. The consequence is material losses due to the necessary test rods when running in the rolling train with a new calibration or after a replacement the worn rollers.

It is also known to set the speeds of the main drives automatically to be set according to the acceptance in the individual roll stands, and these setting values, depending on the torques and the rolling pressures. For this scheme is disadvantageous that the rolling pressure measurement in conventional rolling equipment with Is fraught with inaccuracies, since the rolling force measurement in conventional roll stands on the one hand by the non-linear and different spring characteristics horizontal and vertical scaffolding and on the other hand, for example by tilting and frictional moments due to deflection of the rollers or contractions of the closed ones Stand, due to the rolling forces, is falsified.

The object of the invention is to avoid the aforementioned disadvantages a structural and technical simplification of the continuous rolling mill to propose for semi-finished products and heavy profile bars, which makes it possible, as a result of the structural design features of the roll stands already the roll sets of the interchangeable stands before installation in the rolling train on the one for rolling a finished product with high tolerance to set the necessary value for the roll gap in order to then when starting up the rolling train immediately a corresponding to the permissible tolerances To get the finished product and to simplify the technical problems, like that that the rolling train can thus be run fully automatically with a minimum control can and also an optimal pro- film constancy over the entire production time is maintained and a higher throughput while reducing the number of operating personnel as well as the investment costs is possible.

The use of roll stands is used to solve the problem suggested that both as. Horizontal roll stand as well as vertical roll stand have the same and linear spring-back characteristics, with a release or adjustment under rolling pressure and mutual adjustment of the rolls of the horizontal and the Vertical roll stands, with the roll pressure detection in all roll stands free of falsifying influences exclusively in the the rolling forces on the roll mounting parts transferring components takes place.

Furthermore, an additional regulation of the roll drives of all roll stands depending on the rolling pressure measurement.

Advantage of such a design of a semi-finished profile rolling mill is that, due to the same elongation behavior of all roll stands and the Use of roller adjustment devices with low friction losses and designed for loosening or adjusting under rolling pressure, an exact pre-setting of the roll gap and reproducibility of these adjustment values is possible. Furthermore, an essential Simplification and improvement of the regulation of the roller drives achieved, with a The rolling forces are recorded without distorting influences. Ensure these benefits better tolerances of the rolled semi-finished product or profile steel and low material losses by trial rolling, in addition, will be much simplified and improved Conditions for an automation of the rolling mill created and thus to a simplification of the operation of the rolling train and saving of operating personnel contributed.

In a further embodiment of the invention, there is an additional regulation the stand drives of all roll stands depending on the roll pressure measurement. Through this can the conventional longitudinal tension control by changing the torque the roll drives on the roll stands also regulate the torques of the rolls are superimposed in the roll stands, so that a low-deceleration Regulation of a constant tolerance of the finished profile in areas different temperature is maintained over the length.

The roll stands are available as a stand with a shortened power flow path or designed as so-called standless rolling stands, in which the rolling forces tie rods, tension straps or tie rod spindles transferred from the components form, in which structurally identical strain gauges can be installed.

The components transmitting the rolling forces from the chocks are shorter and smaller in distance than the width of the roller bearing chocks or smaller than the maximum roll barrel diameter. The rollers are adjusted by means of eccentrics or hydraulic piston-cylinder units.

Exemplary embodiments of the invention are shown in the drawing.

1 shows a continuous profile rolling train in a horizontal-vertical arrangement in principle, Fig. 2 shows the formation of the dual horizontal and dual vertical rolling stands as compact scaffolding in strap frame construction, 3 shows the horizontal roll stand in the front view in principle, Fig. 4 the vertical roll stand in the front view in principle and Fig. 5a, 5b the arrangement of the roller pressure transducers in the tabs in the front and side views.

In Fig. 1 is a rolling train for rolling out semi-finished and heavy Profile steels with finished cross-sections of, for example, approx. 60 to 200 mm as round profile cross-sections, from approx. 50 to 200 mm square as square or billet cross-sections or 100 to 400 mm wide and 10 to 100 mm thick shown as flat profile cross-sections.

The starting block cross-section is initially in a known manner in a Duo-Reversier-Walzgerdst 1 pre-rolled to the preliminary profile and then runs in a continuous or semicontinuous framework group consisting of one or more relays of roll stands, which each consist of a duo horizontal roll stand in succession 4 and a vertical roll stand 5 are formed. The horizontal and vertical roll stands 4, 5 are set up on rollers for the stand changeover to traversing tracks 8, 58 to the rolling line. or retractable.

According to the invention, as shown in FIG. 2, the horizontal roll stand 4 and the vertical roll stand 5 structurally identical and with the same almost linear one Expansion behavior and thus the same springiness characteristic as compact scaffolding executed short power flow path to absorb the rolling forces.

The vertical roll stand 5 is only inserted into a guide frame 6 and tense in this. In the present embodiment, the horizontal stand 4 and the vertical frame 5 as a so-called tab frame according to DE-PS 2 002 745 executed. Alternatively, instead of the one shown in the exemplary embodiment Tab stands 4, 5 any other structural design of compact rolling stands such as Standless roll stands or prestressed roll stands with a shortened power flow path for the rolling forces for the stand group described above, analogously for the horizontal-vertical arrangement in heavy continuous or semi-continuous semi-finished or profile lines Find application.

The dual roll stand group shown as an exemplary embodiment in FIGS. 2, 3 and 4 with the horizontal roll stand 4 and the vertical roll stand 5 is in their structural Concept described as follows: In the horizontal roll stand 4 is 10 and 11 denotes a Duo-Horizontal-KaliXerwalzsatz. The rollers 10, 11 are in chocks 10a, 11a stored. The chocks 10a are in pull tabs 13 and the chocks 11a are suspended pivotably in pull tabs 14 in the frame parts 16. the Duo horizontal rolls 10, 11 are driven by articulated spindles 7, 7a from a comb rolling stand 9 driven by a drive motor (not shown).

The tension straps 13, 14 are suspended in the frame parts 16 on the one hand via bolts 17, while the pull tabs 13, 14 on the other hand via the frame parts 16 penetrating eccentric bolts 18 are set. The eccentric bolts 18 are for example non-rotatably connected to worm gears 19, not shown, of worms. The worm gear 19 serve by turning the eccentric bolts 18 for radial adjustment or for releasing the horizontal rollers 10, 11 under rolling pressure in the event of malfunctions in rolling operations. In the neutral phase of the pull tabs 13, 14 are roller pressure transducers 20 (see. Fig. 5a, 5b) are used. The frame parts 16 are for example by means of hydraulic piston-cylinder units 20 releasably connected to the base plate 21. With 23, 24, 25 rolling stock guides are designated.

The horizontal roll stand 4 is connected in the rolling direction R a vertical roll stand 5, which in a guide frame 6, for example by means of hydraulic piston-cylinder units 30 is releasably braced. The real one The structural conception of the vertical roll stand 5 is also a strap stand with the same, approximately straight running spring characteristic as the horizontal rolling stand 4 designed as a compact frame.

The vertical roll stand 5 has vertical duo-caliber rolls 40, 41, the are mounted at both ends in chocks 40a, 41a. The chocks 40a are in Pull tabs 43 and chocks 41a are in pull tabs 44 in the frame parts 46 suspended pivotably.

The tension straps 43, 44 are suspended in the frame parts 46 on the one hand via bolts 47, while the pull tabs 43, 44 on the other hand via the frame parts 46 penetrating eccentric bolts 48 are set. The eccentric bolts 48 are for example non-rotatably connected to worm gears 49 (not shown) by worm gears 49. The worm gears 49 are used by turning the eccentric pin 48 to the radial Setting up or releasing the vertical rollers 40, 41 under roller pressure in the event of malfunctions in rolling operations. In the neutral phase of the pull tabs 43, 44 are roller pressure transducers 50 (cf. FIGS. 5a, 5b) are used, the measured values of which are superimposed on the torque control will and thus a low-delay correction of the torque control of the roller drives cause.

The vertical roll stand 5 is suspended in a cross member 51, which via worm gear 52 and threaded spindles 53 from a not shown Drive can be raised and lowered so that, on the one hand, the respective roll caliber of the vertical rolls 40, 41 can thus be adjusted to the rolling line and, on the other hand, to change the vertical rolling stand 5 this can be lowered into the extension plane or raised from this into the operating position is. The coupling or uncoupling of the roll necks with the drive spindles 62, 63 when changing stands, hydraulic piston-cylinder units 54 and lifting rods are used 54a. In the traverse 51, the vertical roll stand 5 is supported on both sides via rollers 55 on travel paths in the area of the guide frame 6 and is to change the scaffold Traversing tracks 58 arranged on rollers 57 and outside the guide frame 6 can be lowered or can be removed from them (cf. DE-PS 1 905 282).

The vertical rollers 40, 41 are driven by means of articulated spindles 62, 63 from above via a pinion gear 59, which is on the crosshead of the guide frame 6 is arranged. The drive motor 60 can alternatively be on the side of the guide frame 6 coupled to the roller stand 59 via articulated spindles 61 or directly to the Comb roll stand 59 be placed.

The advantage of such a design of the rolling train is on the one hand in that all frames have short power flow paths with the same approximately straight spring-back characteristic have, which is particularly low overall heights of the vertical rolling stands and on the other hand, due to the relatively light construction, does not require any deep foundations. On the other hand, the interchangeable stands can go so far before the stand change during assembly regarding the rollers and fittings are set that when connecting the control and regulation system immediately a tolerance-compliant profile is sent to the roller pressure transducer when the program is changed can be rolled. The control and regulation system is further enhanced by it simplified that the horizontal and vertical rolling stands are the same and almost linear Have spring-up characteristics and the tilting forces caused by the roll deflection can be largely eliminated in the roll pressure measurement.

Instead of the radial adjustment by means of an eccentric bolt, it is also possible an employment by means of hydraulic piston-cylinder units take place to a To enable adjustment of the rollers even under roller pressure.

In addition to the illustrated embodiment, other types of scaffolding are also available with a shortened power flow path such as prestressed roll stands or standless roll stands, where instead of the tension straps tie rods or tie rod spindles are used for the rolling forces Transferred from the chocks of the rollers to the frame parts or pick them up yourself, applicable accordingly.

All roll stands are controlled via the roll force measuring elements of the Gertist Group via the drives of the roll stands.

The components that transmit the rolling forces, such as tension straps, tie rods or tie rod spindles are smaller in their distance from each other than the width of the Roller bearing chocks or smaller than the maximum roller barrel diameter.

Claims (5)

Claims Continuous rolling mill for semi-finished and heavy products Section steels with dual groove roller sets in a horizontal-vertical arrangement, one Regulation of the drives of the roll sets of the individual roll stands and one-sided Employment of the rolls of the horizontal and bilateral employment of the rolls of Vertical roll stands, characterized by the use of roll stands with the same, almost linear expansion behavior (spring deflection curve) for all horizontal and Vertical roll stands (4, 5) with an adjustment under rolling pressure and on both sides Adjustment of the rolls of the horizontal roll stand (5), the roll pressure detection in all roll stands (4, 5) exclusively in the the rolling forces on the built-in parts transferring components takes place. 2. Continuous rolling mill according to claim 1, characterized in that that an additional control of the stand drives of all roll stands (4, 5) as a function from the roll pressure measurement (20, 50) takes place. 3. Continuous rolling train according to one of claims 1 or 2, characterized characterized in that the roll stands (4, 5) as a stand with a shortened power flow path or are designed as standless rolling stands, in which the rolling forces Transferring components tie rods, tension straps (13, 14, 43, 44) or tie rod spindles form. 4. Continuous rolling mill according to claim 3, characterized in that that the components transmitting the rolling forces are shorter and spaced from one another smaller than the width of the roller bearing chock or smaller than the maximum Roll barrel diameters are. 5. Continuous rolling mill according to one of the preceding claims, characterized in that the roller adjustment by means of eccentrics (18, 48) or hydraulic piston-cylinder units.