EP2745948A1 - Coiling device with reel shaft which can be bent back - Google Patents

Abstract

The reel device (3) has reel shaft (5) which is supported by two bearings (6), so that the reel shaft is rotatable by a shaft axis (7). A reel drum (8) is arranged on the reel shaft in the direction of the shaft axis between the bearings. The bending devices (10) are provided for applying back-bending moment to the reel shaft. The back bending moment is made to counteract the load bending moment generated during coiling of metal strip (1) between the two bearings on the reel drum and/or reel shaft.

Description

• wobei die Haspeleinrichtung eine Haspelwelle aufweist, die über mindestens zwei Lager gelagert ist, so dass die Haspelwelle um eine Wellenachse rotierbar ist,
• wobei auf der Haspelwelle in Richtung der Wellenachse gesehen zwischen den beiden Lagern eine Haspeltrommel angeordnet ist,
• wobei die Haspeltrommel in Verbindungsbereichen mit der Haspelwelle verbunden ist.

The present invention relates to a reel device for reeling a metal strip,

• wherein the reel means comprises a reel shaft which is mounted via at least two bearings, so that the reel shaft is rotatable about a shaft axis,
• wherein on the reel shaft in the direction of the shaft axis between the two bearings a reel drum is arranged,
• wherein the reel drum is connected in connecting areas with the reel shaft.

When rewinding metal strip - for example steel strip - often a band end is first inserted into a slot of the reel drum. After the end of the tape has reached a predetermined immersion depth, the reeling process is started. For this purpose, the reel shaft and with it the reel drum are rotated. In this case, the band end is supported radially on an inner shaft of the reel drum. The metal band is bent around a rounded edge of the slot. Then the metal strip is gradually wound up. During coiling, the metal strip is subjected to a strip tension. A uncoiling operation is in principle inverse to coiling.

To rewind a torque is required. The torque is applied by an electric machine. The passage of the torque required for reeling is carried out by the electric machine on the reel shaft and from there - usually arranged on the reel shaft hub and interconnected flanges of the hub and the reel drum - on to the reel drum. The torque transmission is, as is well known to those skilled in the art, for example via feather keys.

Applying the metal strip with the strip tension, the weight of the coiled metal strip, thermal loads occurring during reeling and other effects - such as the weight of the reel drum - lead to a load bending moment acting on the reel drum and the reel shaft. The load bending moment acts between the two bearings of the reel shaft. The passage of the load bending moment takes place from the metal strip on the reel drum and from there - usually via the interconnected flanges of the arranged on the reel shaft hub and the reel drum - on the reel shaft. The load bending moment changes its effective direction and its amount only slowly. In particular, the load bending moment usually only slightly changes its effective direction and its amount during a single revolution of the reel drum. The reel drum is, so to speak, permanently through-rolled by the load bending moment. The term "direction of action" here and also in the following refers to the direction in which the respective bend takes place. For example, if a force from above on the reel shaft and the reel drum acts, the reel shaft and the reel drum so bend down, the direction of action is directed from top to bottom.

Viewed from the outside, the load bending moment-related to a single revolution of the reel drum-is almost static. However, with respect to a co-rotating with the rotation of the coiler drum coordinate system, the load bending moment is dynamic. Both the torque and the load bending moment therefore lead to mechanical loads on the reel shaft and the reel drum, which can lead to damage to the reel device in continuous operation, for example, to cracks at the slot ends of the slot of the reel drum.

The object of the present invention is to provide ways by which the life and life of reels can be improved.

The object is achieved by a reel device with the features of claim 1. Advantageous embodiments of the reeling device according to the invention are the subject of the dependent claims 2 to 18.

• dass in den Verbindungsbereichen oder in Richtung der Wellenachse gesehen außerhalb der beiden Verbindungsbereiche zwei Biegeeinrichtungen angeordnet sind, mittels derer auf die Haspelwelle ein jeweiliges Rückbiegemoment aufbringbar ist, und
• dass die Rückbiegemomente einem in Richtung der Wellenachse gesehen aufgrund des Haspelvorgangs zwischen den beiden Lagern auf die Haspeltrommel und/oder auf die Haspelwelle wirkenden Lastbiegemoment entgegenwirken.

According to the invention, a reel device of the type mentioned at the outset is configured by

• that seen in the connection areas or in the direction of the shaft axis outside the two connection areas two bending devices are arranged, by means of which on the reel shaft, a respective bending-back torque can be applied, and
• the return bending moments counteract a load bending moment acting on the reel drum and / or on the reel shaft as viewed in the direction of the shaft axis due to the reeling operation between the two bearings.

As a result of this configuration, a resultant bending moment in the direction of the shaft axis can be increased outside the two bearings. However, it is crucial that the resulting bending stress between the two bearings and thus in particular in the reel drum is reduced.

In the simplest case, the bending devices act statically, ie they are set during commissioning of the reel device or in advance at the beginning of each reel operation, so that they apply predetermined bending moments on the reel shaft. During the respective reeling process, the rewinding moments are not varied in this case, but they are maintained constant. Preferably, however, the reel device is associated with a control device, are determined by the rewinding moments of the bending devices to be set dynamically during the reeling of the metal strip and are dynamically controlled by the bending devices according to the determined bending moments. It is possible that of the control device during the reeling of the metal strip dynamically exclusively the effective directions of the set bending-back moments are determined. Likewise, it is possible that only the amounts of the set bending-back moments are dynamically determined by the control device during the reeling of the metal strip. Preferably, however, a determination is made both of the directions of action and of the amounts of the back bending moments to be set. In particular, the control device can determine the set backbending moments such that an effective direction of the set backbending moments coincides with a direction of action of the load bending moment.

The way of determining can be done as needed. In general, the amounts of the set bending moments to increase with increasing outer diameter of the coiled metal strip and / or increase with increasing the size of the force exerted on the coiled metal strip strip tension. Alternatively or additionally, the effective directions of the set back bending moments with increasing outer diameter of the coiled metal strip and / or with increasing size of the force applied to the coiled metal strip strip tension can be steeper (relative to the horizontal and the vertical direction).

In a particularly preferred embodiment of the present invention, the control device during the reeling of the metal strip dynamically measured, which is characteristic of a at least one point of the reel shaft or the reel drum between the two camps by superposition of the load bending moment and the rebound moments resulting actual acting resulting bending moment characteristic are. In this case, the control device can determine the set back bending moments such that the actual acting resulting bending moment is reduced at the at least one point or at another point of the reel shaft or reel drum, in particular minimized. This approach has the advantage that regardless of the cause of the bending stress always the actually occurring bending stress is reduced, in particular minimized.

For example, hubs are generally arranged on the reel shaft and the reel drum and the hub have flanges which are connected to one another via screw connections. The torque transmission is usually via positive locking elements, such as feather keys. In this case, it is possible, for example, that the screw connections are assigned detection devices by means of which an actual voltage stress of the screw connections is dynamically detected, that the actual voltage stresses of the screw connections are dynamically fed to the control device and that the control device controls the actually acting resultant bending moment on the at least one Location or at another point of the reel shaft or the reel drum, taking into account the actual stress loads of the screw connections determined.

Preferably, there are in each case a plurality of detection devices per screw connection, for example four detection devices. As a rule, the detection devices are distributed uniformly around the screw connection around the respective screw connection.

As an alternative or in addition to a detection of the tension stress of the screw connections, it is possible for the reel drum to have flanges on the outside, which are adjoined by cylindrical sections, in that the cylindrical sections transition into conical regions, that detection devices are assigned to the cylindrical sections, by means of which an actual stress load of the cylindrical regions is dynamically detected, that the actual stress loads are fed dynamically to the control device, and that the control device determines the actually acting resultant bending moment at the at least one point of the Reel shaft or reel drum determined based on the actual stress loads of the cylindrical sections.

The detection devices as such can be designed as needed. For example, the detection devices may be designed as strain gauges or as pressure-sensitive sensors such as pressure-sensitive films.

A detection of characteristic for an actual bending stress measurements is not always feasible. In a somewhat simpler embodiment of the present invention, it is therefore provided that the control device during the reeling of the metal strip dynamically based on a characteristic of a coil weight of the coiled metal strip size and for a force acting on the reeled metal strip strip tension size for at least one point of the reel shaft or the reel drum between the two bearings an expected load bending moment determined. For example, can be determined on the basis of a conventional tracking the length of currently coiled metal strip, which in turn is in connection with the known thickness of the metal strip characteristic of the coil weight of the coiled metal strip. The tape tension can be detected in the usual way. In the case of determining the expected load bending moment on the basis weight of the coiled metal strip and the strip tension, the control device can determine the set bending moments such that resulting by superposition (superposition) of the expected load bending moment and the set bending moments expected resulting bending moment at the at least one point of the Reel shaft and / or the reel drum is reduced, in particular minimized.

In a particularly preferred embodiment, the control device takes into account at least in addition to the coil weight and the strip tension in determining the expected load bending moment a characteristic of a temperature of the reel drum size and / or a temperature distribution. For example, an ambient temperature of the reel drum and / or a temperature of the wound metal strip can be utilized. Alternatively or additionally, for example, the temperature at a flange of the reel drum and / or at a subsequent to the flange of the reel drum cylindrical portion of the reel drum or the temperature of the flange penetrating screw can be detected. In particular, a detection of temperatures at different locations may be useful to determine a temperature distribution or a temperature gradient can. The particular temperature may alternatively be measured or known due to other circumstances, such as schedule data. In the case of a temperature distribution, this can be up to three-dimensional spatially resolved. It can alternatively be stationary in time or transient in time. Based on the temperatures and / or the temperature distribution temperature-induced tension of the reel shaft and / or the reel drum can be determined.

The at least one location of the reel shaft and / or the reel drum, for which the expected resulting bending moment is reduced, in particular minimized, may be determined as required. For example, the reel drum and arranged on the reel shaft hubs usually flanges over which the reel drum and the hubs are interconnected. In this case, the corresponding location may be determined by the location of the flanges. Furthermore, the reel drum usually has a slot extending in the direction of the shaft axis between two slot ends for insertion of a belt end of the metal strip. In this case, the corresponding location may be determined by the location of the slot ends. Also, a subsequent to the flange of the capstan drum cylindrical portion of the capstan drum may be the appropriate place.

The embodiments according to the invention are particularly advantageous when the reel drum is arranged in a heated housing and the bending devices are arranged outside the housing. Because then there is a relief of the thermally highly stressed, mechanically sensitive area of the reel shaft and the reel drum. The reel shaft is in this case more heavily loaded outside of the housing. In this area, however, the reel shaft has significantly lower temperatures and therefore copes better with the mechanical loads. Embodiments of the reel device with a heated housing are used in particular in connection with Steckel rolling mills.

It is possible that the bending devices are arranged directly in the connecting regions. Furthermore, it is possible that the bending devices are arranged in the region of the bearings. Preferably, however, as viewed in the direction of the shaft axis, the reel shaft projects beyond the two bearings and, viewed in the direction of the shaft axis, the bending devices are arranged outside the two bearings.

In particular, in the case of an arrangement of the bending devices outside the two bearings, the bending devices can be designed as such as needed. For example, the bending devices directly and directly on the reel shaft apply a rebound moment. In a preferred embodiment of the reel device, however, the bending devices each have a bearing ring in which the reel shaft is mounted. The respective bearing ring is acted upon in this embodiment by means of two respective actuators - for example, hydraulic cylinder units - with two mutually linearly independent and orthogonal to the shaft axis bending forces. The bending forces cause in this case by the resulting due to the distance of the flexures of the bearings lever the desired bending moments.

The last-mentioned embodiment can be further improved in that the respective bearing ring is pivotally mounted in a respective bearing block about a respective shaft axis intersecting in a respective intersection, orthogonal to the shaft axis, that the two respective actuators act on a respective point of application of the respective bearing block and that a connecting line of the respective point of application with the respective intersection is orthogonal to the shaft axis and orthogonal to the respective bearing axis. By this design, in particular unwanted additional bending loads are avoided with certainty.

FIG 1

ein Reversierwalzwerk,

FIG 2

eine Haspeleinrichtung im Längsschnitt,

FIG 3

die Haspeleinrichtung von FIG 2 im Schnitt von der Seite,

FIG 4

den Verbindungsbereich einer Haspelwelle und einer Haspeltrommel,

FIG 5 bis 7

verschiedene Wickelzustände,

FIG 8

eine Haspeltrommel,

FIG 9 und 10

je eine Biegeeinrichtung,

FIG 11

einen Flansch und

FIG 12

den Schaftbereich einer Schraubverbindung mit Spannungsmesseinrichtungen.

The above-described characteristics, features and advantages of this invention, as well as the manner in which they are achieved, will become clearer and more clearly understood in connection with the following description of the embodiments, which will be described in more detail in conjunction with the drawings. Here are shown in a schematic representation:

FIG. 1

a reversing mill,

FIG. 2

a reel device in longitudinal section,

FIG. 3

the reel device of FIG. 2 on average from the side,

FIG. 4

the connection area of a reel shaft and a reel drum,

FIGS. 5 to 7

different winding conditions,

FIG. 8

a reel drum,

FIGS. 9 and 10

one bending device each,

FIG. 11

a flange and

FIG. 12

the shank region of a screw connection with voltage measuring devices.

According to FIG. 1 is a metal strip 1 - for example, a steel strip 1, alternatively a non-ferrous strip such as an aluminum, copper or brass strip - rolled in at least one roll stand 2 reversing. For this purpose, the metal strip 1 is rewound between two reeling devices 3 back and forth.

The rolling mill 2 and the reeling devices 3 are controlled by a control device 4. Control information 4 is supplied with control information C for this purpose, for example, stitch plan data and material data of the metal strip 1. The stitch plan data include, for example, the width of the metal strip 1, the initial thickness of the metal strip 1 and the individual stitch decreases. The material data of the metal strip 1 include, for example, its temperature and its chemical composition. Furthermore, the control information C includes the operating state of the (at least one) rolling stand 2 and the reeling means 3, for example, the rolling forces and trains occurring during rolling and reeling, tracking and the like.

The metal strip 1 may be a hot metal strip 1. In this case it has a temperature of several 100 ° C. In the case of a steel strip 1, the temperature may even exceed 1000 ° C.

The FIG. 2 and 3 show one of the reeling means 3. The other reeling device 3 is constructed generally similar.

According to FIG. 2 the reeling device 3 has a reel shaft 5. The reel shaft 5 is mounted on (at least) two bearings 6. The reel shaft 5 is thereby rotatable about a shaft axis 7. On the reel shaft 5 are according to FIG. 4 Hubs 5 'arranged. The torque transmission from the reel shaft 5 to the hubs 5 'is usually via wedges, which are arranged between the reel shaft 5 and the hubs 5' and only in FIG. 4 marked and not provided with reference numerals. A reel drum 8 is connected to the reel shaft 5 via the hubs 5 '. The locations of the hubs 5 'thus correspond to connection areas in which the reel drum 8 is connected to the reel shaft 5. Due to the arrangement of the hubs 5 ', the reel drum 8 is arranged in the direction of the shaft axis 7 between the two bearings 6.

According to FIG. 2 protrudes the reel shaft 5 seen in the direction of the shaft axis 7 beyond the two bearings 6 addition. This embodiment is preferred in the context of the present invention. However, it is not mandatory. In principle, it is sufficient if the reel shaft 5 projects beyond one of the bearings 6 with one of its two ends.

With one of the two ends of the reel shaft 5, an electric drive 9 is connected, by means of which the reel shaft 5 and with it the reel drum 8 are rotated. That of the two bearings 6, which is arranged between the reel drum 8 and the electric drive 9, is generally designed as a fixed bearing. The other of the two bearings 6 is formed as a floating bearing in the rule. There are also embodiments of the reel device possible, in which the reel shaft 5 is connected at both ends, each with an electric drive 9. In this case too, one of the bearings 6 is usually designed as a fixed bearing and as a floating bearing. The connection of the electric drive 9 (or the electric drives 9) with the reel shaft 5 via a coupling, by means of which - based on the axis of rotation of the drive shaft and the shaft axis 7 - an angular offset between the drive shaft of the electric drive 9 and the reel shaft. 5 is made possible to cause no additional bending moments in the transition region from the drive shaft to the reel shaft 5. An example of a suitable clutch is a toothed clutch.

Seen in the direction of the shaft axis 7 acts when reeling the metal strip 1 and due to the reeling of the metal strip 1 between the two bearings 6 on the reel drum 8 and / or on the reel shaft 5, a load bending moment. The load bending moment is seen in the direction of the shaft axis 7 a function of the location z. The load bending moment is considerably affected by the instantaneous weight FG of the (currently) reeled metal strip 1 (bundle weight) and the momentary strip tension Z acting during reeling of the metal strip 1 (see FIG FIG. 1 and 3 ) in conjunction with a distance A of the bearings 6 from each other caused. To counteract the load bending moment, two bending devices 10 are present. The bending devices 10 are preferably arranged outside the two bearings 6 in the direction of the shaft axis 7. Alternatively, the bending devices 10 could be arranged, for example, in the bearings 6 or be arranged between the bearings 6 and the hubs 5 '. By means of the bending means 10, a respective bending-back torque can be applied to the reel shaft 5. For example, by means of the bending devices 10, first of all a respective counterforce F can be exerted on the reel shaft 5, which causes the corresponding re-bending moment via distances A 'of the bending devices 10 to the bearings 6. The distances A 'and the opposing forces F and also the resulting re-bending moments may be the same or different.

As already mentioned, a control device 4 is present, which (among other things) the reels 3 and thus also in the FIG. 2 and 3 shown reel device 3 controls. In particular, in a preferred embodiment of the present invention as shown in FIG FIG. 2 also the bending devices 10 are controlled by the control device 4. In this case, during the reeling of the metal strip 1, the control device 4 determines dynamically for the bending devices 10 the back bending moment to be set by the respective bending device 10 or a corresponding opposing force F * to be set. The determination of the set backbending moments is dynamic, ie the determination is carried out during the reeling of the metal strip 1 dynamically according to the respective current bending load of the coiler 3. The control of the bending devices 10 by the controller 4 is carried out with the same dynamics.

When reeling the metal strip 1, the outer diameter d of the metal strip 1 changes in accordance with the progress of the reeling. For example, during coiling, the metal strip 1 is in accordance with the FIG. 3 and 5 at the beginning of the reeling process one relatively small outer diameter d = a on. In the middle of the reeling operation, the metal strip 1 according to the FIG. 3 and 6 a mean outer diameter d = b. At the end of the reeling operation, the metal strip 1 according to the FIG. 3 and 7 a relatively large outer diameter d = c. Inverse is true when unwinding. Furthermore, the metal strip 1 - regardless of the reel direction - is acted upon during the reeling with the strip tension Z.

The bundle weight of the currently coiled metal strip 1 corresponds to the current outer diameter d of the coiled metal strip 1. The instantaneous outer diameter d may be readily known to the control device 4, for example due to the thickness of the metal strip 1 in connection with a path tracking. The thickness of the metal strip 1 may be known to the control device 4, for example from the stitch plan calculation. The implementation of tracking is well known and familiar to those skilled in the art. The strip tension Z can be measured easily. For example, the specific or absolute strip tension Z can be determined from the force with which the metal strip 1 is attached to a deflection roller 11 (see FIG FIG. 3 ) is pressed.

Based on the amount of (currently) coiled metal strip 1 (ie, as a result, the coil weight), the control device 4 at any time the weight FG (see FIGS. 5 to 7 ), which exerts the metal strip 1 on the reel drum 8 and the reel shaft 5. On the basis of the strip tension Z in conjunction with the geometry of the reeling device 3 and the amount of (currently) coiled metal strip 1, the control device 4 can continue at any time a tensile force FZ (see FIGS. 5 to 7 ), which the belt tension Z exerts on the reel drum 8 and the reel shaft 5. By a vector addition of the weight force FG and the tensile force FZ can therefore be determined at any time an expected resultant force FR, which acts as such on the reel drum 8 and the reel shaft 5 by the reel operation. Based on the expected resulting force FR in conjunction with the known constructive Given conditions of the reel shaft 5 and the reel drum 8, the control device 4 can therefore also determine an associated expected load bending moment.

Optionally, the control device 4 in addition to the weight FG and the strip Z a temperature T (see 1 to 3 ), which as a result is characteristic of the temperature T of the reel drum 8. In particular, the temperature of the metal strip 1 or the temperature in the vicinity of the reel drum 8 can be utilized for each.

In principle, the determination of the expected load bending moment in the direction of the shaft axis 7 is possible for each point. It is therefore possible to determine the expected load bending moment for arbitrary positions. Often, however, it is sufficient to determine the expected load bending moment for a few critical points. In this case, therefore, if the control device 4 determines the expected load bending moment only for one digit or a few digits, the control device 4 determines the set bending moments or counter forces F * to be set such that a resulting expected bending moment, which is due to superposition of the expected Load bending moment and the set bending moments results in at least one point of the reel shaft 5 and / or the reel drum 8 is reduced, in particular minimized.

For example, the hubs 5 'and the reel drum 8 according to FIG. 4 usually flanges 12, 13, via which the hubs 5 'of the reel shaft 5 and the reel drum 8 - are connected to each other - usually via screw 14. The torque transmission between the flanges 12, 13 is usually via wedges, which are arranged between the flanges 12, 13 and only in FIG. 4 marked and not provided with reference numerals. The connection of the flanges 12, 13 together is such a critical location. Also, a to the flange 13 of the reel drum. 8 A subsequent cylindrical region 8 'of the coiler drum 8, which is delimited by a respective notch base both towards the flange 12 of the reel drum 8 and towards a conical region 8 "of the reel drum 8, can define the corresponding point The location of the reel shaft 5 and / or the reel drum 8 for which the expected resulting bending moment is reduced can therefore be determined by the location of the flanges 12, 13. Furthermore, the reel drum 8 - see FIG FIG. 8 - A slot 15, in the beginning of the Aufhaspelvorgangs a band end of the metal strip 1 is introduced. The slot 15 extends in the direction of the shaft axis 7 between two slot ends 16. The areas of the slot ends 16 are such critical points. The location of the reel shaft 5 and / or the reel drum 8, for which the expected resulting bending moment is reduced, can therefore likewise be determined by the location of the slot ends 16. The transition from the conical region 8 "to the winding area of the capstan drum 8 can also be the critical point." Likewise, it is possible to determine the expected resulting bending moment for several locations and, for example by weighted or unweighted averaging, for the several locations in its entirety to minimize.

As is clear from the FIGS. 5 to 7 results in both the direction and the amount of the expected resultant force FR during reeling change. In an analogous manner, both the effective direction and the amount of the expected load bending moment vary. For optimum reduction of the resulting expected bending moment, therefore, the control device 4 should preferably dynamically determine both the amounts and the directions of action of the backbending moments to be set or of the corresponding opposing forces F * to be set. In the sense of a suboptimal, but easier to implement solution, it may be sufficient to determine only the amounts or exclusively the effective directions of the bending moments dynamically. Depending on the location In the individual case, the determination of the opposing forces F * can take place together or separately.

Like from the FIGS. 5 to 7 As can be seen further, the more metal band 1 is coiled, the greater the expected resultant force FR. Accordingly, preferably the set bending-back moments or the counterforces F * to be set are greater, the more metal strip 1 is coiled.

Like from the FIGS. 5 to 7 As can be seen further, the more metal strip 1 is coiled, the steeper the resultant force FR (ie, the more the vertical approaches). An angle α, which forms the resultant force FR with the horizontal H, so more closely approaches a right angle, the more metal strip 1 is reeled. Accordingly, the set backbending moments or the opposing forces F * to be set are preferably also steeper, the more metal strip 1 is wound. In particular, the direction of the resultant force FR defined by the angle α coincides with the direction of the opposing forces F1, F2.

Due to the fact that the reel shaft 5 is usually formed as a continuous shaft, the reel shaft 5 thus extends in the reel drum 8, the system consisting of the reel shaft 5 and the reel drum 8 is statically indeterminate. In order to resolve this indeterminacy, a model of the reel shaft 5 and the reel drum 8 is preferably implemented within the control device 4. The model can be an analytical, semi-analytical and / or numerical model. The model models the reel shaft 5 and the reel drum 8 at least mechanically-constructively, for example, according to an approach of higher strength theory or by means of a finite element model. This model can, if necessary, be supplemented by models that the thermodynamics of the reel shaft 5 and the reel drum 8 - optionally including the Coiler shaft 5 and the reel drum 8 surrounding hot gases - describe. Examples of such models are dynamic fluid models and fluid-structure interaction models. These models can also be designed as required as analytical, semi-analytical and / or numerical models. With such models, among other things, the heat distribution in the reel drum 8, the convection of the coiler drum 8 flowing hot gases, the heat transfer from the reel drum 8 flowing around the hot gases to the reel drum 8 and the thermally induced stresses in the reel shaft 5 and the reel drum 8 are modeled. As a result, the total gas and heat dynamics can be described by these models. Often, for this purpose, the temperatures prevailing in the oven by means of corresponding sensors 27, such as pyrometers 27, (see FIG. 3 ) metrologically recorded.

The configuration of the flexures 10 may be as needed. Crucial is only the functional effect. The following will be in connection with FIGS. 9 and 10 preferred embodiments of one of the bending devices 10 explained in more detail. The other bending device 10 may be formed in an analogous manner.

In the FIG. 9 shown bending device 10 has a bearing ring 17. In the bearing ring 17, the reel shaft 5 is mounted. The bearing ring 17 can be acted upon by means of two actuators 18 with bending forces Fx, Fy. The bending forces Fx, Fy are linearly independent of each other. In particular, they can be exact or nearly orthogonal to one another. Furthermore, the bending forces Fx, Fy are orthogonal to the shaft axis 7. The bending forces Fx, Fy are determined and adjusted in such a coordinated manner that the effective force resulting from the vector addition of the bending forces Fx, Fy is directed parallel to the resultant force FR. The actuators 18 are preferably designed as hydraulic cylinder units.

The actuators 18 act on a point of application 22. A connecting line of the point of application 22 with the shaft axis 7 forms an angle γ with the horizontal H. The parallelism of the effective force F1 or F2 resulting from the vector addition of the bending forces Fx, Fy with the resulting force FR can be seen from the fact that the angle γ is identical to the angle α.

In a particularly preferred embodiment - see FIG. 10 - The bearing ring 17 is pivotally mounted in a bearing block 19 about a bearing axis 20. The bearing axis 20 is orthogonal to the shaft axis 7. It intersects the shaft axis 7 at an intersection 21. The point 22 is in the embodiment of FIG. 10 arranged on the bearing block 19. The connecting line of the point of application 22 and the point of intersection 21 runs orthogonal to the shaft axis 7 and orthogonal to the bearing axis 20.

The reel drum 8 is often in a heated housing 23 (housing 23, Steckel furnace 23, see FIG. 2 and 3 ) arranged. Such designs - ie with heated housing 23 - find particular application in so-called Steckel rolling mills. If the housing 23 is present, the flexures 10 are disposed outside of the housing 23. The bearings 6 are arranged outside of the housing 23.

The above-explained invention and its embodiments are based on easily detectable or readily - for example, from stitch plan data C - known variables such as the coil weight of the coiled metal strip 1 and the strip Z and optionally evaluate the temperature, starting from these sizes, the expected load bending moment to determine and adjust the rebound moments to reduce or minimize the expected load bending moment accordingly. This approach is relatively easy to implement. Even better, however, during the reeling of the metal strip 1 - alternatively or in addition to the exploitation of easily detectable quantities such as (for example) Bund weight and strip tension - to directly and directly dynamically record measured quantities B that are characteristic of an actually acting resulting bending moment. The measured quantities B must in this case be detected at at least one point of the reel shaft 5 or the reel drum 8 between the two bearings 6. For the detection location, the resulting bending moment results - as before - by superimposing the (in this case actual) load bending moment and the (in this case actual) rebound moments. The detected measured quantities B are fed dynamically to the control device 4 during the reeling of the metal strip 1. The control device 4 thereupon determines the set backbending moments (or the counterforces F * to be set) in such a way that the actually acting resultant bending moment at the at least one point of the reel shaft 5 or the reel drum 8 is reduced, in particular minimized.

A determination of the measured variables B as an alternative to coil weight and strip tension may be sufficient if the actual resulting bending moment at the detection location is to be reduced or minimized, ie at the location for which the measured variables B are detected. If a reduction or minimization is to be carried out at another location, the measured quantities B are preferably recorded in addition to coil weight and strip tension and possibly temperature. Furthermore, in this case, in the same way as described above, a model-based determination for the location at which the resulting bending moment is to be reduced or minimized takes place. As a result, the actual resulting bending moment for each location z in the direction of the shaft axis 7 can be determined. Thus, not only are the weight FG and the strip tension Z or comparable variables recorded, on the basis of which model-based an expected load bending moment can be determined, but it directly the measured variables B are detected, at the detection point for the actual bending moment - taking into account all influences, For example, thermal influences - are characteristic.

Possible procedures for detecting such measured quantities B are explained in more detail below.

As already mentioned and in FIG. 2 schematically and in FIG. 11 shown in more detail, the reel drum 8 and the hubs 5 'flanges 12, 13, which are connected to each other via screw 14. The screw 14 are according to FIG. 12 Detecting means 24 assigned (in FIG. 11 only shown for one of the screw 14). By means of the detection means 24 an actual stress B of the screw 14 is detected. At least one single detection device 24 is present per screw connection 14. According to FIG. 12 However, there are several detection devices 24 per screw connection 14. In the FIG. 12 shown number of four detecting means 24 which are arranged evenly distributed on the screw shaft is preferred, but not mandatory. The type of detectors 24 may also be as needed. For example, the detection means 24 may be formed as strain gauges.

The actual stress B of the screw 14 are dynamically fed to the control device 4. The control device 4 is thereby able, on the basis of the actual stress B of the screw 14, the actually acting resultant bending moment at the at least one point of the reel shaft 5 or the reel drum 8 - specifically in the transition region of the hubs 5 'to the reel drum 8 - to determine and To determine the set bending moments or the counter forces F * to be set such that the actual resulting bending moment is reduced, in particular minimized.

The screw 14 rotate together with the reel shaft 5 and the reel drum 8. For the correct evaluation of the transmitted to the control device 4 instantaneous actual Voltage stresses B of the screw 14, therefore, the respective instantaneous rotational position β of the reel shaft 5 must be known, in which the stress B are detected. However, this is usually readily possible since the reel shaft 5 is usually rotated position-controlled by means of the drive 9.

For the manner of detecting the measured quantities B, different approaches are possible. For example, it is possible to detect the rotational position β of the reel shaft 5 and to trigger the detection of the measured variables B as a function of the rotational position β. In this case, the measured quantities B can be detected in each case at a known rotational position β, for example, so that the conversion from a co-rotating coordinate system into a rotationally fixed coordinate system is known in advance. In such a case, it is particularly appropriate to record the measured variables B once to four times per revolution. Alternatively, it is possible to continuously record the measured quantities B and to respectively detect the corresponding rotational position β of the reel shaft 5. In this case, an individual conversion of the co-rotating coordinate system into the non-rotatable coordinate system must be performed for the respective acquisition. Regardless of whether one of these two approaches or a different approach is taken, but the set backbending moments are determined so that the stress B of the screw 14 is as even as possible.

The use of the actual stress loads B has the advantage over the use of only the weight force FG and the tensile force FZ that the actual stress B also reflect other effects that are not caused by the weight FG and the tensile force FZ, such as transient thermal stresses.

In addition to detecting the voltage stresses B on the shank of the screw 14 can according to FIG. 11 Also in the Flanschfuge - ie in the space between the flanges 12, 13 - be arranged further detection means 25, by means of which additional measured variables B are detected. By doing so, an even better result can be achieved. The further detection devices 25 may be formed, for example, as pressure-sensitive films or other pressure-sensitive sensors.

It is also possible - alternatively or additionally to the assignment of the detection means 24 and / or 25 to the screw 14 or the space between the flanges 12, 13 - the cylindrical portions 8 'of the reel drum 8 detectors 26 assign. The number of detectors 26 per cylindrical section 8 'in this case is usually greater than 4, for example 6, 8, 10 or 12. The detectors 26 are (analogous to the detectors 24) on the respective cylindrical portion 8' uniformly around the shaft axis 7 distributed around. By means of the detection means 26 actual stress B in the area of the cylindrical portions 8 'can be detected. These voltage stresses B can likewise be supplied to the control device 4, which in this case determines the actually acting resultant bending moment in the region of the cylindrical sections 8 'on the basis of the voltage stresses B applied thereto. The other measures - in particular the determination of the set bending-back moments - take place in this case in an analogous manner. The detection devices 26 may be formed, for example, as strain gauges analogously to the detection devices 24.

Other approaches for detecting the actual bending stresses are also feasible. For example, in the bearings 6, the actual bearing forces acting there (resolved in the horizontal and vertical directions) be recorded. Based on the actual bearing forces, the resulting force FR can be determined directly. Alternatively, for example (again resolved according to horizontal and vertical direction) inclination angle of the reel shaft 5 can be detected, for example in the camps 6 itself or elsewhere. Also based on this information, the actual or at least the expected resulting bending stress can be determined.

The present invention has many advantages. In particular, in a relatively simple manner, a significant reduction in the acting between the bearings 6 resulting actual bending moment can be achieved. In the case of a determination of the set bending moments on the basis of an expected load bending moment results in a simple implementation. In the case of utilization of the actual stress B, all occurring effects that lead to a bending moment can be detected and compensated.

Although the invention has been further illustrated and described in detail by the preferred embodiment, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention.

LIST OF REFERENCE NUMBERS

1

metal band

2

rolling mill

3

coilers

4

control device

5

reel shaft

5 '

hub

6

camp

7

shaft axis

8th

reel drum

8th'

cylindrical sections

8th"

conical areas

9

electric drive

10

benders

11

idler pulley

12, 13

flanges

14

screw

15

slot

16

slot ends

17

bearing ring

18

Actuators / hydraulic cylinder units

19

bearing block

20

bearing axle

21

intersection

22

attackpoint

23

casing

24, 25, 26

detection devices

27

sensors

A, A '

distances

a to d

outer diameter

B

Voltage stresses / metrics

C

tax information

F

against forces

F *

counter forces to be set

FG

weight force

FR

resulting power

FZ

traction

H

horizontal

T

temperature

Z

Bandzug

z

spatial coordinate

α, γ

angle

β

rotary position

Claims (18)

Coiling device for reeling a metal strip (1), - wherein the reeling device has a reel shaft (5) which is mounted via at least two bearings (6), so that the reel shaft (5) is rotatable about a shaft axis (7), - Wherein on the reel shaft (5) in the direction of the shaft axis (7) seen between the two bearings (6) a reel drum (8) is arranged, - Wherein the reel drum (8) is connected in connection areas with the reel shaft (5), - Be seen in the connection areas or in the direction of the shaft axis (7) outside the connecting portions of two bending means (10) are arranged, by means of which on the reel shaft (5) a respective bending moment can be applied, and - The bending moments counteract a seen in the direction of the shaft axis (7) due to the reeling operation between the two bearings (6) on the reel drum (8) and / or on the reel shaft (5) acting load bending moment. A reel device according to claim 1,
characterized,
in that the reel device is assigned a control device (4), that bending points of the bending device (10) to be dynamically adjusted by the control device (4) during the reeling of the metal strip (1) are determined, and that the bending device (10) corresponds to the control device (4) the determined rebound moments are dynamically controlled. A reel device according to claim 2,
characterized,
that the control device (4) during the reeling of the metal strip (1) dynamically both directions of action and amounts of the set backbending moments are determined. A reel device according to claim 2 or 3,
characterized,
that the control device (4) determines the back bending moments to be set such that a direction in which the rear bending moments to be set agrees with a direction of action of the load bending moment. A reel device according to claim 2, 3 or 4,
characterized,
that the amounts of the adjusted rear bending moments with increasing outer diameter (d) of the gehaspelten metal strip (1) and / or applied with increasing size of the Reeled metal strip (1) strip tension (Z) to rise and / or the directions of action of the discontinuing reverse bending moments (with increasing outer diameter d) of the coiled metal strip (1) and / or become steeper with increasing size of the strip tension (Z) exerted on the coiled metal strip (1). Reel device according to one of claims 2 to 5,
characterized,
that the control device (4) during the winding of the metal strip (1) dynamically measured (B) are supplied, which for at at least one point of the reel shaft (5) or the reel drum (8) between the two bearings (6) by superposition the actual bending moment resulting from the load bending moment and the bending moments are characteristic and that the control device (4) determines the set bending moments such that the actually acting bending moment occurs at the at least one location or another location of the reel shaft (5) or the reel drum (8 ) is reduced, in particular minimized. A reel device according to claim 6,
characterized,
in that hubs (5 ') are arranged on the reel shaft (5), that the reel drum (8) and the hubs (5') have flanges (12, 13), that the flanges (12, 13) have screw connections (14) are connected to the screw (14) associated with detection means (24) by means of which an actual voltage stress (B) of the screw (24) is dynamically detected that the actual voltage stresses (B) of the screw (24) dynamic the control device (4) are supplied and that the control device (4) determines the actual acting bending moment at the at least one point of the reel shaft (5) or the reel drum (8) based on the actual stress loads (B) of the screw (14). A reel device according to claim 7,
characterized,
that in each case a plurality of detection devices (24) are present per screw connection (14). A reel device according to claim 6, 7 or 8,
characterized,
in that the reel drum (8), viewed in the direction of the shaft axis (7), has outer flanges (12), which are adjoined by cylindrical sections (8 ') such that the cylindrical sections (8') merge into conical regions (8 ") the cylindrical sections (8 ') are associated with detection means (26) by means of which an actual stress load (B) of the cylindrical areas (8') is dynamically detected, the actual stress loads (B) are fed dynamically to the control device (4) and the control device (4) determines the actually acting resulting bending moment at the at least one point of the reel shaft (5) or the reel drum (8) on the basis of the actual stress loads of the cylindrical sections (8 '). A reel device according to claim 7, 8 or 9,
characterized,
that the detection means (24 to 26) as strain gauges or are designed as pressure-sensitive sensors such as pressure-sensitive films. A reel device according to claim 2, 3 or 4,
characterized,
that the control device (4) during the reeling of the metal strip (1) dynamically on the basis of a characteristic of a coil weight (FG) of the coiled metal strip (1) size and a characteristic of a strip tension (Z) acting on the coiled metal strip (1) ( FZ) for at least one point of the reel shaft (5) or the reel drum (8) between the two bearings (6) determines an expected load bending moment and that the control device (4) determines the set bending moments such that a by overlaying the expected load bending moment and the resulting bending moments resulting expected bending moment at the at least one point of the reel shaft (5) and / or the reel drum (8) is reduced, in particular minimized. A reel device according to claim 11,
characterized,
that the control device (4), in determining the expected load bending moment in addition to the coil weight (FG) and the strip tension (Z) at least one for a temperature (T) of the reel drum (8) characteristic size and / or a temperature distribution considered. A reel device according to claim 11 or 12,
characterized,
that on the reel shaft (5) hubs (5 ') are arranged, that the reel drum (8) and the hubs (5') have flanges (12, 13) over which the reel drum (8) and the hubs (5 ') and that the location of the reel shaft (5) and / or the reel drum (8) for which the expected resulting bending moment is reduced is determined by the location of the flanges (12, 13). Reel device according to one of claims 6 to 13,
characterized,
that the coiling drum (8) comprises in the direction of the shaft axis (7) between two slot ends (16) extending slot (15) for introducing a strip end of the metal strip (1) and that the location of the reel shaft (5) and / or the reel drum (8), for which the resulting bending moment is reduced, is determined by the location of the slot ends (16). Coiler device according to one of the above claims,
characterized,
in that the reel drum (8) is arranged in a heated housing (23) and in that the bending devices (10) are arranged outside the housing (23). Coiler device according to one of the above claims,
characterized,
that the reel shaft (5) projects beyond the two bearings (6) in the direction of the shaft axis (7) and that the bending devices (10) are arranged outside the two bearings (6) in the direction of the shaft axis (7). Coiler device according to one of the above claims,
characterized,
in that the bending devices (10) each have a bearing ring (17) in which the reel shaft (5) is mounted and in that the respective bearing ring (17) by means of two respective actuators (18) with two mutually linearly independent and to the shaft axis (7) orthogonal Bending forces (Fx, Fy) can be acted upon. A reel device according to claim 17,
characterized,
in that the respective bearing ring (17) is pivotably mounted in a respective bearing block (19) about a respective bearing axis (20) intersecting the shaft axis (7) in a respective intersection (21) and orthogonal to the shaft axis (7) two respective actuators (18) act on a respective point of application (22) of the respective bearing block (19) and that a connecting line of the respective point of application (22) with the respective intersection point (21) orthogonal to the shaft axis (7) and orthogonal to the respective bearing axis (20 ) runs.

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