DE102009055347A1 - Reel winding device - Google Patents

Abstract

The invention relates to a roller coiling device (R) for winding a material web, in particular a paper or cardboard web (M), onto at least one winding core, preferably a winding tube (4), to form a winding roll (5) with the support of at least one with the winding roll ( 5) a nip-forming roll (1, 2, 3), the roll winding device (R) being equipped with at least one electronic means for compensating for vibrations of the at least one roll (1, 2, 3) and / or the winding roll (5) wherein the at least one roller (1, 2, 3) can be driven by at least one drive motor (6) by one rotational degree of freedom. In particular, one would like to be able to handle paper types that are critical to the winding process more calmly and productively. The device according to the invention is characterized in that at least one roller (1, 2, 3) can be controlled and / or regulated in at least one further degree of freedom.

Description

The invention relates to a roll winding device for winding a material web, in particular a paper or board web, on at least one winding core, preferably a winding tube, to a winding roll with support at least one roll forming a nip with the winding roll, wherein the roll winding device with at least one electronic means for compensating vibrations of the at least one roller and / or the winding roll is equipped, wherein the at least one roller is driven by at least one drive motor to a rotational degree of freedom The invention will be explained in the following in connection with the treatment of a paper web. However, it is also applicable to other webs that are similar to handle. These are, for example, but not exhaustive, to webs of cardboard, plastic or metal foils.

Paper webs are produced in relatively large widths of up to more than 11 m in a paper machine. The production is almost endless. In this case, the machine direction of the paper machine defines the longitudinal direction for all machines and devices located in the paper factory and the transverse direction perpendicular thereto in the horizontal plane. To simplify the present document, the longitudinal direction is referred to as the X direction, the transverse direction as the Y direction, and the vertical direction perpendicular to a vertical plane defined by these two directions are referred to as the Z direction. At the end of the paper machine, the paper web produced is wound in full width onto a winding core. This winding core is replaced cyclically, usually during production. The resulting web-width winding roll is commonly referred to as mother roll or full tambour. In order to be manageable for a later user, for example a printing company, the paper web wound on a mother roll has to be cut into several parallel partial webs whose widths are suitable for the respective later user. These widths can vary greatly from case to case, so that the division of the paper web is usually made according to an individually definable pattern. The partial webs are then wound into winding rolls, which are called Teilbahn- or finished rolling and are issued together as a so-called roll throw. The pattern can be changed from roll throw to roll throw. The slitting and winding is advantageously carried out in a single machine, the so-called slitter, which is generally referred to as a reel winder for the purposes of the present application, since, for example, even in the pure rewinding of a mother roll without format changes at least a portion of the possible winding problems can occur.

A roll cutting device essentially consists of a unwinding device, a cutting section and a roll-up device, wherein the cutting section has a number of mostly disk-shaped cutters adapted to the possible pitches. In the embodiment of a roll-cutting device, the person skilled in the art distinguishes between two basic types of construction, namely the support roller and the back-up roller.

Characteristic of the carrier roller type is a retractor, in which the entire roll throw in a winding bed, which usually consists of two support rollers, is wound on winding tubes. The winding tubes of the roller throw can be held by means of tensioning or guiding heads or, in rarer cases, through winding shafts inserted into the winding tubes. The rolls are wound up together, as a complete throw. As a rule, this is done by means of a circumferential winding, for which purpose at least one of the two support rollers can be driven. If a winding shaft is used, a center winding or a combination of both can also take place.

In a roll-up type characterizing the backup roller type, each individual roll to be wound is wound in a separate winding station. The rollers are supported during the winding process on a support roller. Depending on the design, one to two back-up rolls and occasionally additional support rolls are used. The partial web or finished rolls are wound in their winding stations on winding tubes, which are each held by an imported pair of clamping or guide heads. The roles. are driven either via these clamping or guide heads with center winding or on the at least one support roller with circumferential winding or combined.

For the purposes of the present specification, winding rolls wound around a band and / or around the forming winding rolls from a support into a support position are also understood to mean supporting or supporting rolls.

Both machine types generally use additional pinch rollers which provide a desired level of winding hardness, especially at the initial stages of each winding.

The type specification of the reel winders to be used is usually dependent on the type of paper to be produced and the desired winding quality. Regardless of this the operator of a paper mill faces another, fundamental problem:
To ensure competitiveness and achieve high productivity, efforts are being made to achieve high production speeds. In this case, all devices or machines located in the production chain of a paper factory have to be oriented to the production speed or their production output predetermined by the paper machine. As a paper machine, apart from failure cases, works continuously, it is difficult for a discontinuous roll winder to follow the speed provided, since set-up, acceleration and deceleration times are relatively frequent in accordance with the task of size reduction and therefore only by significantly higher production speeds are to be compensated.

However, such high demands on the winding speeds involve a high risk potential due to vibrations occurring. The winding to be produced hardly assumes an ideal round shape. Small winding errors, for example, due to slight profile fluctuations of the paper web to be wound, add up with each full wrapping. In the further course, the winding rollers form hardenings in these areas. Due to the periodic recurrence of the respective winding defects of the rotating coil, vibrations of corresponding frequency are formed depending on its circumference and peripheral speed.

With increasing production speed, the excitation frequency is always greater (with increasing peripheral speed, the same position of the winding more and more often passes through the same winding gap) and the exciter amplitude is increasingly violent (at the same time as its winding diameter and its unevenness and the effective weight increases). In this case, the probability increases greatly that form during this complex process vibrations that are suitable (via integer harmonics) to form resonances with the support rollers of the reel winder, which can lead to a fierce, sometimes rapid "rocking" of the entire machine. As is known, in extreme cases, windings can be ejected from the winding bed.

With today aimed at production speeds of 3000 m / min is hardly the economically viable option to interpret the natural frequencies of the support rollers involved so that a possible Eigenstimmulierung the system can be reliably excluded.

Overlaying this occurs even more vibration problems. For example, the forming winding roll assumes the state of an anisotropic rotor. The reason for this are transverse profile fluctuations of the paper web, which add up with each wrapping. It can then come with each revolution also contact losses or at least different line loads. Paper-technological correlations, such as compressibility or coefficient of friction of the web, then lead to inhomogeneous roles.
Already at a semi-critical speed, which corresponds to about half the resonance speed of the role, it comes to strong deformation of the role. These deformations are also referred to as s2-stroke or 2f-stroke. They are again in massive interaction with the other components involved in the entire winding system and may be jointly responsible for an eccentric roller structure.

In order to combat the resulting vibrations and the subsequent damage, it is known to dampen a roll acting on the winding or rolls to be wound in order to extract energy from a vibration process forming. Further, it is known to act reassuringly on the bobbins by means of the platen roller. One usually follows this by geometrically stabilizing the winding rollers by shifting the platen roller. The still unpublished patent application DE 10 2008 053 931 the applicant, also provides an influence by means integrated in the support roller Tilgern on the bobbins before.

Particularly in the case of paper grades critical for winding, that is to say for paper types whose coefficient of friction is above 0.55 and in particular above 0.7, the winding structure as a result is frequently still unsatisfactory under high production speeds. From this, the productivity, that is primarily the winding speed, can barely be increased beyond a safely implementable level of 2800 m / min.

It is the object of the invention to provide a roll winding device for winding material webs, by means of which, in particular, winding-critical paper grades are more quietly and more productively treatable.

According to the invention, this object is achieved in a roller winding device of the type mentioned above in that at least one roller in the direction of movement of at least one further degree of freedom by means of a control unit ( 9 ) is controllable and / or controllable.

In this way it becomes possible, by means of one and the same nip, to counteract vibrational states consisting of two overlapping ones Vibration types, such as torsional vibrations and vertical vibrations exist. Accordingly, among the degrees of freedom of the rollers, the translational movement directions in the X, Y, and Z directions and the directions of rotation about these axes are to be understood.

Preferably, at least one drivable roller can be controlled and / or regulated in the direction of movement of at least one further degree of freedom.

In this way, the influence spectrum expands considerably, since the control-regulation range is not dependent on injected external energy in relation to the rotational degree of freedom of the roller about the Y-direction and the circumferential forces acting in the nip can always be influenced autonomously.

It is of great advantage if at least one roller can be controlled and / or regulated in at least two further degrees of freedom.

In this way it becomes possible, by means of one and the same nip, to counteract vibrational states which consist of more than two superimposed modes of vibration. In this case, even voltage divergences in the material web to be wound can be evenly compared. This effect can be used quite effectively, particularly in the case of the viscoelastic paper or board webs.

Furthermore, it is advantageous if at least one roller can be controlled and / or regulated in the direction of movement of at least one of the degrees of freedom in a static and a periodic component.

Of course, the term "static" should not be understood here as a permanently unchanged state. The static component is to be understood here as a control technology and, for example, reflects the planned control using the provided control curve. With respect to the roller of a reel-winding apparatus, such a curve usually includes an acceleration phase, a constant-speed phase and a deceleration phase. Relative to a damping device, the static component refers to the active or passive damping of the currently applied resulting vibration, while the periodic component of one, this vibration superimposed, usually higher-frequency, vibration corresponds. Based on this ratio, the present document also speaks of macro-vibration ranges and micro-vibration ranges, the macro-vibration ranges are to describe the commonly perceived, resulting vibrations, while under the micro-vibrations superimposed vibrations, usually higher frequency and lower amplitude, are understood.

In this way, one and the same nip can additionally act on the winding structure in a macro or micro-vibration range. Thus, either even the smallest initial excitations or critical oscillatory movements can be effectively combated.

If a plurality of degrees of freedom in static and periodic portions are controlled / regulated in a preferred manner, it is possible, by means of one and the same nips, additionally to act on the winding structure in at least one macro and / or at least one micro region. Thus, a variety of excitements can be effectively combat.

In particular, even the smallest initial excitations as well as critical oscillatory movements can be effectively combated.

In the further course of the winding process, influence can also be exerted on the particularly influential macrovibrations, from which the usually perceived loss of quality or damage to the winding roll as well as hazards or damage to the roll winding device and its surroundings emanate. At the same time, it is also possible to exert influence on micro vibrations which overlap these oscillations, which are decisive for the further development of the oscillations. In this way, a current danger level can be counteracted and at the same time, germinating oscillation developments can be disturbed.

Advantageously, at least one roller can be controlled and / or regulated by means of a feedback and / or a feedforward influence.

Thus, action and reaction can be suitably used in the winding process to dampen vibrations depending on the phase position.

Preferably, at least the periodic component is high-frequency controllable and / or controllable.

Micro-excitations usually occur at high frequency and with minimal amplitudes. You can best address them with high-frequency control mechanisms. It may well be preferable to use frequencies equal to 8 Hz, in particular frequencies equal to 10 Hz.

Also, it is advantageous if at least one of the rollers, in particular the pressure roller for calming the winding roll about its own axis is driven in such a way that the static portion of Circumferential speed of the forming winding roll corresponds, and the periodic proportion of a, induced by a rocking motion of the winding roll, superimposed torsional vibration of the pressure roller corresponds.

This has proven in tests to be a particularly suitable measure to be able to wind winding rolls of high quality under high speeds reliably even from winding-critical papers, since such a winding method, in particular by the forming winding rollers induced excitation process reflects. Thus, the present vibrations can be very well eliminated and rocking movements of the winding rolls are effectively prevented.

With particular advantage, the periodic component can be adjusted in phase or adjusted in phase.

In this way, a further germination of the microvibrations, in particular a transition from micro to macro vibrations, can be counteracted particularly effectively.

It may also be preferred that at least the periodic components of the motion control of at least two rollers can be aligned in opposite phase to one another.

Experiments have shown quite surprisingly in such a constellation particularly good damping effects, although theoretically one of the rollers would have to contribute to further rocking of the vibration system.

It may also be of particular advantage if at least one of the rollers, in particular at least the pressure roller, has an elastic cover.

In this way, a particularly good transmission and a high contact reliability in the nip can be ensured. Since the pressure roller with a particularly large lever arm acts on the, around the hubs or about an imaginary axis in the winding bed moving, in particular rocking, winding rollers and the pressure roller also has the lowest moment of inertia, it is particularly suitable for influencing.

It is advantageous if at least one of the rollers, in particular at least the support roller, is driven segmented and in particular also controllable and / or controllable.

For material web widths from 6 meters to more than 11 meters, which are usually to be processed today, it is sensible to distribute several smaller drives along the Y axis in order to achieve torsionally stiff drive units which are also suitable for high-frequency control or regulation. If a segmented one, it makes sense if each individual element is driven by its own drive in order to provide particularly good conditions for an ideal field of action.

In this way, shorter roller segments can be used, which are shorter than the material web width in the Y direction. As a result, the rigidity of the rollers can be advantageously influenced and from this synergy effects to the above-mentioned advantages can be achieved.

Furthermore, it is of great advantage if the presence of nip contact can be determined by means of at least one sensor.

There may be a loss of contact between the winding rollers forming in the winding process and the rollers acting on them during the winding process. This loss of contact can occur periodically recurring and is then vibration induced and often only latent. In particular, between winding roll and pressure roller but it can also come from a certain winding roll diameter or from a certain number of material web layers on the winding roll, in the Y direction at least partially longer loss of Nipkontakts.

However, the roller and the winding roller interact with each other only when the nip contact is established. Therefore, it is important, especially in vibration-reducing measures, to be informed discreetly or continuously about the presence of nip contact.

Thus, for example, "skid marks" on the material web surface "can be prevented.

Preferably, at least one roller with an active or passive damping device can be damped.

Also preferably, at least one roller with an active or passive repayment device can be damped.

It may be advantageous if at least one roller, in particular the support roller, segmentally by means of the damping device or the repayment device is damped.

While in previous embodiments in practice, preferably, but not exhaustively, went to vibration-reducing measures that can be achieved by means of the drive means, provide The latter three embodiments possibilities for superimposed action by means in particular by a linear degree of freedom movable Dämpfungsbeziehungsweise eradication devices. Again, all existing nips can be used effectively.

These measures therefore offer a particularly high potential for useful synergy effects, since the oscillations of the nip direction, which initially move around axes of rotation, penetrate the bearings of the rollers and result in linear components of action which, in the macro as well as in the micro range, are mass-laden, ie mainly in the low-frequency range , as in the high-frequency vibration range, can be effectively countered.

It may also be occasionally of additional advantage if a roller, in particular the support roller is arranged to be movable in entirety and / or in segments along the circumferential direction of the winding roller.

In this way, an additional geometric stabilization of the winding rolls is possible, with the resulting synergy effects can be used for process reliable operation of the winding process.

Further advantageous embodiments will become apparent from the description and the drawings.

The invention will be described in detail in an embodiment with reference to the single figure.

As a section of a reel winding device R a take-up area is shown, the two support rollers 1 . 2 has, of which at least one is driven. The carrier rolls 1 . 2 Form a roll bed in which several in the Y direction next to each other bobbins 5 during winding on the support rollers 1 . 2 rest. From a longitudinal cutting device, not shown, a material web M, in particular a paper or board web, cut before winding into a plurality of individual webs, which then through the nip between the support rollers 1 . 2 or laterally around the jacket of one of the two support rollers 1 . 2 are guided around in the roll bed, where they aligned on aligned sleeves 4 be wound up. The carrier rolls 1 . 2 each form a nip with the winding roll 5 ,

A platen roller 3 forms, in the case illustrated via an elastic cover 8th , an additional nip with the winding roll 5 out. Here is the support roller 3 Segmented in the Y direction and each segment is a separate, torsionally stiff drive motor 6 driven. In the example shown are also the support roller 1 and the carrier roll 2 by a drive motor arranged within its roller shell 6 driven. To fulfill the inventive concept, however, it is perfectly sufficient if at least one of the rolls 1 . 2 . 3 is driven. For example, the invention can be used even if only a single roller is used as a support roller for the cut longitudinally paper webs. In this case, the individual bobbins are based 5 usually alternately in an eleven o'clock position and in a one o'clock position with respect to the roller acting as a back-up roller 1 . 2 . 3 from. Instead of eleven o'clock and one o'clock positions, the bobbins can 5 but of course also at other, each symmetrically opposite positions in the region of the two upper quadrants of the support roller are.

It is also conceivable that a roller 1 . 2 . 3 is driven by an external drive motor. It is only important that the connection of the drive motor to the roller of high rigidity, changes in the drive power (motor current, torque, speed) are passed through the roller quickly and unadulterated.

Furthermore, in the region of the roll axis and / or within the roll shell of the support rolls 1 . 2 Sensors for detecting vertical vibrations of the winding roll 5 , of oscillations in the nip direction and of torsional vibrations, ie in the tangential direction of the support rollers 1 . 2 , to be available. At least one roller is preferred 1 . 2 . 3 with at least one sensor 7 equipped to detect existing Nipkontakts. The sensor 7 can be designed as an optical sensor. In the example shown, however, it is designed as a load sensor and is in contact with the respective roller shells. It is conceivable that the sensor 7 circumferentially several discrete sections can monitor. However, it is preferred that the sensor is designed to be suitable for detecting the entire roll surface, and thus any contact loss, as illustrated in the figure for clarity by the open gap h, in the respective nip between the individual rolls and wound rolls 5 can capture. By suitable use of the method according to the invention such contact losses are largely avoidable. In particular, vibration-induced contact losses are avoidable or at least reducible. Contact losses of the platen roller 3 due to cross profile variations are harder to prevent. A detection of a loss of contact in the nip between the pressure roller 3 or a segment of the pressure roller 3 and the bobbins 5 but can then provide important information for the further control strategy. This is at least a sensor with a control unit 9 in contact.

Preferably, the control / regulating unit is also in operative connection, directly or via interposed further control / regulating devices, also with the drive motors and optionally existing damping or erasure devices. In the illustrated embodiment, the support roller 1 , which is also wrapped here as the first of the incoming material web M, with an active damping system 10 equipped while the carrier roll 2 a passive damping system 11 having.

The platen roller 3 or their individual segments are with eradication facilities 12 equipped, symbolically represented by a ring around the driven axle. Also the eradication facilities 12 are in operative contact with the control / regulating device via contact lines or wirelessly.

The carrier roll 1 is from the controller 9 about her drive motor 8th driven by their rotational degree of freedom. The arrow S _1-1 indicates the static component while the arrow pair P _{1-1 represents} the superimposed periodic component. The forming in Niprichtung linear degree of freedom of the support roller 1 is indicated by the arrow S _1-2 . In this case, the permitted movement by means of the active damping device 10 regulated. Here, too, superimposed periodic, that is oscillating, components are introduced, which are represented by the pair of arrows P _1-2 and their influence, in particular when the counter-movement of the support roller is actively initiated 1 are of importance.

The naming of the arrows results as follows: S for static component, P for periodic component, the first index names the roller, the second index the degree of freedom. The periodic component is preferably controlled or regulated high frequency and moves advantageously in frequency ranges above 8 Hz.

For the carrier roll 2 The same applies as for the carrier roll 1 , Only the active superimposable periodic components in the second degree of freedom are missing due to the passive damping device here.

The pressure roller 3 is with an absorber device 12 equipped, in the present case, only the first of the aligned in the Y direction juxtaposed segments of the pressure roller 3 is visible. The same applies to the cores 4 and the winding rolls formed on them 5 ,

The pressure roller 3 In the illustrated case, in the illustrated case, it is controlled and / or regulated at least temporarily via the winding process in a total of 3 degrees of freedom in static and periodic portions. It is therefore able to counteract vibrational states propagating in space in static and periodic proportions and ideally to eliminate the complexly superimposed vibration states. In some cases, the synergy effects from the joint effect on the forming winding rolls over several nips, in this case over all 3 nips, are particularly evident.

Is the pressure roller 3 can be controlled or regulated only in 2 degrees of freedom, the oscillating counteracting path of the pressure roller moves to an orbit. Again, this is often sufficient to achieve significant improvements in the winding process, as the individual bobbins 5 only in rare cases also tilt around their front sides or swing back and forth in the transverse direction (Y-direction). The oscillatory process initiating movements of the bobbins 5 are represented by the arrows S _5-1 and P _5-1 and S _5-2 . S _{5-1 represents} the desired winding speed, P _5-1 the vibration-generating periodic Mirkoanteil due to unevenness of the bobbin circumference and S _5-1 an exemplary rocking motion, as occurs when (over integer harmonics) meet resonance areas of each vibration partner. The pivot point of the swinging motion can thereby change dynamically due to the growing roll diameter, vibrations and winding movements or temporary loss of Nipkontakt, dynamically.

For the controlled / controlled influence of the rolls over the nips, it is therefore often of decisive importance whether the influence is introduced in phase, or phase-shifted, reactive or forward-looking (feedback / feedforward).

Furthermore, it is possible to use a control software which also anticipates machine-related disturbances and, in particular, is designed as a self-learning system.

LIST OF REFERENCE NUMBERS

1

king roll

2

king roll

3

platen

4

mandrel

5

reel

6

drive motor

7

sensor

8th

reference

9

Control / regulating device

10

active damping device

11

passive damping device

12

Tilgereinrichtung

S _1-1

static proportion _{roll 1 degree of freedom 1}

R _1-1

periodic proportion _{roll 1 degree of freedom 1}

S _1-2

static proportion _{roll 1 degree of freedom 2}

P _1-2

Periodic proportion _{roll 1 degree of freedom 2}

S _2-1

static proportion _{roll 2 degree of freedom 1}

P _2-1

Periodic proportion _{roll 2 degree of freedom 1}

S _2-2

static proportion _{roll 2 degree of freedom 2}

S _3-1

static proportion _{roll 3 degree of freedom 1}

P _3-1

periodic proportion _{roll 3 degree of freedom 1}

S _3-2

static proportion _{roll 3 degree of freedom 2}

P _3-2

periodic proportion _{roll 3 degree of freedom 2}

S _3-3

static proportion _{roll 3 degree of freedom 3}

P _3-3

periodic proportion _{roll 3 degree of freedom 3}

M

web

R

Reel winding device

H

(open) gap

X

X-direction

Y

Y-direction

Z

Z-direction

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008053931 [0013]

Claims (16)

Roll winding device (R) for winding a material web, in particular a paper or board web (M), on at least one winding core, preferably a winding tube ( 4 ), to a winding roll ( 5 ) with support of at least one, with the winding roll ( 5 ) a nip-forming roller ( 1 . 2 . 3 ), wherein the roller winding device (R) with at least one electronic means for compensating for vibrations of the at least one roller ( 1 . 2 . 3 ) and / or the winding roll ( 5 ), wherein the at least one roller ( 1 . 2 . 3 ) by at least one drive motor ( 6 ) is drivable by a rotational degree of freedom, characterized in that at least one roller ( 1 . 2 . 3 ) in the direction of movement of at least one further degree of freedom by means of a control / regulating unit (9) is controllable and / or regulated. Roller winding device (R) according to claim 1, characterized in that at least one drivable roller ( 1 . 2 . 3 ) is controllable and / or controllable in the direction of movement of at least one further degree of freedom. Roller winding device (R) according to one of the preceding claims, characterized in that at least one roller ( 1 . 2 . 3 ) in at least two others. Degrees of freedom controllable and / or regulated. Roller winding device (R) according to one of the preceding claims, characterized in that at least one roller ( 1 . 2 . 3 ) is controllable and / or controllable in the direction of movement of at least one of the degrees of freedom in a static (S) and a periodic (P) component. Roller winding device (R) according to one of the preceding claims, characterized in that at least one roller ( 1 . 2 . 3 ) is controllable and / or controllable by means of a feedback and / or a feedforward influence. Roll winding device (R) according to one of claims 4 to 5, characterized in that at least the periodic component (P) is high-frequency controllable and / or controllable. Roller winding device (R) according to one of the preceding claims, characterized in that at least one of the rollers ( 1 . 2 . 3 ), in particular the pressure roller ( 3 ) to calm the winding roll ( 5 ) is drivable about its own axis such that the static portion (S) of the circumferential speed of the developing winding roll ( 5 ), and the periodic portion (P) of a, by a rocking movement of the winding roll ( 5 ), superimposed torsional vibration of the pressure roller ( 3 ) corresponds. Roller winding device (R) according to one of the preceding claims, characterized in that the periodic component (P) can be activated or adjusted in phase out of phase. Roller winding device (R) according to one of the preceding claims, characterized in that at least the periodic portions (P) of the motion control / regulation of at least two rollers ( 1 . 2 . 3 ) are aligned in phase opposition to each other. Roller winding device (R) according to one of the preceding claims, characterized in that at least one of the rollers ( 1 . 2 . 3 ), in particular at least the pressure roller ( 3 ), an elastic cover ( 8th ) having. Roller winding device (R) according to one of the preceding claims, characterized in that at least one of the rollers ( 1 . 2 . 3 ), in particular at least the platen roller ( 3 ), segmented driven and in particular also controllable and / or regulated. Roller winding device (R) according to one of the preceding claims, characterized in that by means of at least one sensor ( 7 ) the presence of nip contact can be determined. Roller winding device (R) according to one of the preceding claims, characterized in that at least one roller ( 1 . 2 . 3 ) with an active or passive damping device ( 10 . 11 ) is attenuable. Roller winding device (R) according to one of the preceding claims, characterized in that at least one roller ( 1 . 2 . 3 ) with an active or passive repayment facility ( 12 ) is attenuable. Roller winding device (R) according to one of the preceding claims, characterized in that at least one of the rollers ( 1 . 2 . 3 ), in particular at least the platen roller ( 3 ), segmentally by means of the damping device ( 10 . 11 ) or the eradication facility ( 12 ) is attenuable. Roller winding device (R) according to one of the preceding claims, characterized in that a roller ( 1 . 2 . 3 ), in particular the support roller ( 3 ) in total and / or segmentwise along the circumferential direction of the winding roll ( 5 ) is arranged movable.

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