CA2260074C

CA2260074C - Process and winding machine for the continuous winding of a material web

Info

Publication number: CA2260074C
Application number: CA002260074A
Authority: CA
Inventors: Rudolf Beisswanger; Zygmunt Madrzak; Walter Kaipf; Roland Moller; Ralf Preising
Original assignee: Voith Sulzer Papiertechnik Patent GmbH
Current assignee: Voith Patent GmbH
Priority date: 1997-05-16
Filing date: 1998-05-15
Publication date: 2006-08-29
Anticipated expiration: 2018-05-15
Also published as: CA2260074A1

Abstract

A winding machine is proposed for continuous winding of a material web, in particular a paper or cardboard web, onto a reel into a winding roll, having a movable pressing drum, which forms a winding gap with the winding roll, having at least one primary transport device by means of which the reel can be moved along a first guide track, and at least one secondary transport device that guides the reel along a second gui de track. The winding machine is distinguished in that in order to prepare for a reel change, the new reel (35; 49) can be shifted by means of the primary transport device (79) into a reel-changing position in which a new winding gap is formed between the new reel (35; 49) and the pressing drum (19), and that in the reel-changing position, the material web (3) is guided over a circumference region of the new reel (35; 49).

Description

PROCESS AND WINDING MACHINE FOR CONTINUOUS
WINDING OF A MATERIAL WEB
The invention relates to a process for continuous winding of a material web in particular a paper or cardboard web and a winding machine for continuous winding of a material web, in particular a paper or cardboard web.
Processes and winding machines of the type mentioned here are known (EP 0 561 128 Al). They are employed, for example, at the end of a machine for manufacturing a material web and are used for continuous winding of the material web onto a reel. The known winding machine includes a horizontally movable pressing drum, also called a Pope drum, over part of whose circumference the material web is guided. The material web is wound into a winding roll on a reel, wherein during the entire winding operation, the winding roll forms a winding gap with the pressing drum. In order to prepare for a change of the reel, an empty reel is pressed against the circumference of the pressing drum, by means of which another, new winding gap is formed. During this winding phase, the material web is guided through both the nip between the new reel and the pressing drum and the closed nip between the almost-finished winding roll and the pressing drum. Then, in the region disposed between the full winding roll and the new reel, the material web is cut directly on the pressing drum and the new web beginning is wound onto the new reel. It has turned out to be disadvantageous that the transfer and winding of the new web beginning onto the empty reel is very difficult. In many instances, a number of attempts are necessary for this, which in turn leads to a relatively high percentage of waste.
The present invention, therefore, is directed toward the creation of a process and a winding machine 5 that do not exhibit these disadvantages.
In accordance with one aspect of the present invention, there is provided process for continuous winding of a material web, in particular a paper or cardboard web, to form a winding roll on a reel, comprising a plurality of steps.
The process takes place in the following steps: The material web is guided by way of a movable pressing drum, which forms a winding gap with the winding roll, which is rotatably secured in a secondary transport device, wherein the line force in the 4' P 16940.S03 winding gap is controlled/regulated during this winding phase by means of a shifting of the pressing drum. In order to prepare for a reel change when a desired winding roll diameter is reached, the winding roll is moved away from the pressing drum by means rrf the secondary transport device so that the material web runs freely from the pressing drum to the winding roll. A new reel rotating at web speed is moved by means of a primary transport device into the free draw and is brought into a reel-changing position in which the new reel forms a new winding gap with the pressing drum. After this, the material web is cut crosswise over its width and with its new web beginning, is wound onto the new reel. During this winding phase, the control/regulation of the line force in the winding gap between the pressing drum and the new reel is in turn carried out by means of a shifting of the pressing drum. Finally, the new reel with the new winding roll is taken over by the secondary transport device, wherein the control/regulation of the line force occurs by means of a shifting of the pressing drum, even when the new reel is guided by the secondary transport device.
Since the empty reel is partly wrapped by the material web before the transfer and winding-on of the new web beginning, i.e. the material web is guided over a circumference region of the new reel while the material web is still being wound onto the nearly finished winding roll, a reliable transfer of the web and start of winding of the winding roll onto the new reel can be assured. The process is distinguished by means of a high degree of change-over reliability.
It is furthermore advantageous that the line force in the winding gap during the entire winding process is adjusted exclusively by means of a relative movement of the pressing drum in relation to the winding roll. The pressing drum can be rapidly shifted due its relatively light weight in comparison to the weight of the growing winding roll.
Consequently, jumps and fluctuations in the sine force can be compensated for very rapidly.
As a result of this, an exact, uniform line force in the winding gap can be adjusted/regulated during the entire, i.e. a complete, winding process so that on the whole, a favorable winding quality can be achieved. Furthermore, it is particularly advantageous that a direction change of the shifting movement of the pressing drum can be carried out very rapidly due to the relatively low weight of the pressing drum in relation to the winding roll.

x P 16940.S03 In a particularly preferred embodiment of the process, the provision is made that with the removal of the winding roll from the pressing drum, this pressing drum follows the winding roll until reaching a stop and that the new reel is subsequently brought into the reel-changing position, wherein before the reel change, the new reel forces the pressing drum back from the stop. By means of this, it can be assured with a relatively low controUregulation cost, that the line force during a complete winding process, i.e. from the start of winding to the final winding of the winding roll, can be exactly adjusted or maintained at a desired value by means of a shifting of the pressing drum.
Finally, an embodiment of the process is also preferable, which is distinguished by virtue of the fact that the empty reel is brought into a position disposed above a pressing drum. After this, a winding gap is formed between the pressing drum and the empty reel by means of a relative movement between the pressing drum and the reel. The disposition of the empty reel in relation to the pressing drum is chosen so that the pressing plane, which is defined by means of the winding gap and by means of the longitudinal axes of the empty reel and-the pressing drum, is inclined in relation to an imaginary horizontal by an angle a, which lies in a range of 5 ° s a s 40°, preferably 10° s a s 35 °, in particular 15 °
s a s 30 °. In this position of the empty reel, the material web is cut and its free end is wound onto the empty reel. Since the winding gap during the winding-on lies in the inclined pressing plane, the deflection resulting from the pressing force and the component of the deflection resulting from the tare weight of the reel, which component lies in the pressing plane, cancel each other out, preferably completely, but at least significantly. As a result, a line force in the winding gap can be adjusted that is uniform viewed in terms of the web width, which in tum leads to an improvement of the-winding quality.
Furthermore, an exemplary embodiment of the process is preferable, which is distinguished by virtue of the fact that after the secondary transport device takes over a reel, a compensation for the diameter increase of the winding roll occurs by means of a preferably horizontal or at least nearly horizontal shifting of the secondary transport device. The adjustment of the line force and consequently the shifting of the pressing drum occurs independently of the compensation movement of the growing winding roll. The load in the winding gap can therefore be modulated or adjusted very precisely. The fluctuations or jumps in the line force that previously occurred on an occasional basis in the winding gap are avoided at least to a large extent. By means of this, a definite, uniform winding hardness can be adjusted; in particular, an exact core winding can be assured.
In accordance with another aspect of the present invention, there is provided winding machine for continuous winding of a material web, in particular a paper or cardboard web, onto a winding roll having a movable pressing drum, which forms a winding gap with the winding roll, having at least one primary transport device by means of which the roll can be moved along a first guide track, and having at least one secondary transport device which guides the roll along a second guide track. This machine is distinguished in that in order to prepare for a reel change, the new reel is shifted by means of the primary transport device into a reel-changing position in which a new winding gap is formed between the new reel and the pressing drum, and that in the reel-changing position, the material web is guided over a circumference region of the new reel. Since the material web that is wound on the almost finished winding roll is already wound part of the way around the new reel before the reel change, a high degree of change-over reliability can be assured.
An exemplary embodiment of the winding machine is particularly preferred in which the reel-changing position is provided above the position in which the secondary transport device takes over the new reel. In an advantageous embodiment, during the winding-on process, the new winding gap is disposed in a pressing plane that is defined by the longitudinal axes of the empty reel and the pressing drum and is inclined in relation to an imaginary horizontal by an angle a, which lies in a range of 5° _< a <_ 40°, preferably 10° <_ a _< 35°, in particular 15° <_ a _< 30°. The component of the deflection resulting from the tare weight of the reel, which component lies in the pressing plane, and the deflection resulting from the pressing force cancel each other out, at least approximately. As a result, during the start of winding, a uniform line force in the winding gap can be assured over the entire web width so that a definite building up, first of the winding core and then of the remaining winding roll, is possible. The improvement of the winding quality in the core thus permits an exact winding of the entire winding roll.

P I 6940.S03 In an advantageous embodiment of the winding machine, the provision is made that the diameter increase can be compensated for by a shifting of the secondary transport device and the line force in the winding gap can be adjusted, preferably regulated~y means of a shifting of the pressing drum while the winding roll is guided by the secondary transport device. The compensation for the growing winding roll diameter and the adjustment of the line force are therefore provided by two separate devices that can be actuated or function separately from each other, the secondary transport device and the pressing drum. Due to the weight of the pressing drum, which is relatively light in comparison to the weight of the growing winding roll, the pressing drum can be rapidly shifted and consequently, jumps and fluctuations in the line force can be compensated for very rapidly. It is particularly advantageous that a direction change of the shifting movement can be carried out very rapidly by means of the pressing device due to the relatively low weight of the pressing drum. A preferably uniformly favorable winding result can be achieved by means of the independent shifting movements of the pressing drum and the secondary transport device.
An exemplary embodiment of the winding machine is also preferable in which the at least one pressing device, with the aid of which the pressing drum can be shifted, is embodied as a preferably hydraulic piston and cylinder unit. In a first embodiment, the maximal stroke of the piston is less than half the material layer thickness of the finished winding roll. Despite the relatively small stroke, i.e. the distance that the pressing drum can be shifted in one direction, the pressing system is not changed during the winding process.
The movable pressing drum remains in practically constant contact with the winding roll except for a few seconds during the reel change. The winding machine is distinguished by means of a simple and reasonably priced design. In another, second embodiment, the provision is made that the maximal stroke of the piston is at least greater than or equal to the layer thickness of a finished winding roll. By means of this, it is possible to replace the movable secondary transport device with a secondary support which is disposed in stationary fashion and in which the reel is rotatably secured. With a stationary support, an optimal rigidity of the reel mount can be assured so that vibrations that possibly occur inside the winding machine have practically no effect on the line force/line force progression. A
continuous reel tracking is therefore not necessary so that the machine design can be simplified.
Finally, another exemplary embodiment of the winding machine is preferable in which the primary and secondary transport devices are each associated with only one individual drive, preferably a central drive, with the aid of which a torque can be exerted on the reel. The drive associated with the primary transport device is preferably also used to accelerate an empty reel to the travel speed of the material web.
The invention will be explained in more detail below in conjunction with the drawings:
Figs. 1 to 4 each show a schematic diagram of an exemplary embodiment of the winding machine according to the invention, in different winding phases;
Fig. 5 shows a schematic diagram of the winding machine according to Figs. 1 to 4, with an embodiment of a control for the line force in the winding gap;
Fig. 6 shows a schematic diagram of another exemplary embodiment of the winding machine, with a regulating device for adjusting the reel-changing position;
Fig. 7 shows a schematic diagram of a reel shown in Fig. 3, in a reel-changing position;
Figs. 8a to 8e each show a very schematically depicted schematic representation of the winding machine according to Figs. 1 to 5, in different winding phases;
-G-4' P 16940. S03 Figs. 9 to 11 each show a detailed schematic representation of a third exemplary embodiment of the winding machine;
Figs. 12 to 13 each show a schematic representation of other exemplary embodiments of the winding machine and Figs. 14a to 14e each show a very schematic representation of a sixth exemplary embodiment of the winding machine.
The winding machine described below can be generally employed for the winding of a material web. The winding machine can be disposed at the end of a machine for manufacturing or upgrading a material web, for example a paper web, in order to wind the finished material web into a winding roll. The winding machine can, however, also be used to re-roll finished winding rolls. Purely by way of example, it is assumed that, in this instance, it concerns a winding machine for the winding of a continuous paper web.
Figs. 1 to 4 each show a schematic representation of a first exemplary embodiment of a winding machine 1, which serves the winding of a paper web, which will be generally referred to below as the material web 3, onto a reel, winding core, or the like. A sequence of operational steps of the winding machine 1 emerges from the Figs. 1 to 4. The winding machine 1 in this exemplary embodiment includes two secondary transport devices 5 and 7, which each include a secondary block 11 that can travel on second rails 9. The rails 9 are disposed parallel to an imaginary horizontal and are fastened to a machine frame 13. The secondary transport devices 5, 7 are used to rotatably secure and guide a reel along a second, horizontally extending guide track 14, which lies in an imaginary plane E--depicted with dashed lines. This plane spans an area that is disposed perpendicular on the plane of the drawing of Fig. 1. Furthermore, guide rails 15 are attached to the machine frame 13, which are disposed parallel to an imaginary horizontal. A reel exhibiting bearing pins can be stored on the guide rails 15 and is carried by them, i.e. the weight of the reel and the weight of the P 16940.S03 winding roll wound onto the reel are supported by the guide rails 15. In a particularly preferable exemplary embodiment of the winding machine 1, not shown in Figs. 1 to 4, only a single secondary transport device is provided, which simplifies the desigrr'ttf the winding machine.
The winding machine 1 furthermore comprises a pressing drum 19, which can be driven by means of a central drive 17 indicated with a symbol and is rotatably secured on a guide block 21, which can be moved on first rails 22. In this exemplary embodiment, the rails 9 and 22 are disposed parallel to one another. The distance between the guide rails 15 and the longitudinal axis 23 of the pressing drum 19, which lies in the plane E, is therefore constant. The guide block 21 is associated with a pressing device 25 that is embodied here as a hydraulic piston and cylinder unit, which is fastened to the machine frame 13. The pressing device 25 exhibits a piston 29 that is guided in a cylinder 27 and is connected to a piston rod 31 that engages the guide block 21. When the piston rod 31 travels outward, the guide block 21 and consequently, the pressing drum 19, which is also called a Pope drum, are shifted toward the right in Fig. 1, in the direction of an arrow 33. When the piston rod 31 travels into the cylinder 27, a shifting of the pressing drum 19 toward the left in Fig. 1 occurs. The maximal stroke of the piston 29, i.e. how far the piston rod 31 can travel out of or into the cylinder 27, is preferably less than half the material layer thickness S of a finished winding roll. In another exemplary embodiment, the provision is made that the stroke of the piston 29 is greater than or equal to the material layer thickness S of a finished winding roll.
In another advantageous embodiment, the pressing device includes two hydraulic piston and cylinder units in order to shift the pressing drum and to generate a desired line force.
As is apparent from Fig. l, the pressing drum 19 forms a winding gap-with a winding roll 37 that has been wound onto a reel 35, i.e. the pressing drum 19 forms a nip together with the winding roll 37. The pressing drum 19 thus touches the circumference of the winding roll over its entire length. The reel 35, which is rotatably secured and guided by the secondary transport device 5 in this winding phase, is engaged by a secondary drive 39, which is indicated with a symbol and is embodied in this instance by a central drive. With _g_ P 16940.S03 the aid of the secondary drive 39, a torque can be exerted on the reel that is resting on the guide rails 15 and is secured by the secondary transport device 5.
The guide rails 15 are attached to the machine frame 13 in suel3 a way that the longitudinal axis 41 of the reel 35, which rests with its bearing pins on the guide rails 15, lies in the same plane E as the longitudinal axis 23 of the pressing drum 19. In another advantageous exemplary embodiment of the winding machine 1, the pressing drum 19 and the reel resting on the guide rails 15 are disposed at different heights (Figs. 9, 12, 13), which nevertheless has no influence on the advantageous operation of the winding machine 1.
The material web 3 is guided by way of the pressing drum 19 and is wound onto the winding roll 37. The line force in the winding gap is controlled by means of the pressing device 25 associated with the pressing drum 19, i.e. the pressing drum 19 is pressed with a definite force against the circumference of the winding roll 37, by means of which a desired winding hardness of the winding roll or a uniform winding hardness progression can be adjusted. In another exemplary embodiment, the provision is made that the line force in the winding gap is regulated, i.e. the pressing device 25 is part of a regulating circuit that automatically maintains or adjusts the line force to a desired value.
Fluctuations in the line force can be reliably compensated for or avoided by means of the shifting of the pressing drum 19 by the pressing device 25 so that a desired winding hardness can be continuously produced. By means of this, the line force can be maintained at a--for example constant--value even if there is a malfunction in the winding process. A malfunction can, for example, be a not-entirely-precise movement of the secondary transport device so that the position of the winding gap formed by the pressing drum 19 and the winding roll 37 shifts slightly, or can be a balance error in the pressing drum and/or the winding roll.
The growing diameter of the winding roll 37 is compensated for by means of a shifting of the winding ro~137 to the right in the direction of the arrow 33.
To this end, the secondary transport device 5 is moved toward the right, which brings about a slaving of the reel 35 and consequently of the winding roll 37. For the moving of the secondary transport P 16940.S03 devices 5 and 7, a stroke device 43 is provided here, which includes a threaded spindle 47 driven by a motor 45.
An empty reel 49, which is secured by a primary transport devicernot shown, is disposed in a ready position above the pressing drum 19 (Figs. l and 2). For the preparation of a reel change, the reel 49 is shifted with the aid of the primary transport device from the ready position into a reel-changing position in which this reel is secured in a stationary and rotatable fashion by the primary transport device, whose design is described in more detail below (Fig. 3). While the empty reel 49 is disposed in the reel-changing position, a winding gap is formed by means of a relative movement between the pressing drum 19 and the empty reel 49, i.e. the pressing drum and the empty reel touch each other on their circumference over their entire length. After the cutting of the material web by means of an intrinsically known cutting device, not shown, (symbolically depicted in Figs. 8c and 14c by means of an arrow T), the web is wound with its new web beginning onto the empty reel 49, which is disposed in the reel-changing position. By means of the primary transport device, the reel 49 1 S can be moved along a first guide track from the ready position into the reel-changing position and from this into a finished winding position (Fig. 4). In connection with the present invention, the "finished winding position" is understood to mean a position of the reel 49 in which it rests with its bearing pins on the guide rails 15. The first guide track can have a curved, preferably arc-shaped and/or linear course. The primary transport device is associated with a central drive, not shown, which is also called the primary drive and is for the reel or winding roll held by this transport device, by means of which the reel can be acted on with a driving and/or a braking moment.
In Fig. 3, the empty reel 49 is disposed in the reel-changing position in which after a cutting procedure, the new web beginning is wound onto the reel 49. The reel 49 forms a winding gap with the pressing drum 19 and this gap lies in a pressing plane P, which is inclined in relation to an imaginary horizontal by an angle a, which lies in a range of 5 ° <_ a <_ 40°, preferably 10° <_ a s 35°, in particular IS° <_ a _< 30°. In this instance, purely by way of example, the angle a amounts to approximately 32°. Angles a that lie in the range from 15° to 30° have turned out to be particularly advantageous.
Since the winding gap lies in the inclined pressing plane P, the deflection resulting from the pressing force and the component of the deflection resulting from the tare weight, which component lies in the pressing plane P, cancel each other out, so that a uniform line force can be adjusted in the winding gap over the width of the web. A
favorable winding quality thus can be achieved.
Beneath the pressing drum 19, a pressing element is provided, which in this exemplary embodiment is constituted by a press roll 51 that extends over the entire width of the winding roll 37 and is also called a squeeze roll. By means of a guide device that is not shown, the press roll 51 can he pressed against the circumference of the winding roll that forms a winding gap with the pressing drum 19. The press roll S 1 serves to prevent air from slipping in between the winding layers of the winding roll, for example when the material web 3 travels in a free draw from the pressing drum to the winding roll. The press roll 51 can be acted on with a torque and accelerated to web speed by a drive, for example a central drive. In another exemplary embodiment not shown in the Figs., the pressing element is constituted by a stationary pressing brush, which is affixed to at least one bar extending over the entire width of the winding roll. By means of a shifting of the bar, the pressing brush is placed against the winding roll, by means of which the air that has slipped between the winding layers is virtually stroked out. In comparison to the press roll, the pressing brush has a simplified and therefore more reasonably priced design since it does not rotate and consequently, an additional drive is not required. This is also true for a so-called air brush, which is an air blower nozzle that extends over the width of the web and acts on the winding roll in a contact-free manner after the fashion of an air squeezing device.
In the following, the function of the winding machine 1 will be explained in more detail in conjunction with a winding process: The material web 3 is guided by way of the pressing drum 19 and wound onto the winding roll 37 that is guided by the secondary transport device 5 (Fig. 1). Before the winding roll 37 reaches its final diameter, the press roll 51 is pressed against the circumference of the winding roll 37 (Fig. 2). The material web 3 is consequently guided both through the winding gap between the pressing drum 19 and the P 16940.S03 winding roll 37, and through the winding gap between the press roll 51 and the winding roll 37. For the transfer of the continuously supplied material web 3 onto the empty reel 49, the winding roll 37 is moved by means of the secondary transport device 5 along-the guide rails 15 in the direction of the arrow 33, by means of which the distance increases between the longitudinal axis 23 of the pressing drum 19 and the longitudinal axis 41 of the winding roll 37, which in this instance both lie in the plane E, and an intermediary space 53 is formed between the pressing drum 19 and the winding roll 37 (Fig. 3). In the region of the intermediary space 53, the material web 3 is transferred in a free draw from the pressing drum 19 onto the winding roll 37. While the secondary transport device 5 is moved along with the winding roll 37, the press roll 51 is guided after the winding roll 37 in such a way that the line force in the winding gap between the press roll S 1 and the winding roll 37 maintains a desired value until the pressing drum 19 comes into contact with at least one stop 54. In this exemplary embodiment, the stop 54 is produced by virtue of the fact that the piston 29 of the pressing device 25 strikes against the inner wall of the cylinder 27, i.e.
reaches its rightward end position, in the depiction according to Fig. 3, in which the piston 29 rests against the inner wall of the cylinder 27. The pressing drum 19 thus has a fixed position.
Then from above, the empty reel 49, which is disposed in the ready position and has been accelerated to the travel speed of the material web 3, is shifted downward along the first guide track and brought into the reel-changing position in the intermediary space 53 between the pressing drum 19 and the winding roll 37 (Fig. 3). The pressing drum 19 that has been moved against the stop 54 is disposed in the first guide track so that when the empty reel 49 is moved into the reel-changing position, this reel is brought into contact with the pressing drum 19. As a result, the reel 49 forces the pressing drum 19 back from the stop 54 counter to the direction of the arrow 33 (not shown), which finishes the formation of the nip/winding gap. Then, by means of a cutting device, not shown, which is disposed, for example, in the region of the intermediary space 53, the material web is cut crosswise over the width and the P 16940.S03 new web beginning is wound onto the reel 49. The reel 49 remains in the reel-changing position for a variable duration of time, for example until the winding of the core of the new winding roll has been finished. Then, the reel 49 that is rotatably secured h~the primary transport device is guided along the first guide track from the reel-changing position into the finished winding position and is lowered directly onto the guide rails 15 (Fig. 4). The reel 49 is taken over, i.e. is guided and held, by the second secondary transport device 7, which is disposed in the take-over position. In the winding phase shown in Fig. 4, a few layers of the material web 3 that are not shown are already wound onto the reel 49 that is still being driven by the primary drive or by a central drive associated with the secondary transport device 7.
After the finished winding roll 33 has been braked, for example with the aid of the secondary drive 39 and/or the press roll, it can be removed from the secondary transport device 5, while the press roll 51 is shifted back into its position shown in Fig. 1. As.long as the secondary drive 39 is associated with both secondary transport devices 5 and 7, after the braking of the full winding roll, now the secondary drive is effectively connected to the reel 49, and the primary drive and the primary transport device are released from the reel 49. The growing diameter of the winding roll that is wound onto the reel 49 and is not shown in Fig.
4 is compensated for by a shifting of the secondary transport device 7 along the guide rails 15 in the direction of the arrow 33. The line force in the winding gap between the pressing drum 19 and the winding roll wound onto the reel 49 is maintained at a desired value during the entire winding process by means of a shifting of the pressing drum '19 by the pressing device 25.
A web guide roll 55 is represented in Fig. 1, which is disposed below the pressing drum 19 and is rotatably attached to the machine frame 13. By means of a unit 57, which is disposed before the web guide roll 55 in terms of the travel direction of the material web and which in this instance, purely by way of example, is a pressing device 59, the material web 3 is guided to the web guide roll 55, deflected by this roll, and conveyed further to the pressing drum 19. The material web 3 is wound around the web guide roll SS, preferably in P 16940.503 a circumference range from 155 ° to 205 °. The winding angle is at least 150°, even when the pressing drum 19 is being shifted during the winding process. It is hereby assured that the line force in the winding gap is not influenced by a change of the web longi~dinal stress in the region between the unit 57 and the pressing drum 19. The pressing device 59 comprises two press rolls that form a nip, at least one of which is driven, as shown in Fig. 1.
In order to uncouple the winding process to a large extent from the fluctuations of the production process of the material web, the material web guidance is preferably embodied so that the material web 3 is wound around the pressing drum 19 by approximately 180°.
Since the material web is guided over a relatively large circumference region of the pressing drum, fluctuations in the draw have practically no influence on the pressure of the pressing drum against the winding roll and consequently have practically no influence on the line force. Furthermore, small movements of the pressing drum are compensated for so that they cause no draw fluctuations; the pressing drum is therefore reactionless. As a result of the relatively large winding angle, a further assurance can be made that a slightly inclined position of the pressing drum does not lead to an undesirable wrinkle formation. It is furthermore possible to connect only stationary guide rolls and spreader rolls before the pressing drum, which do not have to be guided after the movable pressing drum, by means of which the design of the winding machine can be simplified.
The above-mentioned process can be readily inferred from the description of Figs.
1 to 4. This process provides for the fact that the material web is guided by way of a preferably horizontally movable pressing drum, which forms a winding gap with the winding roll that is rotatably secured in a secondary transport device, wherein the line force in the winding gap is controlled or regulated by means of a shifting of the pressing drum. In order to prepare for a reel change when a desired winding roll diameter is reached, the winding roll is moved away from the pressing drum by means of the secondary transport device so that the material web travels freely from the pressing drum to the winding roll; a free draw is thus produced. A primary transport device brings a new reel, i.e. an empty one, which is rotating at web speed, into a reel-changing position in which the new reel forms a winding gap with P 16940.S03 the pressing drum. Then, the material web is cut crosswise over its width and the new web beginning is wound onto the new reel. In this winding phase, the control/regulation of the line force in the winding gap between the pressing drum and the new reel or.the winding roll wound onto it is in tum carried out by means of a shifting of the pressing drum. Finally, the secondary transport device takes over the new reel with the new winding roll, wherein the control/regulation of the line force continues to be carried out by means of a shifting of the pressing drum.
The formation of a winding gap between the pressing drum 19 and the empty reel can be realized by virtue of the fact that the empty reel is moved along the first guide track and strikes against the pressing drum disposed in the first guide track. In another embodiment, the provision is made that the winding gap is formed by means of a shifting of the pressing drum 19 with the aid of the pressing device 25 in the direction of the reel disposed in the reel-changing position. Naturally, both the reel 49 and the pressing drum 19 can be moved toward each other in order to form a winding gap. Independent of how the winding gap is formed, abrupt fluctuations in the line force of the kind that occur, for example, at the moment the reel is transferred from the primary transport device to the secondary transport device, can be compensated for or prevented with the aid of the movable pressing drum. The line force can thus be continuously maintained exactly at a desired value.
As is shown in Figs. 3 and 4, the pressing drum 19 can be embodied as a deflection adjusting roll 140 whose roll jacket 141 is supported on a stationary yoke 143 by means of a series of support elements 142, which produces a bulging outer contour of the pressing drum 19. Only one of the support elements 142 that act in the direction toward the winding gap can be seen in the view according to Figs. 3 and 4. The design of the deflection adjusting roll 140 is intrinsically known (DE-OS 25 55 677) so that this is not described in more detail.
The support elements 142 can preferably be controlled individually, i.e.
independently of one another, whereby a desired bulging of the roll jacket 41 can be adjusted. The yoke 143 can be rotated around a fixed axis, in this instance, the longitudinal axis 23.
The support elements P 16940.503 142 that cooperate with the yoke 143 are pivoted in such a way during a rotation of the yoke 143 that the direction in which they act follows the wandering motion of the winding gap.
Through the adjustment of a desired bulging of the outer contour.ofthe pressing drum, the material web guided by way of it can, viewed crosswise to the travel direction of the web, be definitely stretched, preferably before the material web travels into the winding gap. By means of this, a wrinkle formation of the winding layers wound onto the winding roll can be prevented and consequently, the winding result can be improved. In terms of the longitudinal direction of the drum, the deflection of the pressing drum can preferably be adjusted in sections, as described above. As a result, the desired spreading of the material web can be influenced, preferably adjusted, by varying the outer contour of the pressing drum. In an advantageous exemplary embodiment, the pressing drum 19 is part of an active vibration damping system, i.e. the pressing drum is oscillatory. In connection with the current invention, the tem "oscillatory" is understood to mean that the pressing drum can execute a rapid shifting motion toward the winding roll and in the opposite direction.
The pressing device 25, i.e. the hydraulic piston and cylinder unit represented in Figs. 1 to 4, can therefore very rapidly execute a direction change in the shifting motion of the pressing drum 19.
Fig. 5 shows a schematic representation of the winding machine according to Figs.
1 to 4, with an embodiment of a control. Parts that coincide with those in Figs. 1 to 4 are provided with the same reference numerals so that in this regard, reference will be made to the descriptions of Figs. 1 to 4. For the control of the winding machine 1, a control unit 61 is provided, which controls the motor 45 of the threaded spindle as a function of the speed of the diameter increase of the winding roll 37. The diameter increase of the winding roll 37 is measured by means of a measuring device 63. The position of the secondary transport device 5 thus changes solely, i.e. exclusively, in accordance with the increase of the winding roll diameter. The magnitude of the line force in the winding gap formed between the pressing drum 19 and the winding roll 37 is solely, i.e. exclusively, determined by means of a moving of the guide block 21 holding the pressing drum 19, preferably regulated by means of a regulating device 65. This includes a measuring device 67 for the line force, a regulator P 16940.S03 69, a set point transmitter 71, and a control unit 73. The measuring device 67 is connected by way of a measurement line 75 to the regulator 69 or feeds into this. The set point transmitter 71 is connected by way of a line 75' to the regulator 69 and indicates the desired set point to the this regulator 69. The regulator 69 is in turn connected by way of a line 77 to the control unit 73.
In the event that the value of the line force, which is measured by the measuring device 67 and disposed in the winding gap formed between the pressing drum 19 and the winding roll 37, diverges from the set point predetermined by the set point transmitter, the regulator 69 sends a signal to the control unit 73 by way of the line 77. This control unit then changes the pressure in the cylinder 27 of the pressing device 25 in such a way that the measured value of the line force approaches the set point. By means of this, the line force can be kept at a for example constant value even in the event of a malfunction in the winding process. A malfunction can, for example, be a not-entirely-precise movement of the secondary transport device 5 so that the position of the winding gap formed by the pressing drum 19 and the winding roll 37 guided by the secondary transport device 5 shifts slightly.
In a preferred exemplary embodiment, the provision is made that in order to control the line force, the pressing drum 19 can be shifted independently of the travel speed of the secondary transport device. Furthermore, it is possible that the stroke device 43 that cooperates with the secondary transport device, i.e. the motor 45 that drives the threaded spindle 47, can be controlled in such a way that the position of the winding gap formed between the pressing drum 19 and the winding roll 37 is essentially constant while the winding roll 37 is resting on the guide rails 15. The "constant position" of the winding gap is understood to mean its position inside the winding machine l, i.e. the winding roll 37 is shifted in the direction of the arrow 33 by means of the secondary transport device 5 with a speed such that only the diameter increase of the winding roll 37 is compensated for.
In another exemplary embodiment, the provision is made that the stroke device associated with the secondary transport device 5, 7 can be controlled in such a way that the position of the winding gap formed between the pressing drum 19 and the winding roll 37 4' P 16940.S03 shifts with an increasing winding roll diameter during the winding process, for example in a range from 50 mm to 200 mm.
Fig. 6 shows a schematic representation of another exemplary embodiment of the winding machine 1. Parts that coincide with those in Figs. 1 to 5 are provided with the same reference numerals so that in this regard, reference will be made to the descriptions of Figs.
1 to 5. A part of an exemplary embodiment of the primary transport. device 79 is shown in Fig. 6. This includes two primary pivoting levers 81, only one of which is depicted in this view. The primary pivoting levers 81 to which the new reel 49 is rotatably secured can be pivoted around an axle 83 that runs parallel to the longitudinal axis of the reel 49. The primary pivoting levers 81 are disposed in a stationary manner inside the winding machine 1; i.e., the axle 83 has a fixed, unchangeable position in the machine frame 13, at least during a complete winding operation. The primary pivoting levers 81 are associated with a stroke device 85, which is assigned, for example, to the machine frame 13, and this stroke device includes at least one--preferably hydraulic--piston and cylinder unit associated with a primary pivoting lever. The piston and cylinder unit comprises a piston 89 that is guided in a cylinder 87 and is connected to a piston rod 91 that engages at least one of the primary pivoting levers 81. When the piston rod 91 travels outward out of the. cylinder 87, the primary pivoting levers 81 are pivoted counterclockwise around the axle 83 and when the piston rod 91 travels inward, they are pivoted clockwise. Naturally, the stroke device 85 can also include, for example, two piston and cylinder units, which are each associated with a primary pivoting lever 81.
In this winding phase, the primary pivoting levers 81, which hold the empty reel 49 in the reel-changing position, as shown in Fig. 6, are inclined in relation to an imaginary horizontal H, represented with a dashed line, by an angle w, which in this instance amounts to approximately 26°. The angle w can be adjusted by means of the stroke device 85. In order to adjust the angle w, a regulating device 93 is provided, which includes a regulator 69', a set point transmitter 71', and a measuring device 67' for determining the position of the primary drive levers 81. The set point transmitter 71' is connected to the regulator 69' by 4' P 16940.S03 way of a signal line 95 and the measuring device 67' is connected to the regulator 69' by way of a signal line 97. In order to change the angle w and consequently to change the location of the reel-changing position, a new set point is input into the set point-tr~nsmitter 71'. A
variance comparison is executed with the aid of the regulator 69'. In the event of a deviation, the regulator 69' sends a signal by way of a line 77' to a hydraulic regulating valve 99, which then opens up the through flow between a pump 101 and a medium line 103 leading from the regulating valve 99 to the cylinder 87. The medium supplied by the pump, for example a hydraulic fluid or a gas, can alternatively be introduced into one of the partial chambers of the cylinder 87 that are divided from each other by the piston 89. If the medium is introduced into the upper partial chamber in the depiction according to Fig. 6, as indicated with an arrow, then the piston rod 91 travels into the cylinder 87, which reduces the angle w. If medium flows into the lower partial chamber of the cylinder 87, the piston rod 91 travels out of the cylinder, which increases the angle w. After the desired angle w has been set, the regulating valve 99 interrupts the connection between the pump 101 and the line 103. A
check valve 105 is provided in order to prevent a return flow of the medium from the cylinder 87 in the direction of the regulating valve 99.
With the aid of the regulating device 93, a definite angle w can be set at any time during the winding operation. Moreover, it is particularly advantageous that the location of the reel-changing position can be predetermined before the next reel change, wherein for example if needed, an angle w can also be adjusted that is equal to zero (for example according to Fig. 14c).
Fig. 7 shows a view of the reel 49 in the winding phase shown in Fig. 3, in which the reel 49 is disposed in the reel-changing position and forms a winding gap with the pressing drum 19. The viewing direction of the reel 49 is indicated in Fig. 3 with an arrow 107. In this exemplary embodiment, the force with which the pressing drum 19 is pressed against the circumference of the reel 49 leads to a deflection of the reel 49 that is represented with a double arrow 109. The curvature of the outer contour of the reel 49 that is caused by the deflection is schematically represented with a line 111. The component of the deflection, 4' P 16940. S03 which results from the tare weight of the reel 49, located in the pressing plane P, is represented with a double arrow 113. The curved outer contour of the unsupported reel is schematically represented with a line 115. ---As is apparent from Fig. 7, the deflections act in opposite directions, wherein they are at least basically equal in magnitude. The deflections therefore cancel each other out preferably completely, but at least significantly so that a uniform line force in the winding gap can be adjusted over the entire width of the material web.
Figs. 8a to 8e each show a very schematically depicted schematic representation of a part of the winding machine 1 described in conjunction with the preceding Figs., in different winding phases. The reel-changing procedure already described briefly above will be explained in more detail below in conjunction with Figs. 8a to 8e.
Before the reel change, an empty reel 49 is taken over by the stationary winding station, namely by the primary transport device 79, which in this instance includes primary pivoting levers 81 (Fig. 8a). To this end, the primary pivoting levers 81 are pivoted counter-clockwise upward into the empty reel take-over position shown in Fig. 8a. The empty reel 49 is accelerated by means of the primary drive to a synchronous speed; i.e., the circumference speed of the empty reel 49 corresponds to the travel speed of the material web 3. The pressing element, in this instance the press roll S 1, is pressed against the circumference of the almost full winding roll 37. The winding roll 37, which is secured by the secondary transport device, not shown, and is driven by means of the secondary drive, is moved together with the press roll S 1 away from the pressing drum 19 in the direction of the arrow 33. The pressing drum 19 is guided after the winding roll 37 in order to maintain a desired line force in the winding gap until the pressing drum 1-9 runs up against a stop 117, whereby its shifting motion is stopped. The winding roll 37 travels farther in the direction of the arrow 33, whereby a free draw between the pressing drum and the winding roll is formed.
Since the pressing drum comes into contact with a stop 117 before a reel change, the pressing drum has a fixed, definite position before each reel change. If the distance between the pressing drum and the full winding roll 37 has reached at least a minimal value, the new reel 49 is moved into the reel-changing position in which the reel rests against the circumference of the pressing drum (Fig. 8c). The forming of the nip/winding gap occurs automatically since the pressing drum resting against the stop 117 is disposed in the movement path of the empty reel 49 at this time. The nip is considered to be closed when the pressing drum has been forced by the empty reel 49 so far back from the stop 117 in the opposite direction from the arrow 33 that the pressing drum exerts the desired pressing force against the empty reel 49, for example by means of the regulating device 65 (Fig. 5).
For clarity, in Figs. 8a to 8c, the distance x of the longitudinal axis 23 of the pressing drum 19 from the stationary axle 83 of the primary pivoting levers 81, which is disposed on an imaginary vertical V, is shown immediately before the reel change (Fig. 8a), during the reel change (Fig. 8b), and after the reel change (Fig.
8c). In the winding phase according to Fig. 8b, in which the pressing drum 19 has already come into contact with the stop 117, the distance x2 exists, which is greater than the distance x3, which is set after the pressing drum is forced back by means of the reel 49, which has been shifted into the reel-changing position. It is furthermore apparent that before the pressing drum comes into contact with the stop 11 7, it has a distance xl to the axle 83, which is less than the distance x2.
After the formation of the winding gap, the material web is cut in the region of the free draw using one of the known methods and the new web beginning is guided onto the reel 49. It is particularly advantageous that the empty reel 49 disposed in the reel-changing position is already wound around by the material web over a small circumference region before the cutting, which facilitates the change-over process considerably so that a high degree of reliability can be assured in the reel change.
After the reel change, the reel 49 is preferably held in the reel-changing position until the formation of the winding core of the new winding roll 119 wound onto the reel 49 has been finished, for example until the winding roll 119 exhibits a layer thickness S
of 20 mm to 100 mm.

P 1 G940.S03 During the core winding, i.e. when the reel 49 is rotatably secured on the primary pivoting levers 81, the pressing drum 19 moves away from the longitudinal axis of the reel 49 in accordance with the diameter increase of the winding roll 119. In termgef amount, the shifting of the pressing drum corresponds exactly to the horizontal component of the radius increase. During the winding-on of the new winding roll 119, the full winding roll 37 is braked and removed from the variable winding station, i.e. the secondary transport device.
In a preferred exemplary embodiment in, which only one secondary transport device is provided, the secondary transport device is shifted to the left in the direction of the pressing drum in order to take over reel 49 stored on the guide rails 1 S. In the exemplary embodiment of the winding machine, in which two secondary transport device are provided, they are used alternatingly for the guidance of a new winding roll. The two secondary transport devices therefore only respectively guide every other winding roll. While the reel with the new winding roll wound on it is being guided by the secondary transport device, the radius increase of the winding roll is compensated for by means of a corresponding shifting of the reel with the aid of the secondary transport device. In terms of amount, the shifting of the reel in the horizontal direction corresponds exactly to the radius increase.
In another embodiment of the process that can be carried out using the winding machine described in conjunction with Figs. 8a to 8e, the provision is made that the winding roll 37 guided by the secondary transport device is continuously moved without an intermediate stop from the position shown in Fig. 8a into the position shown in Fig. 8d. At the same time, the primary pivoting levers 81 and the new reel 49 move from the position shown in Fig. 8b to the position shown in Fig. 8e, preferably also without an intermediate stop. The reel change takes place when the new reel 49 being moved by means of the primary pivoting levers passes through the position shown in Fig. 8c. The speed of the movements of the winding roll 37, which is guided by the secondary transport device, and the reel 49, which can be moved with the aid of the primary pivoting levers, can be constant or can change at preferably at least one arbitrary point. The movement course of the primary pivoting levers 81 securing the new reel 49 can be simply controlled by means of a time-4' P 16940.S03 dependent change of the set point for the angle w, which set point is supplied by the set point transmitter 71' (Fig. 6).
Figs. 9 to 11 each show a side view of a part of another exemplary embodiment of the winding machine l, in different winding phases. The design of the winding machine 1 corresponds essentially to the winding machine described in conjunction with Figs. 1 to 8.
The differences will be addressed in more detail below. Parts that are the same are provided with the same reference numerals so that in this regard, reference will be made to the descriptions of the preceding Figs.
First, the function of the winding machine 1 should be explained in more detail below in conjunction with a winding operation: The material web 3 is guided by way of the pressing drum 19 and is wound onto the winding roll 37, which is guided by the secondary transport device 5 and is driven by the secondary drive 39 (Fig. 9). Before the winding roll 37 reaches its final/desired diameter above the pressing drum 19, the empty reel 49 is rotatably attached to the primary pivoting levers 81, i.e. the movement of the empty reel 49 is limited to a rotation around its longitudinal axis, and is moved into the reel-changing position.
It is apparent from Fig. 9 that the reel 49 disposed in the reel-changing position is spaced apart from the pressing drum 19 in such a way that no winding gap is formed yet. In the reel-changing position, the center point of the empty reel 49 is disposed on an imaginary second straight line G2, which is represented with dashed lines and is disposed essentially parallel to an imaginary first straight line G1 and is disposed on a higher level in relation to it. As is apparent from Fig. 9, the center point of the pressing drum 19 is disposed on the straight line G1 extending parallel to the guide rails 15. In a reel change, before the transfer of the material web 3, the empty reel 49 is accelerated by the primary drive 121 associated with the primary pivoting levers 81 and is brought to the travel speed of the material web 3.
In order to transfer the continuous material web 3 onto the empty reel 49, the travel speed of the secondary transport device S guiding the winding roll 37 is increased by means of a corresponding control of the motor 45 driving the threaded spindle 47. The pressing drum P 16940.S03 19 remains in constant contact with the winding roll 37, i.e. when the winding roll 37 is shifted along the linear second guide track 14, the pressing drum is guided after it so that the line force in the winding gap is maintained at a desired value. ---As is apparent from Fig. 9, the distance between the straight lines G1 and G2 is less than the sum of the radii of the pressing drum 19 and the reel 49. As a result, in a shifting toward the right in Fig. 9, the pressing drum 19 comes into contact with the reel 49 that is disposed in the reel-changing position. This corresponds to the winding phase shown in Fig.
10. At the moment in which a winding gap is formed beriveen the pressing drum 19 and the empty reel 49, or at least shortly after this, the reel change is triggered.
In the reel change, the material web 3 is cut by means of a cutting device not shown in Figs. 9 to 11, and the new web beginning is wound onto the reel 49. At the moment of the reel change, i.e. just before the cutting and transfer of the material web 3 onto the empty reel, an intermediary space is already formed between winding roll 37 and the pressing drum 19.
It must be stressed that the pressing drum does not assume any fixed position before 1 S a reel change, i.e. does not come into contact with a stop, as in the exemplary embodiment described in conjunction with Figs. 1 to 8, but comes directly into contact with the empty reel 49, which is held in a fixed position (reel-changing position) by the primary pivoting levers 81.
As shown in Fig. 10, the piston 27 of the pressing drum 25 is spaced apart from the inner wall of the cylinder 29 at this moment; the piston 27 is therefore not disposed in an end/stop position.
After the new web beginning is wound onto the reel 49, this reel is transported along the first guide back 122, which is arc-shaped here, into the finished winding position by a pivoting of the primary pivoting levers 81 clockwise around the axle 83.
During the pivoting procedure, the reel 49 is rotatably secured and supported by the primary pivoting levers 81.
The reel 49 is continuously driven by the primary drive 121, i.e. is likewise moved along the first guide track 122.

P 16940. S03 In Fig. 11, the new reel 49 is shown in its finished winding position, i.e. it rests with its bearing pins on the guide rails 1 S which support the weight of the reel 49 and the winding roll that is wound on it, not shown, which only has a few winding layers.
Daring the transfer of the reel 49 from the reel-changing position (Figs. 9 and 10) into the finished winding position (Fig. 11), the pressing drum 19 is moved along the straight line G1 by means of the pressing device 25 so that the line force in the winding gap is maintained at a desired value during the entire transfer.
In Fig. 11, the winding roll 37 is disposed in a removal position in which the winding roll can be lifted from the guide rails 1 S by means of known devices and removed from the winding machine 1. In the exemplary embodiment of the winding machine 1 shown in Figs.
9 to 11, only a single secondary transport device and only one secondary drive 39 are provided. In Fig. 11, they are already shifted toward the left in the direction of the pressing drum 19 in order for the primary transport device 79 to take over the reel 49.
In this connection, the secondary transport device 5 and the secondary drive 39 can be shifted into the take-over position jointly or independently of each other. While the secondary transport device S is taking over the reel 49 from the primary pivoting levers 81, the secondary drive 39 is coupled to the reel 49 so that temporarily, both drives 39 and 121 are coupled to the reel 49. After this, the primary drive 121 is uncoupled from the reel 49 and moved counterclockwise back along the first guide track into the reel-changing position. The diameter increase of winding roll, not shown, which is wound on the reel 49 guided by the secondary transport device 5, is now compensated for during the finishing winding by means of a shifting of the secondary transport device 5 and consequently the reel 49 toward the right in the direction of the arrow 33. The line force in the winding gap between pressing drum 19 the winding roll wound on the reel 49 the and is controlled by means of a shifting of the pressing drum 19, as described above.

P 16940.S03 For the sake of clarity, only one control of the winding machine 1 is shown in Fig.
10, which includes a regulating device 65. For the explanation of the design and the operation of the regulating device 65, reference is made to the description-of Fig. 5.
In a preferred exemplary embodiment, the provision is made that the pressing drum 19 can be moved independent of the travel speed of the secondary transport device 5, in order to control the line force. It is furthermore possible that the stroke device 43 associated with the secondary transport device 5, i.e. the motor 45 driving the threaded spindle 47 can be controlled in such a way that the position of the winding gap formed between the pressing drum 19 and the winding roll 37 is essentially constant. The "constant position" of the winding gap is understood to mean its position inside the winding machine 1.
The winding roll 37 is thus shifted in the direction of the arrow 33 by means of the secondary transport device S with a speed that compensates for only the diameter increase of the winding roll 37.
In another exemplary embodiment, the provision is made that the stroke device associated with the secondary transport device S can be controlled in such a way that the position of the winding gap formed between the pressing drum 19 and the winding roll 37 shifts with the increasing winding roll diameter during the winding process, for example in a range from 50 mm to 200 mm.
In a preferred exemplary embodiment, during the winding-on of an empty reel, the winding gap is always at the same location, i.e. its position inside the winding machine during a reel change is constant or at least basically constant. As a result, during the winding on of an empty reel, there are always equivalent angular ratios, for example of the pressing forces acting on the reel, so that the deflection of the empty reel can be calculated and correspondingly compensated for in order to adjust a desired line force progression in the winding gap. Naturally, in this exemplary embodiment it is also possible, with a regulating device 93 that is described for example in conjunction with Fig. 6, to shift the reel-changing position in which the winding gap is formed.
Fig. 12 schematically represents a side view of another exemplary embodiment of the winding machine 1. Parts that coincide with those described in conjunction with Figs. 1 to P 16940.503 11 are provided with the same reference numerals so that in this regard, reference will be made to the descriptions of Figs. 1 to 11. In this exemplary embodiment, the primary transport device 79 includes a securing device 127 that can be moved on third rails 123 in the direction of a double arrow 125 and the empty reel 49 is held in a stationary and rotatable fashion in this securing device 127. The securing device 127 thus permits a rotary motion of the reel 49 and hinders it from a translatory motion. By moving the securing device 127, the reel 49 can be moved from the reel-changing position (not shown), along the straight first guide track 14' realized by means of the rails 123, into the finished winding position in which the reel 49 rests on the guide rails 15. In addition, the reel 49 is moved or lowered from a higher level (G2) to a lower level (G1). The third rails 123 are inclined in relation to an imaginary horizontal H represented with a dashed line by an angle z, which in the exemplary embodiment shown in Fig. 12, lies in a range from 45° to 90°. Due to the inclination of the rails 123, the travel path of the reel 49 from the reel-changing position downward into the finished winding position is similar to the travel path of a reel that is pivoted by means of primary pivoting levers around an axle 83 that is fixed in relation to the machine frame (Fig. 9).
Based on Fig. 12, a second embodiment of a control/regulation for adjusting the line force in the winding gap between the pressing drum and a reel or a winding roll can be inferred, which differs from the control/regulation described in conjunction with Fig. 10 by virtue of the fact that the travel speed of the secondary transport device 5 is adjusted or changed as a function of the position of the piston 29 in the cylinder 27 of the pressing device 25. The regulator 73 can control/regulate the pressure in the cylinder 27 and consequently the line force in the winding gap as a function of a number of parameters. The parameters are the longitudinal stress of the material web 3 (draw) measured with a measuring device 129, the diameter D of the winding roll 37, and an angle a, which indicates the position of a reel guided by the primary transport device 79. The diameter D of the winding roll 37 and the angle a are inferred from a calculated and/or determined control curve, which is shown by way of example in Fig. 12.

P 16940.S03 The angle a is measured between the straight line G1 and a plane 131 which intersects the longitudinal axes of the pressing drum 19 and the empty reel 49.
The position of the piston 29 in the cylinder 27 is sent to the control unit 61 by way of a signal line 133 and this unit controls the motor 45 of the stroke device 43, which motor drives the threaded spindle 47.
Fig. 13 shows another exemplary embodiment of the winding machine 1 according to the invention, with a control that is described in conjunction with Figs. 5 and 10. Parts that are the same are provided with the same reference numerals so that in this regard, reference will be made to the descriptions of the preceding Figs. In this exemplary embodiment, the rails 22, upon which the guide block 21 which rotatably secures the pressing drum 19 can be moved, are inclined in relation to an imaginary horizontal by an angle (3, which in this instance lies between 0° and 45°. In a shift by means of the pressing device 25 in the direction of an arrow 135, the pressing drum 19 is raised from a lower-lying level to a higher-situated level, i.e. is moved obliquely upward. As is apparent from Fig. 13, the pressing drum 19 is only in contact with the winding roll 37, but is not in contact with the empty reel 49 disposed in the reel-changing position.
Also in the exemplary embodiment shown in Fig. 13, the weight of the pressing drum 19 is still for the most part supported by the rails 22 so that a sufficiently precise control of the line force in the winding gap is readily possible. Only a small portion of the weight of the pressing drum influences the measurement precision and/or adjustment precision of the line force, namely only the slope descent component.
In another exemplary embodiment not shown in the Figs., the provision is made that the linear guidance, which is for the pressing drum 19 and is constituted by the rails 22 and the guide block 21, can be pivoted, for example with the aid of at least one pivoting lever.
Figs. 14a to 14e each show a very schematic representation of a part of the winding machine 1 that has been described in conjunction with the preceding Figs. 1 to 11 and 13, in various winding phases. Only the differences in operation are addressed in detail below.
In the exemplary embodiment represented in Figs. 14a to 14e, before a reel change, the new P 16940.S03 reel 49 is stored on the guide rails 15, not shown. In order to prepare for a reel change, the pressing drum 19 is moved into contact with a stop 117' which is positioned so that when the new reel 49 is brought into the reel change position, the pressing drum l9is forced back by the stop 117' while the reel 49 approaches the guide rails 15. The winding-on of the new reel 49 is thus carried out only after the reel is set down onto the rails, by means of which fluctuations and/or jumps in the line force progression that can occur when setting the reel down onto the guide rails during the winding-on operation are reliably prevented.
Furthermore, the mechanical engineering costs of the winding machine described in conjunction with Figs. 14a to 14e can be simplified in relation to the other exemplary embodiments since for example, a stable lateral shaft for connecting the primary pivoting levers can be eliminated.
Also in the exemplary embodiment of the winding machine described in conjunction with Figs. 14a to 14e, the winding roll 37 can be continuously moved along the second guide track, i.e. without an intermediate stop. While the winding roll 37 in the Figs. 14a to 14d is guided toward the right, at the same time, the new reel 49 is lowered, preferably continuously, from the position shown in Fig. 14b into the position shown in Fig. 14c. The speed of the movements of the winding roll 37 and the new reel 49 in the winding phases shown in Figs. 14a to 14e can be constant or can change at least one arbitrary point.
The above-mentioned process can be readily inferred from the description of Figs.
1 to 14. It is comprised in that the material web is guided by way of a pressing drum that can be moved horizontally or at least essentially horizontally, which forms a winding gap with the winding roll that is rotatably secured in a secondary transport device.
During this winding phase, the line force in the winding gap is controlled/regulated by means of a shifting of the pressing drum. When a desired winding roll diameter is reached, in order to prepare for a reel change, the winding roll is moved away from the pressing drum with the aid of the secondary transport device so that the material web travels freely from the pressing drum to the winding roll. A new reel, rotating at the web travel speed, is brought into a reel-changing position by means of a primary transport device and forms a new winding gap with the pressing drum.

c.
P 16940.S03 Then, the material web is cut crosswise over its width and the new web beginning is wound onto the new reel. During this winding phase as well, the control/regulation of the line force in the winding gap between the pressing drum and the new reel is in turn realized by means of a shifting of the pressing drum. Finally, the secondary transport device takes over the new reel with the new winding roll. In this winding phase as well, i.e. when the new reel is being guided by the secondary transport device, the control/regulation of the line force in the winding gap is exclusively realized by means of a shifting of the pressing drum. A desirable winding result can be achieved by virtue of the fact that the line force is adjusted by means of a shifting of the pressing drum during the entire winding operation. A high degree of reliability during a reel change can be assured with the above-described process since the new reel, which is moved into the reel-changing position in the free draw, is wound around at least part of the way by the material web before the reel change takes place.
From all of this, it becomes clear that in the above-described exemplary embodiments of the winding machine in which the primary drive can only be moved along the first guide track, whose design can therefore be simplified by virtue of the fact that the primary drive is mounted in a stationary fashion to a part of the primary transport device, which can be moved together with the reel along the first guide track. In another embodiment of the winding machine, the provision is made that the primary drive can be moved both along the first guide track and also part of the way along the second guide track.
Moreover, it is naturally also possible that the secondary drive can be disposed in a stationary fashion on the secondary transport device, which further simplifies the design of the winding machine.
In a particularly preferred exemplary embodiment that is not shown in the Figs., the stroke of the pressing drum, i.e. the maximal distance that the pressing drum can be shifted in one direction, is greater than or equal to the material layer thickness S
of a finished winding roll. A secondary transport device that moves the reel during the completion of the winding process, in accordance with the diameter increase of the winding roll can be refrained from hereby. In this exemplary embodiment, the winding roll is thus wound in two fixed winding stations. A "fixed" winding station" is distinguished by the fact that the reel P 16940.S03 is rotatably secured in such a way that both the diameter increase of the winding roll wound on it and the adjustment of the line force in the winding gap are realized exclusively by means of a shifting of the pressing drum. A fixed winding station has the-advantage that it offers an optimal rigidity of the reel mount so that a transmission of possibly occurring vibrations to the winding roll can be practically ruled out. Since the shifting path of the pressing drum is so great that the diameter increase can be completely compensated for, a constant reel tracking is not required, by means of which the design of the winding machine can be simplified.
It is common to all the exemplary embodiments of the winding machine that in order to prepare for a reel change, an intermediary space/a gap is foimed between the almost finished winding roll and the pressing drum. As a result, it can be assured that before the reel change, the material web is already guided over a circumference region of the empty reel, which is disposed in the reel-changing position. As a result, a high degree of functional reliability can be assured.
It is furthermore advantageous that as a result of the stationary, rotatable securing of the new reel at the beginning of the winding process in the primary transport device, an adj usting device of the kind that is frequently used in known winding machines can be eliminated. This adjusting device is employed to move the reel that is guided by the primary transport device radially in the direction of the pressing drum in order to adjust the line force in the winding gap. Because of this advantageous embodiment, an additional control/regulation for the adjusting device can be omitted so that the costs of the winding machine are reduced.
It is common to all the exemplary embodiments of the winding machine that the control/regulation of the line force in the winding gap can, according to the invention, be exclusively carried out during the entire winding process by a single device, namely by means of a shifting of the pressing drum with the aid of the pressing device 25.

P I G940.S03 It is furthermore particularly advantageous that existing, i.e. already assembled winding machines can be retrofitted so that one of the above-described processes for winding the material web 3 can be realized. ---Alternatively to the reel, the winding machine can be equipped with a winding core S to which a winding sleeve or a number of winding sleeves are attached. In the latter case, the winding machine can be preceded by a longitudinal cutting device. This cuts the web into a number of partial webs, wherein each partial web is wound onto a winding sleeve.

Claims

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. Process for continuous winding of a material web, in particular a paper or cardboard web, to form a winding roll on a reel, comprising the following steps:
- the material web is guided by way of a movable pressing drum, which forms a winding gap with a winding roll rotatably secured in a secondary transport device, wherein the line force in the winding gap is controlled/regulated by means of a shifting of the pressing drum;
- in order to prepare for a reel change when a desired winding roll diameter is reached, the winding roll is moved away from the pressing drum by means of the secondary transport device so that the material web runs freely from the pressing drum to the winding roll;
- a new reel, which rotates at web speed, is moved by means of a primary transport device into a reel-changing position in which the new reel forms a new winding gap with the pressing drum;
- the material web is cut crosswise over its width and with its new web beginning, is wound onto the new reel, wherein the control/regulation of the line force in the winding gap between the pressing drum and the new reel is in turn carried out by means of a shifting of the pressing drum;
- the secondary transport device takes over the new reel with the new winding roll, wherein the control/regulation of the line force continues to be carried out by means of a shifting of the pressing drum.

2. Process according to claim 1, wherein after the secondary transport device takes over a reel, a compensation for the diameter increase of the winding roll is carried out.

3. Processing according to claim 2, wherein said compensation includes horizontal by shifting the secondary transport device.

4. Process according to any one of claims 1 to 3, wherein the winding gap between the new reel and the pressing drum is formed by means of a relative movement of the pressing drum in relation to the empty reel.

5. Process according to any one of claims 1 to 3, wherein the winding gap is formed by means of a relative movement of the empty reel in relation to the pressing drum.

6. Process according to claim 5, wherein, during the movement of the winding roll away from the pressing drum, this pressing drum follows the winding roll until it reaches a stop, and then, the new reel is brought into the reel-changing position, wherein it forces the pressing drum back from the stop.

7. Process according to any one of claims 1 to 6, wherein the winding gap is formed above the position in which the secondary transport device takes over the new reel.

8. Process according to claim 7, wherein the winding gap is formed in a pressing plane defined by the longitudinal axes of the empty reel and the pressing drum, which plane is included in relation to an imaginary horizontal phase by an angle a that ties in a range of 5° <= .alpha.
<= 40°.

9. Process according to claim 8, wherein said angle a lies in the range 10° <= .alpha. <= 35°.

10. Process according to claim 9, wherein said angle a is 15° <=
.alpha. <= 30°.

11. Process according to any one of claims 1 to 6, wherein the reel-changing position is disposed where the secondary transport device take over the new reel.

12. Process according to any one of claims 1 to 11, wherein, while the material web is being guided in a free draw from the pressing drum to the winding roll, a pressing element, preferably a press roll, non-rotating pressing brush or the like is pressed against the circumference of the winding roll.

13. Process according to any one of claims 1 to 11, wherein the material web is already guided over a circumference region of the new reel while this reel is disposed in the reel-changing position.

14. Process according to any one of claims 1 to 13, wherein the winding roll guided by the secondary transport device is continuously shifted in order to compensate for the diameter increase.

15. Process according to any one of claims 1 to 14, wherein the shifting speed of the new reel guided by the primary transport device and the shifting speed of the winding roll guided by the secondary transport device are constant or change at preferably at least one arbitrary point.

16. Winding machine for continuous winding of a material web, in particular a paper or cardboard web, onto a reel into a winding roll, having a movable pressing drum, which forms a winding gap with the winding roll, having at least one primary transport device by means of which the reel can be moved along a first guide track and having at least one secondary transport device which guides the reel along a second guide track, wherein, in order to prepare for a reel change, the new reel is shifted by means of the primary transport device into a reel-changing position in which a new winding gap is formed between the new reel and the pressing drum, and wherein, in the reel-changing position, the material web is guided over a circumference region of the new reel.

17. Winding machine according to claim 16, wherein the reel-changing position is provided above the position in which the secondary transport device takes over the new reel.

18. Winding machine according to claim 16 or 17, wherein the new winding gap is disposed in a pressing plane that is defined by the longitudinal axes of the empty reel and the pressing drum, and this plane is inclined in relation to an imaginary horizontal by an angle a that lies in a range of 5°
<= .alpha. <= 40°.

19. Winding machine according to claim 18, wherein angle a in a range of 10° <= .alpha. <= 35°.

20. Winding machine according to claim 19, wherein angle a in a range of 15° <= .alpha. <= 30°.

21. Winding machine according to claim 16, wherein the reel-changing position is disposed where the secondary transport device takes over the reel.

22. Winding machine according to any one of claims 16 to 21, wherein the pressing drum can be moved by means of a pressing device and wherein the diameter increase can be compensated for and the line force in the winding gap is controlled/regulated by means of a shifting of the pressing drum, while the winding roll is being guided by the primary transport device.

23. Winding machine according to any one of claims 16 to 22, wherein the diameter increase is compensated for by means of a shifting of the secondary transport device and the line force in the winding gap is adjusted by means of a shifting of the pressing drum, while the winding roll is being guided by the secondary transport device.

24. Winding machine according to any one of claims 16 to 23, wherein the winding gap is formed by means of a relative movement of the new reel in relation to the pressing drum and/or by means of the relative movement of the pressing drum in relation to the new reel.

25. Winding machine according to any one of claims 16 to 24, wherein the pressing drum is rotatably secured on a guide block and wherein the guide block is moved on first rails that are disposed parallel to an imaginary horizontal or are inclined in relation to it by an angle .beta..

26. Winding machine according to any one of claims 16 to 24, wherein the pressing drum is rotatably secured to pivoting levers that can be pivoted around an axis that runs parallel to the longitudinal axis of the reel.

27. Winding machine according to any one of claims 16 to 26, wherein the pressing drum is associated with a drive.

28. Winding machine according to claim 27, wherein said drive is a central drive.

29. Winding machine according to any one of claims 16 to 28, wherein the secondary transport device includes a secondary block that is moved on second rails, wherein the rails are disposed parallel to an imaginary horizontal or are inclined in relation to the horizontal.

30. Winding machine according to any one of claims 16 to 28, wherein the secondary transport device includes secondary pivoting levers to which the reel is rotatably secured and these levers are pivoted around an axle that runs parallel to the longitudinal axis of the reel.

31. Winding machine according to any one of claims 16 to 30, wherein the secondary transport device is associated with at least one secondary drive for acting on the reel with a driving and/or braking movement.

32. Winding machine according to claim 31, wherein said secondary drive is a central device.

33. Winding machine according to any one of claims 16 to 31, wherein the secondary transport device is associated with a stroke device and wherein a stroke device is controlled/regulated as a function of the growing winding roll diameter.

34. Winding machine according to claim 33, wherein the stroke device is controlled/regulated independent of the line force acting in the winding gap between the pressing drum and the winding roll.

35. Winding machine according to any one of claims 16 to 34, wherein the pressing device associated with the pressing drum is actuated for the control/regulation of the line force, independently from a stroke device associated with the secondary transport device.

36. Winding machine according to any one of the claims 16 to 35, wherein the pressing device is controlled by means of a regulating device so that the line force in the winding gap between the pressing drum and the winding roll corresponds to a set point.

37. Winding machine according to any one of claims 16 to 36, wherein the position of the winding gap formed between the pressing drum and the winding roll guided by the secondary transport device is constant.

38. Winding machine according to any one of claims 16 to 37, wherein the position of the winding gap formed between the pressing drum and the winding roll guided by the secondary transport device shifts with the increasing winding roll diameter during the winding process.

39. Winding machine according to claim 38, wherein said increasing winding roll diameter is in a range from 50mm to 200mm.

40. Winding machine according to any one of claims 16 to 38, wherein the pressing device is embodied as a hydraulic piston and cylinder unit.

41. Winding machine according to claim 40, wherein the maximal stroke of the piston is less than half the material layer thickness of a finished winding roll.

42. Winding machine according to any one of claims 16 to 41, wherein the pressing drum is embodied in the form of a deflection adjusting roll whose roll jacket is supported on a stationary yoke by means of a series of support elements.

43. Winding machine according to claim 42, wherein the support elements are controlled individually.

44. Winding machine according to claim 42 or 43, wherein the support elements act in the direction toward the winding gap.

45. Winding machine according to any one of claims 16 to 44, wherein the yoke is pivoted in such a way that the direction in which the support elements act follows the wandering motion of the winding gap.

46. Winding machine according to any one of claims 16 to 45, wherein the primary transport device includes primary pivoting levers in which the reel is rotatably secured, and these levers are pivoted around an axle running parallel to the longitudinal axis of the reel.

47. Winding machine according to claim 46, wherein the axle of the primary pivoting levers is disposed in a stationary fashion inside the winding machine.

48. Winding machine according to any one of claims 16 to 47, wherein the primary transport device includes a securing device that is moved on third rails.

49. Winding machine according to claim 48, wherein the third rails are disposed vertically or are inclined in relation to an imaginary vertical by an angle z.

50. Winding machine according to any one of claims 16 to 49, including means of at least one pressing element that is pressed against the circumference of the winding roll.

51. Winding machine according to any one of claims 16 to 49, wherein the angle .alpha. is adjusted, preferably before a reel change.

52. Winding machine according to claim 51 wherein the angle .alpha. is adjusted before a reel change.