EP0912435A1

EP0912435A1 - Method and reeling machine for continuous reeling of a strip of material

Info

Publication number: EP0912435A1
Application number: EP98928270A
Authority: EP
Inventors: Roland Möller; Ralf Preising; Rudolf Beisswanger; Zygmunt Madrzak; Walter Kaipf
Original assignee: Voith Sulzer Papiertechnik Patent GmbH
Current assignee: Voith Patent GmbH
Priority date: 1997-05-16
Filing date: 1998-05-15
Publication date: 1999-05-06
Anticipated expiration: 2018-05-15
Also published as: US6129305A; DE59813447D1; WO1998052858A1; ATE234254T1; JP4391600B2; ATE320996T1; JP2000514770A; BR9804919A; EP0912435B1

Abstract

PCT No. PCT/EP98/02867 Sec. 371 Date Nov. 18, 1998 Sec. 102(e) Date Nov. 18, 1998 PCT Filed May 15, 1998 PCT Pub. No. WO98/52858 PCT Pub. Date Nov. 26, 1998Winding 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 at least one secondary transport device that guides the reel along a second guide track. To prepare for a reel change, the new reel can be shifted by 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. In the reel-changing position, the material web is guided over a circumference region of the new reel.

Description

Method and Wiekelmasehine for the continuous winding of a material web

description

The invention relates to a method for the continuous winding of a material web, in particular paper or cardboard box, according to the preamble of claim 1 and a winding machine for the continuous winding of a material web, in particular paper or cardboard web, according to the preamble of claim 9.

Methods and winding machines of the type mentioned here are known (EP 0 561 128 AI). They are used, for example, at the end of a machine to produce a web of material and are used to continuously wind the web of material onto a reel. The known Wiekelmasehine comprises a horizontally displaceable pressure drum, also referred to as a support drum, over the circumference of which the material web is guided in regions. The material web is wound up into a winding roll on a reel, the winding roll forming a winding gap with the pressure drum during the entire winding process. To prepare a reel change, an empty reel is pressed against the circumference of the pressure drum, which creates a new winding nip. During this winding phase, the material web is closed both by the nip between the new drum and the Anoreßtrom el and by the Nip between the almost finished winding roll and the pressure drum. Then the material web in the area between the full winding roll and the new reel is cut directly on the pressure drum and the new web start is wound onto the new reel. It has turned out to be disadvantageous that it is very difficult to transfer and wind the new start of the web onto the empty reel. In many cases, several attempts are necessary, which in turn leads to a relatively high proportion of rejects.

It is therefore an object of the invention to provide a method and a Wiekelmasehine that do not have these disadvantages.

To achieve this object, a method is proposed which has the features mentioned in claim 1. The process is carried out in the following steps: The material web is guided over a displaceable pressure drum, which forms a winding nip with the winding roll rotatably held in a secondary transport device, the line force in the winding nip being controlled / regulated by a displacement of the pressure drum during this winding phase. To prepare a reel change, when the desired winding roll diameter is reached, the winding roll is removed from the pressure drum by means of the secondary transport device, so that the material web runs freely from the pressure drum to the winding roll. A new spool rotating at the web speed is moved into the free web train by a primary transport device and brought into a spool change position in which the new spool also moves the pressure drum forms a new winding nip. The material web is then cut across its width and wound onto the new reel with its new web start. During this winding phase, the control / regulation of the line force in the winding gap between the pressure drum and the new reel is again realized by moving the pressure drum. Finally, the new reel with the new winding reel is taken over by the secondary transport device, the line force also being controlled / displaced by relocating the pressure drum when the new reel is guided by the secondary transport device. Because the empty reel is already wrapped in areas by the material web before the new web start is transferred and wound up, that is, the material web is guided over a circumferential area of the new reel, while the material web is still being wound onto the almost finished winding roll, a safe transfer of the web and winding of the winding roll onto the new reel can be guaranteed. The process is characterized by a high level of reliability.

It is also advantageous that the line force in the winding gap is set during the entire winding process exclusively by a relative movement of the pressure drum with respect to the winding roll. Due to the relatively light weight of the pressure drum compared to the weight of the winding roller, which is relatively large, it can be moved quickly. Jumps and fluctuations in line force can thus be compensated for very quickly. This ensures an exact, even line force in the winding gap throughout the entire the winding process adjustable / controllable, so that overall a good winding quality can be achieved. It is also particularly advantageous that a change in direction of the displacement movement of the pressure drum can be carried out very quickly due to the relatively low weight of the pressure drum compared to the winding roll.

In a particularly preferred embodiment variant of the method, it is provided that when the winding roll is removed from the pressure drum, the winding roll follows the winding roll until a stop is reached, and that the new drum is then brought into the drum changing position, with the drum winding up with the drum before changing the drum - Cold winding roller pushes the pressure drum back from the stop. In this way, it can be ensured with relatively little control effort that the line force can be set or maintained exactly by moving the pressure drum to a desired value during a complete winding process, i.e. from winding to finished winding of the winding roll.

Finally, an embodiment variant of the method is also preferred, which is characterized in that the empty drum is brought into a winding position lying above a pressure drum. Then a winding gap is formed between the pressure drum and the empty drum by a relative movement between the pressure drum and drum. The arrangement of the empty drum relative to the pressure drum is selected so that the through the winding gap and the longitudinal axes of the empty drum and the pressure flow mel certain contact plane is inclined to an imaginary horizontal by an angle α which is in a range of 5 ° <α <40 °, preferably 10 ° <<35 °, in particular 15 ° <<30 °. With this position of the empty drum, the material web is separated and its free end is wound onto the empty drum. Because the winding gap lies in the inclined pressing plane during winding, the deflection resulting from the pressing force and the component lying in the pressing plane of the deflection resulting from the weight of the spool are preferably completely, but at least essentially eliminated. As a result, a line force which is uniform across the web width can be set in the winding gap, which in turn leads to an improvement in the winding quality.

Also preferred is an embodiment of the method, which is characterized in that after the take-up of a reel by the secondary transport device, the diameter increase of the winding roll is compensated for by a preferably horizontal or at least approximate horizontal displacement of the secondary transport device. The adjustment of the line force and thus the displacement of the pressure drum takes place independently of the compensating movement of the growing winding roll. The load in the winding gap can therefore be adjusted or adjusted very precisely. The fluctuations or jumps in line force that have occasionally occurred in the winding nip so far are at least largely avoided. In this way, a defined, uniform winding hardness can be set; in particular, an exact core winding can be ensured. Further embodiments result from the remaining subclaims.

To achieve the stated object, a winding machine is also proposed which has the features mentioned in claim 11. This is characterized by the fact that, in preparation for a reel change, the new reel can be moved by means of the primary transport device into a reel change position in which a new winding gap is formed between the new reel and the pressure drum, and that in the reel change position the material web is guided over a circumferential area of the new drum. The fact that the new reel is already wrapped in sections by the web of material wound onto the almost finished winding reel before the reel change can ensure a high level of reliability.

An exemplary embodiment of the Wiekelmasehine is particularly preferred in which the reel change position is provided above the position in which the secondary transport device takes over the new reel. In an advantageous embodiment, the new winding nip is located during the winding process in a pressing plane determined by the longitudinal axes of the empty drum and the pressure drum, which is inclined by an angle with respect to an imaginary horizontal which is in a range of 5 ° <<40 ° , preferably from 10 ° <α <35 °, in particular from 15 ° <<30 °. As a result, the component of the deflection resulting from the dead weight and the deflection resulting from the contact pressure lying in the contact plane cancel each other at least approximately. This means that an evenly linear force in the winding gap over the entire web width can be ensured, so that a defined structure of the winding core and then the remaining winding roll is possible. The improvement of the winding quality in the core thus enables an exact winding of the entire winding roll.

In an advantageous embodiment of the winding machine, it is provided that the diameter increase can be compensated for by moving the secondary transport device and the line force in the winding gap can be adjusted, preferably regulated, by moving the pressure drum, while the winding roll is guided by the secondary transport device becomes. The compensation of the increasing winding roll diameter and the adjustment of the line force are thus carried out by two separate, separately operable or working devices, the secondary transport device and the pressure drum. Because the weight of the pressure drum is relatively light compared to the weight of the winding roll, it can be shifted quickly and jumps and fluctuations in the line force can be compensated very quickly. It is particularly advantageous that due to the relatively low weight of the pressure drum, a change in direction of the displacement movement can be carried out very quickly by means of the pressure device. The mutually independent displacement movements of the pressure drum and the secondary transport device can achieve a — preferably consistently — good winding result.

An embodiment of the Wiekelmasehine is also preferred, in which the at least one pressing device, with the help of which the pressing drum is can be stored as a - preferably hydraulic - piston and cylinder unit. In a first embodiment variant, the maximum stroke of the piston is less than half the material layer thickness of a finished winding roll. Despite the relatively small stroke, i.e. the distance that the pressure drum can be moved in one direction, the pressure system is not changed during the winding process. The relocatable pressure drum remains in constant contact with the winding roll for a few seconds while the reel is being changed. The winding machine is characterized by a simple and inexpensive construction. In a further, second embodiment variant it is provided that the maximum stroke of the piston is at least greater than or equal to the layer thickness of a finished winding roll. This makes it possible to replace the displaceable secondary transport device by a stationary secondary storage, in which the drum is rotatably held. In the case of stationary storage, optimum rigidity of the reel tensioning can be ensured, so that any vibrations that may occur within the winding machine have practically no effect on the line force / curve. A constant drum tracking is therefore not necessary, so that the mechanical structure can be simplified.

Finally, an exemplary embodiment of the winding machine is preferred, in which only a single drive, preferably a center drive, is assigned to the primary and the secondary transport device, with the aid of which torque can be applied to the reel. The drive assigned to the primary transport device becomes preferably also used to accelerate an empty reel to the running speed of the material web.

Further advantageous embodiments result from the remaining subclaims.

The invention is explained below with reference to the drawing. Show it:

Figures each a schematic principle 1 to 4 sketch of an embodiment of the Wiekel machine according to the invention in different winding phases;

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;

Figure 6 is a schematic diagram of another embodiment of the winding machine with a control device for setting the reel changing position;

Figure 7 is a schematic diagram of a reel shown in Figure 3 in a reel change position;

FIGS. 8a to 8e each show a schematic diagram of the winding machine according to FIGS. 1 to 5 in different winding phases; FIGS. 9 to 11 each show a detailed outline of a third exemplary embodiment of the winding machine;

Figures each a schematic principle

12 and 13 sketch further exemplary embodiments of the winding machine and

Figures each a highly schematic 14a to 14e representation of a sixth embodiment of the winding machine.

The Wiekelmasehine described below is generally used for winding a web of material. The Wiekelmasehine can be arranged at the end of a machine for producing or finishing a material web, for example a paper web, in order to wind up the finished material web into a winding roll. The winding machine can also be used to rewind finished winding rolls. By way of example only, it is assumed that this is a winding machine for winding a continuous paper web.

FIGS. 1 to 4 each show a schematic basic sketch of a first exemplary embodiment of a winding machine 1, which is used to wind a paper web, generally referred to below as material web 3, onto a reel, winding core or the like. A sequence of functional steps of the winding machine 1 can be seen from FIGS. 1 to 4. In this exemplary embodiment, the winding machine 1 comprises two secondary transport devices 5 and 7, each of which comprises a secondary carriage 11 which can be moved on second rails 9. The rails 9 are parallel to an imaginary hori- zontal arranged and attached to a machine frame 13. The secondary transport devices 5, 7 are used for rotatably holding and guiding a reel along a second, horizontally running guideway 14 which lies in an imaginary plane E, shown in dashed lines. This spans a surface that is perpendicular to the image plane of FIG. 1. Furthermore, 13 guide rails 15 are attached to the machine frame, which are arranged parallel to an imaginary horizontal. A spool having a journal can be placed on and is supported by the guide rails 15, that is, the weight of the spool and the weight of the winding roll wound on the spool is supported by the guide rails 15. In a particularly preferred embodiment of the winding machine 1 (not shown in FIGS. 1 to 4), only a single secondary transport device is provided, as a result of which the structure of the winding machine is simplified.

The winding machine 1 further comprises a pressure drum 19 which can be driven by means of a center drive 17 indicated by a symbol and which is rotatably held on a guide carriage 21 which can be moved on first rails 22. In this embodiment, the rails 9 and 22 are arranged parallel to each other. The distance between the longitudinal axis 23 of the pressure drum 19 lying in the plane E and the guide rails 15 is therefore constant. A pressure device 25, which is designed here as a hydraulic piston and cylinder unit and is attached to the machine frame 13, is assigned to the guide carriage 21. The pressing device 25 has one in a cylinder 27 guided piston 29 which is fixedly connected to a piston rod 31 acting on the guide slide 21. When the piston rod 31 moves out, the guide slide 21 and thus the pressure drum 19, which is also referred to as the support drum, is displaced to the right in the direction of an arrow 33 in FIG. When the piston rod 31 moves into the cylinder 27, the pressure drum 19 is shifted to the left in FIG. The maximum stroke of the piston 29, ie to what extent the piston rod 31 can extend or retract from the cylinder 27, is preferably less than half the material layer thickness S of a finished winding roll. In a further embodiment it is provided 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 pressure device comprises two hydraulic piston and cylinder units in order to displace the pressure drum and to generate a desired line force.

As can be seen from FIG. 1, the pressure drum 19 forms a winding nip with a winding roller 37 wound on a reel 35, that is to say the pressure drum 19 forms a nip together with the winding roller 37. The pressure drum 19 touches the winding roll over its entire length on its circumference. A secondary drive 39 indicated by a symbol, which is formed here by a center drive, acts on the drum 35, which is rotatably held and guided by the secondary transport device 5 in this winding phase. With the help of the secondary drive 39, a torque can rest on the guide rails 15. and the drum held by the secondary transport device 5 are applied.

The guide rails 15 are attached to the machine frame 13 in such a way that the longitudinal axis 41 of the drum 35 resting with its bearing journal on the guide rails 15 lies in the same plane E as the longitudinal axis 23 of the pressure drum 19. In another advantageous embodiment of the winding machine 1 the pressure drum 19 and the reel resting on the guide rails 15 are arranged at different height levels (FIGS. 9, 12, 13), but this has no influence on the advantageous functioning of the winding machine 1.

The material web 3 is guided over the pressure drum 19 and wound onto the winding roll 37. The line force in the winding nip is controlled by means of the pressing device 25 assigned to the pressing drum 19, that is to say the pressing drum 19 is pressed against the circumference of the winding roller 37 with a defined force, as a result of which a desired winding hardness of the winding roller or a uniform winding hardness profile can be set. In another exemplary embodiment, it is provided that the line force is regulated in the rocking gap, that is to say the pressure device 25 is part of a control circuit which automatically maintains or adjusts the line force to a desired value. By shifting the pressure drum 19 by means of the pressure device 25, fluctuations in the line force can be reliably compensated for or avoided, so that a desired winding hardness can be achieved continuously. As a result, the line force can also be kept at a constant value, for example, if there is a fault in the winding process. A malfunction can, for example, be a not very precise movement of the secondary transport device, so that the position of the winding gap formed by the pressure drum 19 and the winding roller 37 shifts slightly, or an unbalance of the pressure drum and / or the winding roller.

The increasing diameter of the winding roller 37 is compensated for by a displacement of the winding roller 37 in the direction - arrow 33 to the right. For this purpose, the secondary transport device 5 is moved to the right, as a result of which the drum 35 and thus the winding roller 37 are carried along. For moving the secondary transport devices 5 and 7, a lifting device 43 is provided here, which comprises a threaded spindle 47 driven by a motor 45.

Above the pressure drum 19, an empty drum 49 held by a primary transport device, not shown, is arranged in a standby position (FIGS. 1 and 2). To prepare a reel change, the reel 49 is shifted from the ready position to a reel change position by means of the primary transport device, in which position it is held stationary and rotatable by the primary transport device, the construction of which will be described below (FIG. 3). While the empty drum 49 is in the drum change position, a winding gap is formed by a relative movement between the pressure drum 19 and the empty drum 49, that is, the pressure drum and the empty drum touch each other on their circumference, and that over their entire length. On the in camouflage empty reel position located at the change of position, the web is wound up with its new beginning of the web by means of a separating device, not shown, which is known per se (symbolically represented by an arrow T in FIGS. 8c and 14c). By means of the primary transport device, the spool 49 can be shifted along a first guideway from the ready position to the spool change position and from there to a finished winding position (FIG. 4). In connection with the present invention, “finished winding position” is understood to mean a position of the reel 49 in which it rests with its bearing journals on the guide rails 15. The first guideway can have a curved, preferably part-circular, and / or linear course. The primary transport device is assigned a center drive (not shown), also referred to as the primary drive, for the drum or winding roll held by the latter, by means of which the drum can be acted upon by a drive and / or a braking torque.

In FIG. 3, the empty reel 49 is arranged in the reel changing position, in which the new web start is wound onto the reel 49 after a separation process. The drum 49 forms with the pressure drum 19 a winding gap, which lies in a pressure plane P, which is inclined relative to an imaginary horizontal by an angle α, which is in a range of 5 ° <α <40 °, preferably 10 ° <α < 35 °, in particular 15 ° <α <30 °. The angle α here is, by way of example, approximately 32 °. Angles α which have been found to be particularly advantageous are in the range from 15 ° to 30 °. Due to the fact that the winding gap lies in the inclined contact plane P, the deflection resulting from the contact pressure and the component lying in the contact plane P of the bending of the drum resulting from the dead weight cancel each other out, so that a uniform line force in the winding gap over the Web width can be adjusted. Good winding quality can be achieved in this way.

Provided below the pressure drum 19 is a pressure element which, in this exemplary embodiment, is formed by a pressure roller 51 which extends over the entire width of the winding roller 37 and is also referred to as a squeeze roller. The drive roller 51 can be pressed by means of a guide device (not shown) onto the circumference of the winding roll forming a winding gap with the pressure drum 19. The pressure roller 51 serves to prevent entrainment of air between the winding layers of the winding roll, for example when the material web 3 runs in a free pull from the pressure drum to the winding roll. The pressure roller 51 can be acted upon by a drive, for example a center drive, with a torque and accelerated to the web speed. In a further exemplary embodiment — not shown in the figures — the pressing element is formed by a stationary pressure brush, which is attached to at least one beam that extends over the entire width of the winding roll. By relocating the bar, the pressure brush is placed on the winding roller, which means that the air that is carried in between the winding layers is practically blown out. The pressure brush has a simplified th and thus more economical construction, since it does not rotate and therefore an additional drive is not required. This also applies to a so-called air brush; which is an air blowing nozzle which extends over the web width and acts on the winding roll in a contactless manner in the sense of an air squeezing device.

The function of the winding machine 1 is to be explained in more detail below with the aid of a winding process: The material web 3 is guided over the pressure drum 19 and wound onto the winding roller 37 guided by the secondary transport device 5 (FIG. 1). Before the winding roller 37 reaches its final diameter, the pressure roller 51 is pressed against the circumference of the winding roller 37 (FIG. 2). The material web 3 is thus guided both through the winding gap between the pressure drum 19 and the winding roller 37 and also through the rocking gap between the pressure roller 51 and the winding roller 37. To transfer the continuously fed material web 3 to the empty reel 49, the winding roller 37 is moved by means of the secondary transport device 5 along the guide rails 15 in the direction of the arrow 33, whereby the distance between the longitudinal axis 23 of the pressure drum 19 and the longitudinal axis 41 of the winding roller 37 , both of which lie in plane E, enlarged and an intermediate space 53 is formed between the pressure drum 19 and the winding roller 37 (FIG. 3). The material web 3 is transferred in the region of the intermediate space 53 in a free train from the pressure drum 19 onto the winding roll 37. The pressure roller 51 is tracked while the secondary transport device 5 is being moved with the winding roller 37, so that the linear force in the winding gap between pressure roller 51 and winding roller 37 maintains a desired value until the pressure drum 19 moves against at least one stop 54. In this exemplary embodiment, the stop 54 is realized in that the piston 29 of the pressing device 25 abuts the inner wall of the cylinder 27, that is to say it reaches its right end position in the illustration according to FIG. 3, in which the piston 29 on the inner wall of the cylinder 27 is present. The pressure drum 19 thus has a fixed position.

The empty drum 49, which is arranged in the standby position and accelerated to the running speed of the material web 3, is then shifted downward along the first guideway and introduced into the intermediate space 53 between the pressure drum 19 and the winding roller 37 into the reel changing position (FIG. 3). The pressure drum 19 driven against the stop 54 is arranged in the first guide track, so that when the empty reel 49 is moved into the reel changing position, the same is brought into contact with the pressure drum 19. The drum 49 pushes the pressure drum 19 back from the stop 54 against the direction of the arrow 33 (not shown), which completes the formation of the winding gap / nip. Then the material web is separated across the width by means of a separation device, not shown, which is arranged, for example, in the area of the intermediate space 53, and the new web start is wound onto the reel 49. The reel 49 remains in the reel changing position for a variable period of time, for example until the winding of the core of the new winding roll is completed. Then the one from the primary trans port device rotatably held reel 49 is guided along the first guideway from the reel changing position into the finished winding position and lowered directly onto the guide rails 15 (FIG. 4). The drum 49 is taken over by the second secondary transport device 7 arranged in the take-over position, that is to say guided and held. In the winding phase shown in FIG. 4, some layers of the material web 3 (not shown) are already wound onto the drum 49, which is still driven by the primary drive or a center drive assigned to 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 pressure roller, it can be brought out of the secondary transport device 5 while the pressure roller 51 is moved back into its position shown in FIG. If the secondary drive 39 is assigned to both secondary transport devices 5 and 7, the secondary drive is now effectively connected to the reel 49 after the full winding roll has been braked, and the primary drive and the primary transport device are detached from the reel 49. The increasing diameter of the winding roll wound on the reel 49 (not shown in FIG. 4) is compensated for by a displacement of the secondary transport device 7 in the direction of arrow 33 along the guide rails 15. The line force in the winding gap between the pressure drum 19 and the winding roll wound on the spool 49 is caused by a displacement of the pressure drum 19 by means of the pressure device 25 during of the entire winding process is kept at a desired value.

FIG. 1 shows a web guide roller 55 arranged below the pressure drum 19 and rotatably fastened to the machine frame 13. The material web 3 is guided to the web guide roller 55 by a unit 57 arranged upstream of the web guide roller 55, viewed in the direction of travel of the material web, which is a pressing device 59 here by way of example, deflected by the latter and passed on to the pressure drum 19. The web guide roller 55 is wrapped around by the material web 3, preferably in a circumferential range of 155 ° to 205 °. The wrap angle is at least 150 °, even if the pressure drum 19 is shifted during the winding process. This ensures that the line force in the winding gap is not influenced by a change in the longitudinal tension of the web in the area between the unit 57 and the pressure drum 19. The press device 59 comprises two press rolls forming a press nip, of which, as shown in FIG. 1, at least one is driven.

In order to largely decouple the winding process from the fluctuations in the production process of the material web, the material web guide is preferably designed such that the pressure drum 19 is wrapped around the material web 3 by approximately 180 °. Because the material web is guided over a relatively large circumferential area of the pressure drum, fluctuations in the web tension have practically no influence on the pressure of the pressure drum on the winding roll and thus on the line force. Furthermore, small movements of the pressure drum compensated, so that this does not cause any train tension fluctuations; the pressure drum is therefore non-reactive. The relatively large wrap angle also ensures that a slight inclination of the pressure drum does not lead to undesired wrinkling. Furthermore, it is possible to connect only stationary guide and spreader rollers to the pressure drum, which do not have to be tracked to the displaceable pressure drum, whereby the structure of the winding machine can be simplified.

The method mentioned above is readily apparent from the description of FIGS. 1 to 4. This provides that the material web is guided over a - preferably horizontally - displaceable pressure drum, which forms a winding nip with the winding roller rotatably held in a secondary transport device, the line force in the winding nip being controlled or regulated by a displacement of the pressure drum. When a desired winding roll diameter is reached, the winding roll is removed from the pressure drum by means of the secondary transport device in preparation for a reel change, so that the material web runs freely from the pressure drum to the winding roll; a free train is thus formed. A new, i.e. empty, spool rotating at the web speed is brought into a spool change position by means of a primary transport device, in which it forms a winding nip with the pressure drum. The material web is then cut across its width and the new web start is wound onto the new reel. In this winding phase, the control / regulation of the line force in the winding gap between the contact current mel and the new drum or the winding roll wound on it, in turn, by relocating the pressure drum. Finally, the secondary transport device takes over the new reel with the new winding roll, with the line force still being controlled by moving the pressure drum.

The formation of a winding gap between the pressure drum 19 and the empty reel can be realized in that the empty reel is displaced along the first guideway and abuts against the pressure drum arranged in the first guideway. In another embodiment variant it is provided that the winding gap is formed by a displacement of the pressure drum 19 with the aid of the pressure device 25 in the direction of the drum arranged in the reel changing position. Of course, both the drum 49 and the pressure drum 19 can be moved towards one another to form a rocking gap. Regardless of how the winding nip is formed, sudden fluctuations in the line force, such as occur at the moment the reel is transferred from the primary transport device to the secondary transport device, can be compensated for or avoided with the help of the displaceable pressure drum. The line force can thus be kept exactly at a desired value continuously.

The pressure drum 19 can, as shown in FIGS. 3 and 4, be designed as a deflection adjusting roller 140, the roller shell 141 of which is supported on a stationary yoke 143 by means of a series of support elements 142, whereby a arched outer contour of the pressure drum 19 achieved. Only one of the support elements 142 acting in the direction of the winding gap can be seen in the view according to FIGS. 3 and 4. The structure of the deflection adjustment roller 140 is known per se (DE-OS 25 55 677), so that this is not described in detail. The support elements 142 are preferably individually controllable, that is to say independently of one another, as a result of which a desired curvature of the roll shell 41 can be set. The yoke 143 is rotatable about a fixed axis, here the longitudinal axis 23. When the yoke 143 rotates, the support elements 142 cooperating with the yoke 143 are pivoted in such a way that their direction of action follows the traveling movement of the winding gap.

By setting a desired curvature of the outer contour of the pressure drum, the material web guided over it can be tensioned in a defined manner, as seen transversely to the running direction of the web, preferably before the material web runs into the winding nip. In this way, wrinkling of the winding layers wound on the winding roll can be prevented and the winding result can thus be improved. The deflection of the pressure drum can be seen in the longitudinal direction of the drum, as described above, preferably in sections. As a result, the desired width extension of the material web can be influenced, preferably adjusted, by varying the outer contour of the pressure drum. In an advantageous embodiment, the pressure drum 19 is part of an active vibration damping system, that is to say the pressure drum is capable of vibration. In connection with the present invention, the term “capable of vibrating” is understood to mean that the pressure drum is a can perform rapid displacement movement in the direction of the winding roll and in the opposite direction. The pressing device 25, that is to say the hydraulic piston and cylinder unit shown in FIGS. 1 to 4, can therefore very quickly carry out a change in direction of the displacement movement of the pressing drum 19.

Figure 5 shows a schematic diagram of the winding machine according to Figures 1 to 4 with an embodiment of a controller. Parts that correspond to those in Figures 1 to 4 are provided with the same reference numerals, so that reference is made to the description of Figures 1 to 4. To control 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 roller 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 therefore changes alone, that is to say only in accordance with the increase in the winding roll diameter. The magnitude of the line force in the winding gap formed between the pressure drum 19 and the winding roller 37 is determined solely, that is to say exclusively by a method of the guide carriage 21 holding the pressure drum 19, preferably by means of a control device 65. This includes a measuring device 67 for the line force, a controller 69, a setpoint generator 71 and a control unit 73. The measuring device 67 is connected to the controller 69 via a measuring line 75 or opens into the latter. The setpoint generator 71 is connected via a line 75 'to the controller 69 and indicates the desired setpoint to the latter. The controller 69 is in turn connected to the control unit 73 via a line 77.

In the event that the value of the line force measured by the measuring device 67 in the winding gap formed between the pressure drum 19 and the winding roller 37 deviates from the desired value specified by the desired value transmitter, the controller 69 sends a signal to the control unit 73 via line 77. The latter changes thereupon the pressure in the cylinder 27 of the pressing device 25 such that the measured value of the line force approaches the target value. As a result, the line force can also be kept at a constant value, for example, if a fault occurs in the winding process. A malfunction can, for example, be a not very precise movement of the secondary transport device 5, so that the position of the winding gap 37 formed by the pressure drum 19 and the winding roller 37 guided by the secondary transport device 5 shifts slightly.

In a preferred embodiment, it is provided that the pressure drum 19 can be displaced independently of the driving speed of the secondary transport device in order to control the line force. Furthermore, it is possible that the lifting device 43 cooperating with the secondary transport device, that is to say 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 pressure drum 19 and the winding roller 37 is essentially constant while the winding roller 37 rests on the guide rails 15. “Constant position” of the winding gap means its position within the winding machine 1, that is, the winding roller 37 is displaced by means of the secondary transport device 5 at a speed in the direction of the arrow 33, so that only the increase in diameter of the winding roller 37 is compensated for.

In another embodiment it is provided that the lifting device 43 assigned to the secondary transport device 5, 7 can be controlled in such a way that the position of the winding gap formed between the pressure drum 19 and the winding roller 37 shifts with increasing winding roller diameter during the winding process, for example in one area from 50 mm to 200 mm.

FIG. 6 shows a schematic illustration of a further exemplary embodiment of the winding machine 1. Parts which correspond to those in FIGS. 1 to 5 are provided with the same reference numerals, so that reference is made to the description of FIGS. 1 to 5. FIG. 6 shows part of an embodiment of the primary transport device 79. This comprises two primary pivot levers 81, of which only one is shown in this view. The primary pivoting levers 81, on which the new drum 49 is rotatably held, can be pivoted about an axis 83 running parallel to the longitudinal axis of the drum 49. The primary pivoting levers 81 are arranged in a stationary manner within the winding machine 1, that is to say the axis 83 has a fixed, unchangeable position on the machine frame 13, at least during a complete winding process. The primary pivoting levers 81 are associated with a lifting device 85, for example attached to the machine frame 13, which is assigned at least one to a primary pivoting lever. nete-preferably hydraulic piston and cylinder unit. The piston and cylinder unit comprises a piston 89 guided in a cylinder 87, which is fixedly connected to a piston rod 91 engaging at least one of the primary pivoting levers 81. When the piston rod 91 moves out of the cylinder 87, the primary pivoting levers 81 are pivoted counterclockwise and when they move in clockwise about the axis 83. Of course, the lifting device 85 can also comprise, for example, two piston and cylinder units, each of which is assigned to 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 by an angle w relative to an imaginary horizontal H, shown with a broken line, which here is approximately 26 °. The angle w is adjustable by means of the lifting device 85. To adjust the angle w, a control device 93 is provided, which comprises a controller 69 ', a setpoint generator 71 • and a measuring device 67' for detecting the position of the primary drive lever 81. The setpoint generator 71 * is connected to the controller 69 'via a signal line 95 and the measuring device 67' is connected to the controller 69 'via a signal line 97. In order to change the angle w and thus the position of the reel changing position, a new setpoint is input to the setpoint generator 71 '. A target / actual comparison is carried out with the aid of the controller 69 '. In the event of a deviation, the controller 69 'sends a signal to a hydraulic control valve 99 via a line 77', which then regulates the flow between a pump 101 and one of the Control valve 99 to the cylinder 87 leading medium line 103 releases. The medium conveyed by the pump, for example a hydraulic fluid or a gas, can optionally be introduced into one of the partial spaces of the cylinder 87 which are separated from the piston 89. When the medium is introduced into the upper partial space in the illustration according to FIG. 6, as indicated by an arrow, the piston rod 91 moves into the cylinder 87, as a result of which the angle w is reduced. When the medium flows into the lower part of the cylinder 87, the piston rod 91 moves out of the cylinder, as a result of which the angle w is increased. After the desired angle w has been set, the control valve 99 interrupts the connection between the pump 101 and the line 103. In order to prevent the medium from flowing back out of the cylinder 87 in the direction of the control valve 99, a check valve 105 is provided.

With the help of the control device 93, a defined angle w can be set at any time during the winding process. It is also particularly advantageous that the position of the reel change position can be predetermined before the next reel change, for example if necessary an angle w can also be set which is 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 in the reel changing position and forms a winding gap with the pressure drum 19. In Figure 3, the direction of view of the drum 49 is marked with an arrow 107. The force with which in this embodiment Pressure drum 19 is pressed against the circumference of the reel 49, leads to a deflection of the reel 49 shown by a double arrow 109. The curvature of the outer contour of the reel 49 caused by the deflection is shown schematically by a line 111. The component in the contact plane P of the deflection resulting from the dead weight of the reel 49 is shown with a double arrow 113. The curved outer contour of the unsupported drum is shown schematically by a line 115.

As can be seen from FIG. 7, the deflections act in opposite directions, the amount of which is at least essentially the same. The deflections thereby cancel each other out completely, but at least essentially so that a uniform line force can be set in the winding gap over the entire width of the material web.

Figures 8a to 8e each show a highly schematic representation of part of the Wiekelmasehine 1 described with reference to the preceding figures in different winding phases. The drum changing process already briefly described above is explained in more detail below with reference to 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 here comprises primary pivoting lever 81 (FIG. 8a). For this purpose, the primary pivoting levers 81 are moved counterclockwise upward into the empty drum transfer position shown in FIG. 8a. pivots. The empty reel 49 is accelerated to synchronous speed by means of the primary drive, that is, the peripheral speed of the empty reel 49 corresponds to the running speed of the material web 3. The pressure element, here the pressure roller 51, is pressed against the circumference of the almost full winding roller 37. The winding roller 37 held by the secondary transport device (not shown) and driven by the secondary drive is removed from the pressure drum 19 together with the pressure roller 51 in the direction of arrow 33. The pressure drum 19 continues to follow the winding roller 37 in order to maintain a desired line force in the rocking gap until the pressure drum 19 moves against a stop 117, thereby stopping its displacement movement. The winding roller 37 continues in the direction of arrow 33, whereby a free web tension is formed between the pressure drum and the winding roller.

Because the pressure drum first moves against a stop 117 before a reel change, the pressure drum has a fixed, defined position before each reel change. When the distance between the pressure drum and the full winding roll 37 has reached at least a minimum value, the new drum 49 is shifted into the drum change position, in which the drum rests on the circumference of the pressure drum (FIG. 8c). The formation of the winding gap / nip takes place automatically, since the pressure drum which is in contact with the stop 117 is at this time arranged in the path of movement of the empty reel 49. The nip is considered to be closed when the pressure drum of the empty drum 49 as far from the stop 117 in the opposite direction of the arrow 33 was pushed back so that the pressure drum exerts, for example by means of the control device 65 (FIG. 5), the desired pressure force against the empty drum 49.

8a to 8c, the distance x of the longitudinal axis 23 of the pressure drum 19 to the stationary axis 83 of the primary pivoting lever 81, which lies on an imaginary vertical V, immediately before the reel change (FIG. 8a), during the reel change ( Figure 8b) and shown after the drum change (Figure 8c). In the winding phase according to FIG. 8b, in which the pressure drum 19 has already moved against the stop 117, there is the distance x2 which is greater than the distance x3 which, after the pressure drum has been pushed back, by the drum shifted into the reel changing position 49 sets. Furthermore, it can be seen that before the pressure roller moves against the stop 117, it has a distance xl from the axis 83 which is smaller than the distance x2.

After the winding nip has been formed, the material web is separated in the area of the free draw using one of the known methods and the new start of the web is performed on the reel 49. It is particularly advantageous that the empty reel 49 arranged in the reel change position is already wrapped over a small circumferential area by the material web before the separation, which considerably simplifies the changeover process, so that a high level of security when changing the reel can be ensured. After the reel change, the reel 49 is preferably held in the reel change position until the formation of the winding core of the new camouflage bour 49 wound winding roll 119 is completed, for example until the winding roll 119 has a layer thickness S of 20 mm to 100 mm.

During the core winding, that is, when the drum 49 is rotatably held on the primary pivoting levers 81, the pressure drum 19 moves away from the longitudinal axis of the drum 49 in accordance with the diameter increase of the winding roll 119. In terms of amount, the displacement of the pressure drum corresponds exactly to the horizontal component of the Radius increase. During the winding of the new winding roll 119, the full winding roll 37 is braked and brought out of the variable winding station, that is to say the secondary transport device. In a preferred exemplary embodiment, in which only one secondary transport device is provided, the secondary transport device is displaced to the left in the direction of the pressure drum in order to take over the drum 49 deposited on the guide rails 15. In the exemplary embodiment of the winding machine, in which two secondary transport devices are provided, these are used alternately, that is to say alternately, for guiding a new winding roll. The two secondary transport devices therefore only carry every second new winding roll. While the reel with the new winding reel wound on it is guided by the secondary transport device, the radius increase of the winding reel is compensated for by a corresponding displacement of the reel with the help of the secondary transport device. In terms of amount, the displacement of the drum in the horizontal direction corresponds exactly to the radius increase. In another embodiment variant of the method which can be carried out with the winding machine described with reference to FIGS. 8a to 8e, it is provided that the winding roller 37 guided by the secondary transport device is continuously moved from the position shown in FIG. 8a to the position shown in FIG. 8d without an intermediate stop. At the same time, the primary pivoting lever 81 and the new drum 49 move from the position shown in FIG. 8b to the position shown in FIG. 8e, preferably likewise without a stop. The drum change takes place when the new drum 49, which is displaced by means of the primary pivoting lever, passes through the position shown in FIG. 8c. The speed of the movements of the winding roller 37 guided by the secondary transport device and of the reel 49 which can be displaced with the aid of the primary pivoting levers can be constant or change at preferably at least any point. The movement sequence of the primary swivel levers 81 holding the new drum 49 can be controlled simply by changing the setpoint for the angle w supplied by the setpoint generator 71 '(FIG. 6) as a function of time.

FIGS. 9 to 11 each show a side view of part of a further exemplary embodiment of the winding machine 1 in different winding phases. The structure of the winding machine 1 essentially corresponds to that of the winding machine described with reference to FIGS. 1 to 8. The differences are discussed in more detail below. The same parts are provided with the same reference numerals, so that reference is made to the description of the preceding figures. The function of the winding machine 1 is first to be explained in more detail below with the aid of a winding process: the material web 3 is guided over the pressure drum 19 and wound onto the winding roller 37 guided by the secondary transport device 5 and driven by the secondary drive 39 (FIG. 9 ). Before the winding roller 37 reaches its final / desired diameter, the empty drum 49 is rotatably attached to the primary pivoting levers 81 above the pressure drum 19, that is to say the movement of the empty drum 49 is restricted to rotation about its longitudinal axis and into that Reel position changed.

It can be seen from FIG. 9 that the reel 49, which is in the reel changing position, is spaced apart from the pressure drum 19 in such a way that no winding nip is formed yet. In the reel change position, the center of the empty reel 49 lies on an imaginary second straight line G2, shown in broken lines, which runs essentially parallel to an imaginary first straight line Gl and is arranged at a higher level with respect to this. As can be seen from FIG. 9, the center of the pressure drum 19 lies on the straight line Eq. Parallel to the guide rails 15. When changing the reel, the empty reel 49 is accelerated by the primary drive 121 assigned to the primary pivoting levers 81 and brought to the running speed of the material web 3 before the transfer of the material web 3. In order to transfer the continuous material web 3 to the empty reel 49, the travel speed of the secondary transport device 5 guiding the winding roll 37 is adjusted by a corresponding Control of the threaded spindle 47 driving motor 45 increased. The pressure drum 19 remains in constant contact with the winding roller 37, that is, the pressure drum is tracked when the winding roller 37 is displaced along the linear, second guideway 14, so that the line force in the winding gap is kept at a desired value.

As can be seen from FIG. 9, the distance between the straight lines G1 and G2 is smaller than the sum of the radii of the pressure drum 19 and the spool 49. As a result, the pressure drum 19 moves to the right against the spool 49 arranged in the spool change position when it is shifted in FIG. This corresponds to the winding phase shown in FIG. 10. The change of drum is triggered at the moment in which a winding gap is formed between the pressure drum 19 and the empty drum 49, or at least shortly thereafter. When changing the reel, the material web 3 is separated by means of a separating device, not shown in FIGS. 9 to 11, and the new beginning of the web is wound onto the reel 49. At the moment of changing the reel, that is to say before the material web 3 is separated and transferred onto the empty reel, a space is already formed between the winding roller 37 and the pressure drum 19.

It should be noted that the pressure drum does not assume a fixed position before changing the drum, i.e. does not - as in the exemplary embodiment described with reference to FIGS. 1 to 8 - drive against a stop, but directly against that of the primary pivoting levers 81 in a fixed position ( Drum change position) held empty drum 49. As shown in FIG. 10, the piston 27 of the pressing device 25 at this moment is at a distance from the inner wall of the cylinder 29; the piston 27 is therefore not in an end / stop position.

After the new start of the web has been wound onto the reel 49, it is moved into the finished winding position by pivoting the primary pivoting lever 81 about the axis 83 in a clockwise direction along the first, here part-circular guideway 122. During the pivoting process, the drum 49 is rotatably held and supported by the primary pivoting levers 81. The drum 49 is constantly driven by the primary drive 121, that is, it is also displaced along the first guide track 122.

FIG. 11 shows the new reel 49 in its finished winding position, that is to say that it rests with its bearing journals on the guide rails 15, which support the weight of the reel 49 and the winding roller (not shown) which has only a few winding layers and is wound thereon. During the transfer of the reel 49 from the reel change position (FIGS. 9 and 10) to the finished winding position (FIG. 11), the pressure drum 19 is displaced along the straight line Gl by means of the pressure device 25, so that the line force in the winding gap is at a desired value during the entire transfer is held.

In FIG. 11, the winding roller 37 is arranged in a deployment position in which the winding roller is lifted from the guide rails 15 and out of the weighing machine 1 by means of known devices can be applied. 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, these have already been shifted from the primary transport device 79 to the left in the direction of the pressure drum 19 in order to take over the drum 49. The secondary transport device 5 and the secondary drive 39 can be moved together or independently of one another into the takeover position. While the secondary transport device 5 takes 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. The primary drive 121 is then uncoupled from the reel 49 and moved counterclockwise along the first guideway back to the reel changing position. The increase in diameter of the winding roll (not shown) wound on the spool 49 guided by the secondary transport device 5 is now compensated for during the final winding by a displacement of the secondary transport device 5 and thus of the spool 49 in the direction of arrow 33 to the right. The line force in the winding gap between the winding roll wound on the reel 49 and the pressure drum 19 is controlled by a displacement of the pressure drum 19, as described above.

For the sake of clarity, only a control of the winding machine 1 is shown in Figure 10, which includes a control device 65. To explain the structure and operation of the Control device 65 is referred to the description of Figure 5.

In a preferred exemplary embodiment, it is provided that the pressure drum 19 can be displaced to control the line force independently of the driving speed of the secondary transport device 5. Furthermore, it is possible that the lifting device 43 assigned to the secondary transport device 5, that is to say 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 pressure drum 19 and the winding roller 37 is essentially constant. “Constant position” of the winding gap means its position within the winding machine 1. The winding roller 37 is thus displaced in the direction of the arrow 33 by means of the secondary transport device 5 at a speed which only compensates for the diameter increase of the winding roller 37.

Another exemplary embodiment provides that the lifting device 43 assigned to the secondary transport device 5 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 increasing winding roll diameter during the winding process, for example in a range of 50 mm up to 200 mm.

In a preferred exemplary embodiment, the winding gap is always in the same place when an empty reel is wound, that is to say its position within the winding machine is constant, or at least essentially constant, during a reel change. As a result, there are nes empty reel always the same angular relationships, for example the pressing forces acting on the reel, so that the deflection of the empty reel can be calculated and compensated accordingly to set a desired line force curve in the winding gap. Of course, it is also possible in this exemplary embodiment with a control device 93, for example described with reference to FIG. 6, to shift _{/ change} the reel position in which the winding gap is formed.

FIG. 12 schematically shows a side view of another exemplary embodiment of the winding machine 1. Parts which correspond to those described with reference to FIGS. 1 to 11 are provided with the same reference numerals, so that reference is made to the description of FIGS. 1 to 11. In this exemplary embodiment, the primary transport device 79 comprises a holding device 127 which can be moved on third rails 123 in the direction of a double arrow 125 and in which the empty drum 49 is held in a stationary and rotatable manner. The holding device 127 therefore allows a rotary movement of the drum 49 and prevents it from translatory movement. By moving the holding device 127, the reel 49 can be shifted from the reel changing position (not shown) along the straight first guideway 14 ′ realized by the rails 123 to the finished winding position in which the reel 49 rests on the guiding rails 15. The drum 49 is shifted or lowered from a higher level (G2) to a lower level (Gl). The third rails 123 are opposite an imaginary, dashed line placed horizontals H inclined 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 of the reel 49 from the reel change position down to the finished winding position is similar to the travel of a reel pivoted by means of a primary pivoting lever about an axis 83 which is fixed with respect to the machine frame (FIG. 9).

FIG. 12 also shows a second embodiment variant of a control / regulation for setting the line force in the winding gap between the pressure drum and a drum or a winding roll, which differs from the control / regulation described with reference to FIG. 10 in that the driving speed of the Secondary transport device 5 is set or changed depending on the position of the piston 29 in the cylinder 27 of the pressing device 25. The controller 73 can control the pressure in the cylinder 27 and thus the line force in the rocking gap as a function of several parameters. The parameters are the longitudinal tension of the material web 3 (web tension) measured with a measuring device 129, the diameter D of the winding roll 37 and an angle α 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 α are taken from a calculated and / or determined control curve shown in FIG. 12 as an example.

The angle α is measured between a plane 131 intersecting the longitudinal axes of the pressure drum 19 and the empty reel 49 and the straight line Gl. The position of the piston 29 in the cylinder 27, which controls the motor 45 of the lifting device 43 driving the threaded spindle 47, is transmitted to the control unit 61 via a signal line 133.

FIG. 13 shows a further exemplary embodiment of the winding machine 1 according to the invention with a control described with reference to FIGS. 5 and 10. The same parts are provided with the same reference numerals, so that reference is made to the description of the preceding figures. The rails 22, on which the guide drum 21 holding the pressure drum 19 rotatably can be displaced, are inclined by an angle β in this exemplary embodiment with respect to an imaginary horizontal, which here lies between 0 ° and 45 °. The pressure drum 19 is raised during a shift by means of the pressure device 25 in the direction of an arrow 135 from a lower level to a higher level, that is to say shifted obliquely upwards. As can be seen from FIG. 13, the pressure drum 19 is only in contact with the winding roller 37, but not with the empty reel 49 arranged in the reel changing position.

In the exemplary embodiment shown in FIG. 13, the weight of the pressure drum 19 is still largely 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 proportion of the weight of the pressure drum influences the measuring and / or the setting accuracy of the line force, namely only the slope drive component. In a further embodiment, not shown in the figures, it is provided that the linear guide formed by the rails 22 and the guide slides 21 can be pivoted for the pressure drum 19, for example with the aid of at least one pivot lever.

FIGS. 14a to 14e each show a highly schematic representation of part of the winding machine 1 described in the preceding FIGS. 1 to 11 and 13 in different winding phases. In the following, only the differences in the mode of operation are discussed in more detail. In the exemplary embodiment shown in FIGS. 14a to 14e, the new drum 49 is placed on the guide rails 15 (not shown) before a drum change. In preparation for a reel change, the pressure drum 19 is moved against a stop 117 ^' , which is positioned such that when the new reel 49 is introduced into the reel change position, the pressure drum 19 is pushed back by the stop 117' while the reel 49 is being guided by the guide rails 15 is approaching. The new reel 49 is thus only wound up after the reel has been placed on the rails, as a result of which fluctuations and / or jumps in the line force curve, such as can occur when the reel is placed on the guide rails during the winding-on process, are reliably avoided. Furthermore, the mechanical engineering outlay in the winding machine described with reference to FIGS. 14a to 14e can be simplified compared to the other exemplary embodiments, since, for example, a stable transverse shaft for connecting the primary pivoting levers can be dispensed with. In the exemplary embodiment of the winding machine described with reference to FIGS. 14a to 14e, the winding roller 37 can also be continuously displaced along the second guide track, that is to say without an intermediate stop. 14a to 14d to the right, the new reel 49 is simultaneously lowered from the position shown in FIG. 14b to the position shown in FIG. 14c, preferably continuously. The speed of the movements of the winding roller 37 and the new reel 49 in the winding phases shown in FIGS. 14a to 14e can be constant or change at least anywhere.

The method mentioned above is readily apparent from the description of FIGS. 1 to 14. It consists in that the material web is guided over a pressure drum which can be displaced horizontally, but at least essentially horizontally, which forms a winding gap with the winding roller which is rotatably held in a secondary transport device. During this winding phase, the line force in the rocking gap is controlled / regulated by moving the pressure drum. When a desired winding roll diameter is reached, the winding roll is removed from the pressure drum with the aid of the secondary transport device in preparation for a reel change, so that the material web runs freely from the pressure drum to the winding roll. A new reel rotating at the web speed is brought into a reel changing position by means of a primary transport device, which forms a new winding nip with the pressure drum. Then the material web is cut across its width and the new web start onto the new reel wound. During this winding phase, too, the control / regulation of the line force in the winding gap between the pressure drum and the new reel is again realized by moving the pressure drum. Finally, the secondary transport device takes over the new reel with the new winding roll. The control / regulation of the line force in the winding gap is also realized in this winding phase, that is, when the new reel is guided by the secondary transport device, only by moving the pressure drum. A desired winding result can be achieved by adjusting the line force during the entire winding process by displacing the pressure drum. With the method described above, a high level of security can be ensured when changing the reel, since the new reel that has entered the free reel into the reel change position is already wrapped in areas by the material web before the reel change takes place.

It is clear from everything that in the above-described exemplary embodiments of the Wiekelmasehine, in which the primary drive can only be displaced along the first guideway, the structure thereof can be simplified in that the primary drive is fixed in place on a part of the primary transport device which is mounted together with the drum can be moved along the first guideway. In a further embodiment variant of the winding machine it is provided that the primary drive can be displaced both along the first guideway and partly along the second guideway. Furthermore, it is of course also possible that the secondary drive on the secondary transport device can be arranged stationary, which further simplifies the construction of the winding machine.

In a particularly preferred exemplary embodiment (not shown in the figures), the stroke of the pressure drum, that is to say the maximum distance that the pressure drum can be moved in one direction, is greater than or equal to the material layer thickness S of a finished winding roll. This eliminates the need for a secondary transport device, which shifts the reel during the finish winding process in accordance with the diameter increase of the winding roll. In this exemplary embodiment, the winding roll is thus wound in two fixed winding stations. A "fixed" winding station "is characterized in that the reel is rotatably held in such a way that both the increase in diameter of the winding roll wound thereon and the adjustment of the line force in the winding gap are achieved exclusively by a displacement of the pressure drum. A fixed winding station points has the advantage that it offers an optimal rigidity of the reel tensioning, so that a transmission of possibly occurring vibrations to the winding roll can be practically ruled out. The fact that the displacement path of the pressure drum is so large that the diameter increase can be completely compensated for is one Constant reel tracking is not required, which can simplify the construction of the winding machine.

All embodiments of the winding machine have in common that in preparation for a reel change there is an intermediate space / a gap between the almost finished winding roll and the pressure drum is formed. This can ensure that the material web is guided over a circumferential area of the empty drum arranged in the drum changing position before the drum change. This ensures a high level of functional reliability.

It is also advantageous that the stationary, rotatable holding of the new drum at the start of the winding process in the primary transport device means that an adjusting device, as is often used in known winding machines, can be dispensed with. This adjusting device serves to shift the drum guided by the primary transport device radially in the direction of the pressure drum in order to adjust the line force in the winding gap. Because of this advantageous embodiment, an additional control for the actuating device can be dispensed with, so that the costs of the winding machine are reduced.

It is common to all of the exemplary embodiments of the Wiekel machine that the control / regulation of the line force in the winding nip can, according to the invention, be carried out exclusively by a single device during the entire winding process, namely by relocating the pressure drum with the aid of the pressure device 25.

It is also particularly advantageous that existing, that is, already assembled winding machines can be converted so that one of the methods described above for winding the material web 3 can be implemented. As an alternative to the reel, the winding machine can be equipped with a winding core on which one winding tube or several winding tubes are attached. In the latter case, the winder can be preceded by a slitter. This cuts the web into several sub-webs, with each sub-web being wound onto a winding tube.

Claims

Expectations

1. A method for the continuous winding of a material web, in particular paper or cardboard web, with the formation of a winding roll on a reel, with the following steps:

- The material web is guided over a displaceable pressure drum, which forms a winding nip with the winding roll rotatably held in a secondary transport device, the line force in the rocking nip being controlled / regulated by a displacement of the pressure drum;

- When a desired winding roll diameter is reached, the winding roll is removed from the pressure drum by means of the secondary transport device in preparation for a reel change, so that the material web runs freely from the pressure drum to the winding roll;

- A new spool rotating at web speed is brought into a spool change position by means of a primary transport device, in which it forms a new winding nip with the pressure drum; - The material web is cut across its width and wound with its new web start on the new reel, the control / regulation of the line force in the winding gap between the pressure drum and the new reel is in turn realized by a displacement of the pressure drum;

- The secondary transport device takes over the new reel with the new winding reel, the line force still being controlled by moving the pressure drum.

2. The method according to claim 1, characterized in that after the takeover of a drum by the secondary transport device, a compensation of the increase in diameter of the winding roll is carried out by a preferably at least approximately horizontal displacement of the secondary transport device.

3. The method according to claim 1 or 2, characterized in that the Wiekelspalt between the new drum and the pressure drum is formed by a relative movement of the pressure drum relative to the empty drum.

4. The method according to claim 1 or 2, characterized in that the winding gap is formed by a relative movement of the empty drum relative to the pressure drum.

5. The method according to claim 4, characterized in that when removing the winding roll from the pressure drum the same of the winding roll until Errei- Chen follows a stop, and that the new reel is then brought into the reel change position, pushing the pressure drum back from the stop.

6. The method according to any one of the preceding claims, characterized in that the winding gap is formed above the position in which the secondary transport device takes over the new drum.

7. The method according to claim 6, characterized in that the winding gap is formed in a pressing plane determined by the longitudinal axes of the empty drum and the pressure drum, which is inclined relative to an imaginary horizontal by an angle α, which is in a range of 5 ° <α <40 °, preferably from 10 ° <α <35 °, in particular from 15 ° <α <30 °.

8. The method according to any one of claims 1 to 5, characterized in that the reel change position is where the secondary transport device takes over the new reel.

9. The method according to any one of the preceding claims, characterized in that while the material web is guided in a free train from the pressure drum to the winding roller, a pressure element, preferably pressure roller, non-rotating pressure brush or the like, is pressed onto the circumference of the winding roller.

10. The method according to any one of the preceding claims, characterized in that the material web is already guided over a peripheral region of the new reel, while this is arranged in the reel changing position.

11. The method according to any one of the preceding claims, characterized in that the winding roller guided by the secondary transport device is continuously displaced to compensate for the increase in diameter.

12. The method according to any one of the preceding claims, characterized in that the displacement speed of the new spool guided by the primary transport device and that of the winding roll guided by the secondary transport device is constant or preferably changes at least at any point.

13. winding machine for the continuous winding of a material web, in particular paper or cardboard web, on a reel to a winding reel, with a displaceable pressure drum, which forms a rocking nip with the winding reel, with at least one primary transport device, by means of which the reel spool along a first guideway is displaceable, and with at least one secondary transport device which guides the reel along a second guideway, characterized in that to prepare a reel change, the new reel (35; 49) is moved into a reel position by means of the primary transport device (79). can be created in which a new rocking gap is formed between the new reel (35; 49) and the pressure drum (19), and that in the reel change position the material web (3) is guided over a circumferential area of the new reel (35; 49) is.

14. Winding machine according to claim 13, characterized in that the reel change position is provided above the position in which the secondary transport device (5; 7) takes over the new reel (35; 49).

15. Wiekelmasehine according to claim 13 or 14, characterized in that the new winding gap in a by the longitudinal axes of the empty reel (35; 49) and the pressure drum (19) determined contact plane (P), which is opposite an imaginary horizontal (H) is inclined by an angle ex which lies in a range of 5 ° <α <40 °, preferably 10 <<35 °, in particular 15 ° <<30 °.

16. Winding machine according to claim 13, characterized in that the reel change position is where the secondary transport device (5; 7) takes over the new reel.

17. Winding machine according to one of claims 13 to 16, characterized in that the pressure drum (19) by means of a pressure device (25) is displaceable, and that by increasing the pressure drum (19) the diameter increase can be compensated and the line force in the winding gap control bar / can be regulated while the winding roll is guided by the primary transport device (79).

18. Winding machine according to one of claims 13 to

17, characterized in that the diameter increase can be compensated for by a displacement of the secondary transport device (5; 7) and the line force in the rocking gap can be adjusted, preferably regulated, by a displacement of the pressure drum (19), while the winding roll is moved by the secondary transport device ( 5; 7) is performed.

19. Winding machine according to one of claims 13 to

18, characterized in that the winding gap is formed by a relative movement of the new drum (35; 49) relative to the pressure drum (19) and / or by the relative movement of the pressure drum (19) relative to the new drum (35; 49).

20. Winding machine according to one of claims 13 to

19, characterized in that the pressure drum (19) is rotatably held on a guide block (21), and that the guide block (21) is movable on first rails (22) which are arranged parallel to an imaginary horizontal line (H) or with respect to this are inclined at an angle β (FIG. 13).

21. Winding machine according to one of claims 13 to 19, characterized in that the pressure drum (19) is rotatably held on pivoting levers which are pivotable about an axis running parallel to the longitudinal axis of the drum.

22. Wiekelmasehine according to one of claims 13 to

21, characterized in that a drive, preferably a center drive (17), is associated with the pressure drum (19).

23. Winding machine according to one of claims 13 to

22, characterized in that the secondary transport device (5; 7) comprises a secondary chute (11) which can be moved on second rails (9), the rails (9) being arranged parallel to an imaginary horizontal (H) or against the horizontal (H ) are inclined.

24. Winding machine according to one of claims 13 to 22, characterized in that the secondary transport device (5; 7) comprises secondary pivot levers on which the drum is rotatably held and which are pivotable about an axis running parallel to the longitudinal axis of the drum.

25. winding machine according to one of claims 13 to

24, characterized in that the secondary transport device (5; 7) is assigned at least one secondary drive, preferably a center drive, for applying a driving and / or braking torque to the reel.

26. Winding machine according to one of claims 13 to

25, characterized in that the secondary transport device (5; 7) is assigned a lifting device (43), and that the lifting device (43) - preferably independently of that in the winding gap between the pressure drum (19) and the winding roll acting line force can be controlled / regulated depending on the increasing winding roll diameter.

27. Wiekelmasehine according to one of claims 13 to

26, characterized in that the pressure device (25) assigned to the pressure drum (19) for controlling / regulating the line force can be actuated independently of the lifting device (43) assigned to the secondary transport device (5; 7).

28. Winding machine according to one of claims 13 to

27, characterized in that the pressing device (25) can be controlled by means of a regulating device (65) in such a way that the line force in the winding gap between the pressing drum (19) and the winding roll corresponds - at least essentially - to a desired value.

29. Winding machine according to one of claims 13 to

28, characterized in that the position of the winding gap formed between the pressure drum (19) and the winding roller guided by the secondary transport device (5; 7) is constant.

30. Winding machine according to one of claims 13 to 28, characterized in that the position of the winding gap formed between the pressure drum (19) and the winding roll guided by the secondary transport device (5; 7) increases with increasing winding roll diameter during the winding process, preferably around 50 mm to 200 mm, moves.

31. Winding machine according to one of claims 13 to 30, characterized in that the pressing device (25) is designed as a — preferably hydraulic — piston and cylinder unit.

32. winding machine according to claim 31, characterized in that the maximum stroke of the piston (29) is less than half the material layer thickness of a finished winding roll.

33. winding machine according to one of claims 13 to 32, characterized in that the pressure drum (19) is designed in the manner of a deflection adjusting roller, the roller shell of which is supported on a stationary yoke by means of a series of supporting elements.

34. Wiekelmasehine according to claim 33, characterized in that the support elements are individually controllable.

35. winding machine according to claim 33 or 34, characterized in that the support elements act in the direction of the winding gap.

36. winding machine according to one of the preceding claims, characterized in that the yoke is pivotable such that the direction of action of the support elements follows the traveling movement of the winding gap (from Figure 3 to Figure 4).

37. winding machine according to one of claims 13 to 36, characterized in that the primary transport device (79) primary pivot lever (81) around- holds on which the drum (35; 49) is rotatably held and which can be pivoted about an axis (83) running parallel to the longitudinal axis of the drum.

38. winding machine according to claim 37, characterized in that the axis (83) of the primary pivot lever (81) within the Wiekelmasehine (21) is arranged stationary.

39. Wiekelmasehine according to one of claims 13 to 38, characterized in that the primary transport device (79) comprises a movable on third rails holding device.

40. winding machine according to claim 39, characterized in that the third rails are arranged vertically or are inclined at an angle z relative to an imaginary vertical.

41. Winding machine according to one of claims 13 to 40, characterized by at least one pressure element which can be pressed onto the circumference of the winding roller (pressure roller (51)).

42. winding machine according to one of the preceding claims 13 to 41, characterized in that the angle α (Figure 3), preferably before a reel change, is adjustable.