FI121228B - Procedure for rolling a paper or cardboard web and a wheelchair - Google Patents

Description

A method of winding a paper or cardboard web and a reel

The invention relates to a method for winding a paper or board web according to the preamble of claim 1.

The invention also relates to a method for winding a paper or board web into a machine roll, i.e. a roll corresponding to the full width of the web. Machine rolls are generally 2.0 to 10.0 m wide and 2.0 to 4.5 m in diameter, depending of course on the size of the paper or board machine.

As is known in the art, machine reels of a paper or board web are generally located at the end of a paper or board web production line and are used to wind the finished paper web into a machine reel around a reel spindle. This is often followed by on-line or off-line finishing equipment, through which the 20 customer rolls required by the customer are produced from the paper or board web. For winding by machine winders, a winding cylinder arranged in a nip contact with the winding shaft and the web roll formed around it is usually used. The nip load, i.e. the force acting on the nip, at the same time affects the quality of the resulting web roll. As is known in the art, the nip load of the roll nip seems to affect the quality of the web roll 25 and, consequently, measuring devices for measuring nip load and adjusting devices for adjusting nip load are provided in the rollers. One problem with prior art reel reels of paper or board machine machines known in the art is that measuring the reel nip load and, on the other hand, nip load adjustment and profiling is problematic. As is known from prior art 30, it is problematic to measure the nip load of a reel having two nip loads acting simultaneously on the reeling cylinder.

2

In some prior art solutions, the winding cylinder is stationary and the winding roll around which the web roll is formed by a nip contact is adapted to be moved as the winding progresses in the support structure, for example, winding ladder sizes. Prior art winders generally have a primary winding station and a secondary winding station, in which at the primary station the web winds around a new winding axis and the web is rolled to the desired diameter, after which the winding is transferred to a secondary station to continue winding to and from the finished roll.

In connection with prior art reel fasteners, a reel nipple of emes in the upstream direction of the web is often followed by a roller for spreading the web, as well as a guide roll which guides the web to a nip between the reel cylinder and the forming web roll.

In the prior art, reference may be made to Fl patent application 20002375 which discloses a method of winding and reeling, in which a machine web is rolled in a sequential manner from a paper web to a fully winding nip in contact with a second winding nip forming device.

20

Reference may also be made, in the prior art, to U.S. Patent No. 5,931,406, which discloses a reel for continuous paper web winding, wherein the reel drum is lowered back to the reel rails with a new reel reel before being rewound with a new reel roll. The roller cylinder is moved vertically and horizontally by means of a lifting table and a transfer means connected thereto. The scrolling cylinder moves vertically to provide a nip at a time with the paper web in turn and moves away from the path of the horizontal movement of the roller towards the scrolling position.

U.S. Patent No. 5,370,327, in turn, discloses a method and web for winding a web roll, in which the winding cylinder moves substantially vertically as the winding progresses, the winding cylinder remaining in contact with the forming web roll until the desired diameter is reached. In this 5 prior art reel winder, the same reel carriage is rolled from start to finish, i.e. the reel comprises only a primary carriage.

Reference may also be made, in the prior art, to DE-A-102 18 722, which discloses a reel which introduces a reel web into a reel via a tracked cellar underneath a machine room 10, using a fixed reel cylinder and adapted to be moved by a reel arm by means of which the spool axis is moved over the spool cylinder.

Reference may also be made, in the prior art, to U.S. Patent No. 6,536,705 15, which discloses a method and apparatus for winding a material web which simultaneously rolls the web and / or rollers in the transverse direction, i.e. is traversed relative to the direction of the incoming material web.

It is an object of the invention to provide a method of winding a paper or board web in which the problems and drawbacks described above and subsequently encountered are eliminated or at least minimized.

It is also an object of the invention to provide new solutions in connection with fastening reels 25 to enhance the winding speed and simplify the construction of the fastener.

In order to achieve the above and later objects, the method according to the invention is essentially characterized by what is stated in the characterizing part of claim 1.

4

The reel winder according to the invention, in turn, is essentially characterized by what is stated in the characterizing part of claim 13.

The winding is started at the primary position of the reel on the primary carriages, from which the winding 5 progresses to the secondary position on the secondary carriages, thereby optimizing e.g. necessary transmission of electrical drives, and at the same time provide a direct movement of the primary and secondary stages of the web to be wound. There is no limit to the maximum diameter of the web roll in the primary position.

The invention utilizes a large winding cylinder having a diameter which provides a longer winding nip in the machine direction, whereby the winder is also more easily adapted to different track widths. According to the invention, the ratio of the diameter of the roller cylinder to the width of the web to be rolled is preferably such that the operating range is chosen from the formula y ~~ 0.0009x3 + 0.025x2 ~ 0.2567x + 1.0902, wherein y-roller cylinder diameter / roll width -width of the roll web, the area above the curve given by the roll. In this way, a completely new operating area has been introduced for winding, which allows the use of different standard structural solutions regardless of the size of the machine, thus minimizing the number of components used, while minimizing different geometrical differences between different rollers. The present invention has, in a completely new way, determined the principles of sizing of a winding drum, completely different from the prior art procedure whereby the diameter sizing of a winding drum is structural alternatives, which is reflected in the high cost of manufacturing and maintenance of mechanics and automation models. Thus, in accordance with the invention, a longer winding nip and a larger winding nip surface area are also provided, whereby adjusting the nip load and thereby influencing the construction of the nip load through the nip load is easier. In addition, the large diameter of the winding cylinder causes the problems caused by the deflection of the winding cylinder to be reduced.

5

Thus, the method and the coil winder of the invention also achieve a long winding nip, which is advantageous in terms of winding quality. This also allows extra space for the changeovers, especially when the roll nip is closed. Likewise, the actuator has more space for different actuators.

5

Also, for the retractor, it is not necessary to make a recess in the floor of the machine room for movement, since the movement steps of the reeling cylinder can be located above the machine plane. In prior art solutions, when the floor of the data center had to be recessed for movement of the roller cylinder, it was also necessary to cut the floor pegs, which has resulted in time-consuming and costly rebuilding of the concrete structures during remodeling.

The reeling cylinder and the resulting web reel can also be oscillated during the reeling, most preferably from the beginning of the reeling to the completion of the finished reel. Oskil-15 can be used to influence track tension so that the track tension remains at the desired value. If the tension profile of the web is skewed, it is oscillated with respect to the cross-direction of the web, whereby the tension profile can be corrected. The amount of oscillation can be adjusted through the measuring arrangement by measuring the position of the web at the edge of the roll or the nip through a pressure sensitive measuring film and by controlling the position and amount of oscillation of the reeling cylinder and machine roll.

The nipple load can be measured using a pressure sensitive membrane called the EmFi membrane, which allows the nipple load to be easily and accurately measured. Such a membrane measurement application for nip load measurement enables e.g. that if two nip forces are applied simultaneously during the winding, the nip force can be measured and adjusted from the side of the winding cylinder and the determination of the forces of each nip is extremely accurate.

30 The measuring diaphragm and fast measuring electronics can be mounted on the rotating drum, the reeling drum, for high sampling frequency and programmability of 6 functions. Multiple forces are measured by rapid sampling and synchronization at a desired point of the roller cylinder rotation to determine the position of the effective force / profile on the periphery of the roller cylinder. The flour diaphragm may be positioned directly, i.e. parallel to the longitudinal axis of the winding cylinder, or spirally or circumferentially, either completely or partially extending along the circumferential path.

In this case, there is no need for a separate tension measuring roller for the roller, since the track width can be measured directly from the roller cylinder via a measuring film. When using an application where the diaphragm is set in a spiral shape, the measurement result between the nipples is also obtained when the roll is changed.

The invention is applicable when a fixed secondary station is used as a secondary roll station as well as when a mobile secondary station is used.

15

If the secondary position of the reel stationary is fixed, the primary reeling takes place on the reel trolleys which move horizontally, preferably placed on rails. The fixed secondary station allows the diameter of larger machine rolls to be eliminated, since it does not need to take into account the requirements of the massive machine roller movement and the maneuverability of the drive when dimensioning the drive and structures. The roll roll nip is then held in the forming web roll during the entire roll, whereby the roll nip load remains desired and does not cause a discontinuity in the roll.

25 To control the roller nip force and vibrations, a brake can be provided adjacent to the roller cylinder which is available during roll-up to suppress nip oscillation without affecting nip force measurement. In addition, in the event of a malfunction, such as a power failure or mechanical failure, the brake prevents uncontrolled movement of the roller cylinder 30 on a slanted surface.

7

The invention will now be described in more detail with reference to the figures in the accompanying drawings.

Figure 1 schematically shows the winding step just before the winding is moved from the secondary position to the primary position, i.e. the changeover step.

Figure 2 schematically shows a winding step in which the secondary station has a finished roll and the winding moves to the primary station.

Figure 3 schematically shows a winding step in which a finished roll is dispensed from the secondary station and the winding from the primary station is transferred to the secondary station.

Figure 4 schematically illustrates a winding step in which the winding carriages move to receive the next winding alley as winding continues in the secondary position.

15

Figure 5 schematically shows the winding step just before the winding is moved from the secondary station to the primary station, i.e. the switching step.

Fig. 6 schematically shows a winding step in which the secondary station has 20 rolls completed and the winding moves to the primary station.

Figure 7 schematically illustrates a winding step in which a finished roll is dispensed from the secondary station and the winding from the primary station is transferred to the secondary station.

Figure 8 schematically illustrates a winding step in which the winding carriages move to receive the next winding axis as winding continues in the secondary position.

Figures 9 to 13 schematically illustrate the steps involved in the switchover of the application of Figures 5-8.

30 8

Fig. 14 schematically illustrates an embodiment using the oscillation method.

Figures 15 to 17 show schematically various embodiments of a measuring arrangement preferably used in connection with the invention,

Figures 18 and 19 schematically illustrate preferred measuring arrangements to be made in connection with the invention.

Fig. 20 schematically shows an operating area of a large diameter reeling inserter according to the invention.

Fig. 21 schematically shows an arrangement according to the invention for controlling nip force and vibration.

15

In the following figures, unless otherwise indicated, the same reference numerals are used for substantially the same parts.

Figures 1-4 schematically illustrate a situation in a winding and a winder using a fixed secondary station, and Figures 5-8 schematically illustrate an application using a mobile secondary station and have a nip-close exchange. Figures 9-13 schematically illustrate an application using a mobile secondary station and a nip open exchange.

In the embodiments shown in Figs. 1-13 and associated steps, the movement of the winding cylinder 10 is substantially consistent with the direction of the web W. The scrolling is started at the primary station on the primary wagons, from where the scrolling progresses to the station station to the secondary wagons. necessary electrical drives while providing direct movement of the primary and secondary stages 30 to the winding web reel 21, 22. The diameter of the reeling sinter 10 is large and the diameter of the reeling sinter 10 is determined such that the ratio of the diameter of the reeling 9 to its width -0,0009x3 + 0.025x2 -0.2567x + 1.0903, where y = the diameter of the roller cylinder / the width of the roller and the width of the roller xx, over the curve given in the example of Figure 20.

5

In the situation of Figure 1, web W is rolled to web 20 at a fixed secondary winding station. The secondary drive 25 is coupled to the winding shaft 24. In the vicinity of the secondary station, there is a surface clamping device 30. During winding, the winding cylinder 10 is in nip contact with the formed web roll 20. The use of the winding cylinder 10 10 is denoted by reference numeral 11 and the movement direction of the winding cylinder 10 is denoted by reference numeral S10. In the situation shown in the figure, the winding is just being changed around the next winding shaft 21, which is provided with a primary drive 26 and is placed in the winding carriages (not shown). The winding shaft 21 is brought into nip contact with the winding cylinder 10 and the exchange is effected by means of the water exchange device 16 by cutting the web W and, for example, by the air blowing device 17 by guiding the web W around the winding shaft 21. The roller W spreader roll is denoted by reference numeral 18, the scrolling carriages move in the embodiment shown in the figure by the scrolling rails 15. The figure also shows dashed axes for the next incoming rollers by reference numeral 2Γ and their direction of movement in transfer step 20 by reference arrows

In the situation of Figure 2, the winding is shifted around the new winding shaft 21 and the resulting web reel is designated by reference numeral 22. The surface of the finished roll 20 located in the secondary station is secured by a surface mounting device 30 to prevent the winding 25 from loosening. Pimiankiinnityslaite 30 is shown by the arrow S30 is moved from its standby position to a surface position (Fig. 2), at this stage the reeling drum 10 and the forming new web roll 22 is moved to the direction of arrows S21 and S10, as indicated by the secondary station from the web roll 20.

30 10

In the situation shown in Fig. 3, a finished web roll 20 'is displaced from the secondary station. The transfer is indicated by arrows S20. The surface securing device 30 is detached from the web roll 30 and at this point, the web roll 22 formed from the primary station is moved to move the forming web roll 22 along the winding cylinder 10 as indicated by arrows S21 and S10 toward the secondary rewind station. The future position of the resulting paper roll 22 and the winding cylinder 10 in the secondary station is indicated by dotted lines.

As shown in Fig. 4, when the web roll in reeling is moved to a secondary position, the web in reel is denoted by reference numeral 20. Rolling-10 wagons are returned by arrow SV towards the next winding axis 21 which is moved by the rolling rails towards wagons to start when the secondary roll has grown to the desired diameter.

1-4, a new winding shaft is introduced onto the winder and driven against the winding cylinder. In this case, the winding cylinder is in nip contact with both the starting roll and the finishing roll. For example, after replacement by means of a water cutting device or other change device known per se, the reeling cylinder is detached from the finished roll, which is passed for further processing from the secondary 20 position. After replacement, the surface can be bonded to the surface in a secondary winding station for retardation during deceleration. The winding cylinder moves out of the way with the primary roll in the primary winding position, and the winding continues as the primary winding. After the finished roll has been delivered at the secondary station, the winding cylinder and the finished roll are moved to the secondary winding station. The scrolling wagons are returned to the primary weapon-25 country to receive the next scrolling axis. Scrolling is continued in the secondary scroll until the next rollover time is reached.

As shown in Figures 1-4, in this embodiment, the winding nip between the web roll 20, 22 formed and the winding cylinder 10 is closed throughout the winding. As the winding progresses, the winding cylinder 10 need not be disconnected at any time from the winding nip contact. Further, in this embodiment of the invention, it is noteworthy that the secondary winding station is a fixed one, whereby a fixed position secondary drive 25 can be used, whereby the design and selection of drive uses is more versatile than prior art solutions since no mobility feature is required.

5

As the winding progresses in the steps of Figures 1 to 4, the winding cylinder 10 first moves backwardly away from the secondary position after the winding moves about the new roll axis 21 from the completed web roll 20. When the finished roll 20 has been released from the secondary position, the reeling cylinder 10 moves in the direction of movement towards the secondary station and as the winding progresses, the winding cylinder 10 shifts so that the load in the winding nip, i.e. the nip pressure, remains desired. The direction of movement of the winding cylinder substantially corresponds to the direction of the web entering the winding cylinder. With the direction of motion of the reeling cylinder substantially the same as the direction of the incoming web, the direction of motion of the reel-15 non-rolling cylinder forms an angle of 30-60 °, most preferably 45 °. The direction of motion of the winding cylinder may deviate slightly from the direction of web entry, however, by a maximum of ± 15 °. This achieves e.g. the advantages of not reversing the loading direction of the reeling cylinder during winding, while avoiding dead points of winding, and simplifying the measurement and control of the nip effect acting on the winding.

In the embodiment shown in Figs. 5-8, in the situation of Fig. 5, web W is wound into web roll 20 at a secondary winding position. The secondary drive 25 is coupled to the winding shaft 24. During winding, the winding cylinder 10 is in contact with the web roll 20 formed in a nip. The use of the winding cylinder 10 is denoted by reference numeral 11 and in the direction of movement of the winding cylinder 10 by reference numeral S10. In the situation shown in the figure, the winding is just being changed around the next winding shaft 21, which is provided with a primary drive 26 and is placed in the winding carriages (not shown). The winding shaft 21 is brought into nip contact with the winding cylinder 10 and the exchange is effected, for example, as shown in Fig. 1 by the water exchange device 16 by cutting the web W and e.g. by the air blowing device 17 by guiding the web W around the winding shaft 21. The spreader roll of web W is denoted by reference numeral 18, The scrolling carriages move in the embodiment shown in the figure by the scrolling rails 15. The figure also shows dashed axes for the next upcoming rollers by reference numeral 2 Γ and

In the situation of Fig. 6, the winding is shifted around a new winding shaft 21 and the resulting web roll is denoted by reference numeral 22. The surface of the finished roll 20 located in the secondary station is secured, e.g., by a surface securing device (not shown 10). At this stage, the reeling cylinder 10 and the forming new web roll 22 is transferred to S10 of the arrow shown in the disconnected from the web roll 20 in the secondary position.

7, the finished web roll 15 20 'is moved away from the secondary station. The transfer is indicated by arrows S20. At this point, the web roll 22 is moved from the primary station together with the winding cylinder n 10 as shown by the arrows S21 and S10 towards the secondary winding station.

As shown in Fig. 8, when the web roll in reeling is moved to a secondary position, the web in reel is denoted again by reference numeral 20. Rolling-20 wagons are returned by arrow SV towards the next winding axis 21 which is moved by rolling rails towards wagons to start next roll rotation axis 21 when the secondary roll has grown to a desired diameter. The movement of the winding cylinder 10 as the web roll 20 is formed is indicated by arrow S10.

25

As the winding progresses in the steps of Figs. in the indicated direction of movement and as the winding progresses, the winding cylinder 10 moves so that the load in the winding nip, i.e. the nip pressure, remains desired. The direction of movement of the winding cylinder substantially corresponds to the direction of the web entering the winding cylinder. With the movement direction of the winding cylinder substantially the same as the direction of the incoming web, the direction of motion of the winding cylinder forms an angle of 30-60 °, preferably at most 45 °. The direction of motion of the winding cylinder may deviate slightly from the direction of web entry, however, by a maximum of ± 15 °. This achieves e.g. the advantages of not reversing the loading direction of the reeling cylinder during winding, while avoiding dead spots in the reeling, and simplifying the measurement and control of the nip load acting on the reeling.

10

Figures 9 to 13 show in more detail the steps of the embodiment of the embodiment illustrated in Figures 5-8, above, when changing from a finished roll to a new roll axis.

In the situation of Fig. 9, web W is wound in a secondary position to web web 20 and the next winding shaft 21 is being moved from the winding shaft storage towards the replacement station. The surface tying device 30 of the secondary station roll 20 is brought into contact with the web roll 20 and the secondary station roll 20 is moved as indicated by arrow S20.

20

In the situation of Figure 10, the winding cylinder 10 moves to receive a new winding shaft 21. The movement of the winding cylinder is indicated by the arrow S10 and the movement of the new winding shaft by the arrow S21. The roll 20 in the secondary station is moved towards the felting station.

25

11, the web roll 20 in the secondary station is finished and the surface is bonded to the surface tying device 30, and the web W entering the secondary station is cut and the web W rolled around a new winding shaft 21 which is nip contacted with the winding cylinder 10.

30 14

In the situation of Fig. 12, winding has begun around a new winding shaft 21 and the resulting web roll is denoted by reference numeral 22. The finished web roll 20 is in the secondary position and its surface is bound by a surface tying device 30.

In the situation of Figure 13, the finished roll 20 from the secondary station is moved to further processing and the secondary station waits for the web roll 22 to move from the primary station to be rolled in the secondary station and the movement of the web roll is indicated by arrow S21. During the secondary winding, the winding cylinder 10 remains substantially in the same position, i.e. the winding cylinder 10 moves according to Figures 10-11 above during the changeover 10, being in place during the actual winding, as the winding progresses and the web roll increases.

As shown in Fig. 14, the web may be oscillated during winding by rotating a nip between the winding cylinder 10 and the forming web roll 22 about a vertical axis 15 by moving the ends of the winding cylinder 10 and formed web roll 22 in the machine longitudinal direction (MD). lie 10 through a spreading roll 18 and a subsequent track guide roll 72. An air turning device can also be used instead of the track guide roll 72. The movement and direction of the reeling cylinder 10 are indicated by dashed lines in the figure. 20 in accordance with arrow S10, the direction of movement of the reeling cylinder 10 is substantially vertical and corresponds the incoming direction of the web W.

Figures 15 to 17 show various mounting options for mounting a sensor in the form of a pressure sensitive diaphragm metering arrangement for use with a reel. The measuring array is also suitable for use in other paper and board-machine applications where multiple nip measurement applications are required against the same roll, such as surface sizing, pigmenting or coating film transfer presses, calenders, presses, and winder machines. Figure 15 shows an alternative in which the sensor 50 is mounted directly parallel to the longitudinal axis of the roll winding cylinder 10. In Fig. 16, the sensor 50 is mounted as a spiral sensor, making it suitable for measuring profiles. The figure shows a so-called gentle spiral having an angle as large as possible in resolution of the axis of the roll winding cylinder 10 but smaller than the sector between the primary nip and the secondary nip illustrated in Fig. 18, for which only one 5 nips can be measured. Fig. 17 illustrates circumferential sensors mounted on the surface of the winding cylinder for measuring forces and / or pressures on the surface of the winding cylinder. As shown in the figure, the sensors 50 can be positioned over the entire circumference of the winding cylinder 10 or a portion thereof.

10 The measuring probe uses an EmFi membrane 50 as a sensor, which is a pressure transducer 50 suitable for detecting pressure or movement and having good sensitivity to small movements. It measures dynamic shape and is measured over the entire sensor area with the same weight. Such a measurement method is known per se and the signal produced by the sensor is sampled and transmitted from the winding cylinder preferably wirelessly for processing the measurement results.

Fig. 18 shows a measuring arrangement used in connection with the method and roller of the invention for measuring multiple nip loads and profiles.

In the embodiment of Figure 18, using the mounting arrangement of Figure 15, the total line load level of both winding nipples N1, N2 is measured with the same sensor. The measurement can be done in the same round using fast sampling and synchronization. First, the EmFi membrane sensor 50 is reset by shorting the terminals. The line load level of nip N1 is then measured as the sensor passes through the nip. The machine direction profile profile of the 25 nip can also be determined as needed. The sensor is then reset again and the line load level of the second nip N2 is measured. With the measurement electronics of the measuring arrangement, up to 8000 measurements / second can be sampled, so multiple measurements in the same round can be achieved for this purpose.

30 16

In the embodiment of Fig. 18, using the mounting option 2 of Fig. 16, the tension profile of both nipples N1, N2 is measured as indicated by the same sensed arrows II. The measurement is made as above, but a sample string representing the profile is collected as the spiral passes through each nip. The coils are very gently sloping, the circumferential 5 coverage being preferably shorter than the distance between the primary and secondary winding nipples. The total line load profile can also be calculated from the spiral sensor signal.

Fig. 19 illustrates the measurement of a web tension profile with a measuring arrangement used in connection with the method of the invention and the reel. The measurement can be performed using the mounting option of Figure 15, where the total level of track curvature is measured before the secondary nipple, or using the mounting option of Figure 16, where the tension profile is measured. In this context, it is also possible to measure the nip load profile from multiple nips and the total nip load level from multiple 15 nip and the track tension profile and level with a single sensor. In the situation where the primary nip is also present, depending on the construction, the track tension or the track tension profile between the primary and secondary nip or before the primary nip can be measured. Sampling can be centered on the point where the measurement is to be made.

The schematic example shown in Figure 20 illustrates a new range of operation made possible by the large-diameter winding cylinder of the invention. The vertical axis y in the figure has a ratio of the diameter of the winding cylinder to the width of the web to be rolled and the horizontal axis the track width. Above the curve k, defined by the formula y ^ -0,0009x3 + 0,025x2-0,2567x + 1,0903, there is a new operating area T possible according to the invention. In the present invention, it is completely new to determine the design principles of the winding cylinder a prior art procedure in which the diameter of a winding drum is determined by deflection and vibration criteria and certain geometric conditions, whereby the winders have a variety of winding cylinder diameters and thus a variety of reel sizes and design variations, - 17 passing. Thus, the method and the coil winder of the invention also achieve a long winding nip, which is advantageous in terms of winding quality. This also allows additional space for the changeovers, especially when the winding nip is closed, as well as more space for different actuators in the frame.

5

As shown in Figure 21, to control the roll nip force and oscillation, a brake 60 is provided adjacent to the winding cylinder 10 which is operable during winding to dampen the nip oscillation without affecting the nip force measurement. In addition, in the event of a malfunction such as a power failure or failure of the me-10 mechanical structure, the brake 60 prevents the uncontrolled movement of the reeling cylinder 10 moving on an oblique surface. The brake 60 is disposed in connection with the loading / moving actuator of the winding cylinder 10 between the nip force measurement and the loading actuator 65, thereby not affecting nip force measurement and causing problems with nip force control. The braking force of the brake 60 is adjustable such that, during winding 15, the brake 60 is operated with a small, adjustable nipple-damping force and, in the event of a disturbance, an anti-uncontrolled movement of the winding cylinder 10. The brake 60 may be, for example, a spring-loaded hydraulic brake. According to one embodiment, the brake comprises a friction shoe adapted to brake the actuator shaft or a slider attached to the actuator loop. According to one embodiment, the brake may also comprise a combination of a screw and a hydraulic cylinder comprising an active brake part / damper. The braking force measurement can be fitted to the coarse friction surfaces so that, for example, there is a brake part between the hydraulic cylinder loop and the force transducer, which is braked with brake shoes. When implemented in this way, the brake force measurement is also suitable for use in other paper and board machine equipment such as surface sizing, pigmenting or coating film transfer presses, calenders, presses and winders for winders.

18

The invention has been described above only with reference to a preferred embodiment thereof, the details of which, however, are not to be construed as being limited in any way.

Claims (24)

19 A method for winding a paper or board web, wherein the web (W) is wound around a winding axis (21; 24) into a web roll (22; 20) via a winding nip between the winding roller-5 blades (10) and the forming web roll (22, 20). takes place in the primary stage in the primary station and in the secondary stage in the secondary station, characterized in that the paper or cardboard web is wound through a large diameter roller (10) whose diameter relative to the width of the web to be rolled -0,0009x3 + 0.025x2 -0.2567x + 1.0903, where the y ~ scrolling cylinder is divided by a 'a / the width of the web to be rolled and x = the width of the web to be rolled. Method according to Claim 1, characterized in that the winding nip 15 is rotated about a vertical axis to adjust the track tension. Method according to claim 1 or 2, characterized in that the nip acting on the winding nip is measured by means of at least one pressure sensitive measuring film (50), which pressure sensitive measuring film (50) is mounted on the surface of the winding cylinder (10). Method according to claim 3, characterized in that the pressure-sensitive measuring film (50) is mounted on the surface of the winding cylinder (10) parallel to the longitudinal axis of the winding cylinder. 25 Method according to Claim 3, characterized in that the pressure-sensitive measuring film (50) is mounted helically on the surface of the winding cylinder (10). Method according to Claim 3, characterized in that the pressure-sensitive measuring film (50) is mounted on the surface of the winding cylinder (10) in the direction of the circumference of the winding cylinder, extending in whole or in part. 20 Method according to one of Claims 1 or 3 to 6, characterized in that the web (W) to be rolled is guided to the rallying cylinder (10) directly from the distribution roll (18), Method according to one of Claims 1 to 7, characterized in that the forming web roll (22; 20) and the winding cylinder (10) have a winding nipple substantially throughout the winding, Method according to claim 8, characterized in that the horizontal position of the web roll (20) formed in the secondary station 10 remains the same until the formed web roll is released. Method according to one of Claims 1 to 9, characterized in that the surface of the web roll (20) to be produced is bonded by a surface fastening device (30) upon removal of the winding cylinder (10) to prevent loosening of the surface layer. Method according to one of Claims 1 to 10, characterized in that the nip force and vibrations of the roller are controlled by the loading / moving device of the winding cylinder (10). with a jam (60). 20 Method according to one of Claims 1 to 11, characterized in that, in the event of failure, the brake (60) arranged in connection with the loading / moving device of the winding cylinder (10) prevents uncontrolled movement of the winding cylinder (10). A roller roller for winding a paper or cardboard web into a web roll, comprising a winding cylinder (10) for providing a winding nip and for starting the primary station to continue winding a secondary station into a finished web roll, characterized in that the the area is the area above the curve given by y = -0,0009x3 + 0.025x2 -0.2567x + 1.0903, where the y-reeling cylinder would have a? / a width of the web to be rolled and x = the width of the web to be rolled. 21 A reel winder according to claim 13, characterized in that the reel comprises means for moving the ends of the reel inserter (10) and the formed web reel (22, 20, 24) in the longitudinal (MD) direction of the machine to adjust the web tension profile. A retractor according to claim 13 or 14, characterized in that the reel comprises a pressure-sensitive measuring film (50) for measuring the nip load acting on the winding nip. 10 A retractor according to claim 15, characterized in that the pressure-sensitive measuring film (50) is disposed on the surface of the reel core (10) in the longitudinal axis of the reel core. A retractor according to claim 15, characterized in that the pressure-sensitive measuring film (50) is mounted helically on the surface of the reeling inserter (10). Clamping reel according to claim 15, characterized in that the pressure-sensitive measuring diaphragm (50) is mounted on the surface of the winding sinter (10), extending wholly or partially along the circumference of the winding sinter. A retractor according to one of claims 13 to 18, characterized in that the secondary position of the reel is movable. 25 Roller according to one of Claims 13 to 19, characterized in that a surface mounting device (30) is provided in connection with the roller, after the reeling core (10) has been removed, to prevent the surface layer of the web reel (20) from loosening. Roller according to one of Claims 13 to 20, characterized in that the roller comprises a changing device, preferably a water cutting device (16). 22 A fastener reel as claimed in any one of claims 13 or 15-20, characterized in that the reel reelable web (W) is adapted to be fed to the reel roll directly from the application roller (18). 5 A retractor according to any one of claims 13 to 22, characterized in that a brake (60) is provided in connection with the loading / moving device of the retractor winding cylinder (10) to control nip force and vibrations and prevent uncontrolled movement of the reeling cylinder (10). 10 A retractor according to any one of claims 13 to 23, characterized in that a damper is disposed between the nip load measuring device and the power generating device. 23