EP1900663A2 - Winding machine - Google Patents

Abstract

Winding machine has winding tube (4) and the rollers (1,2) are deflected due to inertia changing during winding of the winding roll (3). The deflection corresponds to a spring constant suitable through an auto-adaptive system for each roller side as function of the inertia of the winding roll. An independent claim is also included for a method for rolling a material web.

Description

The invention relates to a winding machine for winding a material web, in particular a paper or board web, on at least one winding tube to a winding roll by means of at least one elastically mounted roller on which the winding roll when winding up or rests.

Material webs must be wound up on shipping or finishing rolls before they can be shipped. As reel cores usually winding cores are used, which are preferably made of cardboard. The finished rolls are produced by so-called mother or spool rolls, which are produced at the exit of a paper machine or after the calendering, unwound, cut in the longitudinal direction and then wound on each winding cores. These cores are either on a support roller of a back-up roll winding machine or laterally on this, or the cores are in one of two support rollers of a double carrier roll winding machine formed winding bed.

In the case of a double carrier roll winding machine, as for example from the DE 200 13 319 U1 or the EP 0 792 245 B1 is known, at least one of the two support rollers is driven. In this way, according to the number of individual webs produced from the original material web by longitudinal cuts several cores next to each other in the winding bed, even if subsequently for reasons of simplicity always only a single winding tube is addressed in conjunction with a wound on her web winding. However, it is also possible to wind only a single winding roll in a double carrier roll winding machine.

In the EP 0 829 438 B1 a backup roll winding machine will be described. In this case, a web supported on a support roll is wound on a winding mandrel as it passes through a nip formed between the support roll and the wound roll to be formed, the winding roll being additionally supported by another device comprising two small rolls becomes. In a back-up roll winding machine, either only a single winding roll may be wound or a plurality of winding rolls each held in winding stations by individual tensioning devices, the tensioning devices alternating the winding rolls to both sides from a vertical axis passing through the center of the backing roll hold, wherein the connecting lines between the centers of the bobbins and the support roller are inclined in each case to both sides of the vertical at an acute angle or form a right angle with the vertical. Here, the clamping heads and the winding tubes in the winding stations can also have different diameters.

When winding rolls are caused by vibrations of the role and the two support rollers indentations in the role, which occur by resonances always at the same circumferential location and thus become stronger. As a result, on the one hand the entire winding machine harmful vibration stresses subjected, and on the other hand, the winding roll is wound with winding faults.

From the DE 71 21 923 U1 is a support device for rolls wound from webs known in which at least one of the two support rollers is elastically mounted. Due to the elastic support receives the one support roller with the same design of both rolls a different natural frequency to each other, so that a summation of the vibrations of the two rolls and thus a roll damage is excluded.

By the DE 73 05 837 U1 is a support device has become known in the both support rollers are supported on springs. By this measure, a decoupling and damping of vibrations is achieved. It can also provide the use of damping elements whose damping effect is adjustable in dependence on the bearing load.

One from the DE-AS 23 18 351 known supporting device is characterized in that in all the essential parts and with respect to the characteristics of the same springs, the spring systems are arranged asymmetrically with respect to the plane passing through the winding roll axis vertical plane. In this way, the two support rollers associated lines of action are at an angle to each other, so that the vibrations also impinge on the respective suspension system in a different angle or at different locations. As a result, the suspension behavior of the suspension systems of the two support rollers is different, without that therefore the support roller suspension or its storage or the support rollers themselves would have to be designed differently or adjustable.

Although the known solutions in which bearings are used with variable bearing stiffness and damping, achieve a substantial suppression of resonant or natural vibrations of the support rollers, but occur especially in the processing of papers with a high coefficient of friction, so-called vibration-critical papers, increasingly strong vibrations. The frequency of the vibrations is always a multiple of the winding speed. The coils are out of round by these vibrations, which is due to the excitation of the system. To reduce or eliminate in the EP 1 260 470 A2 an active damping of the carrier roll by hydraulic cylinders, in the DE 10 2004 062 890 A1 a change in the system natural frequency of a support roller by a switchable stiffness of the support roller bearing with a damper as a locking device, in the DE 10 2005 000 052 A1 a position-controlled carrier roll with a variable damper and in the DE 10 2005 024 266 A1 an adjustable 2-chamber damping cylinder in combination with a spring-loaded roller bearing proposed.

It is the object of the invention to provide an improved winding machine, in which the one carrier roll (in the case of a backup roll winding machine) or the two carrier rolls (in the case of a carrier roll winding machine) are optimally damped.

According to the invention this object is achieved in a winding machine of the type mentioned in that the deflection of the roller due to the changing during winding mass of the winding roll according to a pre-defined or adaptable by a adaptive or self-learning system spring stiffness per roll side as a function of the mass of the winding roll he follows.

A support roller is optimally damped at their bearings when the bearing stiffness c _L goes to zero. Then the support roller is mounted on each side only on a hydraulic cylinder in a linear guide or a lever. The hydraulic cylinder initiates the damping forces directly on the roll neck. However, this procedure is technically very complicated, since the position of the support roller must be kept exactly by a separate position control at each bearing point. The smallest misalignment of a carrier roll has a massive effect on the winding structure of the winding roll. To circumvent this expensive and technically susceptible solution, the support rollers are still stored today on mechanically acting spring stiffness, for example on a flexible rocker, as in the above-mentioned DE 10 2005 024 266 A1 is disclosed. When designing a fixed bearing rigidity, one must therefore orientate oneself inevitably on the maximum occurring paper roll weight. This means that the system can work almost optimally only at the end of the winding process. At the beginning of a winding process, the system is tuned too hard, since the roll weight is missing and thus the natural frequencies of the vibration system are higher.

wobei c_L die Federsteifigkeit und m_W die Masse der Wickelrollen bedeuten. Die Federwirkung kann in dem Lager einer Walze integriert sein, so dass man in diesem Fall statt von Federsteifigkeit ebenso von Lagersteifigkeit sprechen kann.
Vorteilhafte Weiterbildungen ergeben sich aus den Unteransprüchen, der Beschreibung und den Zeichnungen.A technically sensible compromise between the technically complex position control with mechanically optimal damping on the one hand and a self-adjusting mechanical stiffness roller position - with increasing spring stiffness a decreasing damping capability is connected - thus represents a variable spring stiffness, as provided by the invention. The spring stiffness is controlled as a function of the paper roll weight so that the damping always works almost optimally. Where: $${\mathrm{C}}_{\mathrm{L}}\mathrm{=}\mathrm{f}\left({\mathrm{m}}_{\mathrm{W}}\right)\mathrm{.}$$

where c _{L is} the spring stiffness and m _W the mass of the winding rolls. The spring effect can be integrated in the bearing of a roller, so that one can speak in this case instead of spring stiffness as well as bearing stiffness.
Advantageous developments emerge from the subclaims, the description and the drawings.

Preferably, the system comprises an actuator, a spring, in particular with a non-linear spring characteristic, a damper and a measuring device in order to be able to determine the position of the support rollers accurately.

Particularly suitable is an embodiment of the winding machine in which the spring stiffness of the spring and / or the damping of the damper are variable. There are a variety of ways to design the springs; Preferably, springs are used in the form of bending beams or as spiral springs.

In a preferred embodiment of the invention, the damper comprises a damping cylinder, which is filled with an electrorheological or a magnetorheological fluid whose damping is changed by changing an applied electric or magnetic field.

Advantageously, the winding machine is developed so that the at least one roller is equipped with a linear guide or another element, with the at least one roller is displaceable in the direction of the other roller.

In this case, it is additionally advantageously provided that at least one of two rollers, for example of two carrier rollers, is fastened to a rocker, by means of which it is pivotable in the vertical direction or in the direction of the other carrier roller. The rocker is preferably infinitely adjustable in length.

The invention also relates to a method for winding a material web, in particular a paper or board web, in a winding machine on a sleeve to a winding roll by means of at least one elastically mounted roller on which the winding roll on winding up or rests.

kontinuierlich angepasst wird, wobei c_W die Walzensteifigkeit, c_L die Lagersteifigkeit je Walzenseite und ω die Kreisfrequenz des zu dämpfenden Schwingungsproblems bedeuten.The method according to the invention is characterized in that the damping characteristic (d) as a function of the changing spring or bearing stiffness (c _L ) according to the equation $$\mathrm{d}\mathrm{=}\left({\mathrm{C}}_{\mathrm{W}}\mathrm{+}\mathrm{2}\mathrm{*}{\mathrm{C}}_{\mathrm{L}}\right)\mathrm{/}\mathrm{\omega }$$

is continuously adjusted, where c _{W is} the roll stiffness, c _{L is} the bearing stiffness per roll side and ω is the angular frequency of the vibration problem to be damped.

The quantity c _W is a dynamic equivalent stiffness, which can be calculated from the bending natural frequency f _{0 of} the support roller (on rigid bearings) and the support roller mass m _TW according to the following equation: $${\mathrm{C}}_{\mathrm{W}}\mathrm{=}\mathrm{1536}\mathrm{/}\left(\mathrm{5}\mathrm{*}{\mathrm{<figure-callout\; id="2"\; label="\pi "\; filenames="imgf0001.png,imgf0003.png"\; state="\{\{state\}\}">\pi </figure-callout>}}^{\mathrm{2}}\right)\mathrm{*}{\mathrm{m}}_{\mathrm{TW}}\mathrm{*}{{\mathrm{f}}_{\mathrm{0}}}^{\mathrm{2}}\mathrm{,}$$

As a rule, the frequency of the oscillation problem, ie the problematic resonance frequency, is in a narrowly limited frequency range, so that the angular frequency ω = 2 * π * f can be preselected as constant. In this case, the tracking of the damping characteristic d is controlled as in the case of spring stiffness c _L or controlled according to the mass m _{W of} the winding roll.

It is sufficient if, for the problem frequency f, a mean value between the second highest contact frequency of the carrier roll and the winding roll and the carrier roll is set without the influence of the paper pulp. In this case, those frequencies are to be understood as meaning the frequencies at which the winding roll beats either in-phase or out-of-phase against the two winding rolls and thereby generates undesirable vibrations.

In the case of a carrier roll winding machine, the damping is preferably set to an intermediate value between the bending natural frequency of the roll and the second highest contact natural frequency of the roll to the winding rolls, or the damping is optimized for the strongest oscillation.

Should also other frequency ranges, such. B. the known low-frequency roll swings lead to significant vibration, the damping behavior can be optimized to the strongest of these vibrations. In this case, the damper setting is controlled as a function of the occurring problem frequencies ω. The determination of the problem frequencies is carried out by a vibration measurement with subsequent harmonic analysis by Fourier transforms.

The entire invention can be used in a double-winder winding machine, but also when only a single roller is used as a support roller for the cut longitudinally paper webs. In this case, the individual coils are supported alternately in an eleven o'clock or one o'clock position with respect to the support roller. Also in this case, there is a desire for optimal damping of the support roller, which is realized by the use of a system according to the invention. Instead of the eleven o'clock and the one o'clock positions, the windings can also be located at other symmetrically opposite positions in the region of the two upper quadrants of the support roller.

The invention will be described in embodiments with reference to FIGS Drawings explained in more detail.

Fig. 1

eine Seitenansicht einer ersten Doppeltragwalzen-Wickelmaschine in Längsrichtung, in der die Tragwalzen jeweils durch ein Positioniermittel gelagert sind,

Fig. 2

eine Seitenansicht einer weiteren Doppeltragwalzen-Wickelmaschine in Längsrichtung, in der die Tragwalzen zusätzlich mit einer Linearführung bzw. mit einer Schwinge ausgestattet sind,

Fig. 3

eine Vorderansicht einer dritten Doppeltragwalzen-Wickelmaschine, in der die Federn jeweils als Biegebalken ausgestaltet sind,

Fig. 4

eine weitere Seitenansicht einer Doppeltragwalzen-Wickelmaschine, in der einstellbare Positioniermittel (nur an der linken Tragwalze dargestellt) zum Einsatz kommen,

Fig.5

ein Hydraulikzylinder, der zu einer Feder mit einer nicht-linearen Federkennlinie parallel geschaltet ist,

Fig. 6

die Kennlinie der Feder aus Fig. 5,

Fig.7

eine Seitenansicht einer Stützwalzen-Wickelmaschine, in der zwei Wickelrollen jeweils waagrecht gegen die Stützwalze drückbar sind, und

Fig. 8

eine weitere Seitenansicht einer Stützwalzen-Wickelmaschine, in der zwei Wickelrollen in einer Elf-Uhr-Position bzw. in einer Ein-Uhr-Position gegen die Stützwalze drückbar sind.

Show it

Fig. 1

a side view of a first double-carrier roll winding machine in the longitudinal direction, in which the support rollers are each mounted by a positioning means,

Fig. 2

a side view of a further double-takeup roller winding machine in the longitudinal direction, in which the support rollers are additionally equipped with a linear guide or with a rocker,

Fig. 3

a front view of a third double carrier roll winding machine, in which the springs are each designed as a bending beam,

Fig. 4

another side view of a double carrier roll winding machine, in the adjustable positioning (used only on the left support roller) are used,

Figure 5

a hydraulic cylinder connected in parallel with a spring having a non-linear spring characteristic,

Fig. 6

the characteristic of the spring of Fig. 5,

Figure 7

a side view of a backup roll winding machine, in which two winding rollers are each pressed horizontally against the support roller, and

Fig. 8

another side view of a backup roll winding machine, in which two winding rollers can be pressed in an eleven o'clock position or in a one o'clock position against the support roller.

A winding device formed by a double-winder winding machine (Fig. 1) has two support rollers 1, 2, at least one of which is driven. The support rollers 1, 2 form a roller bed, in which several adjacent bobbins 3 rest during winding on the support rollers 1, 2. From a longitudinal cutting device (not shown), a material web, in particular a paper or board web, is cut into a plurality of individual webs before winding, which are then passed through the gap between the support rollers 1, 2 or laterally around the web Cloak one of the two support rollers 1, 2 are guided around in the roll bed, where they are wound up in aligned rows of sleeves 4.

The support roller 1 is mounted on a positioning means 6 via a bearing 5, which comprises an actuator 7, a spring 8, a damper 9 and a measuring device 10. This generates according to the current position of the support roller 1, a signal that passes the measuring device 10 to the actuator 7, so that this according to a deviation between an actual position and a required target position of the support roller 1, a piston 11 of a hydraulic or pneumatic cylinder 12 actuated. Instead of the cylinder 12, an electromotive adjusting means, such as a pneumatically operated bellows cylinder or a rolling diaphragm can be used. The piston 11 in turn presses on the spring 8, and this acts on the support roller 1 a.

If this should get into vibration, the vibrations are damped by the damper 9 quickly. The damper 9 is a vibration energy dissipation element and includes, for example, a cylinder 13 filled with a gas. The gas is compressed by a punch 14 connected to the bearing 5. If, as a result of the vibrations of the support roller 1, the bearing 5 passes this to the punch 14, this compresses the gas, and a part of the vibration energy is converted into heat. It is understood that the vibrational energy can be derived in other ways from the system, for example by electrical eddy currents. The support roller 2 is mounted on a bearing 15 which, like the bearing 5 of the support roller 1 is mounted. Preferably, the spring stiffness of the spring 8 can be changed.

In a further embodiment (FIG. 2), a linear guide 16 is arranged on the bearing 5 of the support roller 1, by which the height position and / or the horizontal position of the bearing 5 and thus the position of the support roller 1 with respect to the support roller 2 and in Reference to the winding 3 can be adjusted. The support roller 2 is mounted on a rocker 17 pivotally mounted about a pivot point 18 to their position with respect to the support roller 1 and the coil. 3 to be able to change.

In another exemplary embodiment (FIG. 3), the actuator 7 comprises on both sides of the shaft of the support roller 1 springs designed as bending beams 19, 20 for elastically supporting the support roller 1, via which bearings 5, 25

Piston 21, 22 of cylinders 23, 24 act. The bending beam 19, 20 press in turn against the bearings 5, 25 of the support rollers 1, 2 and are mounted in brackets 26, 27. The rigidity of the bending beams 19, 20 can be changed by changing the position of the cylinders 23, 24 in the direction of the axes of the bending springs 19, 20. On both sides of the shaft journal of the support roller 1, a damper 28, 29 is also provided in each case. At least on one side of the support roller 1, a measuring device 30 for determining the position of the support roller 1 is provided.

In another embodiment (FIG. 4), the support rollers 1, 2 are mounted on positioning means 31, each comprising a hydraulic cylinder 32 and 33, respectively. The cylinder 32 has an oil column 34 whose length is adjustable via a valve 35 from an oil reservoir. Likewise, there is also preferably a pressurized air supply above the oil column 35 in the space of the cylinder 32 in which the piston rod moves, the pressure of which is adjusted via a valve 37 connected to a bubble chamber 36. Throttles 38, 39 are preferably present, via which the speed with which the oil or the air can escape from the interior of the cylinder 32 is set.

The cylinder 33 is preferably constructed in the same way as illustrated by the example of the cylinder 32.

Parallel to the cylinder 32, 33 or instead of the spring 8 (FIGS. 1, 2), it is also possible to use a spring 40 with a non-linear characteristic in order to support the bearings 5, 15 of the support rollers 1, 2.

In the path-force diagram (Figure 6), in which the spring force (F) is shown as a function of the distance traveled by the spring (s), the spring characteristic of the spring 40 with increasing distance s a greater slope; d. H. the spring 40 has a non-linear spring characteristic and acts the harder, the greater the distance traveled.

In another embodiment, a back-up roll winding machine (Figure 7) is shown with a back-up roll 41 against which two bobbins 42, 43 are respectively supported in the nine o'clock position and the three o'clock position. The winding rollers 42, 43 are supported by (not shown here) supporting devices and pressed against the jacket of the support roller 41. The support roller 41 is mounted on a positioning means 45 via a bearing 44, which, like the positioning means 6, comprises an actuator 46, a spring 47, a damper 48 and a measuring device 49.

As in the carrier roll winding machine illustrated with reference to FIGS. 1 to 3, a setting or control device can be arranged in the backup roll winding machine to adjust the position of the positioning means 45 according to the weight of the winding rolls 40, 41 changing during the winding operation ,

In Fig. 8, another embodiment of a backup roll winding machine is shown, are employed in the winding rollers 50, 51 against a support roller 52. Incidentally, there is provided a positioning means having the same construction as the positioning means 45 of FIG. 7 and therefore designated by the same reference numerals.

LIST OF REFERENCE NUMBERS

1

king roll

2

king roll

3

reel

4

shell

5

camp

6

positioning

7

actuator

8th

feather

9

damper

10

measuring device

11

piston

12

cylinder

13

cylinder

14

stamp

15

camp

16

linear guide

17

wing

18

pivot point

19

bending beam

20

bending beam

21

piston

22

piston

23

cylinder

24

cylinder

25

camp

26

bracket

27

bracket

28

damper

28

damper

30

measuring device

31

positioning

32

cylinder

33

cylinder

34

oil column

35

oil column

36

bubble chamber

37

Valve

38

throttle

39

throttle

40

feather

41

supporting roll

42

reel

43

reel

44

camp

45

positioning

46

actuator

47

feather

48

damper

49

measuring device

50

reel

51

reel

52

supporting roll

Claims (10)

Winding machine for winding a material web, in particular a paper or board web, onto at least one winding tube (4) to form a winding reel (3; 42, 43; 50, 51) by means of at least one elastically mounted roller (1, 2; 41; 52), on which the winding roll (3; 42, 43; 50, 51) rests or rests during winding,
characterized,
in that the deflection of the roll (1, 2, 41, 52) as a result of the mass (m _W ) of the winding roll (3; 42, 43; 50, 51) changing during the winding process corresponds to a predetermined or an adaptive or self-learning system adjustable spring stiffness (c _L ) per roll side as a function (c _L = f (m _W )) of the mass (m _W ) of the winding roll (3; 42, 43; 50, 51) takes place. Winding machine according to claim 1,
characterized,
in that the system (6; 45) has an actuator (7; 46), a spring (8; 40; 47), in particular with a non-linear spring characteristic, a damper (9; 48) and a measuring device (10,30; ). Winding machine according to claim 1 or 2,
characterized,
that the spring stiffness of the spring (8; 40; 47) and / or the damping of the damper (9; 48) is variable. Winding machine according to claim 3,
characterized,
that the damper comprises a damping cylinder which is filled with an electrorheological or a magnetorheological fluid whose damping is variable by changing an applied electric or magnetic field. Winding machine according to one of claims 2, 3 or 4,
characterized,
that the spring is designed as a bending beam (19, 20). Winding machine according to one of the preceding claims,
characterized,
in that the at least one roller (1, 2; 41; 52) is provided with an element (16) with which the at least one roller (1, 2; 41; 52) moves in a vertical direction or in the direction of another roller (1 , 2, 41, 52) is displaceable. Winding machine according to claim 6,
characterized,
in that the at least one roller (1, 2) is fastened to a rocker (17) by means of which it is pivotable in the direction of the other roller (1, 2). Winding machine according to claim 7,
characterized,
that the rocker (17) is infinitely adjustable in length. Method for winding a material web, in particular a paper or board web, in a winding machine onto a winding tube to at least one winding roller (3; 42, 43; 50, 51) by means of at least one elastically mounted roller (1, 2; 41; 52), on which the winding roll (3; 42, 43; 50, 51) rests or rests during winding,
characterized,
that the damping characteristic (d) in dependence of the changing spring or bearing stiffness (c _L ) according to the equation $$\mathrm{d}\mathrm{=}\left({\mathrm{C}}_{\mathrm{W}}\mathrm{+}\mathrm{2}\mathrm{*}{\mathrm{C}}_{\mathrm{L}}\right)\mathrm{/}\mathrm{\omega }$$

cW is the roll stiffness, cL is the bearing stiffness per roll side and ω is the angular frequency of the vibration problem to be damped. Method according to claim 9,
characterized,
in that the damping (d) is reduced to an intermediate value between the bending natural frequency of the roller (1, 2; 41; 52) and the second highest contact natural frequency of the roller (1, 2; 41; 52) to the winding rollers (3; 42,43; , 51) or that the damping is optimized for the strongest oscillation.

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