EP1206403B1 - Slitter-winder - Google Patents

Description

Technical area

The invention relates to a slitter and winder for webs of paper, plastic or composite materials, with a longitudinal cutting device for dividing the web into strips and a winding device in which the strips are wound on cores.

State of the art

For winding a plurality of material strips produced by longitudinal cutting from a material web next to one another, roll cutting and winding machines with winding shafts are known, over which the winding tubes are pushed for winding. About the connected to a rotary drive winding shafts, the winding rollers are driven during winding.

There are known machines with only a single winding shaft on which all bobbins are wound directly adjacent to each other. In order to transmit the torques required for winding, the cores are braced either axially or radially expanding winding shafts to a rigid unit. Due to the tension of all cores to a rigid unit, the individual winding rollers can not rotate individually. From differences in thickness of the material web resulting differences in diameter in the winding rollers can not be compensated. Such winding machines can thus be used only for winding very uniformly thick webs of material.

For winding webs of varying thickness are known Rollenschneid- and winding machines with two winding shafts to which the strips are fed alternately. Each two adjacent strips are fed to different winding shafts, so that between two winding rollers on a winding shaft, a distance corresponding to the width of the adjacent, on the other winding shaft wrapped strip is present. The winding shafts are designed as so-called Friktionswickelwellen that keep constant the tension during winding for each winding roll even with different diameters. The friction shafts have a central drive shaft and a plurality of arranged on this, annular friction elements which are rotated by friction from the drive shaft. Each friction element comprises an annular friction body and externally arranged on this, radially outwardly pressed clamp body, which connect the friction body frictionally with the interior of a winding tube. A slitter-winder with two friction winding shafts is in the U.S. Patent 4,431,142 described.

• Die Schneidmesser der Längsschneidevorrichtung sind besser zugänglich. Die Zugänglichkeit ist bei Maschinen mit zwei Wickelwellen insbesondere erschwert, wenn wegen großer Wickelrollendurchmesser die beiden Wickelwellen nicht mehr übereinander, sondern hintereinander angeordnet werden müssen.
• Falls für einen schnellen Wickelrollenwechsel die Wickelwelle in ein Wendesystem eingebaut werden soll, ist die sogenannte Einspindelaufwicklung besonders platzsparend und preisgünstig, da nur ein Wendesystem benötigt wird. Im Wendesystem ist zwar eine zweite Wickelwelle vorhanden. Diese wird im Wechsel mit der ersten Wickelwelle zum Entladung und Aufwickeln der Wickelrollen benutzt. Es Wickeln niemals zwei Wickelwellen gleichzeitig.
• Die Entnahme hilfsmittel für die Fertigrollen werden nur einmal benötigt.

Machines with only one winding shaft offer several advantages over machines with two winding shafts:

• The cutting blades of the slitter are more accessible. The accessibility is particularly difficult for machines with two winding shafts, if due to large winding roll diameter, the two winding shafts no longer one above the other, but must be arranged one behind the other.
• If the winding shaft is to be installed in a turning system for a rapid change of bobbin, the so-called single spindle winding is particularly space-saving and inexpensive, since only one turning system is needed. In the turning system, although a second winding shaft is present. This is used in alternation with the first winding shaft for unloading and winding the bobbins. It never wind two winding shafts at the same time.
• The removal tools for the finished rolls are needed only once.

Despite these advantages, the known Einspindelwickelmaschinen can be used only limited in certain applications, as resulting from thickness variations of the material web diameter differences in the winding rollers can not be compensated.

From the DE 20 07 569 B is a slitter and winding machine for webs with a slitter for dividing the web into strips known. The roll cutting and winding machine further has a spreading device for diverging the strips, so that their longitudinal edges run parallel with each other at a distance from each other and is provided with a winding device for winding each strip on a sleeve which contains only one winding station with a single winding shaft.

It is also known from the US 5,464,168 A a web slitting and winding machine for webs with a slitter for splitting the web into strips and a winding device for winding this strip on a sleeve which includes a winding station with a winding shaft which is rotatably supported at both ends in the machine frame. Here, the winding shaft is mounted on a machine side in a bearing which is pivotable about an axis extending horizontally and transversely to the winding shaft axis.

A Friktionswickelwelle for slitter winder and winders with a central drive shaft, arranged on the circumference at a distance distributed longitudinal grooves with slidably mounted therein in the radial direction and preferably changing the pressure in each an inflatable pressure fluid hose controllable sliding axes are arranged, is from the DE 195 15 723 A1 known. Described herein are clamping elements that allow winding tubes to move freely on an axis and to fix.

Presentation of the invention

The invention has for its object to provide a slitter and winder that allows unrestricted rotatability of each winding roll for an individual diameter adjustment using only one winding shaft.

This object is achieved by the combination of the features according to the patent claim 1.
The expiring from the slitter strip strips are first separated by means of a spreading, so that they run in a decency of 0.5 - 1.5 millimeters. Due to the distance later, the winding rollers can not touch with their faces during winding.

Subsequently, the strips are wound on cores, which are clamped on the single winding shaft on individually rotatable friction elements with a distance corresponding to the distance of the strips from each other. The Friction elements are designed so that their clamping bodies, even if they are located exactly in the boundary region of two adjacent sleeves, do not cause a connecting effect between the adjacent sleeves. A connecting effect would prevent the free rotatability of a winding roll. To ensure this, the clamping body have no effective for a power transmission to the winding tube expansion in the axial direction of the winding shaft. Particularly suitable are balls as clamping body, which have only a punctiform clamping surface.

A further object is to improve a slitter rewinding and winding machine with a winding shaft so that winding rollers can be wound with a greater weight at very low deflection of the winding shaft.

The storage according to the invention for the winding shaft can be used particularly advantageously in a winding machine according to the claims 1 to 14, since this only contains a winding shaft. This winding shaft must therefore bear the weight of all bobbins.

Short description of the drawing

The drawing serves to explain the invention with reference to simplified illustrated embodiments.

Figur 1

die Seitenansicht einer erfindungsgemäßen Rollenschneid- und Wickelmaschine,

Figur 2

ausschnittsweise einen Längsschnitt durch die Wickelwelle, und

Figur 3

einen Querschnitt durch ein Friktionselement,

Figur 4

eine Draufsicht auf eine alternative Ausführungsform,

Figur 5

einen Schnitt durch ein Lager für die Wickelwelle.

Show it

FIG. 1

the side view of a roll cutting and winding machine according to the invention,

FIG. 2

partially a longitudinal section through the winding shaft, and

FIG. 3

a cross section through a friction element,

FIG. 4

a plan view of an alternative embodiment,

FIG. 5

a section through a bearing for the winding shaft.

Ways to carry out the invention

In the FIG. 1 shown slitting and winding machine is used for processing relatively thick, since at least two layers constructed material webs, especially based on paper. Such material webs have thickness variations that can not be compensated for when winding on their elasticity in the required for the winding quality dimensions. Each winding roll must therefore be able to rotate freely for an individual diameter adjustment.

In front of the slitter winder and unwinding an unwinding device is arranged in which a supply roll is suspended between support arms. The film 4 is withdrawn from the supply roll and fed by guide rollers 5 a longitudinal cutting device 6. In the longitudinal cutting device 6, the film 4 is divided by longitudinal sections into individual strips 7. Subsequent to the longitudinal cutting device 6 is followed by a spreading device 8, by means of which the strips 7 are guided apart, so that subsequently the longitudinal edges of the strips 7 parallel to a distance of at least 0.5 mm, preferably between 0.8 mm and 1.5 mm, to run. Preferably, as a spreading device 8, a so-called "dual spreader" is used, as it is for example in the DE-AS 20 07 569 or in the DE-OS 15 61 710 is described. Such dual spreaders contain two guide rollers 9, 10 or deflection strips arranged one behind the other, which extend with a curvature across the working width. The curvature of the inlet-side guide roller 9 causes the strips 7 run spread apart on the way to the outlet-side guide roller 10. The curvature of the outlet-side guide roller 10 causes the spaced strips 7 then parallel to each other, wherein the scoring achieved by the distance between two strips 7 is maintained. The strips 7, which run parallel to one another at a distance from one another, are fed to the subsequently arranged winding device, where they are wound onto sleeves 11.

The winding device includes at least one extending over the working width winding shaft 12, which is mounted with its ends on both sides of the machine. Preferably, the winding device is a so-called two-turn winding with two winding shafts 12, which are each mounted at their ends in pivoting elements. In the embodiment according to FIG. 1 two Schwenkarmpaare 13, 14 are arranged on each side of the machine, which are offset by 180 ° to each other. The Both Schwenkarmpaare 13, 14 are pivotable about a central axis 15 in the machine frame, so that they alternately from the winding position in the winding station ( FIG. 1 right) can be swiveled into an unloading position. In the unloading position, the lateral bearings of the winding shafts 12 can be opened at least on one side in order to pull off the finished winding rolls 16 from the winding shaft 12. At the in FIG. 1 illustrated embodiment, the pivot axis 15 extends within a fixed cross-beam 28, at both ends of which a respective pivot arm of a Schwenkarmpaares 14, 15 is mounted.

In FIG. 4 (Top view), the preferred embodiment is shown without a central cross-beam between the winding position and the unloading position. This embodiment is easy to use, as it allows an operator in case of failure unhindered access to the winding station and unhindered access to the bobbins.

To prevent the access of an operator from the operating side (In FIG. 4 right), the winding device does not include a crossbeam between the winding position and the unloading position. The two pivot arms are replaced on this side by a pivotable about the central pivot axis 15 two-armed pivot lever 29. At the free end of each arm of the pivot lever 29 is in each case a fork-shaped receptacle in which the end of a winding shaft 12 is detachably mounted. The pivot lever 29 is connected to its own pivot drive motor 30. The pivot drive motor 30 serves on the one hand to move a winding shaft 12 with finished wound reels 16 of the winding station in the unloading position, on the other hand, the pivot lever 29 can be placed without a winding shaft 12 in a vertical position, the access to an operator in the area between the two winding shafts 12 allows to remedy a fault on the winding rollers 17. The pivot lever 29 is thus pivotable independently of other elements. When winding the winding shaft 12 is held on the operating side not by the pivot lever 29, but by a disengageable bearing 31, which is arranged stationary in the machine frame. The structure of the preferred embodiment of the bearing 31 is shown in FIG FIG. 5 shown enlarged.

On the drive side (in FIG. 4 left), the two winding shafts 12 are mounted in a turning disc 32 which is mounted by means of its own pivot drive motor 33 about the central axis 15 pivotally mounted in the machine frame. The storage of Winding shafts 12 in the turning plate 32 is so stable that the winding shafts 12 are held without support on the other side by the pivot lever 29 or the bearing 31 in a horizontal position. After prior support of the winding rolls by a removal car, the finished bobbins 16 can be deducted in the unloading position on the operating side of a winding shaft 12. As a winding drives 32 two electric motors 46 are attached to the outside of the turning disk on the drive side, each rotate a winding shaft 12 and are pivoted with this from the winding position to the unloading position.

The pivotal movement of the pivot lever 29 is electrically synchronized with the pivotal movement of the turning disc 32, so that a winding roller 12 can be moved without being misjudged on one side evenly from the winding position to the unloading position and back. In addition, the pivot lever 29 can be pivoted on the operating side independently of the turning disc 32 to put it without winding shafts in a vertical position. Preferably, each winding shaft 12 is supported in the winding position on its non-drive side -soo the operating side- of a bearing pair designed as a bearing 31 which is pivotable about an axis 34 extending horizontally and transversely to the winding axis by an angle. A pivotable bearing 31 makes it possible to reduce the deflection of the winding shaft 12 due to the winding roll weight. For this purpose, the winding shaft 12 is bent against the direction of the weight bending by pivoting the bearing 31 about the axis 34 upwardly elastic.

In FIG. 5 a particularly advantageous embodiment of a bearing 31 is shown that in the direction of the arrow 35 is pivotable and in which the end of the winding shaft 12 is releasably secured. This camp 31 can be not only in the in the FIGS. 1 and 4 use shown double Wendeaufwicklungen, but in each winding machine with a winding shaft, which tends to sag as a result of the winding roll weight.

The bearing 31 has a bearing housing 36 which is pivotally mounted around the horizontally and perpendicular to the axis of the winding shaft 12 extending axis 34 and at the same time in and against the axial direction of the winding shaft 12 slidably in the machine frame of the winding device. Within the bearing housing 36, a clamping device is arranged, in which the end of the winding shaft 12 is releasably clamped. The clamping device includes a clamping cylinder 37, by means of two rolling bearings 38, 39 is rotatably mounted about the axis of rotation of the winding shaft 12. The front roller bearing 38 is arranged so that its plane of rotation passes through the axis of rotation 34. The rear roller bearing 39 is arranged at a distance from the front roller bearing 38, so that upon pivoting of the bearing housing 36, a sufficiently large torque is transmitted to the clamping cylinder 37. The clamping cylinder 37 has on its winding shaft 12 side facing a conical opening into which the fitting frusto-conical shaped end 39 of the winding shaft 12 can be inserted. At the end of the winding shaft 12, a pin 40 is fixed, whose end is widened like a bead. The opposite end of the clamping cylinder 37 has a bore in which a clamping piston 41 is mounted axially displaceable. The clamping piston 41 has at its inner end collets 42 which engage over the bead of the pin 40 of the winding shaft 12. The other, protruding from the clamping cylinder 37 end of the clamping piston 41 is pressed by a compression spring 43 to the outside, so that the collets 42 pull in the axial direction of the winding shaft 12 and so keep them under tension. For releasing the collets 42, a hydraulic piston-cylinder unit 44 is mounted on the outside of the bearing housing 36, the piston 45 presses the clamping piston 41 against the force of the spring 43 in the direction of the winding shaft 12. In this case, open the collets 42 and the bearing housing 36 with all attached thereto elements can be deducted from the end 39 of the winding shaft 12.

In order to pivot the bearing housing 36 about the axis 34, a pin is fixed on both sides in each case, which are rotatably mounted in the machine frame. So that upon an upward pivoting of the bearing housing 36 in the direction of the arrow 35 an upward bending force in the winding shaft 12 occurs, the axis of rotation 34 is in the direction perpendicular to the winding shaft axis plane through the front bearing 38th

The bend-generating pivoting of the bearing housing 36 is automatically readjusted as a function of the current winding roll weight or the current winding roll diameter via an actuator. The acting on the bearing housing 36 actuator carries out the pivoting movement either position-determined or force-determined. As the position determining actuator either a threaded spindle or a hydraulic cylinder is used. If the pivotal movement is performed force-determined, preferably a pneumatic piston-cylinder unit is used as an actuator.

If only small deflection forces occur, it may be sufficient to avoid bending of the winding shaft 12, that bearing housing 36 and set a mean pivoting angle fixed. The so-biased winding shaft 12 can accommodate larger bobbin weights without deflection.

In the winding position, the strips 7 are supplied to the arranged on a single winding shaft 12 winding rollers 17 via a contact roller 18 which is pressed against the circumference of the winding rollers 17 mounted in a movable carriage 19. In the carriage 19 and the longitudinal cutting device 6, the spreading device 8 and the web transporting devices are stored. As the winding roll diameter increases, the carriage with the devices fastened thereto is moved in the direction of the unwinding device 1, the contact roller 18 abutting the winding rollers 17 with the required contact pressure. The movable carriage 19 makes it possible to keep the position of the winding shaft 12 during winding stationary.

The bobbins 17 are wound on sleeves 11, which are mounted only on the winding shaft 12 located in the winding station. In the FIG. 2 shown winding shaft 12 is designed as a so-called Friktionswickelwelle. It has a central drive shaft 20, which is connected to a machine side with a rotary drive. Over the entire working width a plurality of annular friction elements 21 are arranged side by side on the drive shaft 20, whose structure in the Figures 2 and 3 is shown. Each friction element 21 consists of an annular friction body 22, the inner surface of which can slide over the lateral surface of the drive shaft 20. The friction body 22 are driven by a frictional engagement of the drive shaft 20. The frictional force can be adjusted by means of pressure hoses 23, which are arranged in axial grooves of the drive shaft 20. Between a pressure hose 23 and the friction body 22, a sliding strip 24 is in each case arranged in the axial groove, which is pressed by the pressure hose 23 to the outside against the friction body 23.

In the outer circumferential surface of each friction body 22, a series of radially outwardly extending ramps are incorporated, which serve as a guide surface for each of a ball 25. In the embodiment, six balls on the corresponding number of ramps over the circumference are evenly distributed in one to the winding shaft axis vertical plane arranged. The balls 25 are held by an annular cage 26. They can be moved by openings in the cage 26 by means of the ramps circumferentially out of the cage 26 out against the inner surface of a sleeve 11 and act as a clamping body which connect the friction body 22 frictionally with a sleeve 11. Such constructed Friktionswickelwelle is in the DE-OS 195 15 723 described.

Essential for the invention is that the clamping body (in the embodiment, the balls 25) have no effective for a power transmission to a sleeve 11 expansion in the axial direction of the winding shaft 12. This prevents two adjacent sleeves 11 are frictionally connected via a friction element 21. In FIG. 2 the extreme case is shown that the balls 25 of a friction element 21 are located exactly below the dividing line between two sleeves 11. Even in this case, no power transmission from a sleeve 11 to the adjacent sleeve 11 takes place, since the balls 25 are not able to form with both winding tubes 11 sufficiently large force transmission surfaces as a clamping body.

The measured in the axial direction of the winding shaft 12 width of a friction element is between 20 mm and 50 mm, preferably about 25 mm. So that sufficiently large torques can be transmitted from the drive shaft 20 in the circumferential direction, each sleeve 11 is held during winding with at least two friction elements 21.

As an alternative to balls 25 with a punctiform clamping surface, ring segments or other elements can be used as clamping body whose outer surface is designed so that no power transmission between two adjacent sleeves 11 is possible. Therefore, these clamp body also have no effective extension in the axial direction of the winding shaft 12th

In order to wind very heavy bobbins 17 with a large diameter, a bobbin support device 27 is arranged in the winding station. The supporting device 27, movable from below against the underside of the winding rollers 17, prevents the winding shaft 12 from bending during winding due to the weight of the winding roll. The support device 27 preferably consists of a plurality of individual support elements, such as, for example, narrow individual belts or individual support rollers 28 'with a soft covering. All Support elements are mounted on a beam 29 ', which is readjusted in dependence on the roll diameter in the vertical direction. To compensate for different diameters of the winding rollers 17, the individual support elements are also mounted individually movable in the vertical direction. The support device 27 may additionally or alternatively be used to a pivotally configured bearing 31 of the winding shaft 12.

Claims (14)

1. Slitter and winder for material webs having

   - a slitting apparatus (6) for dividing the material web (4) into strips (7),

   - a spreading apparatus (8) for guiding the strips (7) apart from one another, with the result that their longitudinal edges run in parallel at a spacing from one another, and

   - having a winding apparatus for winding each strip (7) onto an empty bobbin (11), which winding apparatus comprises only one winding station having a single winding shaft (12) which is designed as a frictional winding shaft and comprises a central drive shaft (20) and a multiplicity of annular friction elements (21) which are arranged next to one another on the drive shaft (20),

   - each friction element (21) having a friction body (22) which can be driven frictionally by the drive shaft (20) and outer clamping bodies (25) for a non-positive connection to an empty bobbin (11), and the clamping bodies (25) not having any extent in the axial direction of the winding shaft (12), which extent is active for transmitting force to an empty bobbin (11), characterized in that the winding shaft (12) is mounted on a machine side in a bearing (31) which can pivot about an axis (34) which extends horizontally and transversely with respect to the winding-shaft axis, and the winding shaft (12) in the bearing is mounted rotatably in a clamping apparatus by means of two bearings (38, 39), the bearing (38) which faces the winding shaft being arranged in such a way that its rotational plane extends through the rotational axis (34).
2. Slitter and winder according to Claim 1, characterized in that the clamping elements (25) have a punctiform clamping face, in particular are designed as balls.
3. Slitter and winder according to Claim 1 or 2, characterized in that the clamping bodies (25) are arranged on the friction body (22) in a plane which is perpendicular with respect to the winding-shaft axis.
4. Slitter and winder according to one of Claims 1 to 4, characterized in that the width of a friction element (21) as measured in the axial direction of the winding shaft (12) is between 20 mm and 50 mm, preferably approximately 25 mm.
5. Slitter and winder according to one of Claims 1 to 4, characterized in that the spreading apparatus (8) is designed in such a way that the longitudinal edges of the strips (7) are moved to a spacing of at least 0.5 mm, preferably between 0.8 mm and 1.5 mm.
6. Slitter and winder according to one of Claims 1 to 5, characterized in that a dual spreader having two deflection elements (9, 10) which are arranged behind one another and extend with a curvature transversely over the working width is used as spreading apparatus (8) .
7. Slitter and winder according to one of Claims 1 to 6, characterized in that the position of the winding shaft (12) is stationary during winding, and in that the slitting apparatus (6) and the spreading apparatus (8) are mounted in a displaceable carriage (19).
8. Slitter and winder according to one of Claims 1 to 7, characterized in that a supporting apparatus (27) which can be moved from below against the underside of the reels (17) is arranged in the winding station.
9. Slitter and winder according to one of Claims 1 to 8, characterized in that the winding apparatus comprises two winding shafts (12) which are mounted in each case at their ends on pivoting elements (13, 14, 29, 32) which can pivot about a central pivoting axis (15), by which pivoting elements (13, 14, 29, 32) the said winding shafts (12) are pivoted alternately from a winding position into a removal position.
10. Slitter and winder according to Claim 9, characterized in that the winding apparatus does not comprise a crossmember between the winding position and the removal position, and in that the pivoting elements (29, 32) have in each case a dedicated pivot drive (30, 33) on each machine side.
11. Slitter and winder according to Claim 10, characterized in that the pivoting movement of the pivoting elements (29) on one machine side can be synchronized electrically with the pivoting movement of the pivoting elements (32) on the other machine side.
12. Slitter and winder according to Claim 11, characterized in that the pivoting element (29) on the operating side can be pivoted additionally independently of the pivoting element (32) on the other machine side.
13. Slitter and winder according to one of Claims 1 to 12, characterized in that the bearing (31) comprises a clamping apparatus (41, 42, 43), in which the end (39) of the winding shaft (12) can be firmly clamped releasably under a tensile stress which acts in the axial direction.
14. Slitter and winder according to one of Claims 1 to 13, characterized in that the bearing (31) is pivoted as a function of the reel weight in a manner which is determined by position or force.

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