EP1460011B1 - Roll winder drum or roller of a press - Google Patents

Abstract

The roller has a contact area for another roller or a material length. It consists of two parts, which have a bearing in the joint. The joint (10) is bridged by a band (11). When in operational condition, the outer surface of the band within the contact area is aligned with the peripheral surface of the roller parts (8,9). One of the sections has a step (26) with reduced outer diameter in the area of the joint, and the band engages on the step. The band has a main body of metal, has a drive, and a toothed belt profile (29) or V-belt profile (27) on the inside.

Description

The invention relates to a Rollenwickler- or press roll having a contact area for a roll or track and which is divided in the axial direction into at least two sections which form a joint between them and are mounted in the region of the joint, wherein in the joint for each section each bearing is provided.

Such a roller is out WO 98/23514 A known.

The invention will be described below with reference to a roller for a reel winder. However, it is also applicable to other rolls where similar problems exist. Another preferred application is with a roll that uses a press for a fibrous web, particularly a paper or board web.

In a roll winding device, a winding roll, on which a paper or board web is wound, abuts the contact area on the roll. With the help of the roller, a contact pressure is exerted on the winding roll. This contact pressure is, inter alia, a parameter that influences the winding hardness. Upstream of a reel-winding device is usually a longitudinal cutting device with which an incoming web, which may have a width of up to 10 m, is subdivided into a plurality of sub-webs. These partial webs must be wound up at the same time. It is therefore necessary that the roller has at least the same width as the incoming web.

The speeds at which the roller is operated, are getting higher. Currently, peripheral speeds of 2,500 to 3,000 m / min are quite common. This causes the roll to come within the range of critical speeds. Operation in this speed range is undesirable because the roller tends to oscillate here.

One measure to change the critical speeds is to increase the diameter of the roller. The increase in diameter of the roller are set by certain geometric requirements limits. If the roll is used as a carrier roll in a double take-up roll winder, then it must not exceed a certain diameter. Otherwise, a winding tube, on which the material web is wound, would sink so deeply into the winding bed that it would no longer be reached by a pressure roller.

It has therefore in the aforementioned WO 98/23514 A Attempts to shift the limits of critical speeds by thinner rolls with smaller diameters, which are divided into at least two sections in the axial direction. The sections are in this case mounted at their two axial ends, that is to say also in the region of the joints arising between two roller sections.

However, this approach has the disadvantage that the continuous roll shell is interrupted at the joints. This can lead to undesirable phenomena for some types of material. When used in a reel winding device, this may for example lead to Wikkelfehlern, which are caused by the fact that in the region of the joint another pressure of the roller against the winding roll results than in the other areas.

EP 0 811 570 A2 shows a paper feeder and a rotor for it. The rotor has two sections, which are formed as a hollow cylinder, wherein the wall of the hollow cylinder is provided with openings. The two sections are mounted on a suction line, which has an opening in a region facing a paper sheet stack. If an opening in the sections of the rotor coincides with this opening in the suction line, then the corresponding opening in the rotor is subjected to negative pressure and can suck the uppermost sheet of a paper stack. A conveyor belt extends from the rotor tangentially in the conveying direction to supply the single sheet to a pair of rollers, with which the single sheet can be further promoted.

US 2 743 065 A describes a web winding machine for towels. The web runs over several adjacent and in the same direction encircling bands. The bands are guided at a certain distance from each other around pulleys. In the gaps between the bands in each case a further circulating belt is arranged, which is guided over the deflection roller and two further deflection rollers. This tape serves to lift the incoming web from the former bands to form a winding at all.

The invention has for its object to enable high speeds with small diameter of the roller.

This object is achieved in a roller of the type mentioned above in that the joint is bridged by a circulating belt, the outer surface is in the operative state in the contact region flush with the peripheral surface of the sections.

With this embodiment, it is possible to make the axial lengths of the individual sections so that the critical speeds are shifted even with relatively small diameter rollers upwards. In the area of the joint, there is basically no noticeable gap in the surface of the roll as a whole, at which the Railway is present. Accordingly, the joint does not create negative influences on the web. When using the roller in a reel winding winding errors are avoided by the joint.

Preferably, at least a portion in the region of the joint on a step with a reduced outer diameter and the tape is located on the step. This is a particularly simple embodiment to support the band. At the same time, the position of the band relative to the surface of the roller is defined.

Preferably, both sections have the step. In this embodiment, the band lies on its two longitudinal edges on the step, that is each supported on the adjacent portion of the roller. In addition to this support function, this embodiment has a further advantage. It is then possible with the aid of the belt to be able to couple the two sections of the roller together with respect to their rotational movement. This is an easy way to give the adjacent sections the same speeds, if you do not want to assign a separate drive to each section. Loads of the web, which could result from different peripheral speeds of the individual sections are avoided. The web is treated the same over the entire axial length of the roll.

Preferably, the reduction in the outside diameter of the step corresponds to the effective thickness of the belt in the operative tensioned state. The thickness of the band in operationally tensioned state is fixed.

It results from the thickness of the band, different material properties and the voltage present during operation. Incidentally, it can be determined experimentally relatively easily. The step can be easily made by twisting off at the respective axial ends of the sections, which fabrication is accurate enough to provide in operation a substantially continuous surface of the roller in the contacting section. The belt will leave the roller outside of the contact section. However, this is not critical because there is no contact with the web outside of the contact area.

Preferably, the band has a surface corresponding to the surface of the sections. The web is thus acted upon by the surface of the belt as well as by the surface of the sections. This also avoids that results in the region of the joint differences in the treatment of the web.

It is particularly preferred that the tape has a surface layer corresponding to a surface layer at the periphery of the sections. Thus, the similarity of the treatment is not simply limited to the properties on the surface. Further properties, for example the compression behavior of the surface layer of the sections, are transferred to the belt.

Preferably, the band has a base body made of metal. This embodiment has several advantages. For one, a band with a metal base is relatively stable. One can therefore expect a long life. On the other hand, one can then design the band with its surface layer basically exactly as the sections of the roller which as a rule also have a metallic basic body with an elastic surface layer. In the joint then results in virtually no noticeable change over the axial length of the roller.

Preferably, the belt has a drive. As stated above, it is difficult for several sections to uniformly drive the individual sections. This difficulty is elegantly overcome by using the tape to drive the two sections. For example, it is possible to provide a drive in a section of the belt outside the roller which transmits a corresponding drive power to the belt. The band, in turn, then transmits this drive power to the adjacent sections uniformly, which is of particular advantage.

Preferably, the band has a toothed belt profile on its inside. This toothed belt profile is engaged with a corresponding toothing on the sections of the roller. Such a toothing may for example be provided on the peripheral surface of the step, ie in the region of the diameter reduction. This also makes it possible to arrange the drive at the end of a roll section and to drive over the belt, the adjacent roller.

In an alternative embodiment it can be provided that the band has a V-belt profile on its inner side. Even with a V-belt profile relatively large drive power can be transmitted. Even if a drive does not take place over the belt, such profiles, ie toothed belt or V-belt profile, advantageous because they allow a defined engagement between the belt and the sections of the roller, which in turn can be used to a speed match between the sections of the To achieve roller.

Preferably, the band is guided through a gap in a support structure. The support structure serves to receive the bearings on which the roller sections are mounted. Of course, the support structure must not obstruct a circulation of the band. However, since the band has a relatively small thickness as seen in the radial direction of the portions of the roller compared to the diameter of the roller, it is sufficient to provide a gap in the support structure.

It is particularly preferred that the support structure is formed by a floor and the gap through a tunnel in the floor. The roller is thus on the storage of their individual sections on the floor. The tape is passed under the point of contact. The "ceiling" of the tunnel is sufficiently stable to support the roller sections. The tunnel therefore provides a path for the band in a simple manner.

Preferably, the two bearings can be removed and installed separately from each other. Individual sections of the roll can then be completely removed and installed with their storage.

It is particularly preferred that the two bearings have a planar guide surface which extends perpendicular to the axial direction. Thus, the sections can each be displaced perpendicular to the axial direction during installation and removal of the individual roller sections, for example by lifting, without interfering with each other projections on the bearings.

Fig. 1

eine schematische Seitenansicht einer Walze,

Fig. 2

eine Stirnseitenansicht eines Doppeltragwalzenwicklers,

Fig. 3

einen Schnitt III-III nach Fig. 1 und

Fig. 4

eine vergrößerte Darstellung der Walze im Schnitt.

The invention will be described in more detail below with reference to preferred embodiments in conjunction with the drawings. Herein show:

Fig. 1

a schematic side view of a roller,

Fig. 2

an end view of a double carrier roll winder,

Fig. 3

a section III-III after Fig. 1 and

Fig. 4

an enlarged view of the roller in section.

A roller 1, which in Fig. 2 is shown in connection with a Doppeltragwalzenwickler 2, forms with a second roller 3, a winding bed 4 in which a Wikkelhülse 5 is kept to a tapered material web 6, for example, a paper or board web, wind up.

The web 6 has a width of up to 10 m and a speed of up to 3,000 m / min. This results in that the rotational speeds of the rollers 1, 3 come into a critical range, which should be avoided as much as possible during operation.

How out Fig. 2 can be seen, any increase in the diameter of the rollers 1, 3 is not possible. Although this measure would continue to shift the critical speeds upwards. If the diameter of the rollers 1, 3 is too large, then the winding tube 5 drops too far in the winding bed 4, so that a loading roller 7 would not be able to a required for winding contact pressure on the winding tube 5 and to apply to the winding tube 5 building winding roll.

It is therefore possible to divide the roller axially into two sections 8, 9. Of course it is possible to use more than the two sections shown, if the axial length of the roller 1 so requires.

Between the two sections 8, 9 there is a joint 10, at which the sections 8, 9 of the roll 1 in the axial direction must have a certain distance, because they are stored there. This goes out Fig. 4 which will be discussed below.

A joint which causes a distance of a few centimeters between the sections 8, 9, for example, in a winding device is not acceptable, because the web 6 would not be supported in the region of the joint.

To remedy this problem, a band 11 is arranged in the joint 10, which bridges the joint 10. The outer surface of the belt 11 extends in the operational state, at least in a contact region 12 between the roller 1 and the winding tube 5 and the winding roll built thereon flush with the peripheral surface of the sections 8, 9. In the contact area therefore results in an axially continuous, virtually uninterrupted Surface of the Roller 1. The contact area may extend over a peripheral portion B (FIG. Fig. 3 ).

The sections 8, 9 are mounted on the two end faces of the roller 1 in bearings 13, 14. In the region of the joint 10 there are corresponding bearings 15, 16, so that each section is supported at both axial ends. The bearings 15, 16 are preferably designed as a fixed bearing so that changes in length of the roller sections can only affect the outside and not to the band out. The bearings 15, 16 are, just like the bearings 13, 14, on the floor 17 of a hall. If necessary, the bearings 15, 16 may each have a base 18, 19 which is supported on the floor 17 over a larger area.

In order to allow a circulation of the belt 11, a tunnel 20 is provided in the floor 17, through which the belt 11 is guided. This tunnel 20 is schematically shown in FIG Fig. 3 shown. There are two pulleys 21, 22 are provided which guide the belt 11. With the pulleys, the band can also be stretched.

Fig. 4 now shows the joint 10 with the band 11 in more detail. Same parts are denoted by the same reference numerals as in FIGS Fig. 1 to 3 Mistake.

The two sections 8, 9 of the roller 1 have a surface layer 23, which gives the surface of the sections 8, 9 a certain flexibility. A corresponding surface layer 24 is provided on the outside of the belt 11.

The band 11 may comprise a base body 25 made of metal. For example, the main body may be formed like a chain. It is only necessary that in the contact region 12, the band 11 of the curvature of the surface of the sections 8, 9 can follow.

The sections 8, 9 have at their ends in the region of the joint a step 26, which is formed by a reduction in the diameter of the sections 8, 9. At this stage 26, the band 11 is on. The band 11 has, in the ready state, when it is under a certain voltage, a thickness which corresponds exactly to a height h of the step 26.

The band 11 may have on its inside a V-belt profile 27 which cooperates with a corresponding spline 28 at the end of the section 8.

The band 11 can also, as on the right half of Fig. 4 is shown having a toothed belt profile 29 which cooperates with a corresponding toothing 30 on the circumference of the step 26 of the section 9.

Both profiles 27, 29 are able to cooperate with the sections 8, 9 slip-free or at least almost slip-free, so that not only the gap in the joint 10 is covered by the band 11, but also a coupling of the two sections 8, 9th is achieved, which causes both sections 8, 9 to rotate at the same peripheral speed.

You can also exploit the band 11 to drive the sections 8, 9. For this, as in Fig. 3 can be seen, a guide roller 21 provided with a drive 31. So you can drive the two sections 8, 9 from the axial center of the roller 1 ago.

In Fig. 4 It can be seen that the two bearings 15, 16 abut each other with a flat contact surface 32. So if you want to remove a section, then the band 11 is relaxed and moved to the peripheral surface of the non-excavated section. Thereafter, the section can be lifted vertically by a hall crane, without it with the camp the other section there are any conflicts.

The bearing 15 has a bearing ring 33 into which a pin 34 of the section 8 protrudes. Between the bearing ring 33 and the pin 34, a rolling bearing 35 is arranged. The rolling bearing 35 may also be replaced by a plain bearing. The bearing ring 33 is closed by a seal 35 on its side which is open towards the section 8. The bearing 16 is mirror-inverted constructed accordingly.

Between the band 11 and the sections 8, 9 even smaller gaps 36, 37 may remain. However, these gaps 36, 37 can be kept so small that they do not disturb or damage the web 6.

The roller 1 was shown with the bridged by the band 11 joint in connection with a reel winding device. However, it is obvious that such a roller can also be used in other applications, for example as a press roller with which a paper or board web can be dehumidified.

Claims (14)

1. Roll winder drum or press roll, which has a contact area for a roll or web and is subdivided in the axial direction into at least two sections (8, 9), which form a joint area (10) between themselves and are mounted in the region of the joint area (10), in each case a bearing (15, 16) being provided in the joint area (10) for each section, characterized in that the joint area (10) is bridged by a revolving belt (11), whose outer surface, in the operationally ready state, runs flush with the circumferential surface of the sections (8, 9) in the contact area (12).
2. Roll according to Claim 1, characterized in that at least one section (8, 9) in the region of the joint area (10) has a step (26) with a reduced external diameter, and the belt (11) rests on the step (26).
3. Roll according to Claim 2, characterized in that both sections (8, 9) have the step (26).
4. Roll according to Claim 2 or 3, characterized in that the reduction in the external diameter of the step (26) corresponds to the effective thickness of the belt (11) in the operationally ready tensioned state.
5. Roll according to one of Claims 1 to 4, characterized in that the belt (11) has a surface which corresponds to the surface of the sections (8, 9).
6. Roll according to Claim 5, characterized in that the belt (11) has a surface layer (24) which corresponds to a surface layer (23) on the circumference of the sections (8, 9).
7. Roll according to one of Claims 1 to 6, characterized in that the belt (11) has a basic body of metal.
8. Roll according to one of Claims 1 to 7, characterized in that the belt (11) has a drive (31).
9. Roll according to one of Claims 1 to 8, characterized in that the belt (11) has a toothed belt profile (29) on its inner side.
10. Roll according to one of Claims 1 to 8, characterized in that the belt (11) has a V-belt profile (27) on its inner side.
11. Roll according to one of Claims 1 to 10, characterized in that the belt (11) is led through a gap (20) in a supporting structure (17).
12. Roll according to Claim 11, characterized in that the supporting structure (17) is formed by a floor and the gap (20) by a tunnel in the floor.
13. Roll according to one of Claims 1 to 12, characterized in that the two bearings (15, 16) can be removed and installed separately from each other.
14. Roll according to Claim 13, characterized in that the two bearings (15, 16) have a level guide surface (32) which extends at right angles to the axial direction.

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