EP1941096A1

EP1941096A1 - Expander roller

Info

Publication number: EP1941096A1
Application number: EP06764142A
Authority: EP
Inventors: Josef Kerschbaumer; Georg Gobec; Norbert Gamsjaeger; Benno Bader; Thomas Gruber-Nadlinger
Original assignee: Voith Patent GmbH
Current assignee: Voith Patent GmbH
Priority date: 2005-09-20
Filing date: 2006-07-12
Publication date: 2008-07-09
Also published as: CA2623185A1; US20080207419A1; WO2007033844A1; US7862492B2; DE102005044957A1

Abstract

The invention relates to a roller (10) for a web processing machine, comprising a supporting core (16) which is supported in the region of both ends thereof via a respective bearing (14), and an outer covering (18) whereby the central area thereof (20), when seen in an axial manner, is mounted in a radially fixed manner in relation to the supporting core, and both ends thereof are supported by an additional bearing (22) in a radially displaceable manner in relation to the supporting core. The central plane (26, 28) extends in the radial direction, and the supporting core bearing and also the outer cover bearing are arranged in an axial manner inside the outer cover. The outer cover in the region of both ends thereof can be adjusted, respectively, by an actuator (30) which is arranged inside the outer cover.

Description

Spreader roll

The invention relates to a roller for a web-processing machine. This may in particular be a machine for producing a fibrous web, in particular paper, board or tissue web. The invention also relates to a web-processing machine having such a roller.

So far, arrangements are provided for the web guide in web-processing machines, in which in particular guide, regulating and spreader rollers are arranged successively. Such a conventional arrangement is shown, for example, in FIG. 1, in which, in the web running direction L, a guide roller 54 and a spreader roller 56 are successively arranged in front of a pair of press rollers 52. In the left part of Figure 1, this arrangement is shown in side view and in the right part in plan view.

Disadvantage of these known arrangements include high investment and maintenance costs.

Due to the simple construction of a guide roller whose components are indeed extremely inexpensive. The disadvantage, however, is that the web run can be adversely affected due to a deflection of the guide roller.

Spreader rolls are used in web-processing machines in order to avoid wrinkling or sagging due to spreading of the material web while the material web is running. Furthermore, spreader rollers are used to guide side by side juxtaposed material webs apart. Parallel juxtaposed webs can For example, be produced by slitting a wide web. Such wide-section rollers are known for example from DE 199 27 897 A1 and DE 10 2004 045407 A1.

Spreader rolls often consist of several individually mounted segments, which bring a high maintenance and are correspondingly costly. In general, the maintenance costs of such a spreader roller make up about 60% of the original price. In addition, the usual spreading rollers have a very slim design and accordingly a low load capacity, so that use as a guide roller is excluded.

Although the most recent designs of spreader rolls based on high-performance plastics have optimized curvatures. However, they have the disadvantage that the constructions in question are not stored without torque, i. the stiction of the machine in question, for example paper machine, is undesirably loaded. For new systems, the occurring moments must be taken into account, which requires costly reinforcements. For existing systems even more complex auxiliary structures are required.

The invention has for its object to provide an improved roller of the type mentioned, in which the aforementioned problems are eliminated. In this case, the roller concerned should be able to fulfill several of the aforementioned functions at the same time. In addition, in particular, the moments introduced into the staging should be reduced to a minimum.

This object is achieved according to the invention by a roller for a web-processing machine, with a supported in the region of its two ends via a respective support core and an outer shell, which is mounted radially immovably in its axially middle region relative to the support core and in the Area of its two ends via a respective further storage relative to the support core is supported radially adjustable, wherein the radially extending center plane of both the Stützkernlagerung and the Außenmantella- delay axially within the outer shell and the outer shell in the region of its two ends in each case by a preferably arranged within the outer shell actuator is adjustable.

Due to this design, the roller concerned can simultaneously perform the functions of at least two different types of rollers. By corresponding omission of a roller is saved according to space. In general, a cost-saving design is possible.

The combination of at least two functions in a roll brings, as already mentioned, the advantage of considerable cost reductions. In particular, the installation space of the functional group is reduced, the screening and felt costs are reduced, and fewer replacement rollers have to be kept ready, whereby the maintenance expenditure and / or the expense of spare parts inventory is correspondingly reduced. Finally, there is less product diversity, which also reduces costs.

In particular, the torque introduced into the stool is reduced to a minimum, and in the optimal case, it can even be brought to zero. By also the actuator is disposed within the outer shell, resulting in a compact adjustment, which makes it possible to reduce the forces for the position and to control the forces occurring.

According to a preferred practical embodiment of the roller according to the invention, the actuators are adjustable or controllable in such a way that the functions of at least two of the following types of rollers are simultaneously fulfilled by one roller: Spreader roll Guide roll

Regulating roller, in particular web guiding or a kind of deflection adjustment roller - tensioning roller.

Advantageously, the actuators are so adjustable or controllable that at the same time the functions of a guide roller and a spreader roller are met with the one roller.

It is also particularly advantageous if the actuators are adjustable or controllable in such a way that the functions of a guide roller and a tension roller are simultaneously fulfilled by one roller.

According to a further preferred embodiment, the actuators are so adjustable or controllable that at the same time the functions of a guide roller and a control roller are met with the one roller.

In particular, such an embodiment is also conceivable in which the actuators are adjustable or adjustable in such a way that the functions of a spreader roller and a control roller are simultaneously fulfilled by one roller.

In a further expedient embodiment of the roller according to the invention, the actuators are so adjustable or controllable that at the same time the functions of a spreader roller and a tension roller are met with the one roller.

A further expedient embodiment is characterized in that the actuators are adjustable or controllable in such a way that the functions of a tensioning roller and a control roller are simultaneously fulfilled by one roller. In order to minimize occurring static loads and unwanted vibrations, the roller preferably has an outer diameter> 280 mm, in particular> 300 mm and preferably> 320 mm. Optionally, this achieves a stable spreading effect.

In particular for the fulfillment of the functions of a spreader roll, the actuators are advantageously at least so adjustable or controllable that the roll is curved and pivoted into the web.

In particular for the fulfillment of the functions of a guide roller and / or a control roller, the actuators are expediently at least so adjustable or controllable that a deflection of the roller due to its own weight and / or due to the web tension is at least substantially compensated.

The actuators are preferably adjustable or controllable as a function of the various operating states in the respective installation situations. Thus, for example, a tension roller can be adjusted via the actuators in accordance with the particular circumstances and requirements in the desired manner. The same applies to the other types of rollers.

In particular for the fulfillment of the functions of a web guiding roller, the actuators can advantageously be differently adjusted or controlled on the operating side and on the driver's side, in order to bring about an imbalance of the roller.

It can therefore be realized by a separate, independent setting of the end portions of the roller another function, namely a regulating roller. The actuator is advantageously arranged radially between the support core bearing and the outer jacket bearing.

In a preferred practical embodiment of the roller according to the invention, the actuator is supported on the stool.

Advantageously, the actuator comprises at least one eccentric, wherein preferably two mutually supported eccentrics are provided.

Conveniently, the two eccentrics are jointly and / or separately adjustable.

With such an eccentric arrangement, the position of the curvature height or the extent of the curvature and / or the position of the curvature plane can each be set separately or jointly or simultaneously.

With respect to a possible moment-free storage, it is advantageous if the respectively extending in the radial direction middle planes of the support core bearing and the outer shell storage at least substantially coincide. Advantageously, therefore, an aligned or symmetrical arrangement of the support core bearing and the outer shell bearing is provided.

A preferred practical embodiment of the roller according to the invention is characterized in that the support core bearing and the outer jacket storage each comprise only one bearing and that the support core bearing and the outer shell bearing are arranged at least substantially in a common radial plane. Advantageously, the support core storage and / or the Außenmantellage- tion also each comprise two or more bearings.

If the outer casing bearing comprises two or more bearings, the center plane of this outer casing bearing extending in the radial direction expediently coincides at least substantially with the center plane of the supporting core bearing extending in the radial direction. If the support core bearing is formed only by a bearing, then this support core bearing is preferably arranged at least substantially in the radially extending center plane of the outer sheath bearing.

Basically, however, the support core storage include two or more bearings. In this case, the bearings of the outer jacket bearing and the bearings of the support core bearing are advantageously arranged symmetrically with respect to a radial plane common to the two bearings.

If the support core bearing comprises two or more bearings, the center plane of this support core bearing extending in the radial direction expediently coincides at least substantially with the middle plane of the outer jacket bearing extending in the radial direction.

If, in this case, the outer casing bearing comprises only one bearing, then this outer casing bearing is advantageously arranged at least essentially in the center plane of the supporting core bearing extending in the radial direction.

If the outer casing bearing also comprises two or more bearings, then the bearings of the support core bearing and the bearings of the outer casing bearing are advantageously again arranged symmetrically with respect to a radial plane common to the two bearings. The corresponding arrangement of the bearings and / or the actuator results in a very rigid structure, which is particularly insensitive to vibrations. Nevertheless occurring vibrations can be at least reduced by suitable damping elements. Thus, in a preferred practical embodiment, damping means are provided between the support core bearing and the outer jacket bearing. In this case, a viscous liquid is preferably introduced into the cavity between the support core storage and outer shell storage.

It is also conceivable, for example, to provide a membrane in the area between the support core bearing and the outer jacket bearing.

Alternatively or additionally, it is advantageous if the roller is fastened to the chair via vibration-damping elements. Alternatively or additionally, it may in particular also be attached to the stool via actively damping hydraulic elements.

Due to the small installation space, it may be necessary to use small bearings and preferably bearings, which combine the bearing function and an angle-compensating function in itself. The support core bearing and / or the outer jacket bearing preferably each comprise at least one angle-compensating bearing.

In particular with larger forces, the support core bearing and / or the outer jacket bearing advantageously comprise in particular at least one conical, cylindrical or barrel roller bearing, which, since these do not permit angular adjustment, must be supported in such a way that an angular adjustability of the outer jacket axis and / or the Support core axis is guaranteed. In a preferred practical embodiment of the roller according to the invention, the support core is rotatable together with the outer jacket. In this case, the outer jacket is preferably connected rotationally fixed to the support core.

In principle, however, such embodiments are conceivable, for example, in which the support core is not rotatable about its longitudinal axis.

It is also particularly advantageous if, viewed in the axial direction, the support core has an at least sectionally different cross-sectional shape. In this case, the support core may have, in particular at least in sections, a cross-sectional shape tapering conically towards its ends.

In the case of the roller according to the invention, the force flow which is caused by the corresponding structure and the loads occurring is thus transmitted as directly as possible and without auxiliary structures between the two bearings.

The web-processing machine according to the invention is characterized in that it comprises at least one roller according to the invention and a preferably electronic control and / or regulating device, via which the actuators of the roller can be controlled accordingly.

In this case, preferably at least one sensor for determining the web position is connected to the control device, so that the web position can be regulated via this control device that actuates the actuators.

Advantageously, at least one position sensor integrated in the roller is provided. Appropriately, at least one position sensor is provided in the two edge regions of the web. In particular, in each case at least one position sensor can be integrated into the two end regions of the roller.

In principle, however, at least one position sensor arranged outside the roller can also be provided.

In accordance with a further advantageous embodiment of the machine according to the invention, at least one sensor for determining the web tension is connected to the control device, so that the web tension can be regulated via this control device that actuates the actuators.

Preferably, at least one web tension sensor integrated into the roller is provided.

However, at least one web tension sensor arranged outside the roller is also conceivable.

The sensors in question may, for example, be optical sensors, pressure sensors, mechanical sensors and / or the like.

The roller according to the invention is thus preferably usable as a universal roller which simultaneously fulfills the functions of at least two of the following types of roller: spreader roller, guide roller, control roller, in particular web guiding or deflection adjustment roller, tension roller.

To monitor the bearings of the roller further may be provided a vibration sensor which detects the vibration state of the roller and the measured vibration values, for example, a control system zuleitet, which dampens the vibrations by suitable means.

The invention will be described in more detail below with reference to exemplary embodiments with reference to the drawing; in this show:

FIG. 1 shows a schematic representation of a conventional arrangement in which a guide roller and a spreader roller are arranged in succession in the web running direction in front of a pair of press rollers,

FIG. 2 shows a schematic longitudinal sectional view of a roller according to the invention with associated stiffening,

FIG. 3 shows a diagrammatic cross-sectional view of an actuator of a roller according to the invention in the zero position comprising a double eccentric,

FIG. 4 shows a diagrammatic cross-sectional view of the actuator comprising a double eccentric of an inventive device

Roller in a maximum deflection effecting setting,

5 is a schematic cross-sectional view of one end of a roller according to the invention with associated support core bearing, outer shell bearing and actuator, and with a worm gear associated with the actuator, FIG.

FIG. 6 shows a partially sectioned schematic side view of the roller end according to FIG. 5, Figure 7 is a simplified schematic cross-sectional view of a

End of a roller according to the invention with associated actuator in relation to the outer jacket position in the region of the web center at different settings of the actuator,

FIG. 8 shows a schematic longitudinal sectional illustration of one end of the roller according to the invention according to FIG. 2, the support core bearing and the outer jacket bearing each comprising only one bearing,

FIG. 9 is a view comparable to FIG. 8, but with the support core bearing comprising two bearings;

FIG. 10 is a view comparable to FIG. 8, but with the outer jacket bearing comprising two bearings;

FIG. 11 shows a schematic illustration of a wafer according to the invention arranged in the web running direction in front of a further roll, which at the same time has different functions

Roller types met, and

Figure 12 is a schematic representation in which two arrangements b) and c), in each of which a function of several different types of rolls fulfilling roller according to the invention is arranged in the web running direction in front of another roller, an arrangement a) are compared with a conventional guide roller. FIG. 2 shows, in a diagrammatic longitudinal section, a roller 10 with associated stiffening 12. This roller 10 can be used in particular in a web-processing machine, in particular a paper machine. In this case, this roller is preferably used as a spreader roller, guide roller, control roller, in particular web-run control or a kind of deflection adjustment and / or as a tensioning roller. At the same time, it preferably simultaneously fulfills the functions of at least two of the mentioned types of rolls.

As can be seen with reference to FIG. 2, the roller 10 comprises a support core 16 supported in the region of its two ends by a respective bearing 14 and an outer jacket 18.

The outer casing 18 is mounted radially non-displaceable in its axially central region 20 relative to the support core 16 and supported radially adjustable in the region of its two ends via a respective further bearing 22 relative to the support core 16.

As can be seen from FIG. 2, the center plane 26 and 28 extending in the radial direction of both the support core bearing 14 and the outer casing bearing 22 lies axially within the outer casing.

In the region of its two ends of the outer sheath 18 is in each case adjustable by a disposed within the outer shell 18 actuator 30, which is arranged radially between support core storage 14 and outer shell bearing 22. This actuator 30 is supported on the frame 12 and variably adjustable by means of a pivoting, in particular worm gear 32 to be described in greater detail below. In addition, FIG. 2 shows a material web 34 guided over the roller 10, which can be, for example, a paper, board or tissue web.

This material web 34 brings about the corresponding web train with a constant load 36, which leads only to a small introduced into the chair 12 tilting moment.

The actuator 30 comprises two mutually supported eccentric, which can be adjustable together or separately.

In the illustrated state, the roller is bent. For this purpose, the supporting core is displaced by the actuator comprising the two eccentrics. The force for lifting the support core is introduced in the inner eccentric. The outer jacket is curved with the force and is supported on the outer jacket bearings. Since these lie in one plane, no moment arises. Prerequisite for this are swiveling bearings.

If the roller to take their unbent neutral position, so the actuator is to be adjusted so that the eccentricity of the inner eccentric is offset by 180 ° with respect to the eccentricity of the outer eccentric.

As bearings bearings, etc. are provided in the present case, for example, spherical roller bearings. As can be seen with reference to FIG. 2, the outer jacket bearing provided at the left-hand end of the roll is a loose bearing and the outer jacket bearing provided at the right-hand roll end is a fixed bearing. The support tube bearings are each formed by a floating bearing.

FIG. 3 shows, in a schematic cross-sectional representation, the actuator 30 comprising the two eccentrics 30 ', 30 "in a zero position, in which the maximum explosion rate The axis 38 of the circular-cylindrical boundary surface 40 between the two eccentrics 30 ', 30 "is thus here by an amount" e "relative to the axis 42 of the support core bearing 14 after moved up, which also results in a corresponding positioning of the outer casing bearing 22 and thus the respective roll shell end.

4 shows a representation comparable to that of FIG. 3, but in the present case the actuator 30 comprising the two eccentrics 30 ', 30 "is set in such a way that a maximum deflection results, whereby the extremities of the two eccentrics 30', 30" fall. together. Accordingly, here the axis 38 of the circular cylindrical boundary surface 40 between the two eccentrics 30 ', 30 "relative to the axis 42 of the support core bearing 14 by the amount" 2e ", for example, moved to the left, causing again a corresponding displacement of the outer shell bearing 22 and thus the relevant Walzenmantelendes results.

The extremities of the two eccentrics 30 ', 30 "are therefore the same size.

5 shows, in a diagrammatic cross-sectional view, a roller end with associated supporting core bearing 14, outer casing bearing 22, actuator 30 and a double pivoting mechanism (cf. also FIG. 5) for adjusting the two eccentricities 30 ", 30" of the actuator 30.

In view of the small available installation space, in particular small bearings are used, preferably bearings, for example self-aligning bearings, which combine the bearing function and the angle-compensating function in one. If the forces continue to increase, preferably conical, cylindrical or barrel roller bearings (also several) are provided, which however must be supported in such a way that a Angle variability of the axis of the outer jacket 18 and / or the axis of the support core 16 can be ensured.

FIG. 6 shows the end of the roll in a partially sectioned schematic side view.

As can be seen in FIGS. 5 and 6, the two eccentrics 30 ', 30 "are each connected to a worm gear 46', 46" via an eccentric shaft 44 ', 44 ", to which a respective worm shaft 48', 48" is assigned. over which the two eccentrics 30 ', 30 "are rotatable together or separately.

As best seen with reference to FIG 5, by rotating the eccentric 30 ', 30 "is a corresponding adjustment of eccentricity and position of the respective roll end.

FIG. 7 shows, in a simplified schematic cross-sectional illustration, a roll end with associated actuator 30 in comparison to the outer jacket position in the region of the center of the web at different settings of the actuator 30.

In this figure 7, the neutral line of the outer jacket 18 is designated by "50". In addition, in the various sections a) to d) in addition to the two eccentrics 30 ', 30 "of the actuator 30 of the support core 16 and the outer shell 18 can be seen, with 18' the position of the outer shell 18 at a respective roll end and 18" the position of the outer jacket 18 is shown in the middle of the track.

According to FIG. 7 a), the two eccentrics 30 ', 30 "are adjusted such that the maximum curvature of the outer jacket 18 points downwards and the outer jacket 18 is offset upwards in the region of the two roll ends. According to FIG. 7b), the two eccentrics 30 ', 30 "are adjusted such that the maximum curvature of the outer jacket 18 points upwards and the outer jacket 18 is offset downwards at the roll ends.

According to FIG. 7c), the two eccentrics 30 ', 30 "are adjusted such that no casing curvature occurs and the outer casing is offset downwards.

According to FIG. 7d), the two eccentrics 30 ', 30 "are adjusted such that no casing curvature results and the outer casing 18 is offset upwards.

In the two cases cited in FIGS. 7c and 7d, the outer jacket 18 is inclined without curvature relative to the support core 16. As a result, with the spreader roller and a control function can be realized.

Of course, it is also conceivable that the outer sheath 18 is simultaneously curved relative to the support core 16 and at the same time is inclined to the support core 16.

FIG. 8 shows, in a schematic longitudinal section, one end of the spreader roll 10 according to FIG. 1.

In this case, the support core bearing 14 and the outer jacket bearing 22 each comprise only one bearing. In this case, the support core bearing and the outer shell bearing are arranged in a common radial plane. The outer shell bearing is larger in size than the support core bearing. In this case, the center planes 26 and 28 of the support core 14 and of the outer jacket bearing 22 extending in the radial direction respectively fall together. In this Figure 7 again the outer jacket 18, the support core 16 and the actuator 30 can be seen.

In some designs of bearings, it may be conceivable that the normally stronger outer tube bearing by smaller rollers, etc. on the approximately the same Load capacity as that of the inner tube bearing is brought. Thus, at low curvature both bearings have an approximately equal minimum load whereby a roll of inner and outer tube bearing is given, ie a bearing destroying sliding of the rolling elements is reduced or largely prevented.

This results in a favorable arrangement, since a direct support leads to a reduction of the load on the intermediate sleeves or eccentrics and allows a very rigid low-vibration design.

This arrangement can only be realized if the resulting due to the roll diameter and the outer sheath bearing size outer diameter of the support core bearing is still possible for bearings with corresponding load ratings.

9 shows a representation comparable to that of FIG. 8, but in the present case the support core bearing 14 comprises two axially spaced bearings 14 ', 14 ". Here, too, the outer jacket bearing 22 is formed only by a bearing.

While the right-hand bearing 14 "of the support core bearing 14 is disposed within the outer shell 18, the left bearing 14 'lies outside of this outer shell 18. However, the mid-plane 26 of this support core support 14 still lies within the outer shell 18. The bearing of the outer shell bearing 22 is again larger dimensions than the bearings 14 ', 14 "of the support core bearing 14.

As can be seen with reference to FIG. 9, the center plane 26 of the support core bearing 14, which extends in the radial direction, coincides with the radially extending center plane 28 of the outer jacket bearing 22. Again, the two eccentric 30 ', 30 "comprehensive Akutator again radially between the two bearings 14', 14" comprehensive support core bearing 14 and the outer shell bearing 22 is arranged.

When using bearings of different sizes, the axial distances x and y may differ to achieve a load distribution in relation to the load capacity of the bearings.

With an inclination of the roller, a corresponding oblique position of the bearings must be possible for freedom of moment. This can be done either directly by selecting an angularly adjustable bearing or, as required for example in a double arrangement, by an area in the force introduction plane, which leaves an inclined position, as is the case for example with a spherical surface.

The arrangement of the outer shell bearing 22 shown in Figure 9 can also be realized by two or more bearings. Similarly, the number of core support is not limited to two camps. The direct support and adjustment of the example shown Doppelexzenterlagerung must be carried out when using two or more bearings per axis of rotation by appropriately vigorously designed bearing housing internally redirect the force to two or more bearings and therefore burdened by an internal moment.

FIG. 10 shows a representation comparable to FIG. 8, but in the present case the outer casing bearing 22 comprises two bearings 22 ', 22 ".

The bearings 22 ', 22 "of the outer jacket bearing 22 are dimensioned larger in the present case than the support core bearing 14 formed again only by a bearing. In the present case, both the support core bearing 14 and the outer jacket bearing 22 are each completely within the outer jacket 18.

As already mentioned, the support core bearing 14 in the present case comprises only one bearing. As can be seen from FIG. 10, this support core bearing is arranged in the radially extending center plane 28 of the outer casing ply 22. Here again, the center plane 28 of the outer casing bearing 22 extending in the radial direction coincides with the center plane 26 of the supporting core bearing 14 extending in the radial direction.

In principle, such embodiments are conceivable in which both the support core bearing 16 and the outer shell bearing 22 are each composed of two or more bearings. Such designs, each with two or more bearings are used to achieve a higher overall bearing load capacity, and / or they are used in the case that the radially available space for an arrangement of radially nested bearings is not sufficient.

The support core 16 may be rotatable together with the outer shell 18. In this case, the outer sheath 18 may be rotatably connected to the support core 16. In principle, however, such designs are conceivable in which the support core 18 is not rotatable about its longitudinal axis.

As can be seen with reference to FIG. 2, the support core 16 viewed in the axial direction may have an at least sectionally different cross-sectional shape. In the present case, this support core 16 has, at least in sections, a cross-sectional shape tapering conically towards its ends.

FIG. 11 shows, in a schematic representation, a roller 10 according to the invention which is arranged in front of another roller 58 in the direction of travel of the web and which at the same time serves as the roller Functions of several different types of rolls met. In this case, the left part of Figure 11 shows a plan view and the right part of this figure 11 is a side view of the relevant arrangement.

As shown in FIG. 11, the roll according to the invention can be used simultaneously, for example, as a spreader roll and controlled roll.

The actuators 30 (see also Figures 1 to 10) may therefore be at least as adjustable or controllable, in particular to fulfill the functions of a spreader roller that the roller is curved and pivoted into the web, while on the other hand in particular to fulfill the functions of Rule or web guide roller on the drive side and on the driver's side are different adjustable or can be controlled to cause a misalignment of the roller. The two actuators 30 can thus be adjusted for example on the drive side and on the driver's side so that the curvature remains constant, but the axis of the support core is adjusted to the opposite direction control of the actuators at the two roll ends.

FIG. 12 shows, in a schematic representation, an arrangement a) with a conventional guide roller 60, which is arranged in the web running direction L in front of a further roller 62. This conventional arrangement is compared with two arrangements b) and c), in each of which a roller 10 according to the invention fulfilling the functions of several different types of roller is arranged in the web running direction L in front of a further roller 64.

In the left part of Figure 12, the respective slack of the rollers 10, 60 can be seen. In the middle of Figure 12, the respective arrangements a) to c) are each shown in a side view. In the right part of Figure 12, the orders are again shown in plan view. As can be seen with reference to FIG. 12a), in the case of the arrangement comprising the conventional guide roller, a sag caused by the weight g and a web tension are produced, wherein the paper or the web 66 is compressed.

In contrast, Figure 12b) shows a compensated roller 10 according to the invention without sag, which simultaneously fulfills, for example, the functions of a guide roller and a control roller. The actuators 30 (cf., again, FIGS. 1 to 10) are thus also at least adjustable and / or controllable again such that a deflection of the roller 10 due to its own weight and / or due to the web tension is at least substantially compensated. The roller 10 is again arranged in the web running direction L in front of a further roller 62.

FIG. 12c) again shows an arrangement in which a roller 10 according to the invention fulfilling the functions of several different types of roller is arranged in the web running direction L in front of the further roller 62. In the present case, the actuators 30 provided at the two roll ends (see again FIGS. 1 to 10) are adjustable or controllable in such a way that the functions of a guide roll and a spreader roll are fulfilled simultaneously with the roll 10. As can be seen in this figure 12, results in the present case, a deflection of the roller 10 upwards or to the web 66 out.

LIST OF REFERENCE NUMBERS

10 roller

12 strangulation

14 support core bearing

14 'camp

14 "camp

16 support core

18 outer jacket

20 middle range

22 outer sheath storage

26 center plane of the support core bearing

28 middle plane of the outer jacket storage

30 actuator

30 'eccentric

30 "eccentric

32 swivel gear, worm gear

34 material web

36 DC load

38 axis

40 circular cylindrical interface

42 axis of the support core bearing

44 'eccentric shaft

44 "eccentric shaft

46 'worm gear

46 "worm gear

48 'worm shaft

48 "worm shaft

50 neutral line of the outer jacket

52 press roller pair guide roll

Spreader roller further roller

guide roll

roller

train

Web direction

Claims

claims

1. roller (10) for a web-processing machine with a supported in the region of its two ends via a respective bearing (14) supporting core (16) and an outer casing (18) in its axially central region (20) relative to the support core (16 ) radially non-displaceably mounted and in the region of its two ends via a respective further bearing (22) relative to the support core (16) is supported radially adjustable, wherein extending in the radial direction center plane (26 bzw.28) both the Stützkernlagerung (14) and the outer casing bearing (22) lies axially inside the outer casing (18) and the outer casing (18) lies in the region of its two

Ends in each case by a preferably within the outer shell (18) arranged actuator (30) is adjustable.

2. Roller according to claim 1, characterized in that the actuators (30) are adjustable or controllable such that the functions of at least two of the following types of rollers are simultaneously fulfilled by one roller:

- Spreader roll - Guide roll

- Regulating roll, in particular Bahnlaufregel- or deflection adjustment

- tension roller.

3. Roller according to claim 2, characterized in that the actuators (30) are adjustable or controllable in such a way that the functions of a guide roller and a spreader roller are fulfilled simultaneously with the one roller.

4. Roller according to claim 2 or 3, characterized in that the actuators (30) are adjustable and / or controllable in such a way that the functions of a guide roller and a tension roller are simultaneously fulfilled by one roller.

5. Roller according to one of the preceding claims, characterized in that the actuators (30) are adjustable and / or controllable such that the functions of a guide roller and a control roller are simultaneously fulfilled by one roller.

6. Roller according to one of the preceding claims, characterized in that the actuators (30) are adjustable and / or controllable in such a way that the functions of a spreader roller and a roller are simultaneously controlled by one roller

Regulating roll are satisfied.

7. Roller according to one of the preceding claims, characterized in that the actuators (30) are so adjustable or controllable that the functions of a spreader roller and a tension roller are simultaneously fulfilled by one roller.

8. Roller according to one of the preceding claims, characterized in that the actuators (30) can be adjusted or controlled in such a way that the functions of a tensioning roller and a control roller are fulfilled simultaneously with the one roller.

9. Roller according to one of the preceding claims, characterized in that it has an outer diameter> 280 mm.

10. Roller according to claim 9, characterized in that it has an outer diameter> 300 mm.

11. Roller according to claim 10, characterized in that it has an outer diameter> 320 mm.

12. Roller according to one of the preceding claims, characterized in that the actuators (30) are at least as adjustable or controllable, in particular for the fulfillment of the functions of a spreader roller, that the

Roller is curved and swung into the track.

Roller according to one of the preceding claims, characterized in that the actuators (30) in particular for the fulfillment of the functions of a

Guide roller and / or a control roller are at least as adjustable or controlled that a deflection of the roller due to its own weight and / or due to the web tension is at least substantially compensated.

14. Roller according to one of the preceding claims, characterized in that the actuators (30) are adjustable or controllable depending on the various operating conditions in the respective installation situations.

15. Roller according to one of the preceding claims, characterized in that the actuators (30) are in particular for the fulfillment of the functions of a web guide roller on the drive side and on the driver's side differently adjustable or controllable to cause a misalignment of the roller.

16. Roller according to one of the preceding claims, characterized in that the actuator (30) is arranged radially between the support core bearing (14) and outer jacket bearing (22).

17. Roller according to one of the preceding claims, characterized in that it e e e c e e n e that the actuator (30) on a chair (12) is supported.

18. Roller according to one of the preceding claims, characterized in that the actuator (30) comprises at least one eccentric (30 ¹ , 30 ").

19. Roller according to claim 18, characterized in that the actuator (30) comprises two mutually supported eccentrics (30 ¹ , 30 ").

20. Roller according to claim 19, characterized in that the two eccentrics (30 ¹ , 30 ") can be adjusted jointly and / or separately.

21. Roller according to one of the preceding claims, characterized in that in each case in the radial direction extending central planes (26 bzw.28) of the support core bearing (14) and the outer casing storage (22) at least substantially coincide.

22. Roller according to one of the preceding claims, characterized in that the support core bearing (14) and the outer casing bearing (22) each comprise only one bearing and that the support core bearing (14) and the outer shell bearing (22) at least substantially in a common Radial plane are arranged.

23. A roll according to any one of claims 1 to 21, characterized in that the support core bearing (14) and / or the outer shell bearing (22) each comprise two or more bearings.

24. Roller according to claim 23, characterized in that the outer casing bearing (22) comprises two or more bearings (22 ¹ , 22 ") and that the radially extending center plane (28) of this outer casing bearing (22) with in Radial direction extend- the center plane (26) of the support core bearing (14) at least substantially coincides.

25. Roller according to claim 24, characterized in that the support core bearing (14) comprises only one bearing and that this support core bearing at least substantially in the radially extending center plane (28) of the outer casing bearing (22) is arranged.

26. Roller according to claim 24, characterized in that the support core bearing (14) also comprises two or more bearings.

27. Roller according to claim 26, characterized in that the bearings of the outer casing bearing (22) and the bearings of the support core bearing (14) are arranged symmetrically relative to a radial plane common to the two bearings (22, 14).

28. Roller according to claim 23, characterized in that the support core bearing (14) comprises two or more bearings (14 ¹ , 14 ") and that the radially extending center plane (26) of this support core bearing (14) extending in the radial direction Center plane (28) of the outer casing storage (22) at least substantially coincident.

29. Roller according to claim 28, characterized in that the outer casing bearing (22) comprises only one bearing and that this outer casing bearing is arranged at least substantially in the radially extending center plane (26) of the supporting core bearing (14).

30. The roller according to claim 28, characterized in that the outer jacket bearing (22) also comprises two or more bearings.

31. Roller according to claim 30, characterized in that the bearings of the support core bearing (14) and the bearings of the outer jacket bearing (22) are each arranged symmetrically with respect to a radial plane common to the two bearings.

32. Roller according to one of the preceding claims, characterized in that e e c e n e t e c h e n e, that between support core bearing (14) and outer shell storage (22) damping means are provided.

33. Roller according to claim 32, characterized in that a viscous liquid is introduced into the cavity between the support core bearing (14) and the outer jacket bearing (22).

34. Roller according to claim 32 or 33, characterized in that in the region between the support core bearing (14) and outer sheath storage (22) is provided a membrane.

35. Roller according to one of the preceding claims, characterized in that it can be fastened to the stool (12) via vibration-damping elements.

36. Roller according to one of the preceding claims, characterized in that it can be attached to the chair (12) via actively damping hydraulic elements.

37. Roller according to one of the preceding claims, characterized in that the support core bearing (14) and / or the outer sheath bearing (22) each comprise at least one angularly compensating bearing.

38. A roll according to one of the preceding claims, characterized in that the support core bearing (14) and / or the outer shell bearing (22) each comprise at least one self-aligning bearing.

39. Roller according to one of the preceding claims, characterized in that the support core bearing (14) and / or the outer casing bearing (22) each comprise at least one tapered, cylindrical or spherical roller bearing.

40. Roller according to one of the preceding claims, characterized in that the support core (16) via the support core bearing (14) is rotatably mounted about its longitudinal axis.

41. Roller according to claim 40, characterized in that the support core (16) is rotatable together with the outer jacket (18).

42. Roller according to claim 40, characterized in that the outer sheath (18) is non-rotatably connected to the support core (16).

43. Roller according to one of claims 1 to 39, characterized in that it e e n e c e s e s that the support core (16) is not rotatable about its longitudinal axis.

44. Roller according to one of the preceding claims, characterized in that, as viewed in the axial direction, the support core (16) has an at least sectionally different cross-sectional shape.

45. Roller according to claim 44, characterized in that the support core (16) has, at least in sections, a cross-sectional shape which conically tapers towards its ends.

46. Web-processing machine with at least one roller according to one of the preceding claims, with a preferably electronic control and / or regulating device, via which the actuators (30) can be controlled accordingly.

47. Web-processing machine according to claim 46, characterized in that at least one sensor for determining the web position with the Re- connected geleinrichtung and the actuators (30) controlling controller the web position is adjustable.

48. Web-processing machine according to claim 47, characterized in that at least one position sensor integrated in the roller is provided.

49. Web-processing machine according to claim 47 or 48, characterized in that in each case at least one position sensor is provided in the two edge regions of the web.

50. Web-processing machine according to claim 49, characterized in that at least one position sensor is integrated into the two end regions of the roller.

51. Web-processing machine according to one of the preceding claims, characterized in that at least one arranged outside the roller position sensor is provided.

52. Web-processing machine according to one of the preceding claims, characterized in that at least one sensor for determining the web tension is connected to the control device and the web tension is controllable by means of the control device activating the actuators (30).

53. Web-processing machine according to claim 52, characterized in that at least one web tension sensor integrated into the roller is provided.

54. Web-processing machine according to one of the preceding claims, characterized in that at least one arranged outside the roller web tension sensor is provided.

55. Use of the roll according to one of the preceding claims 1 to 45 as a universal roll, which simultaneously fulfills the functions of at least two of the following types of rolls:

- Spreader roll - Guide roll

- Regulating roll, in particular Bahnlaufregel- or deflection adjustment

- tension roller.

56. Use according to claim 55, characterized in that, at the same time, the functions of a guide roller and a spreader roller are fulfilled with one roller.

57. Use according to claim 55 or 56, characterized in that the functions of a guide roller and a tension roller are simultaneously fulfilled with the one roller.

58. Use according to one of the preceding claims, characterized in that a roller simultaneously performs the functions of a guide roller and a control roller.

59. Use according to one of the preceding claims, characterized in that one roller simultaneously fulfills the functions of a spreader roller and a control roller.

60. Use according to one of the preceding claims, characterized in that a roller simultaneously performs the functions of a spreader roller and a tension roller.

61. Use according to one of the preceding claims, characterized in that one roller simultaneously fulfills the functions of a tensioning roller and a control roller.