EP1080267A1

EP1080267A1 - Method for calendering a line of a product with a vertical multi-roll calender, and corresponding calender

Info

Publication number: EP1080267A1
Application number: EP99919260A
Authority: EP
Inventors: Bernhard Brendel; Peter Svenka
Original assignee: Eduard Kuesters Maschinenfabrik GmbH and Co KG
Current assignee: Eduard Kuesters Maschinenfabrik GmbH and Co KG
Priority date: 1998-05-06
Filing date: 1999-04-21
Publication date: 2001-03-07
Anticipated expiration: 2019-04-21
Also published as: DE19820089A1; DE19820089C2; EP1080267B1; WO1999057369A1

Abstract

The invention relates to a method for calendering a line of a product with a vertical multi-roll calender (1). According to said method, several intermediate rolls (4, 5, 6) are situated between a top bend-controlled roll (2) and a bottom bend-controlled roll (3). This roll assembly forms nips (N), with a top and bottom nip, the line passing through said nips. The roll assembly also determines line loads in these nips. The line loads of the nips can be modified by introducing deformation forces through the roll pins (7, 8, 9) of the intermediate rolls. In order to adapt the line loads in the nips to the line to be calendered, the deformation forces introduced through the roll pins of the intermediate rolls are selected with the aim of ensuring that the intermediate rolls receive essentially the same bend for exerting load pressures or relief pressures. The degree of bend is regulated in accordance with a determined modification of the line load differential between the top and bottom nip determined by the rolls. The bend-controlled rolls are then adjusted to suit this bend.

Description

Method for calendering a web with a vertical multi-roll calender and a calender therefor

The invention relates to a method for calendering a web with a vertical multi-roll calender according to the preamble of claim 1 and a calender therefor.

Vertical multi-roll calenders comprise a set of rolls consisting of several rolls stacked one on top of the other, which in the operating state are in constant motion

Interaction stand, and through the nips, a web to be calendered runs.

As is known from the weekly paper for paper manufacture 121, 1993, pp. 29 to 33, calendering brings about a mechanical or mechanical-thermal - 2 -

Mix forming of the web. To optimize this forming, in particular of a paper web, different types of rollers are combined in a roller package. Bending adjustment rollers are preferably used in the uppermost and lowermost positions, and the intermediate rollers arranged between them are designed as hard rollers and elastic rollers. Hard rolls are metal rolls with a smooth and hard roll, which are essentially responsible for the smoothness and gloss. Soft rollers are rollers with an elastic or soft surface that essentially ensure uniform compaction.

The compressive stress in the nips increases from top to bottom due to the dead weight of the rolls and the guide means connected to them, such as guide rolls, roll journals and bearing housings. The highest line load is in the lowest nip. This line load increase, which is permanently assigned to a roll package, results in the characteristic, approximately linear natural line load characteristic.

One problem, however, is that because of the low line load in the upper columns, only a small proportion of the deformation is carried out there. A load on the roller package from the upper end increases the usable line load range, but without influencing the line load increase in the roller package, i.e. the slope of the natural characteristic remains unchanged. Since the line load prevailing in the lowest nip cannot be chosen to be as large as desired, the usable line load range is severely restricted in the case of wide calenders with high dead weights of the rolls and a flat line load characteristic.

As is known from US-A-3,060,843, compensation of the overhanging weights, in which the dead weights of the guide means are eliminated, so that practically straight, bend-free intermediate rolls and correspondingly straight, horizontally running nips result in a steeper line load characteristic curve become. With the same line load in the bottom nip the line load in the upper part of the calender is increased.

To keep the effective roller weights small, it is also known from DE 295 21 610 U1 to incline the active plane of the roller stack to the vertical. As a result, only the vertical component of the weight is included in the increase in the line load. The line load increase is consequently reduced, but firmly assigned to the roller set.

Other proposals aim to reduce the weight of the rollers. Rollers with the smallest possible diameter or in a lightweight construction are used for this. A calender roll with a thin jacket and an inner supporting cell structure is disclosed in DE-A-195 11 595. The roller according to DE-A-195 33 823 is based on a similar concept. A decrease in line load that is reduced in this way is in turn firmly assigned to the roller set. A line load specification is only possible in either an upper or a lower nip. The other line load results from the dead weight.

Finally, WO 95/14813 discloses a vertical multi-roll calender with a bend-controllable top and bottom roll and intermediate rolls, in which the intermediate rolls are selected so that they all have an essentially identical natural deflection. By completely lifting or compensating for the weights of the intermediate rolls including guide means, these weights have no influence on the line load in the nips. As a result, the same line loads prevail in the lowest nip and the top nip, the same inherent deflections of the intermediate rolls ensuring essentially flat line load profiles. The line loads in the nips can then be set via a selectable load on the top or bottom roller. The disadvantage here is that only intermediate rolls with the same inherent deflection can be used. In addition, a certain difference in line load from one nip to another nip is desirable to keep a web tension between to build two nips, which is necessary for a crease-free running of the material web.

The object of the invention is therefore to provide a method for calendering a web with a vertical multi-roll calender, which allows the line loads in the nips to be adapted to a web to be calendered. Another task is to create a calender for this.

These objects are solved by the features of claims 1 and 11, respectively.

This creates a process that changes the design-related natural or compensated line load characteristic of a calender in order to be able to optimally adjust a multi-roll calender to a web, in particular a type of paper. Deviating from the natural or compensated characteristic, flatter or steeper characteristics are set depending on the web to be calendered, whereby the setting of a negative slope, i.e. the highest nip has a higher line load than is possible in the lowest nip.

In order to ensure that there is uniformity of the line load distributions between the intermediate rolls, all intermediate rolls must undergo essentially the same deflection, i.e. have the same bending lines.

The gradient of the line load characteristic curve and thus the line load difference between the upper and lower nip can be freely set by a specific bending of the intermediate rolls, which leads to a relief or loading of the own weights of the rolls. The calendering potential of such a calender is therefore not predetermined by the design, but can be adjusted to the respective web during operation. In addition, the nip number can be reduced below that in the supercalender and good smoothing effects even with high ones Speeds can be realized.

The variable setting of the line load characteristic is still possible when using rolls with different roll diameters in a roll set. As is known, smaller roller diameters result in a smaller gap width, which results in a higher compressive stress. Since the compressive stress and not the line load is the mechanical variable that is essentially responsible for the forming, the load can be influenced via the roller diameter. The steep line load characteristic curve given because of the smaller roller diameter can be changed by the method according to the invention without losing the advantage of a smaller gap width.

Furthermore, it is not necessary to construct the intermediate rolls in such a way that their deflections from their own weight and their bending stiffnesses are equal to one another.

If a roll set consists of intermediate rolls of different bending stiffness, the amount of deformation force can be selected depending on the respective bending stiffness. Although this leads to different line load differences from intermediate roll to intermediate roll or from nip to nip, it ensures the same deflections.

To set a desired line load characteristic, line loads that are to prevail in the upper and lower nip during calendering can be specified independently of one another. Associated average line loads can be determined via loading or unloading pressures of the intermediate rolls. The starting point for this are preferably the intermediate rolls which are completely relieved of the overhanging weights and the deflection and spreader rolls, so that all rolls form straight nips. In this respect one speaks of a compensated roll stack with a compensated line load characteristic. This compensated line load characteristic preferably serves as a reference characteristic. On the basis of this reference characteristic curve, the intermediate rolls can be loaded or relieved in such a way that the sum of the desired line load differences between the upper and lower nip results across all intermediate rolls and the desired characteristic curve thus changed.

The bar bending of the intermediate rolls can be used to calculate setpoints for the deformation forces. For a more refined adjustment, the shear deformation, a shell deflection and / or a shell shear deformation can be included in a calculation of the target values.

Further refinements and advantages of the invention can be found in the subclaims and the description below.

The invention is explained in more detail below on the basis of the exemplary embodiments illustrated in the attached figures.

1 shows schematically the side view of a vertical multi-roll calender for calendering,

2a schematically shows intermediate rolls of a calender according to FIG. 1 with a bend for a relief pressure for setting a steeper characteristic curve according to a first exemplary embodiment,

2b shows a diagram of a compensated and a line load characteristic curve according to FIG. 2a changed by roller bending,

3a schematically shows intermediate rolls of a calender according to FIG. 1 with a bend for a relief pressure for setting a vertical characteristic curve according to a second exemplary embodiment,

3b shows a diagram of a compensated and a line load characteristic curve according to FIG. 3a changed by roller bending,

4a schematically shows intermediate rolls of a calender according to FIG. - 7 -

1 with a bend for a relief pressure for setting a characteristic curve with a negative slope according to a third exemplary embodiment,

4b shows a diagram of a compensated and a line load characteristic curve according to FIG. 4a changed by roller bending,

5a schematically shows intermediate rolling of a calender according to FIG. 1 with a bend for a loading pressure for setting a flatter characteristic according to a fourth exemplary embodiment,

5b shows a diagram of a compensated and a line load characteristic curve according to FIG. 5a changed by roller bending,

6 schematically shows intermediate rolls of a calender according to FIG. 1 with six intermediate rolls and a line load characteristic curve varied by roll bends.

Fig. 1 shows a vertical multi-roll calender with a frame 1, in which a roll stack of an upper bend-controllable roll 2, a lower bend-controllable roll 3 and three intermediate rolls 4, 5, 6 are arranged supported. The intermediate rolls 4, 5, 6 can be designed as hard or elastic rolls and have different roll diameters. The rolls are arranged one above the other in the roll stack, successive rolls each delimiting a nip, the roll working gap. In the calender shown in FIG. 1, a first nip, called an upper nip, lies between the upper bend-controllable roller 2 and the first intermediate roller 4. A nip N _? lies between the first intermediate roller 4 and the second intermediate roller 5. A nip N ₃ lies between the second intermediate roller 5 and the third intermediate roller 6. A last nip, called the lower nip, lies between the third intermediate roller 6 and the lower controllable roller 3.

In the nips N, ₂ , ₃ , N there are compressive stresses which are determined by the dead weights of the rollers 2, 4, 5, 6 and the associated one - 8th -

Guide means as well as loads that can be applied to one end of the roll stack. The force acting in a nip per unit length of the roller is called the line load. Accordingly, there is a line load q in the upper nip, a line load q in the nip N, the line load q ~ in the nip o and the line load q in the lower nip. The line load, measured in N / mm, for a number of nip results in a line load characteristic.

The nips N, ₂ , ,, N are passed through from top to bottom by a web of material to be processed, in particular a paper web.

The intermediate rolls 4, 5, 6 have roll journals 7, 8, 9 for an articulated arrangement on both sides. For this purpose, the roller journals 7, 8, 9 are fastened to levers 10, 11, 12, on each of which a pressure cylinder 13, 14, 15 acts in order to introduce deformation forces onto the roller journals 7, 8, 9 and thus the intermediate rollers 4, 5, 6 . A bending line B of the intermediate rolls 4, 5, 6 (cf. FIG. 2a) can hereby be set, wherein the curvature of the bending line B can be controlled via the level of the deformation forces introduced. The pressure cylinders 13, 14, 15 are preferably hydraulic cylinders. The pressure cylinders 13, 14, 15 can be controlled separately in order to be able to act upon each intermediate roller 4, 5, 6 individually with a selectable deformation force. The pressure cylinders 13, 14, 15 are preferably designed to act on two sides in order to be able to introduce loading and relief pressures on the intermediate rolls 4, 5, 6.

In a method for calendering a material web with such a multi-roll calender, a variable characteristic of the compressive stresses in the successive nips N _Q , N ₂ , N ₃ can be achieved by pressing on the roll journals 7, 8, 9 of the intermediate rolls 4, 5, 6 introducible deformation forces are chosen such that the intermediate rollers 4, 5, 6 receive an essentially identical deflection for exerting loading or relieving pressures, a degree of deflection according to a determinable change in a roller-related line load difference between the upper and lower nip N "o and Now, a ³ is set and the bend-controllable rollers 2, 3 can be adapted to this bend.

For such a determination of the change in the roller-related line load difference, only the stiffnesses and the dead weights of the intermediate rollers 4, 5, 6 are taken into account. On the other hand, it is not necessary to construct these intermediate rolls 4, 5, 6 in such a way that their deflections from their own weight are identical to one another, nor that their bending stiffnesses are identical to one another.

When using different intermediate rollers 4, 5, 6, in particular hard and elastic intermediate rollers, the amount of the deformation forces required to set a certain degree of bending can rather be determined for each intermediate roller 4, 5, depending on the respective bending stiffness of the respective intermediate roller 4, 5 , 5 can be selected.

For the calendering of a web, a compensated line load characteristic curve K is assumed here (see FIG. 2b), in which overhanging weights are compensated so that flat line load profiles are present in the nips N, N ₂ , N ₃ , N. The compensation forces introduced for this purpose are introduced via the pressure cylinders 13, 14, 15. A line load difference z3, q _E then follows from the dead weights of the intermediate rolls 4, 5, 6

To set a desired line load characteristic curve K _ß by roller bending (see FIG. 2b), the line loads in the upper nip q and in the lower nip q are specified independently of one another. Starting from a compensated line load characteristic curve K _κ with an upper line load q, a desired lower line load q is determined. If this differs from the inherent weight, the line load characteristic curve g becomes steeper or flatter than the compensated line load characteristic curve K _κ , since a line load difference Δ q _{ß has to be} subtracted or added, which results from a total line load from the bending of all intermediate rolls 4, 5, 6 results. The lower line load q can be smaller - 10 -

be chosen as q. The total change in line load from the bending is divided into deviations for the mean line loads, here q ₂ and q ₃ , which is achieved by a specific roll bending of the intermediate rolls 4, 5, 6, whereby additional line loads (positive or negative) q _{ß are} generated.

For a compensated line load characteristic curve K _κ , q _u = q ₀ + Δq _E ,

while for the variable line ^load characteristic K _ß ^{A =} % ^{+ Δq} E ^" V applies

The division of this line load difference Δ q _ß by roller bending on the individual intermediate rollers 4, 5, 5 takes into account the bending stiffness of the intermediate rollers 4, 5, 6, preferably according to the theory of beam bending. Instead of an arithmetically equal division of the line load difference .DELTA.Q _ß to the number intermediate rolls 4, 5, 6 is hereby carried out a roll type-dependent splitting.

According to a first embodiment shown in FIGS. 2a and 2b, the first intermediate roller 4 and the third intermediate roller 6 are identical in construction and are designed as a hard, heatable roller. In contrast, the second intermediate roller 5 is designed as an elastic roller.

A predetermined total line load difference Δq _β from roll bending is then divided between the intermediate rolls 4, 5, 6 according to

.DELTA.Q _ß = 2 q + _HSS _ESS 1 q,

where q. n is the desired line load additive on the hard intermediate rolls 4, 6 from roll bending and q "the desired line load additive on the elastic intermediate roll 5 from roll bending is. These two line load additives bend the intermediate rolls 4, 5, 6, the deformation forces required for this being absorbed by the pressure cylinders 13, 14, 15. - 1 1 -

brings and introduced into the bearings of the intermediate rolls 4, 5, 6 as additional forces and kept in balance.

In order to ensure the uniformity of the nip forces, the bending lines B of the intermediate rolls 4, 5, 6 are adapted to one another. That is, the intermediate rolls 4, 5, 6 are deformed in such a way that the nips delimited by them are curved essentially the same and consequently run parallel to one another.

The equality of the bending arrows f of the intermediate rolls can be used as a criterion for such an adaptation of the bending lines of the intermediate rolls 4, 5, 5. This leads to the requirement

^{f ■ f} e ^•

where f. the bending arrow of the hard intermediate rolls 4, 6 and f is the bending arrow of the elastic intermediate roll 5. According to the beam theory, the following applies to the deflection of a hard intermediate roller 4, 6, which is articulated on both sides and an elastic intermediate roller 5 under its own weight

^{5 '} B ^{' l4 5 'q} eB ^{* l4}

384 E _h h • JXh 384 E _Ω e • each

By equating the formulas for the two bending arrows one obtains:

eB

Ee _Ω • e Eh • Century

where E _e , E _h indicate the elasticity modules and J _h the moments of inertia of the respective of the respective intermediate rolls. From the formulas above, the line load additives q can be searched. Determine _R and q _B and calculate corresponding setpoints for actuating cylinders 22. The elasticity modules are known in each case - 12 -

or can be determined experimentally, and the area moment of inertia is predetermined by the geometry of the cross sections of the intermediate rolls 4, 5, 6.

The following applies to the line load supplements sought

Δq _ß

'hB ⁼ - 2 +. ^E e ^{* J} e

V ^J h

Δ q _ß

^q eB ⁼ _{1 + 2} hh ee

The additional journal forces F for the hard intermediate rolls 4, 5 belonging to the calculated line load supplements for the roll bends result as follows:

Paper width ^F h =% B ²

the additional journal forces F _e for the elastic intermediate roller 5 result from

Paper width ^F e ^{= q} eB ²

If a characteristic curve K _{β which} is steeper than the compensated line load characteristic curve K _κ is obtained, the intermediate rolls 4, 5, 6 bend downwards, ie relief pressures act on the roll journals 7, 8, 9 of the intermediate rolls 4, 5, 6, as is the case with this is illustrated in Fig. 2a by the force arrows F. and F acting from below. - 13 -

In the first exemplary embodiment shown in FIGS. 2a and 2b, line load supplements q are exemplary. _ß and q _ß indicated by bends of identical hard intermediate rolls 4, 6 and an elastic intermediate roll 5. 2b shows the line load additions q, _β and q _R in relation to the line load and FIG. 2a illustrates the degree of curvature of the bending lines B of the intermediate rolls 4, 5, 6. The line load additions q. _ß and q "are negative in terms of amount with respect to the compensated line load characteristic K _κ and consequently lead to a steeper variable line load characteristic K _ß . In the upper nip N there is a line load q, which can be adjusted via the upper bending-controllable roller 2. The amount of the line load q in the upper nip and the height of the line load q in the lower nip, due to the dead weights of the rollers 2, 4, 5, 6 and the line load additions of the intermediate roller 4, 5, 6, are shown by force arrows.

The second exemplary embodiment shown in FIGS. 3a and 3b differs from the first exemplary embodiment described above only in that Δq corresponds to Δq _{F in} terms of amount. The result is a vertical variable characteristic K _R. Since higher deformation forces than pin forces are introduced here, ie stronger relief pressures are at the intermediate rolls 4, 5, 6, there is a greater degree of curvature for intermediate rolls 4, 5, 6. Otherwise, the explanations for the first embodiment apply accordingly.

The third exemplary embodiment shown in FIGS. 4a and 4b differs from the exemplary embodiments described above only in that Δq _{β is} greater in magnitude than Δq _E - the result is a variable characteristic curve K _β with a negative slope since q is smaller than q , as well as the representation of the force arrows for q and q illustrate. Since even higher deformation forces than pin forces are introduced here, ie there are even stronger relief pressures at the intermediate rolls 4, 5, 6, there is an even greater degree of curvature for intermediate rolls 4, 5, 6. Otherwise, the explanations for the first and second exemplary embodiments apply accordingly. - 14 -

The fourth exemplary embodiment shown in FIGS. 5a and 5b shows a characteristic curve K _β which is flatter than the compensated characteristic curve K _κ due to roll bends, which requires the intermediate rolls 4, 5, 6 to be bent downwards. This is also illustrated by the force arrows F. and F, which act on the roller journals 7, 8, 9 of the intermediate rollers 4, 5, 6 from above and consequently initiate loading pressures. Δq _ß does not subtract from Λq _{F here} , but adds up, as shown in Fig. 5b. The bending lines B of the intermediate rolls 4, 5, 6 are convex in contrast to a concave shape of the previously described exemplary embodiments. Otherwise, the explanations for these exemplary embodiments apply accordingly.

6 finally shows a concrete numerical example for a flatter characteristic curve K _ß by roller bending compared to a compensated characteristic curve K _j. For this purpose, a calender comprises a total of six intermediate rollers 30, 31, 32, 33 in addition to the upper bending-controllable roller 2 and the lower bending-controllable roller 3 , 34, 35, of which the intermediate rolls 30, 32 and 35 are cast iron rolls which cause a line load q _£ of 8.1 N / mm each. The intermediate rollers 31, 33 and 34 are elastic rollers made of aluminum, which cause a line load q ^ of 4.6 N / mm each.

For the compensated characteristic curve K., an upper line load q of zero is assumed, for a lower line load q here follows 38.1N / mm. If, however, a lower line load q of 100 N / mm is required, the introduction of load pressures on the roll journals of the intermediate rolls is necessary, whereby the intermediate rolls are given a convex bending line, the intermediate rolls 30 to 35 must be additionally loaded by a total of 61.9 N / mm

q _b = 100 - 38.1 N / mm q _ß = 61.9 N / mm

If one takes into account the associated elasticity modules and bending moments of inertia of the intermediate rolls 30 to 35 selected here by way of example, it follows - 15 -

Δq

^ eB 10.7 N / mm

5,769 Q _R

^ hB 9.9 N / mm

6.250

Instead of the arithmetic mean 100 N / mm / 6 nips = 16.66 N / mm, additive section loads result from q _E and q _R of 4.6 N / mm and 10.7 N / mm, i.e. 15.3 N / mm as well as from q. _£ and q. _ß of 8.1 N / mm and 9.9 N / mm, i.e. 18 N / mm.

In the described exemplary embodiments, the hydraulic pressures of the two bending adjustment rollers 2, 3 are set so that the bending lines of the bending adjustment rollers conform to the predetermined bending lines B of the intermediate rollers 4, 5, 6.

By means of a control unit, the pressures in the pressure cylinders 13, 14, 15 for adapting the intermediate rolls 4, 5, 6 and the pressures in hydraulic elements of the bending adjustment rolls 2, 3 can be adjusted synchronously with one another, so that a homogeneity of the line load distributions in all nips also during a pressure adjustment for a new web is retained. In this way, the elastic covers in particular are protected from destruction even when they are changed while the calender is in operation.

In the exemplary embodiments described, the compensated characteristic curve K. (overhanging weights compensated) was chosen as the reference line, in which plane line load profiles are present. Alternatively, the natural characteristic curve can also serve as a reference line without compensation. The calculation of the setpoints must then be adjusted accordingly.

Other deformations have been neglected in the calculation of the setpoints for line load _additives q _ß described above. In addition to the bending deformations, shear deformations can also be - 16 -

measurements of the intermediate rolls are included in the calculation. In addition, it is also possible to take account of any existing tube roll adjustments of the intermediate rolls in the calculation.

Alternatively, for a calculation of the line load supplements q _R by roller bending for an adjustment of the bending lines B of the intermediate rollers 4, 5, 6, as another criterion for the uniformity of the nip forces between the intermediate rollers 4, 5, 6, the minimization of the square of the error, formed from the deviations adjacent bending lines B can be used at a predetermined number of discrete support points.

Claims

- 17 patent claims

1. A method for calendering a web with a vertical multi-roll calender, in which a plurality of intermediate rolls are arranged between an upper bend-controllable roll and a lower bend-controllable roll, this roll package forms nips with an upper and a lower nip that passes through the web, and line loads determined in these nips, the line load profile of which can be changed by introducing deformation forces on the roll journals of the intermediate rolls, characterized in that the deformation forces which can be introduced on the roll journals of the intermediate rolls are selected such that the intermediate rolls receive an essentially identical deflection for exerting loading or relief pressures , wherein a degree of deflection is set according to a determinable change in a roller-related line load difference between the upper and lower nip, and the deflection-controllable rollers are adapted to this deflection.

2. The method according to claim 1, characterized in that for each intermediate roller, the amount of the deformation force required to set a certain degree of bending is selected as a function of the respective bending stiffness of the respective intermediate roller.

3. The method according to claim 1 or 2, characterized in that a line load in the upper and in the lower nip is predetermined independently of one another and a deviation of a resulting line load difference from a compensated line load difference assigned to the rolls is divided into deformation forces for the individual intermediate rolls.

4. The method according to any one of claims 1 to 4, characterized in that the beam bending of the intermediate rolls is used for a calculation of target values for the deformation forces.

5. The method according to claim 4, characterized in that for a loading - 18 -

calculation of setpoints for the deformation forces, shear deformations of the intermediate rolls can also be used.

6. The method according to claim 4 or 5, characterized in that in the case of tubular intermediate rolls for the calculation of target values for the deformation forces, a shell bending is additionally used.

7. The method according to claim 6, characterized in that in addition the shell shear deformation of tubular rollers is used.

8. The method according to any one of claims 1 to 7, characterized in that a thickness of the nips is formed uniformly over a length of the rollers.

9. The method according to any one of claims 1 to 8, characterized in that the line load profiles between two intermediate rollers and between an intermediate roller and a bend-controlled roller with the same shape are set.

10. The method according to any one of claims 1 to 9, characterized in that a deviation of the line load difference is set, the amount of which corresponds to the compensated line load difference to form a vertical line load characteristic.

11. Vertical multi-roll calender for performing the method according to one of claims 1 to 10 with an upper bend-controllable roll, a lower bend-controllable roll and a plurality of intermediate rolls arranged in between, which are arranged one above the other and form nips between two rolls through which the web runs , and at least the intermediate rolls have roll journals on both sides, which are arranged in articulated bearings to which deformation forces can be introduced via pressure cylinders, characterized in that the pressure cylinders (13, 14, 15) can be controlled individually and for introducing loading and relief pressures are designed to work on both sides.