Roller arrangement

Abstract

Roller arrangement (1) with at least two axially parallel rollers (2, 3), wherein a roller gap (5) is formed between adjacent rollers, wherein each of the rollers (2, 3) has a roller journal (7, 8) at each of its two axial ends (6) and each roller (2, 3) is supported via its two roller journals (7, 8), wherein at least two bearings (9, 10) are arranged axially next to each other at least on a first roller journal (7) of a first of the rollers (2) and on an adjacent first roller journal (7) of a second of the rollers (3), wherein a compressive stress (20) is generated between an inner bearing (9) on the first roller journal (7) of the first roller (2) and an outer bearing (10) on the first roller journal (7) of the second roller (3) and a tensile stress (21) is generated between an outer bearing (10) on the first roller journal (7) of the first roller (2) and an inner bearing (9) on the first roller journal (7) of the second roller (3) or vice versa.

Description

[0001] The invention relates to a roller arrangement with at least two axially parallel rollers, wherein a roller gap is formed between adjacent rollers, wherein each of the rollers has a roller journal at each of its two axial ends and each roller is supported via its two roller journals, wherein at least two bearings are arranged axially next to each other at least on a first roller journal of a first of the rollers and on an adjacent first roller journal of a second of the rollers.

[0002] In a rolling mill, the rolls are positioned relative to each other via bearings in the mill blocks. The distance between the rolls can be adjusted by adjusting the position of at least one of them. When processing conventional materials with homogeneous properties, the rolls are pressed against each other by the more or less constant force flow through the material being rolled, pressing them into the opposite bearing recesses, where they remain. This does not pose a problem for the processing quality as long as the force directions are more or less constant and the pressure in the roll gap, and consequently the adjustment, remains reasonably consistent. For the majority of rolling processes, this adjustment is sufficiently precise, as there are no significant load changes.

[0003] Conventional rolling mills are unsuitable for processing materials that, during continuous production, develop different material properties due to the rolling process and its progression, thereby generating varying process forces in the roll gap. Different density distributions within a material web result in varying rolling forces, causing the rolls to collapse or the rolls to be forced apart. This ultimately leads to varying material thicknesses and different properties in the finished rolled product, whether it be a web, film, coated web, or multi-layered web.

[0004] DE 20 2014 104 438 U1 relates to a calender for embossing, smoothing or laminating material webs or pieces of material, with two rollers rotatably mounted about their respective longitudinal axes, which are arranged parallel to each other with a gap forming a gap, wherein the rollers each have an axially pivotable external rotary bearing at their opposite ends, which has a pivoting position preset via a bearing clearance adjustment.

[0005] DE 10 2011 018 874 B3 relates to a roller arrangement with a device for controlling the roller gap in a supported roller pair, wherein the bearing block located inside the roller journal is arranged in a bearing block and the bearing block located outside the roller journal is arranged in a clamping bracket which has a first lever arm and a second lever arm, wherein the first lever arm of a clamping bracket of the upper roller and the first lever arm of a clamping bracket of the lower roller are rigidly connected to each other.

[0006] US Patent 4,817,407 A relates to a rolling mill stand comprising a stationary roll and at least one moving roll spaced apart, the journals of the moving roll being supported in a bearing unit that interacts with a control mechanism to displace the moving roll radially relative to the stationary roll, thereby adjusting the gap between them. The bearing unit comprises two separate radial bearings, one radial bearing interacting with a control element and the other radial bearing being acted upon by a working element that exerts a counterforce to the force exerted by the control element.

[0007] DE 297 16 031 U1 relates to an adjusting device for a pair of rollers for adjusting a roller gap formed by the two rollers of the roller pair, wherein each roller is provided on both sides with axial bearing journals for the respective bearing in a rotary bearing and an adjusting device is arranged on each side of the roller pair between the bearing journals of the two rollers and the adjusting devices are equipped with means for displacing the at least one roller in order to change the center-to-center distance of the rollers from each other by displacing at least one roller to adjust the roller gap, wherein the operative connection between the means of the adjusting device for displacing the at least one roller and the bearing journals of the rollers is provided in an area spaced apart from the rotary bearings.

[0008] Particularly in a roller arrangement with more than two rollers in a line and continuous meandering passage of the rolled material through the individual roller gaps one after the other, the problem arises of alternately pre-tensioning the side of the bearing facing the load without play and bringing the side of the bearing facing away from the roller gap into contact in order to be able to apply the load required for rolling in both roller gaps on both sides of the roller.

[0009] It is therefore the object of the present invention to improve a roller arrangement in such a way that it enables improved feeding while simultaneously achieving low bearing clearance.

[0010] This problem is solved by the proposed roller arrangement according to claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

[0011] Accordingly, a roller arrangement with at least two axially parallel rollers is proposed, wherein a roller gap is formed between adjacent rollers, wherein each of the rollers has a roller journal at each of its two axial ends and each roller is supported via its two roller journals, wherein at least two bearings are arranged axially side by side at least on a first roller journal of a first of the rollers and on an adjacent first roller journal of a second of the rollers, wherein a compressive stress is generated between an inner bearing on the first roller journal of the first roller and an outer bearing on the first roller journal of the second roller and a tensile stress is generated between an outer bearing on the first roller journal of the first roller and an inner bearing on the first roller journal of the second roller, or vice versa.Conversely, this means that the tensile and / or compressive stresses can also be reversed, as long as they exist between diagonally opposed adjacent bearings. This cross-bracing allows two roller bearings in series to be pre-tensioned against each other on the roller journals in such a way that a nested force transmission is achieved, thus enabling the necessary clearance.

[0012] In one embodiment, it may be provided that only compressive or tensile stresses are supplied to all bearings.

[0013] Furthermore, the roller arrangement can comprise at least three axially parallel rollers, wherein at least on a first roller journal of a third roller, two bearings can be arranged axially side by side, wherein a compressive stress is generated between the inner bearing on the first roller journal of the second roller and an outer bearing on the first roller journal of the third roller, and a tensile stress is generated between the outer bearing on the first roller journal of the second roller and an inner bearing on the first roller journal of the third roller, or vice versa. The stress states between diagonally spaced bearings can alternate, in particular, from roller to roller. That is, the inner bearing of the middle roller can be under tensile stress towards the first roller and under compressive stress towards the third roller, or vice versa.Furthermore, this means that the outer bearing of the middle roller can be under compressive stress towards the first roller and under tensile stress towards the third roller, or vice versa. In particular, the stresses acting on both sides of a bearing can be equal. It is therefore possible to arrange any number of additional rollers with the same bearing configuration parallel to each other, with the stress distribution through the bearings continuing as described above.

[0014] Furthermore, at least two bearings can be arranged on at least one second journal of the first roll and on an adjacent second journal of the second roll, wherein a compressive stress is generated between an inner bearing on the second journal of the first roll and an outer bearing on the second journal of the second roll, and a tensile stress is generated between an outer bearing on the second journal of the first roll and an inner bearing on the second journal of the second roll, or vice versa. "Mirror image" here means mirrored about a central axis running radially perpendicular to the rolls. Thus, in particular, tensile or compressive stresses in the same direction can be present on both inner and both outer bearings of opposite journals.

[0015] Furthermore, at least two bearings can be arranged on at least the second roller journal of the third roller, wherein, mirroring the first roller journal opposite, a compressive stress is generated between an inner bearing on the second roller journal of the second roller and an outer bearing on the second roller journal of the third roller, and a tensile stress is generated between an outer bearing on the second roller journal of the second roller and an inner bearing on the second roller journal of the third roller, or vice versa.

[0016] In particular, it can be provided that at least three bearings are arranged axially side by side at least on a first roller journal of the first roller and the adjacent first roller journal of the second roller, wherein a compressive stress is generated between, on the one hand, an inner bearing and an outer bearing on the first roller journal of the first roller and, on the other hand, a central bearing unit on the first roller journal of the second roller, and a tensile stress is generated between, on the one hand, a central bearing unit on the first roller journal of the first roller and, on the other hand, an inner bearing and an outer bearing on the first roller journal of the second roller, or vice versa. This arrangement becomes particularly relevant under high loads, where it is necessary to nest the bearings in a multiple arrangement such that the loads in the journals superimpose with the load collectives in such a way that the journal deflection or...the bending moment at the roller ball transition, i.e. at the roller-side end of the rolling bearing directed towards the roller ball, is reduced to zero Nm.

[0017] Furthermore, at least three axially parallel rollers can be provided, wherein at least three bearings are arranged axially side by side at least on the first roller journal of the third roller, wherein a compressive stress is generated between, on the one hand, an inner bearing and an outer bearing on the first roller journal of the second roller and, on the other hand, a central bearing unit on the first roller journal of the third roller, and a tensile stress is generated between, on the one hand, a central bearing unit on the first roller journal of the second roller and, on the other hand, an inner bearing and an outer bearing on the first roller journal of the third roller, or vice versa. The stress states between diagonally spaced bearings can alternate, in particular, from roller to roller.This means that the inner bearing of the middle roller can be under tensile stress towards the inner and outer bearings of the first roller, and under compressive stress towards the inner and outer bearings of the third roller, or vice versa. Furthermore, this means that the inner and outer bearings of the middle roller can be under compressive stress towards the middle bearings of the first roller, and under tensile stress towards the middle bearings of the third roller, or vice versa. In particular, the stresses acting on both sides of a bearing can be equal. It is therefore possible to arrange any number of additional rollers with the same bearing configuration parallel to each other, with the stress distribution through the bearings continuing as described above.

[0018] Furthermore, at least three bearings can be arranged on the second journal of the first roll and on the adjacent second journal of the second roll, wherein a compressive stress is generated, mirrored to the opposite side of the first journal, between an inner bearing and an outer bearing on the second journal of the first roll and a central bearing unit on the second journal of the second roll, and a tensile stress is generated, or vice versa, between a central bearing unit on the second journal of the first roll and an inner bearing and an outer bearing on the second journal of the second roll. "Mirrored" here means mirrored about a central axis running radially perpendicular to the rolls.Thus, in particular, the same type of stress can be provided on both inner and both outer bearings of opposing roller journals, as well as on both middle bearings of opposing roller journals. Furthermore, it can be provided that the individual stress states of immediately adjacent, mutually facing bearing surfaces are complementary to each other.

[0019] Furthermore, at least three bearings can be arranged on at least the second journal of the third roll, with a compressive stress being generated, mirrored to the opposite side of the first journal, between an inner bearing and an outer bearing on the second journal of the second roll and a central bearing unit on the second journal of the third roll, and a tensile stress being generated between a central bearing unit on the second journal of the second roll and an inner bearing and an outer bearing on the second journal of the third roll, or vice versa. Such a bearing arrangement and bearing tension creates a compressive and a tensile state, respectively, crosswise between opposing journals, with the pressure profiles of similar pressures of adjacent tensions exhibiting the same profile.For example, compressive stresses from roller journal to roller journal always run from the outer and inner bearings inwards to the middle bearing unit, and in contrast, tensile stresses always run from the middle bearing unit outwards to the outer and inner bearings.

[0020] It can be designed so that the material to be rolled is fed alternately through the roll gaps in opposite directions from one gap to the next. This allows inner rolls to be used for rolling from both sides. Due to the different directions of rotation of adjacent rolls, it is necessary to feed the material alternately from above and below through adjacent roll gaps.

[0021] Furthermore, a roll position control unit can be arranged to generate the tensile and / or compressive stresses between the roll journals, via which the respective roll gap adjustments are realized.

[0022] The roller position control unit can include a pressure-controlled actuator. Preferably, a separate actuator is provided between each coupled bearing pair. A pressure-controlled actuator has the advantage, particularly with materials exhibiting an inhomogeneous density distribution, that the feed rate can be adjusted very effectively.

[0023] In particular, the actuator can have a hydraulic, mechanical, or electrical actuating element. Alternatively, the actuator can have a hydraulic actuating element, a mechanical spindle, and a linear motor.

[0024] Furthermore, the roller position control unit can be in operative connection with the outer bearing rings of the bearings.

[0025] In particular, the central bearing unit can have one or more, preferably two, bearings. If the central bearing unit has two bearings, these can be arranged directly next to each other in the axial direction. Furthermore, adjacent bearings of the central bearing unit can be axially preloaded against each other.

[0026] Furthermore, the bearing can include a rolling and / or a sliding bearing.

[0027] Exemplary embodiments of the invention are explained with reference to the following figures. These show: Fig. 1a a cross-sectional representation of a roller arrangement showing process forces in the rolling process; Fig. 1b a schematic view of a roller arrangement known from the prior art showing process forces acting on the bearings during the rolling process; Fig. 2 a schematic view of an embodiment of a roller arrangement according to the invention; Fig. 3 a schematic view of a further embodiment of an inventive roller arrangement; Fig. 4 a cross-sectional view of an exemplary roller arrangement with a plurality of rollers arranged in a row; Fig. 5a a side view of an embodiment of a roller arrangement according to the invention with four bearings per roller journal; Fig. 5b a semi-transparent side view of an embodiment of a roller arrangement according to the invention with four bearings per roller journal; Fig. 6 a view of a force triangle of an embodiment of a roller arrangement according to the invention with four bearings per roller journal.

[0028] In a roller mill, the rollers are positioned relative to each other via bearings in the mounting blocks. Fig. Figure 1a shows a roller arrangement 1 of a rolling mill with two axially parallel rollers 2, 3, between which a roll gap of width h1 is formed. The side view shows that the roller bearing consists of an inner bearing ring 15 and an outer bearing ring 14, in which the inner bearing ring 15 is rotatably mounted. The outer bearing rings 14 are anchored in the mounting blocks. By passing the material web 16 with a thickness h0 through the roll gap 5, the material web 16 is reduced to a compacted material web 18 with a material thickness of height h1. Due to the more or less constant direction of force flow through the material web 16 of the rolled stock, the rollers are pressed against each other into the opposite bearing recesses and remain there. The resulting process forces are the force F from the rolled stock, which is perpendicular to the direction in which the material 16 is passed. WThe inner bearing ring 15 exerts a force on the outer bearing ring 14. Simultaneously, the approach force F acts from the outer bearing rings 14 on the inner bearing rings 15. As a result, the inner bearing rings 15 are pressed outwards within the outer bearing rings 14, creating a bearing clearance 17 on the side of the outer bearing ring 14 facing the rolling gap 5.

[0029] A representation of the process forces according to Fig. 1a is also in Fig. 1b shows a top view of the storage arrangement. Fig. Figure 1a shows two rolls 2, 3 arranged axially parallel to each other, forming a roll gap 5. Each roll 2, 3 has a journal 7, 8 at its axial ends 6, with a bearing 9 arranged on each journal 7, 8, so that the roll 2, 3 is supported by this bearing arrangement. When a web of material 16 passes through the roll gap 5, process forces are generated perpendicular to the direction of passage. These forces are transmitted via the roll barrels to the journals and from the journals to the inner bearing rings 15 arranged on them, which in turn are supported by the outer bearing rings 14. These forces F WThe inner bearing rings 15 are pressed outwards within the outer bearing rings 14 by the rolled material, so that a bearing clearance 17 is created on the inside of each bearing. In addition, by adjusting the width of the roll gap 5, the force F from the adjustment is exerted on the outer bearing rings 14 in the direction of the roll gap 5.

[0030] The in the Fig. 2 and Fig. The embodiments of the invention shown in the three examples shown have the advantage, particularly in the case of large load changes caused by the rolled material, of being able to react to the load changes with micrometer precision independently of the roll gap 5 to the roll gap 5, while simultaneously eliminating bearing clearances. With the arrangement 1 of the roll bearings relative to each other described in the invention, it becomes possible to arrange the mounting elements with the force application and the opposing gap adjustments in a nested arrangement, each of which is arranged in a cascade. In a first embodiment according to Fig. In a series of axially parallel rollers 2, 3, 4, two roller bearings can be provided for each roller journal 7, 8 and preloaded against each other in such a way as to create a nested force transmission, thus enabling the necessary clearance. In the illustrated example, the outer rings 14 of diagonally adjacent bearings are in a operative relationship that generates either a tensile or compressive stress between the bearings. For example, the outer ring 15 of the outer bearing 10 on the first roller journal 7 of the first roller 2 is under tensile stress with the diagonally adjacent outer ring 15 of the inner bearing 9 on the first roller journal 7 of the second roller 3.Furthermore, a compressive stress exists between the side of the outer bearing ring 15 of bearing 9 on the first roller journal 7 of the second roller 3 facing away from the first roller 2 and the diagonally adjacent outer bearing ring 15 of the outer bearing 10 on the first roller journal 7 of the third roller 4. Simultaneously, a operative connection exists between the outer bearing ring 15 of the inner bearing 9 on the first roller journal 7 of the first roller 2 and the outer bearing ring 15 of the outer bearing 10 on the first roller journal 7 of the second roller 3 in the form of a compressive stress. The side of the outer bearing ring 15 of the outer bearing 10 on the first roller journal 7 of the second roller 3 facing away from the first roller 2 is in turn in a operative connection with the diagonally adjacent outer bearing ring 15 of the inner bearing 9 on the first roller journal 7 of the third roller 4 in the form of a tensile stress.Thus, the tensile or compressive stresses alternate in a zigzag pattern along the series of interconnected bearings. Therefore, in the... Fig. In the illustrated embodiment 2, the tensile stresses on the side of the first roller journal 7 always run from the outer bearing 10 of the left roller to the inner bearing 9 of the roller located to its right. Conversely, the compressive stresses on the side of the first roller journal 7 always run from the inner bearing 9 of the left roller to the outer bearing 10 of the roller located to its right. The stress distribution on the side of the second roller journal 8 is exactly the mirror image of that on the first side of the roller journal 7. In the illustrated embodiment in Fig. 2. The compressive stresses always run from the inner bearing 9 of the left roller to the outer bearing 10 of the roller to its right. Conversely, the tensile stresses always run from the left bearing 10 of the left roller to the inner bearing 9 of the roller to its right. This bearing arrangement with the corresponding stress distributions can be continued over any number of axially parallel rollers with roller gaps 5 formed between them.

[0031] The exemplary embodiment in Fig. Figure 3 shows a further embodiment of a roller arrangement 1, in which four bearings 9, 10, 11 are arranged axially side by side on a first roller journal 7 of the first roller 2 and the adjacent first roller journal 7 of the second roller 3. The two middle bearings 11 form a bearing unit in which both bearings 11 are arranged directly next to each other and are preloaded against each other. In contrast, the two outer bearings 9 and 10 are each spaced apart from the middle bearing unit. A compressive stress is generated between, on the one hand, the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the first roller 2 and, on the other hand, the middle bearing unit on the first roller journal 7 of the second roller 3. Furthermore, a tensile stress is generated between, on the one hand, the middle bearing unit on the first roller journal 7 of the first roller 2 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the second roller 3.This arrangement 1 becomes particularly relevant under high loads, where it is necessary to nest the bearings 9, 10, 11 in a multiple arrangement such that the loads in the journals 7, 8 superimpose with the load collectives in such a way that the journal deflection or the bending moment at the roller core transition, i.e. at the roller-side end of the rolling bearing facing the roller core, is reduced to zero Nm. Fig. Figure 3 further shows a roller arrangement 1 consisting of three axially parallel rollers 2, 3, 4, wherein four bearings 9, 10, 11 are also arranged axially next to each other on the first roller journal 7 of the third roller 4, wherein a compressive stress is generated between, on the one hand, the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the second roller 3 and, on the other hand, the middle bearing unit on the first roller journal 7 of the third roller 4, and a tensile stress is generated between, on the one hand, the middle bearing unit on the first roller journal 7 of the second roller 3 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the third roller 4.Furthermore, four bearings 9, 10, 11 are arranged on the second roller journal 8 of the first roller 2 and on the adjacent second roller journal 8 of the second roller 3, wherein, mirroring the opposite side of the first roller journal 7, a compressive stress is generated between, on the one hand, the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the first roller 2 and, on the other hand, the middle bearing unit on the second roller journal 8 of the second roller 3, and a tensile stress is generated between, on the one hand, the middle bearing unit on the second roller journal 8 of the first roller 2 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the second roller 3.Furthermore, four bearings are also arranged on the second roller journal 8 of the third roller 4, wherein, mirroring the first roller journal side 7 opposite, a compressive stress is generated between the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the second roller 3 and, on the other hand, a middle bearing unit on the second roller journal 8 of the third roller 4, and a tensile stress is generated between, on the one hand, the middle bearing unit 11 on the second roller journal 8 of the second roller 3 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the third roller 4.

[0032] Fig. Figure 4 shows a roll arrangement 1 with seven rolls in a line, in which the five innermost rolls each form roll gaps 5 with the adjacent rolls on both their front and rear sides. The finished rolled material web 16 is wound onto a winding reel 19 after passing through all roll gaps 5. Due to the requirement in such roll arrangements 1 to provide the necessary feed in both roll gaps 5 of the affected rolls, the invention is particularly advantageous for such roll arrangements 1 with more than two rolls. In such arrangements 1, the problem arises of alternately pre-tensioning the side of the bearing facing the load without play and simultaneously bringing the bearing face away from the roll gap 5 into contact in order to apply the load required for rolling in the roll gap.

[0033] The Fig. 5a and Fig. Figure 5b shows side views of an embodiment of a roller arrangement 1 according to the invention, with four bearings 9, 10, 11 on each roller journal 7, 8. It is particularly evident how the individual bearings 9, 10, 11 are preloaded relative to each other. Each of the illustrated rollers 2, 3 has four bearings 9, 10, 11 on the illustrated roller journal 7, which are adjusted relative to each other under defined preloads by means of a roller position control unit 12 arranged between the roller journals 7 of both rollers 7, 8. The bearings are nested vertically next to each other on both journals 7 in the axial direction of the rollers 2, 3. It can be seen that the roller position control unit 12 has four actuators 13, which are arranged one above the other. In the example shown, the uppermost and the lowermost actuator 13 generate a tensile stress that acts on the middle bearings 11 of the left roller 2 and the inner and outer bearings of the right roller 3.In contrast, the two central actuators 13 each exert a compressive stress on the inner and outer bearings 9, 10 of the left roller 2 and on the central bearings 11 of the right roller 3. These stresses are transmitted via pressure transmission elements, which are coupled to the corresponding outer bearing rings 14 of the actuated bearings on both sides of the actuator. The pressure transmission elements are arranged horizontally one above the other, forming a drawer-like structure. It can be seen that the inner bearing ring 15 of the front outer bearing 10 of the left roller 2, which is under compressive stress, rests against the rolling elements of the outer bearing ring 14 towards the roller gap 5, and that there is bearing clearance on the side facing away from the roller gap 5.It can also be seen that the inner bearing ring 15 of the front-facing outer bearing 10 of the right-hand roll 3, which is under tensile stress, bears against the rolling elements of the outer bearing ring 14 on the side facing away from the roll gap 5, while there is bearing clearance on the side facing the roll gap 5. The roll position control unit makes it possible to vary the individual tensile and compressive forces of the individual actuators and, in particular, to regulate them via the pressures prevailing in the various roll gaps 5. It is also possible to reverse the pressure configuration, so that the bearings under tensile stress are converted to a compressive stress state and those under compressive stress are converted to a tensile stress state. In the illustrated embodiment, the bearings are cylindrical roller bearings.

[0034] Fig.Figure 6 shows a force flow diagram from roller journal to roller journal using the example of a four-bearing arrangement. In this exemplary embodiment, the dashed outline represents the positioning of the two adjacent rollers 2 and 3 relative to each other. The bearings labeled a1, d1, b2, and c2 in the diagram are positioned by pressure control using two actuators labeled 2 and 3. Simultaneously, the bearings labeled b1 and c1, as well as a2 and d2, are positioned by displacement control via the actuators labeled 1 and 4. This pre-tensions the respective bearings against each other and pre-positions the respective rollers relative to each other. The design can be adapted in the same way at positions in a row, so that the rollers can continuously form the next roller gap relative to each other.

[0035] The features of the invention disclosed in the foregoing description, in the figures and in the claims can be essential for the realization of the invention, both individually and in any combination. Reference symbol list: 1 Roller arrangement 2 First roller 3 Second roller 4 Third Roller 5 Roll gap 6 Axial end 7 First roller journal 8 Second roller journal 9 Inner Camp 10 Outer Camp 11 Middle Camp 12 Roller position control unit 13 Actuator 14 Outer bearing ring 15 inner bearing ring 16 Material track 17 Camp game 18 Compacted material web 19 winding roller 20 Pressure stress 21 Tension F force from delivery F W Power from rolled material h1 Material track h0 compacted material web v rolling speed

Claims

[1] Roll arrangement (1) with at least two axially parallel rolls (2, 3) wherein a roll gap (5) is formed between adjacent rolls, wherein each of the rollers (2, 3) has a roller journal (7, 8) at each of its two axial ends (6) and each roller (2, 3) is supported via its two roller journals (7, 8), wherein at least two bearings (9, 10) are arranged axially next to each other at least on a first roller journal (7) of a first of the rollers (2) and on an adjacent first roller journal (7) of a second of the rollers (3), wherein a compressive stress (20) is generated between an inner bearing (9) on the first roller journal (7) of the first roller (2) and an outer bearing (10) on the first roller journal (7) of the second roller (3) and a tensile stress (21) is generated between an outer bearing (10) on the first roller journal (7) of the first roller (2) and an inner bearing (9) on the first roller journal (7) of the second roller (3) or vice versa. [2] Roller arrangement (1) according to claim 1, with at least three rollers (2, 3, 4) arranged axially parallel, wherein at least on a first roller journal (7) of a third of the rollers (4) two bearings (9, 10) are arranged axially next to each other, wherein a compressive stress (20) is generated between the inner bearing (9) on the first roller journal (7) of the second roller (3) and an outer bearing (10) on the first roller journal (7) of the third roller (4) and a tensile stress (21) is generated between the outer bearing (10) on the first roller journal (7) of the second roller (3) and an inner bearing (9) on the first roller journal (7) of the third roller (4) or vice versa. [3] Roller arrangement (1) according to claim 1 or 2, wherein at least two bearings (9, 10) are arranged at least on a second roller journal (8) of the first roller (2) and on an adjacent second roller journal (8) of the second roller (3), wherein a compressive stress (20) is generated between an inner bearing (9) on the second roller journal (8) of the first roller (2) and an outer bearing (10) on the second roller journal (8) of the second roller (3) in a mirror image to the opposite side of the first roller journal, and a tensile stress (21) is generated between an outer bearing (10) on the second roller journal (8) of the first roller (2) and an inner bearing (9) on the second roller journal (8) of the second roller (3), or vice versa. [4] Roller arrangement (1) according to claim 2, wherein at least two bearings (9, 10) are arranged at least on the second roller journal (8) of the third roller (4), wherein a compressive stress (20) is generated between an inner bearing (9) on the second roller journal (8) of the second roller (3) and an outer bearing (10) on the second roller journal (8) of the third roller (4) in a mirror image to the opposite first roller journal side (7), and a tensile stress (21) is generated between an outer bearing (10) on the second roller journal (8) of the second roller (3) and an inner bearing (9) on the second roller journal (8) of the third roller (4), or vice versa. [5] Roller arrangement (1) according to one of the preceding claims, wherein at least three bearings (9, 10, 11) are arranged axially next to each other at least on a first roller journal (7) of the first roller (2) and the adjacent first roller journal (8) of the second roller (3), wherein a compressive stress (20) is generated between, on the one hand, an inner bearing (9) and an outer bearing (10) on the first roller journal (7) of the first roller (2) and, on the other hand, a middle bearing unit (11) on the first roller journal (7) of the second roller (3), and a tensile stress (21) is generated between, on the one hand, a middle bearing unit (11) on the first roller journal (7) of the first roller (2) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the first roller journal (7) of the second roller (3), or vice versa. [6] Roller arrangement (1) according to claim 5 with reference to claim 2, with at least three rollers (2, 3, 4) arranged axially parallel, wherein at least three bearings (9, 10, 11) are arranged axially next to each other at least on the first roller journal (7) of the third roller (4), wherein a compressive stress (20) is generated between, on the one hand, an inner bearing (9) and an outer bearing (10) on the first roller journal (7) of the second roller (3) and, on the other hand, a middle bearing unit (11) on the first roller journal (7) of the third roller (4), and a tensile stress (21) is generated between, on the one hand, a middle bearing unit (11) on the first roller journal (7) of the second roller (3) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the first roller journal (7) of the third roller (4), or vice versa. [7] Roller arrangement (1) according to claim 5 or 6, wherein at least three bearings (9, 10, 11) are arranged at least on the second roller journal (8) of the first roller (2) and on the adjacent second roller journal (8) of the second roller (3), wherein a compressive stress (20) is generated in a mirror image to the opposite side of the first roller journal (7) between, on the one hand, an inner bearing (9) and an outer bearing (10) on the second roller journal (8) of the first roller (2) and, on the other hand, a middle bearing unit (11) on the second roller journal (8) of the second roller (3), and a tensile stress (21) is generated between, on the one hand, a middle bearing unit (11) on the second roller journal (8) of the first roller (2) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the second roller journal (8) of the second roller (3), or vice versa. [8] Roller arrangement (1) according to one of claims 5 to 7 with reference back to claim 2, wherein at least three bearings (9, 10, 11) are arranged at least on the second roller journal (8) of the third roller (4), wherein a compressive stress (20) is generated in a mirror image to the opposite first roller journal side (7) between, on the one hand, an inner bearing (9) and an outer bearing (10) on the second roller journal (8) of the second roller (3) and, on the other hand, a middle bearing unit (11) on the second roller journal (8) of the third roller (4), and a tensile stress (21) is generated between, on the one hand, a middle bearing unit (11) on the second roller journal (8) of the second roller (3) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the second roller journal (8) of the third roller (4), or vice versa. [9] Roll arrangement (1) according to one of the preceding claims with reference back to claim 2, wherein a material to be rolled is passed alternately through the roll gap (5) in opposite directions from roll gap (5) to roll gap (5). [10] Roll arrangement (1) according to one of the preceding claims, wherein a roll position control unit (12) is arranged between the roll journals (7, 8) to generate the tensile and / or compressive stresses (20), via which the respective roll gap adjustments are realized. [11] Roller arrangement (1) according to claim 10, wherein the roller position control unit (12) has a pressure-controlled actuator (13). [12] Roller arrangement (1) according to claim 10 or 11, wherein the actuator has a hydraulic, mechanical or electrical actuating element. [13] Roller arrangement (1) according to one of claims 10 to 12, wherein the roller position control unit (12) is in operative connection with the outer bearing rings (14) of the bearings (9, 10, 11). [14] Roller arrangement (1) according to any one of claims 5 to 13, wherein the central bearing unit (11) has one or more bearings. [15] Roller arrangement (1) according to one of the preceding claims, wherein the bearing (9, 10, 11) comprises a rolling and / or a sliding bearing.

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