ROLLER ARRANGEMENT
Patent Information
- Application Number
- MX2022007031
- Authority / Receiving Office
- MX · MX
- Patent Type
- Patents
- Current Assignee / Owner
- Priority Date
- 2019-12-20
- Filing Date
- 2022-06-08
- Publication Date
- 2026-06-12
- Estimated Expiration
- 2040-11-30
AI Technical Summary
Conventional roller mills struggle with processing materials that develop different material properties during continuous production, leading to varying rolling forces and resulting in inconsistent material thickness and properties due to the collapse of the nip and separation of rollers.
A roller arrangement with axially parallel rollers featuring a compressive and tensile force system between adjacent bearings, allowing for adjustable contact lines and reduced bearing clearance through a roller position control unit with pressure-controlled actuators.
Enables precise adjustment of feed and stress distribution across multiple rollers, maintaining consistent material thickness and quality even with non-homogeneous materials by alternating tensile and compressive stresses, reducing bearing clearance and shaft deflection.
Smart Images
Figure MX434791B0
Abstract
Description
ROLLER ARRANGEMENT The invention relates to a roller arrangement having at least two axially parallel rollers, forming a respective contact line / point / narrowing between adjacent rollers, each roller having a roller shaft at each of its two axial ends and each roller being mounted through its two roller shafts, at least two axially adjacent bearings being arranged at least on a first roller shaft of a first roller and on a first adjacent roller shaft of a second roller. In a roll mill, the rolls are positioned against each other by bearings in chokes. The distance between the rolls can be adjusted by advancing at least one of them. When processing conventional materials with homogeneous material properties, the rolls are pressed against each other in the more or less constant direction of force flow through the rolled material toward the opposite recess of the bearings and remain there. This does not pose a problem for processing quality as long as the force directions are more or less constant and the pressure at the contact line and the associated feed remain reasonably constant. For most rolling processes, this feed is sufficiently accurate because there are no large changes in load. Conventional roller mills of this type, on the other hand, are not suitable for processing materials that, during continuous production, develop different material properties as a result of the rolling process. This process generates varying forces at the contact line. Different density distributions within a material web result in varying rolling forces, causing the contact line to collapse or the rollers to separate under pressure. This leads to varying material thicknesses and different properties in the finished rolled product, such as a material web, film, coated material web, or multi-layer material web. In particular, in the case of a roller arrangement with more than two rollers in a line and a continuous and sinuous passage of the rolled material through the various contact lines, the problem arises of alternately preloading the side of the bearing that is oriented towards the load without clearance and, on the other hand, making the side of the face that is looking away from the contact line come into contact so that the load necessary for rolling can be applied on both contact lines on both sides of the roller. Therefore, the object of the present invention is to improve a roller arrangement in such a way as to allow improved feeding while at the same time achieving reduced bearing clearance. This objective is achieved by the arrangement of rollers according to claim 1. Advantageous embodiments of the invention are the subject of the dependent claims. Accordingly, a roller arrangement is proposed with at least two axially parallel rollers, where a respective contact line is formed between adjacent rollers, where each roller has a roller axis at both of its two axial ends and each roller is mounted through its two roller axes, where at least two respective bearings are arranged axially adjacent to each other at least on a first roller axis of a first roller and an adjacent first roller axis of a second roller, where a compressive stress is generated between an inner bearing on the first roller axis of the first roller and an outer bearing on the first roller axis of the second roller, and a tensile stress is generated between an outer bearing on the first roller axis of the first roller and an inner bearing on the first roller axis of the second roller, or vice versa.Conversely, tensile and / or compressive forces can also be reversed, provided they exist between diagonally spaced adjacent bearings. This transverse tensioning allows two roller bearings to be tensioned against each other in series on the roller shafts, creating a force guide engagement and thus enabling the necessary clearance. In one embodiment, in contrast to this, it may be provided that only compressive or tensile stresses are present in all bearings. Furthermore, the roller arrangement may have at least three axially parallel rollers, where two bearings may be axially adjacent to each other, at least on the first roller axis of a third roller. A compressive stress is generated between the inner bearing on the first roller axis of the second roller and an outer bearing on the first roller axis of the third roller, and a tensile stress is generated between the outer bearing on the first roller axis of the second roller and an inner bearing on the first roller axis of the third roller, or vice versa. The stress states between diagonally spaced bearings may alternate, particularly from one roller to another. This means that the inner bearing of the center / intermediate roller may be under tensile stress toward the first roller and under compressive stress toward the third roller, or vice versa.Furthermore, this means that the outer bearing of the center 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 a bearing on both sides can be equal. Therefore, it can be expected that any number of additional rollers with the same bearing configuration will be arranged axially parallel to each other, and the stress curves across the bearings will continue as described above. Furthermore, at least two bearings may be arranged on both a second roller shaft of the first roller and an adjacent second roller shaft of the second roller. A compressive force is generated between an inner bearing on the second roller shaft of the first roller and an outer bearing on the second roller shaft of the second roller, mirrored to the opposite side of the first roller shaft. A tensile force is generated between an outer bearing on the second roller shaft of the first roller and an inner bearing on the second roller shaft of the second roller, or vice versa. In this context, "mirror-reversed" means reflected across a radial axis perpendicular to the rollers. Specifically, this means that the same tensile or compressive forces can be applied to the inner and outer bearings of opposing roller bearings. Furthermore, at least two bearings may be arranged at least on the second roller shaft of the third roller, where a compressive stress is generated between an inner bearing on the second roller shaft of the second roller and an outer bearing on the second roller shaft of the third roller, mirrored towards the opposite side of the shaft of the first roller, and a tensile stress is generated between an outer bearing of the second shaft of the second roller and an inner bearing on the second roller shaft of the third roller, or vice versa. In particular, it may be provided that at least three bearings are arranged axially adjacent to each other at least on a first roller shaft of the first roller and the adjacent first roller shaft 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 shaft of the first roller and, on the other hand, a center bearing unit on the first shaft of the second roller, and a tensile stress is generated between, on the one hand, a center bearing unit on the first roller shaft of the first roller and, on the other hand, an inner bearing and an outer bearing on the first roller shaft of the second roller, or vice versa.This arrangement becomes particularly relevant for high loads where it is necessary to nest the bearings in a multiple arrangement in such a way that the loads on the shafts overlap with the load collectives in such a way that the shaft bending or bending moment towards the MA / t / ZUZZ / U^OO^D transition of the roller pack (“bale”), i.e., at the end of the roller side of the roller bearing directed towards the roller pack, is reduced to zero Nm. Furthermore, at least three axially parallel rollers may be provided, with at least three axially adjacent bearings arranged on the first roller axis of the third roller. A compressive force is generated between, on the one hand, an inner and an outer bearing on the first roller axis of the second roller and, on the other hand, a central bearing unit on the first roller axis of the third roller. A tensile force is generated between, on the one hand, a central bearing unit on the first roller axis of the second roller and, on the other hand, an inner and an outer bearing on the first roller axis of the third roller, or vice versa. The tensile forces between diagonally spaced bearings may alternate, particularly from one roller to another.This means that the inner bearing of the center 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 center roller can be under compressive stress towards the center bearing of the first roller and under tensile stress towards the center bearing of the third roller, or vice versa. In particular, the stresses acting on a bearing on both sides can be equal. Therefore, it can be expected that any number of additional rollers with the same bearing configuration will be arranged axially parallel to each other, and the stress curves across the bearings will continue as described above. Furthermore, at least three bearings may be arranged on both the second roller shaft of the first roller and the adjacent second roller shaft of the second roller. A mirror-image compressive force is generated on the opposite side of the first roller shaft between, on one side, an inner and an outer bearing on the second roller shaft of the first roller and, on the other side, a central bearing unit on the second roller shaft of the second roller. A tensile force is also generated between, on one side, a central bearing unit on the second roller shaft of the first roller and, on the other side, an inner and an outer bearing on the second roller shaft of the second roller, or vice versa. In this context, "mirror-image" means reflected across a radial central axis running perpendicular to the rollers.Thus, in particular, the same type of tension can be provided, on the one hand, in both the inner and outer bearings of opposing roller shafts and, on the other hand, in both center bearings of opposing roller bearings. It may also be provided that the states of. MA / t / ZUZZ / U^OO^O individual effort of the directly adjacent facing support sides are complementary to each other. Furthermore, at least three bearings may be arranged on at least the second roller shaft of the third roller, generating a mirror-image compressive stress on the opposite side of the first roller shaft between, on the one hand, an inner and an outer bearing on the second roller shaft of the second roller and, on the other hand, a central bearing unit on the second roller shaft of the third roller. A tensile stress is also generated between, on the one hand, a central bearing unit on the second roller shaft of the second roller and, on the other hand, an inner and an outer bearing on the second roller shaft of the third roller, or vice versa. By means of such a bearing arrangement and bearing stress, a state of compression or tension is generated between transversely opposed roller shafts, with the pressure curves of similar adjacent clamps having the same curve.For example, compressive stresses from one roller shaft to another roller shaft always extend from the outer and inner bearings into the center bearing unit, while tensile stresses always extend from the center bearing unit outward from the inner and outer bearings. It may be possible to guide a material to be rolled through the rollers alternately in opposite directions, from one contact line to the other. In this way, the inner rollers can be used for rolling / laminating from both sides. Due to the different rotational directions of the adjacent rollers, it is necessary to guide the material alternately from above and below through the contact lines of the adjacent rollers. In addition, to generate the tensile and / or compressive forces, a roller position control unit may be arranged between the roller shafts, through which the respective adjustments of the contact lines are made. In this case, the roller bearing control unit can have a pressure-controlled actuator. Preferably, a separate actuator is provided between each pair of coupled bearings. A pressure-controlled actuator has the advantage, especially for materials with non-homogeneous density distribution, that the feed can be adjusted particularly effectively. Specifically, the actuator may be hydraulic, mechanical, or electric. Alternatively, the actuator may consist of a hydraulic actuator, a mechanical spindle, and a linear motor. ML / t / ZUZZ / U^OO^O In addition, the roller bearing control unit can be operationally connected to the outer rings of the bearings. In particular, the center bearing unit may have one or more, preferably two, bearings. If the center bearing unit has two bearings, these may be arranged directly side by side in the axial direction. Furthermore, adjacent bearings of the center bearing unit may be axially braced to each other. Additionally, the bearing may include a bearing and / or a sleeve bearing. Examples of embodiments of the invention are explained with reference to the following figures. Thus it shows: MA / t / ZUZZ / U^OO^O Figure 1a Figure 1b Figure 2 Figure 3 Figure 4 Figure 5a Figure 5b Figure 6 is a cross-sectional view of a roller arrangement showing the process forces in the rolling process; It is a schematic view of a prior art roller arrangement showing the process forces acting on the bearings in the rolling process; is a schematic view of an embodiment of a roller arrangement according to the invention; is a schematic view of another embodiment of an inventive roller arrangement; It is a cross-sectional view of an example of a roller arrangement with a plurality of rollers arranged in series; is a side view of an example of a roller arrangement according to the invention with four bearings per roller shaft; is a semi-transparent side view of an example of a roller arrangement according to the invention with four bearings per roller shaft; It is a view of a force polygon of an embodiment of a roller arrangement according to the invention with four bearings per roller shaft. In a roller mill, the rollers are supported by bearings in chocks. Figure 1a shows a roller arrangement 1 of a roller mill with two axially parallel rollers 2, 3, between which a contact line of width hi is formed. In the side view shown, the roller bearing arrangement consists of an inner bearing ring 15 and an outer bearing ring 14, the inner bearing ring 15 being rotatably mounted. The outer bearing rings 14 are anchored in the chocks. As the material strip 16, with a thickness ho, passes through the contact / narrowing line 5, the material strip 16 is reduced to a compacted material strip 18 with a material thickness of height hi.Due to the more or less constant direction of force flow through the material strip 16 of the rolled material, the rollers are pressed against each other in the opposite recess of the bearings and remain there. The resulting process forces exerted perpendicular to the direction of advance of the material strip 16 are the respective forces of the rolled material Fw from the inner bearing ring 15 to the outer bearing ring 14. At the same time, the linear force F from the outer bearing rings 14 acts on the inner bearing rings 15. As a result, the inner bearing rings 15 are pressed outward toward the inward of the outer bearing rings 14, so that on the side of the outer bearing ring 14 facing the bearing space 5 there is a respective bearing clearance 17. Figure 1b also shows a representation of the process forces according to Figure 1a, which shows a top view of the bearing arrangement in Figure 1a. Two rollers 2, 3 are arranged axially parallel to each other, forming a contact line 5. Each roller 2, 3 has roller shafts 7, 8 at its axial ends, with a bearing 9 arranged on each roller shaft 7, 8, so that the roller 2, 3 is supported by this bearing arrangement. When a strip of material 16 passes through the contact line of roller 5, process forces perpendicular to the direction of passage are generated. These forces are transmitted through the roller shafts to the roller shafts and then from the shafts to the inner bearing rings 15 arranged on them, which in turn are supported by the outer bearing rings 14.As a result of these forces Fw from the rolled material, the inner bearing rings 15 are pressed outwards into the outer bearing rings 14, creating a bearing clearance 17 inside each bearing. Furthermore, the linear force F from the feed in the direction of the roller contact line 5 is exerted on the outer bearing rings 14 by feeding the bearings against each other, i.e., adjusting the width of the bearing clearance 5. The design examples according to the invention shown in Figures 2 and 3 have the advantage, particularly in the case of large load changes caused by the laminated material, of being able to react to load changes independently with micrometer precision from the roller contact line 5 to the roller contact line 5 by means of the provided roller position control, while simultaneously eliminating bearing backlash. With the arrangement 1 of the roller bearings relative to each other described in the invention, it is possible to arrange the shims with the applied force, as well as the opposing clearance feeds, in a nested configuration, each arranged in a cascade. In a first embodiment according to Figure 2, it is possible to provide ML / t / ZUZZ / U^OO^O Two roller bearings for each roller shaft 7, 8 in a row of rollers 2, 3, 4 arranged axially parallel and clamped together such that the force guide nesting results in the necessary backlash-free position. In the example shown, the outer bearing rings 14 of diagonally adjacent bearings are in an operational connection that generates tensile or compressive stress between the bearings. For example, the outer bearing ring 15 of the outer bearing 10 on the first roller shaft 7 of the first roller 2 is under tensile stress with the diagonally adjacent outer bearing ring 15 of the inner bearing 9 on the first roller shaft 7 of the second roller 3.Furthermore, there is a compressive force between the side of the outer bearing ring 15 of bearing 9 on the first roller shaft 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 shaft 7 of the third roller 4. At the same time, there is an effective connection between the outer bearing ring 15 of the inner bearing 9 on the first roller shaft 7 of the first roller 2 and the outer bearing ring 15 of the outer bearing 10 on the first roller shaft 7 of the second roller 3 in the form of a compressive force.The side of the outer bearing ring 15 of the outer bearing 10 on the first roller shaft 7 of the second roller 3, facing away from the first roller 2, is in turn in operative connection with the diagonally adjacent outer bearing ring 15 of the inner bearing 9 on the first roller shaft 7 of the third roller 4, in the form of a tensile stress. Therefore, tensile or compressive stresses always alternate in a zigzag pattern along the series of bearings in operative connection with each other. Thus, in the example shown in Figure 2, the tensile stresses on the side of the first roller shaft 7 always extend from the outer bearing 10 of the left roller to the inner bearing 9 of the roller adjacent to the right.Conversely, the compressive stresses on the side of the first roller shaft 7 always extend from the inner bearing 9 of the left roller to the outer bearing 10 of the adjacent roller on the right. The stress curves on the side of the second roller shaft 8 are exact mirror images of those on the first roller shaft 7 side. In the example shown in Figure 2, the compressive stresses always extend from the inner bearing 9 of the left roller to the outer bearing 10 of the adjacent roller on the right. Conversely, the tensile stresses always extend from the left bearing 10 of the left roller to the inner bearing 9 of the adjacent roller on the right. This bearing arrangement with the corresponding stress curves can continue over any number of axially parallel rollers with contact lines 5 formed between them. The embodiment in Figure 3 shows another embodiment of a roller arrangement 1, in which four bearings 9, 10, and 11 are arranged axially adjacent to each other on a first roller shaft 7 of the first roller 2 and the adjacent first roller shaft 7 of the second roller 3. In this case, the two central bearings 11 form a bearing unit in which both bearings 11 are arranged directly next to each other and braced against each other. Conversely, the two outer bearings 9 and 10 are each arranged at a distance from the central bearing unit. A compressive force is generated between, on the one hand, the inner bearing 9 and the outer bearing 10 on the first roller shaft 7 of the first roller 2 and, on the other hand, the central bearing unit on the first roller shaft 7 of the second roller 3.Furthermore, a tensile stress is generated between, on the one hand, the central bearing unit on the first roller shaft 7 of the first roller 2 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the first roller shaft 7 of the second roller 3. This arrangement 1 becomes particularly relevant for high loads where it is necessary to nest the bearings 9, 10, 11 in a multiple arrangement in such a way that the loads on shafts 7, 8 overlap with the load collectives in such a way that the bending or bending moment of the shaft towards the roller pack transition, i.e., at the roller-side end of the roller bearing facing the roller pack, is reduced to zero Nm.Figure 3 further shows a roller arrangement 1 comprising three axially parallel rollers 2, 3, 4, four bearings 9, 10, 11 also arranged axially adjacent to each other on the first roller shaft 7 of the third roller 4, a compressive stress being generated between, on the one hand, the inner bearing 9 and the outer bearing 10 on the first roller shaft 7 of the second roller 3 and, on the other hand, the center bearing unit on the first roller shaft 7 of the third roller 4, and a tensile stress being generated between, on the one hand, the center bearing unit on the first roller shaft 7 of the second roller 3 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the first roller shaft 7 of the third roller 4.Furthermore, four bearings 9, 10, 11 are arranged respectively on the second roller shaft 8 of the first roller 2 and on the adjacent second roller shaft 8 of the second roller 3, generating a mirror-image compressive force to the opposite first roller shaft 7 between, on the one hand, the inner bearing 9 and the outer bearing 10 on the second roller shaft 8 of the first roller 2 and, on the other hand, the central bearing unit on the second roller shaft 8 of the second roller 3, and a tensile force is generated between, on the one hand, the central bearing unit on the second shaft 8 of the first roller 2 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the second roller shaft 8 of the second roller 3. In addition, four bearings are also arranged on the second roller shaft 8 of the third roller 4, so that MA / t / ZUZZ / U^OO^O generates a compressive stress between the inner bearing 9 and the outer bearing 10 on the second roller shaft 8 of the second roller 3 and, on the other hand, a central bearing unit on the second roller shaft 8 of the third roller 4 mirror-inverted to the opposite side of the first roller shaft 7, and a tensile stress is generated between, on the one hand, the central bearing unit 11 on the second roller shaft 8 of the second roller 3 and, on the other hand, the inner bearing 9 and the outer bearing 10 on the second roller shaft 8 of the third roller 4. Figure 4 shows a roller arrangement 1 with seven rollers in line, in which the five inner rollers form contact lines 5 with the respective adjacent rollers at the front and rear. The finished rolled material web 16 is wound onto a take-up reel 19 after passing through all the roller contact lines 5. Due to the requirement in such roller arrangements 1 to provide the necessary feed on both contact lines 5 of the rollers in question, the invention is particularly advantageous, especially for such roller arrangements 1 with more than two rollers. In such arrangements 1, the problem arises of alternately preloading the bearing side facing the load without clearance and simultaneously bringing into contact the housing side facing away from the contact line 5 in order to apply the load required by rolling on the contact line. Figures 5a and 5b each show side views of an embodiment of a roller arrangement 1 according to the invention with four bearings 9, 10, 11 per roller shaft 7, 8, showing in particular how the individual bearings 9, 10, 11 are braced against each other. Each of the rollers 2, 3 shown herein has four bearings 9, 10, 11 on the roller shaft 7 shown, which are adjusted against each other under preloads defined by means of a roller bearing control unit 12 disposed between the roller shafts 7 of both rollers 7, 8. The bearings are nested side by side on both shafts 7 vertically in the axial direction of the rollers 2, 3. It can be seen that the roller bearing control unit 12 has four actuators 13, which are arranged one above the other.In the example shown, the upper and lower actuators 13 generate a tensile force acting on the center bearings 11 of the left roller 2 and the inner and outer bearings of the right roller 3. Conversely, the two center actuators 13 each exert a compressive force on the inner and outer bearings 9, 10 of the left roller 2 and on the center bearings 11 of the right roller 3. The stresses are transmitted through pressure transmission elements that are coupled on both sides of the actuator to the corresponding outer bearing rings 14 of the driven bearings. The pressure transmission elements are arranged horizontally, one below the other, forming a box structure. It can be seen that the inner bearing ring 15 of the front-side outer bearing 10 of the left roller 2, which is under compressive stress, rests against the bearing elements of the outer bearing ring 14 towards the contact line 5 and that there is bearing clearance on the side facing away from the contact line 5. Similarly, it can be seen that the inner bearing ring 15 of the front-side outer bearing 10 of the right roller 3, which is under tensile stress, rests against the bearing elements of the outer bearing ring 14 on the side facing away from the contact line 5 and that there is bearing clearance on the side facing towards the contact line 5.Through the roller bearing control unit, it is possible to vary the individual tensile and compressive forces of the individual actuators and, in particular, to control them by means of the pressures prevailing on the various contact lines of the rollers 5. Furthermore, it is possible to interchange the pressure configuration so that bearings under tensile stress are transferred to a compressive stress and those under compressive stress are transferred to a tensile stress condition. In the embodiment shown, the bearings are cylindrical roller bearings. Figure 6 shows a force flow diagram from one roller shaft to another using a quadruple bearing arrangement as an example. In this design example, the frame highlighted with a dashed line feeds the two adjacent rollers 2 and 3 to each other. The bearings labeled a1, d1, b2, and c2 in the illustration are pressure-controlled by two actuators labeled 2 and 3. Simultaneously, the bearings labeled b1, c1, a2, and d2 are held in position by actuators labeled 1 and 4. In this way, the respective bearings are preloaded against each other and against one another, and the respective rollers are prepositioned relative to each other. Similarly, the design can be adapted in the positions along a row so that the rollers can be continuously positioned relative to each other to represent the respective subsequent line of contact. The features of the invention described in the preceding description, both in the figures and in the claims, may be essential to the realization of the invention either individually or in any combination. List of reference numbers: Roller arrangement First roller Second roller Third roller Roller contact line Axial end First roller shaft Second roller shaft Inner bearing Outer bearing Center bearing Roller bearing control unit Actuator Outer bearing ring Inner bearing ring Material strip Bearing clearance Belt of compacted material Collection reel Compressive strength Tensile stress F Line force Fw Force of the rolled material h1 Height of material strip hO Height of compacted material strip v Rolling speed
Claims
1. A roller arrangement (1) with at least two axially parallel rollers (2, 3), characterized in that a respective line of contact (5) is formed between adjacent rollers, each of the rollers (2,3) having a roller axis (7, 8) at both axial ends (6), each roller (2, 3) being pivotally mounted through its two roller axes (7, 8), at least two bearings (9,10) being arranged axially adjacent to each other at least on a first roller axis (7) of a first roller (2) and on an adjacent first roller axis (7) of a second roller (3),where a compressive stress is generated between an inner bearing (9) on the first roller shaft (7) of the first roller (2) and an outer bearing (10) on the first roller shaft (7) of the second roller (3) and a tensile stress is generated between an outer bearing (10) on the first roller shaft (7) of the first roller (2) and an inner bearing (9) on the first roller shaft (7) of the second roller (3) or vice versa.
2. The roller arrangement (1) according to claim 1, having at least three axially parallel rollers (2, 3, 4), characterized in that two bearings (9, 10) are axially adjacent to each other at least on a first roller shaft (7) of a third roller (4), wherein a compressive stress is generated between the inner bearing (9) on the first roller shaft (7) of the second roller (3) and an outer bearing (10) on the first roller shaft (7) of the third roller (4), and wherein a tensile stress is generated between the outer bearing (10) of the first roller shaft (7) of the second roller (3) and an inner bearing (9) on the first roller shaft (7) of the third roller (4), or vice versa.
3. The roller arrangement (1) according to claim 1 or 2, characterized in that at least two bearings are arranged on at least a second roller shaft of the first roller and on an adjacent second roller shaft of the second roller, wherein a compressive stress is generated between an inner bearing on the second roller shaft of the first roller and an outer bearing on the second roller shaft of the second roller mirrored towards the opposite side of the first roller shaft, and a tensile stress is generated between an outer bearing on the second shaft of the first roller and an inner bearing on the second roller shaft of the second roller, or vice versa.
4. The roller arrangement (1) according to claim 2 or 3, characterized in that at least two bearings (9, 10) are arranged at least on the second roller shaft (8) of the third roller (4), wherein a compressive stress is generated between an inner bearing (9) on the second roller shaft (8) of the second roller (3) and an outer bearing (10) on the second roller shaft (8) of the third roller (4) mirror-inverted towards the opposite side of the first roller shaft (7), and a tensile stress is generated between an outer bearing (10) on the second roller shaft (8) of the second roller (3) and an inner bearing (9) on the second roller shaft (8) of the third roller (4), or vice versa.
5. The roller arrangement (1) according to any of the preceding claims, characterized in that at least three bearings (9, 10, 11) are arranged axially adjacent to each other at least on a first roller shaft (7) of the first roller (2) and the adjacent first roller shaft (8) of the second roller (3), wherein a compressive stress is generated between, on the one hand, an inner bearing (9) and an outer bearing (10) of the first roller shaft (7) of the first roller (2) and, on the other hand, a central bearing unit (11) on the first roller shaft (7) of the second roller (3), and a tensile stress is generated between, on the one hand, a central bearing unit (11) on the first roller shaft (7) of the first roller (2) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the first roller shaft (7) of the second roller (3), or vice versa.
6. The roller arrangement (1) according to claim 5, having at least three axially parallel rollers (2, 3, 4), characterized in that at least three bearings (9, 10, 11) are axially arranged side by side at least on the first roller shaft (7) of the third roller (4), wherein a compressive stress is generated between, on the one hand, an inner bearing (9) and an outer bearing (10) of the first roller shaft (7) of the second roller (3) and, on the other hand, a central bearing unit (11) on the first roller shaft (7) of the third roller (4), and a tensile stress is generated between, on the one hand, a central bearing unit (11) on the first roller shaft (7) of the second roller (3) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the first roller shaft (7) of the third roller (4), or vice versa.
7. The roller arrangement (1) according to claim 5 or 6, characterized in that at least three bearings (9, 10, 11) are arranged at least on both the second roller shaft (8) of the first roller (2) and the adjacent second roller shaft (8) of the second roller (3), wherein a mirror-image compressive force is generated toward the opposite side of the first roller shaft (7) between, on the one hand, an inner bearing (9) and an outer bearing (10) on the second roller shaft (8) of the first roller (2) and, on the other hand, a central bearing unit (11) on the second roller shaft (8) of the second roller (3), and a tensile force is generated between, on the one hand, a central bearing unit (11) on the second roller shaft (8) of the first roller (2) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the second roller shaft (8) of the second roller (3). roller (8) of the second roller (3), or vice versa.
8. The roller arrangement (1) according to any one of claims 5 to 7, characterized in that at least three bearings (9, 10, 11) are arranged at least on the second roller shaft (8) of the third roller (4), wherein a mirror-inverted compressive force is generated towards the opposite side of the first roller shaft (7) between, on the one hand, an inner bearing (9) and an outer bearing (10) on the second roller shaft (8) of the second roller (3) and, on the other hand, a central bearing unit (11) on the second roller shaft (8) of the third roller (4), and a tensile force is generated between, on the one hand, a central bearing unit (11) on the second roller shaft (8) of the second roller (3) and, on the other hand, an inner bearing (9) and an outer bearing (10) on the second roller shaft (8) of the third roller (4), or vice versa.
9. The roller arrangement (1) according to one of the preceding claims, characterized in that a material to be rolled is passed through the contact lines (5) alternately in opposite directions from one contact line (5) to another contact line (5).
10. The roller arrangement (1) according to one of the preceding claims, characterized in that for the generation of tensile and / or compressive stresses, a respective roller bearing control unit (12) is arranged between the roller shafts (7, 8), through which adjustments are made.
11. The roller arrangement (1) according to claim 10, characterized in that the roller bearing control unit (12) comprises a pressure-controlled actuator (13).
12. The roller arrangement (1) according to claim 10 or 11, characterized in that the actuator comprises a hydraulic, mechanical or electric actuator.
13. The roller arrangement (1) according to any of claims 10 to 13, characterized in that the roller bearing control unit (12) is in operative connection with each of the outer bearing rings (14) of the bearings (9,10,11).
14. The roller arrangement (1) according to any of claims 5 to 13, characterized in that the central bearing unit (11) comprises one or more bearings.
15. The roller arrangement (1) according to one of the preceding claims, characterized in that the bearing (9, 10, 11) comprises a roller bearing and / or a plain bearing.