Roller device

Abstract

The invention relates to a first roller arrangement (1) having at least two axially parallel arranged rollers (2, 3), wherein between adjacent rollers a roller gap (5) is formed, wherein each of the rollers (2, 3) has a roller journal (7, 8) on each of its two axial ends (6) and each roller (2, 3) is supported via its two roller journals (7, 8), wherein at least on the first roller journal (7) of a first roller (2) and on the adjacent first roller journal (7) of a second roller (3) of the rollers at least two bearings (9, 10) are arranged axially side by side, wherein between the inner bearing (9) on the first roller journal (7) of the first roller (2) and the outer bearing (10) on the first roller journal (7) of the second roller (3) a compressive stress and between the outer bearing (10) on the first roller journal (7) of the first roller (2) and the inner bearing (9) on the first roller journal (7) of the second roller (3) a tensile stress occurs or vice versa.

Description

TECHNICAL FIELD

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

[0002] In a roller mill, the rollers are positioned to one another by means of the support portions in the frame. The distance between the rollers can be set by the feed of at least one roller. In the processing of conventional materials having uniform material properties, the rollers are pressed to the opposite soffits of the support portions by a more or less constant force flow direction through the roller pressure and remain there. This is not a problem for the processing quality as long as the force direction is more or less constant and the pressure in the roller gap or the feed that follows it remains constant to a certain extent. For most roller processes, this feed is sufficiently precise, since there are no large load changes.

[0003] In contrast, this conventional type of roller mill is not suitable for the processing of materials in which the roller pressure process and the construction of different material properties in the course thereof and thus different process forces in the roller gap are involved in the course of continuous manufacture. By different density distributions in the material web to be manufactured, different roller pressure totals occur, which either coincide with one another or push the rollers away from one another. This results in different material thicknesses and different properties of the finished roller pressure in the subsequent finished roller pressure, which is a material web, a film, a coating material web or a multi-layer material web.

[0004] A problem that exists, in particular, in the case of a roller arrangement having more than two rollers in a line and a continuous meandering guidance of the roller pressure through the individual roller gaps is that the load-facing sides of the support portions are alternately preloaded without play on the one hand and the soffit sides facing away from the roller gap are brought into contact on the other hand in order to be able to exert the required load for the roller pressure in the two roller gaps on both sides of the rollers. SUMMARY

[0005] It is therefore the task of the invention to improve a roller arrangement in such a way that an improved feed is achieved and at the same time a small bearing play is achieved.

[0006] This task is solved by the proposed roller arrangement. Advantageous embodiments of the invention are the subject matter of the dependent claims, respectively.

[0007] According to the application, a roller arrangement is proposed, having at least two rollers which are arranged axially parallel to one another, 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 is supported by its two roller journals, wherein at least on the first roller journal of a first roller and on the adjacent first roller journal of a second roller at least two bearings are arranged axially side by side, wherein a compressive stress occurs between the inner bearing on the first roller journal of the first roller and the outer bearing on the first roller journal of the second roller and a tensile stress occurs between the outer bearing on the first roller journal of the first roller and the inner bearing on the first roller journal of the second roller, or vice versa. Contrary here means that the tensile stress and / or the compressive stress can also be exchanged, as long as the tensile stress and / or the compressive stress occurs between diagonally spaced adjacent bearings. By this crosswise tensioning, two roller supports can be tensioned on the roller journals relative to one another in a row in such a way that a force-guided nesting occurs, so that the necessary gap-free position can be achieved.

[0008] In an embodiment, it can be provided differently that only a compressive stress or a tensile stress is provided on all bearings.

[0009] Furthermore, the roller arrangement can have at least three rollers which are arranged axially parallel to one another, wherein at least on the first roller journal of a third roller two bearings can be arranged axially side by side, wherein a compressive stress occurs between the inner bearing on the first roller journal of the second roller and the outer bearing on the first roller journal of the third roller and a tensile stress occurs between the outer bearing on the first roller journal of the second roller and the inner bearing on the first roller journal of the third roller, or vice versa. The stress state between the diagonally spaced bearings can here in particular alternate from roller to roller. That is to say, the inner bearing of the middle roller is under tensile stress in the direction towards the first roller and under compressive stress in the direction 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 the bearings on both sides can be of the same size. It can thus be provided that an arbitrary number of further rollers with the same bearing configuration are arranged axially parallel and side by side and the stress distribution through the bearings is continued accordingly to the above description.

[0010] Furthermore, at least two bearings can be arranged on the second roll neck of the first roll and on the adjacent second roll neck of the second roll, respectively, wherein, mirror-symmetrically to the opposing first roll neck sides, compressive stress occurs between the inner bearing on the second roll neck of the first roll and the outer bearing on the second roll neck of the second roll and tensile stress occurs between the outer bearing on the second roll neck of the first roll and the inner bearing on the second roll neck of the second roll, or vice versa. Mirror-symmetry here means mirror-symmetry in the radial direction perpendicular to the roll axis. Thus, in particular, tensile stress or compressive stress of the same direction can be exerted on both inner bearings and on both outer bearings of the opposing roll necks.

[0011] Furthermore, at least two bearings can be arranged on the second roll neck of the first roll and on the adjacent second roll neck of the second roll, respectively, wherein, mirror-symmetrically to the opposing first roll neck sides, compressive stress occurs between the inner bearing on the second roll neck of the first roll and the outer bearing on the second roll neck of the second roll and tensile stress occurs between the outer bearing on the second roll neck of the first roll and the inner bearing on the second roll neck of the second roll, or vice versa. Mirror-symmetry here means mirror-symmetry in the radial direction perpendicular to the roll axis. Thus, in particular, tensile stress or compressive stress of the same direction can be exerted on both inner bearings and on both outer bearings of the opposing roll necks.

[0012] In particular, it can be provided that at least three bearings are arranged axially side by side on the first roll neck of the first roll and on the adjacent first roll neck of the second roll, respectively, wherein compressive stress occurs between the inner bearing and the outer bearing on the first roll neck of the first roll and the intermediate bearing unit on the first roll neck of the second roll, respectively, and tensile stress occurs between the intermediate bearing unit on the first roll neck of the first roll and the inner bearing and the outer bearing on the first roll neck of the second roll, respectively, or vice versa. This arrangement is in particular important in the case of high loads, in which the bearings in the multiple arrangement are nested such that the load in the roll neck and the load set add up such that the roll neck bending or the bending moment on the roll side end of the rolling bearing towards the roll body transitions are reduced to zero Nm.

[0013] Furthermore, it is possible to provide at least three rollers arranged axially in parallel, wherein at least three bearings are arranged axially side by side on the first roller journal of the third roller, wherein either a compressive stress occurs between the inner bearing and the outer bearing on the first roller journal of the second roller on the one hand and the intermediate bearing unit on the first roller journal of the third roller on the other hand and a tensile stress occurs between the intermediate bearing unit on the first roller journal of the second roller on the one hand and the inner bearing and the outer bearing on the first roller journal of the third roller on the other hand or vice versa. The stress states between the diagonally spaced bearings can here in particular alternate from roller to roller. That is to say, the inner bearing of the intermediate roller can be under tensile stress towards the inner bearing and the outer bearing of the first roller and under compressive stress towards the inner bearing and the outer bearing of the third roller or vice versa. Furthermore, that is to say, the inner bearing and the outer bearing of the intermediate roller can be under compressive stress towards the intermediate bearing of the first roller and under tensile stress towards the intermediate bearing of the third roller or vice versa. In particular, the stresses acting on the bearings on both sides can be of the same magnitude. It is thus possible to provide that any number of further rollers having the same bearing configuration are arranged axially in parallel side by side and the stress distribution through the bearings is continued accordingly in accordance with the above description.

[0014] Furthermore, at least three bearings can be arranged on the second roller journal of the first roller and on the adjacent second roller journal of the second roller, respectively, wherein, mirror-symmetrically with respect to the opposite first roller journal sides, a compressive stress occurs between the inner bearing and the outer bearing on the second roller journal of the first roller on the one hand and the intermediate bearing unit on the second roller journal of the second roller on the other hand and a tensile stress occurs between the intermediate bearing unit on the second roller journal of the first roller on the one hand and the inner bearing and the outer bearing on the second roller journal of the second roller on the other hand or vice versa. Mirror-symmetry here means mirror-symmetry in the radial direction perpendicular to the central axis along which the rollers extend. It is thus possible in particular to provide the same type of tensioning on the two inner and the two outer bearings of the opposite roller journals on the one hand and the same type of tensioning on the two intermediate bearings of the opposite roller journals on the other hand. It is also possible here that the individual stress states of the bearing sides directly adjacent to each other facing each other are respectively complementary to each other.

[0015] Furthermore, at least three bearings can be arranged on the second roll neck of the third roll, wherein, in mirror-symmetrical fashion to the opposing first roll neck side, a compressive stress arises between the inner bearing on the second roll neck of the second roll and the outer bearing on the second roll neck of the second roll on the one hand and the intermediate bearing unit on the second roll neck of the third roll on the other hand, and a tensile stress arises between the intermediate bearing unit on the second roll neck of the second roll and the inner bearing and the outer bearing on the second roll neck of the third roll on the one hand and the other hand, or vice versa. By means of this bearing arrangement and bearing tensioning, a compressive stress state or a tensile stress state, respectively, arises crosswise between the opposing roll necks, wherein the pressure change profile of the adjacent tensioned identical compressive stresses has the same change profile, respectively. For example, the compressive stress from roll neck to roll neck always extends inwards from the outer bearing and the inner bearing to the intermediate bearing unit, and, in contrast thereto, the tensile stress always extends outwards from the intermediate bearing unit to the outer bearing and the inner bearing.

[0016] It can be provided that the material to be rolled is passed through the roll gaps alternately in respectively opposite directions from roll gap to roll gap. The built-in rolls can thus be used for rolling on both sides. By virtue of the different rotational directions of the adjacent rolls it is necessary for the material to be passed alternately from above and from below through the adjacent roll gaps.

[0017] Furthermore, in order to generate a tensile stress and / or a compressive stress between the roll necks, respectively, a roll position adjustment unit can be arranged by means of which the respective roll gap feed is effected.

[0018] Here, the roll position adjustment unit can have a pressure-regulated actuator. Preferably, a separate actuator is provided between each coupled bearing pair. A pressure-regulated actuator has the advantage, inter alia, in materials having a non-uniform density distribution that the feed can be set particularly effectively.

[0019] In particular, the actuator can have a hydraulic, mechanical or electrical actuator. Alternatively, the actuator can have a hydraulic actuator, a mechanical spindle and a linear motor.

[0020] Furthermore, the roll position adjustment unit can be in operative connection with the bearing outer ring of the bearing, respectively.

[0021] The intermediate bearing unit can have one or more, preferably two, bearings, in particular. If the intermediate bearing unit has two bearings, these can be arranged directly side by side in the axial direction. Furthermore, the side-by-side bearings of the intermediate bearing unit can be tensioned axially to one another.

[0022] Furthermore, the bearings can comprise rolling bearings and / or sliding bearings. BRIEF DESCRIPTION OF DRAWINGS

[0023] Exemplary embodiments of the application are set forth hereinafter and in the accompanying drawings. Shown here is:

[0024] Figure 1a a cross-sectional view of a roller arrangement in the case where the process forces acting during the rolling process are shown;

[0025] Figure 1b a schematic diagram of a roller arrangement disclosed by the prior art in the case where the process forces acting during the rolling process are shown on the bearings;

[0026] Figure 2 a schematic diagram of an embodiment of a roller arrangement according to the application;

[0027] Figure 3 a schematic diagram of a further embodiment of a roller arrangement of the application;

[0028] Figure 4 a cross-sectional view of an exemplary roller arrangement with a plurality of rows of rollers;

[0029] Figure 5a a side view of an embodiment of a roller arrangement according to the application, wherein each roller journal has four bearings;

[0030] Figure 5b a semi-transparent side view of an embodiment of a roller arrangement according to the application, wherein each roller journal has four bearings; and

[0031] Figure 6 a view of a force polygon of an embodiment of a roller arrangement according to the application, wherein each roller journal has four bearings. DETAILED DESCRIPTION

[0032] In a roll mill, the rollers are positioned relative to one another by means of the support in the mounting. Figure 1a A roller arrangement 1 of a roll mill is shown, with two rollers 2, 3 arranged axially parallel to one another, between which a roller gap of width hi is configured. It can be seen in the side view shown that the roller supports consist of a bearing inner ring 15 and a bearing outer ring 14, respectively, the bearing inner ring 15 being rotatably supported in the bearing outer ring. The bearing outer ring 14 is anchored in the mounting. By passing a material web 16 having a thickness ho through the roller gap 5, the material web 16 is reduced to a compressed material web 18 having a material thickness of height hi. By the more or less constant direction of the force flow through the material web 16 of the roll mill, the rollers are pressed into the opposing soffits of the bearings relative to one another and held there. Here, the forces F wA feed force F is applied from the inner ring 15 of the bearing to the outer ring 14 of the bearing. At the same time, a feed force F is applied from the outer ring 14 to the inner ring 15 of the bearing. As a result, the inner ring 15 of the bearing is pushed outward into the inner ring 14 of the bearing, thereby creating bearing clearance 17 on the side of the outer ring 14 facing the roll gap 5.

[0033] according to Figure 1a The representation of process force can also be found in Figure 1b As seen in the middle, Figure 1b Show Figure 1a A top view of the bearing assembly. Two rollers 2 and 3 are arranged axially parallel to each other with a roll gap 5. Each roller 2 and 3 has a roller journal 7 and 8 at its axial end 6, respectively, on which a bearing 9 is arranged, such that rollers 2 and 3 are supported by this bearing assembly. As the material web 16 passes through the roll gap 5, a process force is generated perpendicular to the passing direction. This process force is transmitted via the roller body to the roller journal and from the journal to the inner bearing ring 15 arranged thereon, which is in turn supported by the outer bearing ring 14. The force F from the roller pressing element... w The inner ring 15 of the bearing is pressed outward within the outer ring 14 of the bearing, thereby creating bearing clearance 17 on the inner side in each bearing. Additionally, by feeding the bearings relative to each other, that is, by setting the width of the roll gap 5, a force F from the feed is applied to the outer ring 14 of the bearing along the direction of the roll gap 5.

[0034] exist Figure 2 and Figure 3 The embodiment of the invention shown in the figure has the advantage, particularly when large load variations are caused by the rolling elements, that it can independently respond to load variations with micron precision and simultaneously eliminate bearing clearance by adjusting the roller position from the roll gap 5 to the roll gap 5. Using the device 1 between the roller supports described in the invention, inserts can be arranged in a nest using force loading and the opposite gap feed; these inserts are arranged in a cascaded manner. Figure 2In the first embodiment of the application, in the case of a row of axially parallel arranged rollers 2, 3, 4, two roller bearings can be provided on each roller journal 7, 8, respectively, and so tensioned relative to each other that a force-guided nesting is obtained, which achieves the necessary gapless position. In the example shown, the bearing outer rings 14 of diagonally adjacent bearings are in an operative connection, which either generates a tensile stress or a compressive stress between the bearings. For example, the bearing outer ring 15 of the outer bearing 10 on the first roller journal 7 of the first roller 2 is in tensile stress with the diagonally adjacent bearing 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 bearing outer ring 15 of the bearing 9 on the first roller journal 7 of the second roller 3, which faces away from the first roller 2, and the diagonally adjacent bearing outer ring 15 of the outer bearing 10 on the first roller journal 7 of the third roller 4. At the same time, an operative connection in the form of a compressive stress exists between the bearing outer ring 15 of the inner bearing 9 on the first roller journal 7 of the first roller 2 and the bearing outer ring 15 of the outer bearing 10 on the first roller journal 7 of the second roller 3. The side of the bearing outer ring 15 of the outer bearing 10 on the first roller journal 7 of the second roller 3, which faces away from the first roller 2, is again in operative connection in the form of a tensile stress with the diagonally adjacent bearing outer ring 15 of the inner bearing 9 on the first roller journal 7 of the third roller 4. The tensile stresses or compressive stresses thus always alternate with each other in a zigzag manner in the course of the row of bearings in operative connection with each other. Accordingly, in the example shown, the compressive stresses always extend from the inner bearing 9 of the left roller to the outer bearing 10 of the roller arranged to the right thereof on the side of the first roller journal 7. In contrast, the tensile stresses always extend from the outer bearing 10 of the left roller to the inner bearing 9 of the roller arranged to the right thereof on the side of the first roller journal 7. The stress distribution on the side of the second roller journal 8 is exactly mirror-symmetrical to the stress distribution on the first side of the roller journal 7. In the example shown, the compressive stresses always extend from the inner bearing 9 of the left roller to the outer bearing 10 of the roller arranged to the right thereof. In contrast, the tensile stresses always extend from the outer bearing 10 of the left roller to the inner bearing 9 of the roller arranged to the right thereof. The bearing arrangement in the form of the respective stress distribution can be continued on an arbitrary number of rollers arranged axially parallel to each other with the interposed roller gap 5. Figure 2 Figure 2

[0035] Figure 3 ​​The embodiments in Figures 1 to 3 show further embodiments of the roller arrangement 1, in which on the first roller journal 7 of the first roller 2 and on the adjacent first roller journal 7 of the second roller 3 four bearings 9, 10, 11 are arranged axially side by side, respectively. Here, the two middle bearings 11 form a bearing unit, in which the two bearings 11 are arranged directly side by side and are tensioned against each other. In contrast thereto, the two outer bearings 9 and 10 are arranged spaced apart from the middle bearing unit, respectively. Here, between the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the first roller 2 on the one hand and the middle bearing unit on the first roller journal 7 of the second roller 3 on the other hand a compressive stress arises. In addition, between the middle bearing unit on the first roller journal 7 of the first roller 2 on the one hand and the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the second roller 3 on the other hand a tensile stress arises. This arrangement 1 is important, in particular, in the case of high loads, in which the bearings 9, 10, 11 in the multiple arrangement need to be nested such that the load in the journal 7, 8 and the load set add up such that the bending moment on the roller side end on the roller body, i.e. on the rolling bearing towards the roller body, is reduced to zero Nm. Figure 3 It is also shown that the roller arrangement 1 is composed of three axially parallel arranged rollers 2, 3, 4, in which on the first roller journal 7 of the third roller 4 likewise four bearings 9, 10, 11 are arranged axially side by side, in which between the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the second roller 3 on the one hand and the middle bearing unit on the first roller journal 7 of the third roller 4 on the other hand a compressive stress arises and between the middle bearing unit on the first roller journal 7 of the second roller 3 on the one hand and the inner bearing 9 and the outer bearing 10 on the first roller journal 7 of the third roller 4 on the other hand a tensile stress arises. In addition, on the second roller journal 8 of the first roller 2 and on the adjacent second roller journal 8 of the second roller 3 four bearings 9, 10, 11 are arranged, respectively, in which, mirror-symmetrically to the opposite first roller journal side 7, between the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the first roller 2 on the one hand and the middle bearing unit on the second roller journal 8 of the second roller 3 on the other hand a compressive stress arises and between the middle bearing unit on the second roller journal 8 of the first roller 2 on the one hand and the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the second roller 3 on the other hand a tensile stress arises. In addition, on the second roller journal 8 of the third roller 4 likewise four bearings are arranged, in which, mirror-symmetrically to the opposite first roller journal side 7, between the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the second roller 3 on the one hand and the middle bearing unit on the second roller journal 8 of the third roller 4 on the other hand a compressive stress arises and between the middle bearing unit 11 on the second roller journal 8 of the second roller 3 on the one hand and the inner bearing 9 and the outer bearing 10 on the second roller journal 8 of the third roller 4 on the other hand a tensile stress arises.

[0036] Figure 4A roll device 1 with seven rolls is shown in line, wherein the five rolls built in each are configured with the respectively adjacent rolls on the front side and on the back side a roll gap 5. The material web 16, which is to be rolled, is wound onto a winding tube 19 after passing through all roll gaps 5. Since in such a roll device 1 it is required to provide the required feed in both roll gaps 5 of the rolls concerned, the invention is particularly advantageous for such roll devices 1 with more than two rolls. Namely, in such a device 1 the problem arises that the load-facing side of the support of the pre-tensioning is brought into contact alternately each time without a gap and at the same time the soffit side facing away from the roll gap 5 is brought into contact in order to be able to exert the required load in the roll gap for the roll-pressing.

[0037] Figure 5a and Figure 5b A side view of an embodiment of a roll device 1 according to the invention is shown, wherein each roll journal 7, 8 has four bearings 9, 10, 11. It can be seen here in particular how the individual bearings 9, 10, 11 are tensioned relative to one another. Here, each of the rolls 2, 3 shown has four bearings 9, 10, 11 on the roll journal 7 shown, which are set relative to one another under defined prestress by means of a roll position adjustment unit 12 arranged between the roll journals 7 of the two rolls 7, 8. Here, the bearings are nested vertically on both roll journals 7 respectively in the axial direction of the rolls 2, 3. It can be seen that the roll position adjustment unit 12 has four actuators 13, which are arranged one above the other. Here, in the example shown the uppermost and lowermost actuators 13 generate a tensile stress, which acts on the middle bearing 11 of the left roll 2 and on the inner bearing and the outer bearing of the right roll 3. In contrast, the two actuators 13 in the middle each exert a compressive stress on the inner bearing and the outer bearing 9, 10 of the left roll 2 and on the middle bearing 11 of the right roll 3. Here, the stresses are transmitted via pressure transmission elements, which on both sides of the actuators are coupled with the respective outer bearing ring 14 of the bearings being actuated. Here, the pressure transmission elements are arranged one above the other horizontally and constitute a drawer structure. It can be seen that the inner bearing ring 15 of the outer bearing 10 of the left roll 2 under compressive stress at the front side rests on the rolling elements of the outer bearing ring 14 towards the roll gap 5 and that there is a bearing play on the side facing away from the roll gap 5. It can also be seen that the inner bearing ring 15 of the outer bearing 10 of the right roll 3 under tensile stress at the front side rests on the rolling elements of the outer bearing ring 14 on the side facing away from the roll gap 5 and that there is a bearing play on the side facing towards the roll gap 5. It is possible with the roll position adjustment unit to change the individual tensile forces and compressive forces of the individual actuators and to adjust in particular by the compressive forces prevailing in the different roll gaps 5. It is furthermore possible to exchange the pressure configuration, so that the bearings under tensile stress are converted into compressive stress and the bearings under compressive stress are converted into tensile stress. In the embodiment shown, the bearings are cylindrical roller bearings.

[0038] Figure 6 A force flow diagram from the roller necks to the roller necks is illustrated by way of example for a four-bearing. In the exemplary embodiment, the feed of two adjacent rollers 2, 3 to one another is effected by the frame highlighted by the dashed line. The bearings, which are designated by al, dl, b2 and c2 in the illustration, are pressure-regulated by the actuators designated by the numbers 2 and 3. At the same time, the position of the rollers is maintained by the bearings designated by bl, cl and a2 and d2 by the actuators designated by 1 and 4, which are displacement-regulated. Thus, the bearings are pre-tensioned relative to one another and the rollers are pre-positioned relative to one another. In the same way, the structure can be adapted on the positions in a row, so that the rollers can present the next roller gap one after the other.

[0039] The features of the present application disclosed in the above specification, drawings and claims can be important both separately and in any combination thereof.

[0040] List of reference signs

[0041] 1 roller device

[0042] 2 first roller

[0043] 3 second roller

[0044] 4 third roller

[0045] 5 roller gap

[0046] 6 axial end

[0047] 7 first roller neck

[0048] 8 second roller neck

[0049] 9 inner bearing

[0050] 10 outer bearing

[0051] 11 intermediate bearing

[0052] 12 roller position adjustment unit

[0053] 13 actuator

[0054] 14 bearing outer ring

[0055] 15 bearing inner ring

[0056] 16 material web

[0057] 17 bearing play

[0058] 18 compressed material web

[0059] 19 winding bobbin

[0060] 20 compressive stress

[0061] 21 tensile stress

[0062] F force from the feed

[0063] F w force from the rolling member

[0064] hi material web

[0065] ho compressed material web

[0066] V rolling speed

Claims

1. A roller arrangement (1) having at least three rollers (2, 3, 4) arranged axially in parallel, wherein Between adjacent rollers, respectively, a roller gap (5) is formed, wherein each of the rollers (2, 3, 4) has a roller journal (7, 8) on each of its two axial ends (6) and each roller (2, 3, 4) is supported via its two roller journals (7, 8), wherein at least on the first roller journal (7) of a first roller (2), on the first roller journal (7) of a second roller (3) and on the first roller journal (7) of a third roller (4), respectively, at least two bearings (9, 10) are arranged axially side by side, wherein between the inner bearing (9) on the first roller journal (7) of the first roller (2) and the outer bearing (10) on the first roller journal (7) of the second roller (3) a compressive stress and between the outer bearing (10) on the first roller journal (7) of the first roller (2) and the inner bearing (9) on the first roller journal (7) of the second roller (3) a tensile stress occur, or vice versa; wherein between the inner bearing (9) on the first roller journal (7) of the second roller (3) and the outer bearing (10) on the first roller journal (7) of the third roller (4) a compressive stress and between the outer bearing (10) on the first roller journal (7) of the second roller (3) and the inner bearing (9) on the first roller journal (7) of the third roller (4) a tensile stress occur, or vice versa.

2. The roller device (1) according to claim 1, wherein At least on the second roller journal of the first roller and on the adjacent second roller journal of the second roller, respectively, at least two bearings are arranged, wherein, mirror-symmetrically to the opposite first roller journal side, between the inner bearing on the second roller journal of the first roller and the outer bearing on the second roller journal of the second roller a compressive stress and between the outer bearing on the second roller journal of the first roller and the inner bearing on the second roller journal of the second roller a tensile stress occur, or vice versa.

3. The roller device (1) according to claim 2, wherein At least on the second roller journal (8) of the third roller (4), at least two bearings (9, 10) are arranged, wherein, mirror-symmetrically to the opposite first roller journal side (7), between the inner bearing (9) on the second roller journal (8) of the second roller (3) and the outer bearing (10) on the second roller journal (8) of the third roller (4) a compressive stress and between the outer bearing (10) on the second roller journal (8) of the second roller (3) and the inner bearing (9) on the second roller journal (8) of the third roller (4) a tensile stress occur, or vice versa.

4. The roller device (1) according to claim 3, wherein At least on the first roller journal (7) of the first roller (2) and on the adjacent first roller journal (8) of the second roller (3), respectively, at least three bearings (9, 10, 11) are arranged axially side by side, wherein, mirror-symmetrically to the opposite first roller journal side (7), between the inner bearing (9) on the first roller journal (7) of the first roller (2) and the outer bearing (10) on the first roller journal (8) of the second roller (3) a compressive stress and between the outer bearing (10) on the first roller journal (7) of the first roller (2) and the inner bearing (9) on the first roller journal (8) of the second roller (3) a tensile stress occur, or vice versa. wherein, in one aspect, the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the first roll (2) generate a compressive stress with the intermediate bearing unit (11) on the first roll neck (7) of the second roll (3) and, in the other aspect, the intermediate bearing unit (11) on the first roll neck (7) of the first roll (2) generates a tensile stress with the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the second roll (3), or vice versa.

5. The roller device (1) according to claim 4, having at least three axially parallel arranged rollers (2, 3, 4), wherein, At least three bearings (9, 10, 11) are arranged axially side by side on the first roll neck (7) of the third roll (4), wherein, in one aspect, the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the second roll (3) generate a compressive stress with the intermediate bearing unit (11) on the first roll neck (7) of the third roll (4) and, in the other aspect, the intermediate bearing unit (11) on the first roll neck (7) of the second roll (3) generates a tensile stress with the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the third roll (4), or vice versa.

6. The roller device (1) according to claim 5, wherein At least three bearings (9, 10, 11) are arranged axially side by side on the first roll neck (7) of the third roll (4), wherein, in one aspect, the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the second roll (3) generate a compressive stress with the intermediate bearing unit (11) on the first roll neck (7) of the third roll (4) and, in the other aspect, the intermediate bearing unit (11) on the first roll neck (7) of the second roll (3) generates a tensile stress with the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the third roll (4), or vice versa.

7. The roller device (1) according to claim 6, wherein At least three bearings (9, 10, 11) are arranged axially side by side on the first roll neck (7) of the third roll (4), wherein, in one aspect, the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the second roll (3) generate a compressive stress with the intermediate bearing unit (11) on the first roll neck (7) of the third roll (4) and, in the other aspect, the intermediate bearing unit (11) on the first roll neck (7) of the second roll (3) generates a tensile stress with the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the third roll (4), or vice versa.

8. The roller device (1) according to the preceding claim 7, wherein At least three bearings (9, 10, 11) are arranged axially side by side on the first roll neck (7) of the third roll (4), 9. The roller device (1) according to any one of the preceding claims, wherein wherein, in one aspect, the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the second roll (3) generate a compressive stress with the intermediate bearing unit (11) on the first roll neck (7) of the third roll (4) and, in the other aspect, the intermediate bearing unit (11) on the first roll neck (7) of the second roll (3) generates a tensile stress with the inner bearing (9) and the outer bearing (10) on the first roll neck (7) of the third roll (4), or vice versa. The material to be rolled is alternately passed through the roll gaps (5) in respectively opposite directions from roll gap (5) to roll gap (5). For generating a tensile stress and / or a compressive stress between the roll necks (7, 8) respectively roll position adjustment units (12) are arranged by means of which a corresponding roll gap feed is effected.

10. The roller device (1) according to claim 9, wherein The roller position adjustment unit (12) has a pressure-regulated actuator (13).

11. The roller device (1) according to claim 10, wherein The actuator has a hydraulic, mechanical or electrical actuator.

12. The roller device (1) according to claim 9, wherein The roller position adjustment unit (12) is in each case in operative connection with a bearing outer ring (14) of the bearings (9, 10, 11).

13. The roller device (1) according to any one of claims 4 to 8, wherein The intermediate bearing unit (11) has one or more bearings.

14. The roller device (1) according to any one of claims 4 to 8, wherein The bearings (9, 10, 11) have rolling bearings and / or sliding bearings.

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