TORQUE SUPPORT FOR ABSORBING DRIVE TORQUES AND ROLLER ARRANGEMENT WITH TORQUE SUPPORT

Abstract

The invention relates to a torque support for absorbing drive torques from at least one shaft drive, comprising two first force-transmitting elements, each rotatably fixed at a first end to the shaft drive and separated from each other, and a support element arranged at a distance from the shaft drive, to which each of the first force-transmitting elements is rotatably fixed at a second end opposite the first in each case, and two second force-transmitting elements, each rotatably fixed at a first end to the support element and each rotatably fixed at a second end opposite the first in each case to an independent fixed element of the shaft drive. A corresponding roller arrangement is also described.

Description

TORQUE SUPPORT FOR ABSORBING DRIVE TORQUES AND ROLLER ARRANGEMENT WITH TORQUE SUPPORT FIELD OF INVENTION The invention relates to a torque support / arm for absorbing / damping drive torques from at least one shaft drive, comprising two first force-transmitting elements, each of which is rotatably fixed at a first end to the shaft drive and separated from each other, and a support element disposed at a distance from the shaft drive, wherein the first force-transmitting elements are each rotatably fixed at a distance from each other by a second end opposite the first in each case, and two second force-transmitting elements, each of which is rotatably fixed at a distance from each other by a first end to the support element and each of which is rotatably fixed at a distance from each other by a second end opposite the first in each case to a fixed element independent of the shaft drive. TECHNICAL BACKGROUND In prior art calender or rolling mill drives, the drive torques are absorbed by simple torque supports, in which the drives are connected directly to the roll and torque absorption usually occurs through the connection to the machine frame, external frames, or by mutual absorption of two rigid, one-piece torque supports. A torque support is known, for example, from utility model DE 87 12 742 U1. This type of torque support with one-sided torque absorption introduces a force on the bearing. If torques are generated, they are absorbed by the torque support, as the support acts like a lever arm, with a force acting in the opposite direction at its end. However, this creates a reaction force on the drive, which forces the roller out of position. Depending on the absorbed drive torque, this can have varying degrees of impact on system accuracy. Since the reaction force has a component in the same direction as the actual rolling action, it directly influences the rolling force or roller clearance. Another problem that exists, for example, with interconnected torque supports, is that when the rollers move linearly in the horizontal direction—that is, when the gap between the rollers changes—the angular position of the rollers relative to each other also changes. Furthermore, if the torque support is externally connected, the bearing / roller bearing can only move freely within a limited range if its mounting point is externally fixed. If the torque is absorbed through two external points located on opposite sides of the drive, there is no reaction force on the bearing or the drive. However, the problem with this implementation of a torque support is that the drive is fixed in its position both rotationally and linearly by the use of two coupling points and, therefore, cannot fully compensate for movements acting upon it or move relative to another roller. BRIEF DESCRIPTION OF THE INVENTION Therefore, the object of the present invention is to improve a torque support in such a way that, on the one hand, no reaction forces are transmitted to the drive system and, on the other hand, there is less influence of the torque support on the position of the roller bearing. This objective is achieved by means of the torque support proposed according to claim 1 or by means of the roller arrangement proposed according to claim 15. Advantageous embodiments of the invention are the subject of the dependent claims. Accordingly, a torque support is proposed for absorbing drive torques from at least one shaft drive, with two first force-transmitting elements, each of which is rotatably fixed at a first end to the shaft drive and separated from each other, and with a support element disposed at a distance from the shaft drive, to which each of the first force-transmitting elements is rotatably fixed at a distance from each other with a second end opposite the first in each case, and with two second force-transmitting elements, each of which is rotatably fixed at a distance from each other with a first end to the support element and each of which is rotatably fixed at a distance from each other with a second end opposite the first in each case to a fixed element independent of the shaft drive.When absorbing torques, one of the first two force-transmitting elements is a force-transmitting element and the other is a traction element. The first ends of the first force-transmitting elements can be arranged, in particular, opposite each other around the first drive axis. The support element can be made as a flat element, extending essentially in the same plane of attachment as the attachment points of the force-transmitting elements. The second ends of the first force-transmitting elements can be arranged opposite each other, and the first ends of... QQRRnn / ZZnZ / E / YIAI The second force-transmitting elements can be arranged opposite each other on the support element. The attachment points of the force-transmitting elements can be arranged on the support element in such a way as to define the corner points of a square. As a result, the corner points in this square can be defined alternatively by a first force-transmitting element and a second force-transmitting element. The independent fixed element can be, in particular, a machine frame, an independent attachment point of the calender, or an additional drive. In particular, the support element can be arranged centrally below the drives and aligned in the plane of the front surfaces / faces or parallel to the front surfaces of the drives. The advantage of the torque support according to the invention is that the torque is further transmitted to the power transmission elements via two rotating bearings. These bearings connect the power transmission elements to the drive or drives, one of which is a tension element and the other a compression element, depending on the direction of the torque. Due to the rotating bearings, it is only possible to transmit a torque in the form of a tension force and a compression force, for systemic reasons. Because of this design, the torque support can only transmit one type of torque. No other forces are introduced into the system. This means that fluctuations in the drive torque do not cause inaccuracies in the system. In particular, the second ends of the second force-transmitting elements can be rotatably fixed to a second drive shaft arranged parallel to and separated from the first drive shaft. In this case, the second ends of the second force-transmitting elements can be arranged opposite each other around the second drive shaft. This can result in a mirror-symmetric arrangement of the two drives and of the first and second force-transmitting elements, with the axis of symmetry passing vertically through the support element. Adjustment of the distance between the rollers with the torque support according to the invention is also possible, since the support element is freely movable. By changing the roller spacing, the support element would only move upwards or downwards.The angular position of the two rollers remains identical even when the roller position is adjusted. Furthermore, each of the force-transmitting elements can be rotatably mounted around its respective fixing points. In this way, only tensile and compressive forces are directed through the force-transmitting elements to the externally arranged support element, which is supported or connected only by them. QQRRnn / ZZnZ / E / YIAI by the rotating bearing at the end of the force-transmitting elements. The fact that each of the force-transmitting elements is rotatably mounted around its respective fixing points means that each of the force-transmitting elements can rotate in a plane perpendicular to the axial direction of the associated drive. The force-transmitting elements can be fixed in particular by means of rotating threaded connections to the respective drive. Alternatively, a bearing can be arranged between the respective drive and the force-transmitting element. Furthermore, as an alternative, the force-transmitting element can be fixed to the respective drive by means of a hinged connection. It can be envisaged that the first ends of the first force-transmitting elements are rotatably fixed opposite a flange surrounding the drive shaft of the first shaft drive. Alternatively, as an intermediate element, a fixing disc can be mounted on the flange of the first drive, to which the force-transmitting elements are in turn fixed. Furthermore, it can be envisaged that the second ends of the second force-transmitting elements are rotatably fixed opposite a flange surrounding the drive shaft of the second shaft drive. Alternatively, a fixing disc can also be mounted on the flange of the second drive as an intermediate element, to which the force-transmitting elements are in turn fixed. Each of the force-transmitting elements can be attached to the drives in such a way that a first line crossing the first ends of the first force-conducting elements and a second line crossing the second ends of the second force-transmitting elements intersect at an angle of 60° or 120°, preferably 80°-100°, and particularly preferably 90°. In addition, a spacer can be mounted on the flange of the first or second drive, to which the respective ends of the power transmission elements are attached. This ensures that the power transmission elements attached to the spacer and those attached to the other drive run in different planes perpendicular to the axial direction of the drive shafts. Alternatively, if clamping discs are provided on the flanges, the spacer can be mounted between the respective clamping disc and the flange. The clamping discs can be mounted to the flange using screws. The spacer can be screwed directly to the flange or have holes aligned with the clamping discs, through which the spacer and its associated clamping disc are screwed together to the flange. Furthermore, the front power transmission elements can be fixed at the front and the rear power transmission elements can be fixed to the element of QQRRnn / ZZnZ / E / YIAI support at the rear. In this way, the drives can move freely relative to each other or move the support element up and down without one of the force-transmitting elements obstructing any of the aforementioned movements. Furthermore, the ends of the force-transmitting elements fixed to the support element can be fixed to the support element distributed in a circular circumference or define the corner points of a square. Furthermore, the first and second force-transmitting elements may be arranged parallel to each other. This means that the distance between the attachment points of the first force-transmitting elements and the distance between the attachment points of the second force-transmitting elements are each the same size. Furthermore, one of the first and one of the second force-transmitting elements may cross between the attachment points of the drives and the attachment points of the support element. In particular, the first and second force-transmitting elements attached to the side of the support element opposite the drives may cross between their respective attachment points on the drives and their respective attachment points on the support element. Conversely, the other respective first and second force-transmitting elements may be designed not to cross. Furthermore, the second ends of the first force-transmitting elements and the first ends of the second force-transmitting elements can be fixed opposite each other and at regular intervals on the support element. Furthermore, by increasing the distance between the two parallel drive axes of both drives, the support element can be moved in the direction of the drive axes. Furthermore, the force-transmitting elements can be rod-shaped. In particular, they can be designed as flat bars. All force-transmitting elements can be of the same length. Holes can be provided at the first and second ends of the first and second force-transmitting elements, respectively, through which the force-transmitting elements can be fixed to their respective mounting points. The distance between the holes can be the same for all force-transmitting elements. The ends of the force-transmitting elements can be rounded. Furthermore, the support element may be ring-shaped. In particular, the circumference of the support element to which the ends of the force-transmitting elements are attached may correspond to the circumference of the flange of the first and / or second drive to which the opposite ends of the elements are attached. QQRRnn / ZZnZ / E / YIAI force transmitters respectively. In particular, the support element may have a flat circumferential ring in which holes are arranged at regular intervals for fixing the force transmitter elements. Alternatively, the support element may be in the form of a round or polygonal disk, provided that the force transmitter elements can be secured as described above. The invention also proposes a roller arrangement with at least two parallel rollers, in particular counter-rotating, between which a gap is formed between rollers, the rollers being driven by counter-rotating shaft drives arranged side by side, which have at least one torque support as described above. BRIEF DESCRIPTION OF THE FIGURES Examples of embodiments of the invention are explained by the following figures. Where: Fig. 1 shows a perspective view of a known embodiment of the prior art of mutually absorbing torque supports; Fig. 2 is a front view of the design of a known prior art embodiment of a torque support according to Fig. 1; Fig. 3 shows a front view of a known prior art embodiment of a two-sided bearing torque support; Fig. 4 shows a front view of a first embodiment of the torque support according to the invention; Fig. 5 shows a front view of another embodiment of the torque support according to the invention; Fig. 6 shows a perspective view of another embodiment of the torque support according to the invention; Fig. 7 shows a front view of the embodiment of the torque support according to the invention shown in Fig. 6; Fig. 8 shows a perspective view of another embodiment of the torque support according to the invention; Fig. 9 shows a front view of the embodiment of the torque support according to the invention shown in Fig. 8. BRIEF DETAILED DESCRIPTION OF THE INVENTION Fig. 1 shows a known prior art solution of a torque support 1 for absorbing torques, in which the drive torques produced in the The drives 5, 6 of the calender or rolling mill are absorbed by mutually supporting torque supports, which are rigidly fixed to a flange 19 of the drive 5, 6 on one side and rotatably anchored to each other at a common fixing point on the other. The drives 5, 6 are directly connected to the respective rolls 7, 8. The drive shafts 21, 22 are aligned parallel to each other, so that an equidistant roll gap 23 is formed between the rolls 7, 8. As can be seen in Fig. 2, this unilateral absorption of forces always induces a force in the corresponding bearing. Fig. 2 illustrates only the right-hand drive side 5 as an example. As soon as a torque 2 is generated on the drive side, the torque support 1 of the right-hand drive 5 absorbs the torque 2 through force 3 and lever arm 26. However, this creates a reaction force 4 in the drive 5. This force 4 ensures that the roll 7 is pushed out of position, and depending on the size of the drive torque, the accuracy of the system can be affected to varying degrees. Since the reaction force 4 has a component in the same effective direction as the calender's inlet direction, it has a direct influence on the rolling force or the roll gap 23. The example of a torque support 1 shown in Fig. 3, unlike the examples in Figs. 1 and 2, has a two-sided mounting, in which the torque support 1 has two opposing lever arms 26 of the same length. By mounting the torque support 1 on two sides, the torque-absorbing force 3 and the reaction force 4 cancel each other out, and therefore no force acts on the bearing and there is no influence on the roller gap 23. In this case, however, the drive 5 is disadvantageously fixed in its position by two points and therefore cannot completely compensate for the movements. The first embodiment of the torque support 1 according to the invention, shown in Fig. 4, shows a shaft drive 5 with a first roller 7, wherein the torque support is supported by a support element 17. This support element 17 is connected on one side via two first force-transmitting elements 9 to a flange 19 of the drive and on the other side via two second force-transmitting elements 10 to two fixed bearings 27. The fixed bearings 27 can be external elements, i.e., elements decoupled from the shaft drive 5, such as the machine frame or other suitable structures. The first force-transmitting elements 9 are rotatably fixed at their first ends 11 to fixing points 18 on the flange 19 of the first shaft drive 5, wherein the rotating means are in particular in a plane perpendicular to the shaft drive 21. QQRRnn / ZZnZ / E / YIAI The first force-transmitting elements are also rotatably fixed with second ends 12 at fixing points 18 on the support element 17. The force-transmitting elements 9 run parallel to each other. This means that the fixing points 18 on the flange 19 on one side and the support element 18 on the other side are equidistant. The force-transmitting elements are designed as flat bars, preferably made of metal. The support element 17 is ring-shaped, formed from a flat part that has the same width as the force-transmitting elements. On average, the diameter of the ring corresponds to the distance between the fixing points 18. The first force-transmitting elements 9 are arranged opposite each other on the support element 17.The second force-transmitting elements 10 are preferably offset by 90° with respect to the first force-transmitting elements 9 and are rotatably fixed at their first ends 13 to attachment points 18 on the support element 17. In this way, the second force-transmitting elements 10 are also arranged opposite each other on the support element 17. The second force-transmitting elements 10 are rotatably fixed at their second ends 14 to attachment points 18 that are specially configured as fixed bearings 27. The distances between the attachment points 18 of the second force-transmitting elements 10 are also the same, so that the second force-transmitting elements 10 also run parallel to each other. This arrangement ensures that the force-transmitting elements transmit only compressive or tensile forces, but not torques.Compared to conventional torque mounts, this significantly reduces the drive's deviation from its set position due to large torques. Figure 5 shows another embodiment of the torque support 1, in which two shaft drives 5, 6 or two rollers 7, 8 driven by shaft drives 5, 6 are arranged parallel to each other and form a common roller gap 23 between them. Thus, the drive direction of the drives 5, 6 is always opposite to each other. Each of the drives 5, 6 has a separate torque support 1, i.e., each of the drives 5, 6 has separate force-transmitting elements 9, 10 and support elements 17. Each of the second force-transmitting elements 10 is rotatably fixed with its second ends 14 in separate fixed bearings 27.The torque supports 1 ensure that the drives 5, 6 do not deviate from their target positions even with large torques, for example, when there are load changes, so that the distance d between the drive shafts of the shaft and, consequently, the entry into the roller gap 23 remains the same. QQRRnn / ZZnZ / E / YIAI In another embodiment of the torque support 1, depicted in Figs. 6 and 7, the two opposing drives 5, 6 have a common torque support 1, so that both drives 5, 6 support each other. Torque 2 is now dissipated through two parallel force-transmitting elements 9, 10 attached to drives 5, 6, which are fixed at their ends 12, 13 to a ring-shaped support element 17. The force-transmitting elements 9, 10, configured as flat bars, are each rotatably mounted at their attachment points 18. As a result, the force-transmitting elements 9, 10 serve only to transmit tensile or compressive forces, but not to transmit a torque to the support element 17. Ultimately, this means that no reaction forces act on drives 5, 6, so the distance between cylinders 23 remains unaffected even under high torques. For this purpose, two first ends 11 of the first force-transmitting elements 9 are rotatably fixed to attachment points 18 on a flange 19 of the first drive 5, radially opposite each other and orthogonal to the first drive shaft 21. The first force-transmitting elements 9 are designed as flat bars and have the same length, and each is rotatably fixed to the support element 17 with opposite second ends 12 on the circumference of a ring-shaped support element 17 at respective attachment points 18. The first force-transmitting elements 9 can be rotated parallel to the plane in which the support element 17 extends. The attachment points 18 on the flange 19 and the attachment points 18 on the support element 17 of the first force-transmitting elements 9 are each equidistant, so that the two first force-transmitting elements 9 run parallel to each other.Two radially opposite second ends 14 of second force-transmitting elements 10 are fixed to the flange 19 of the second drive 6 and can be rotated orthogonally to the second drive shaft 22 at fixing points 18. The second force-transmitting elements 10 are also designed as flat bars and have the same length as the first force-transmitting elements 9, and each is rotatably fixed to the support element 17 with the opposite first ends 13 on the circumference of the ring-shaped support element 17 at the respective fixing points 18. The second force-transmitting elements 10 can be rotated parallel to the plane in which the support element 17 extends.The fixing points 18 on the flange 19 and the fixing points 18 on the support element 17 of the second force-transmitting elements 10 are also each the same distance apart, so that the two second force-transmitting elements 10 also run parallel to each other. A straight line connecting the fixing points 18 of the first force-transmitting elements. QQRRnn / ZZnZ / E / YIAI force 9 on the flange 19 of the first drive 5 and a straight line connecting the fixing points 18 of the second force-transmitting elements 10 on the flange 19 of the second drive 6 intersect above the roller arrangement at an angle α. By adjusting the angle, the vertical distance of the support element 17 with respect to the parallel drive axes 21, 22 of the roller arrangement can be adjusted. The ring-shaped support element 17 is formed by a flat ring, on whose circumference the fixing points 18 of the first and second force-transmitting elements 9, 10 are arranged alternately, the first force-transmitting elements 9 being fixed at the front and the second force-transmitting elements 10 at the rear of the support element 17, so that the force-transmitting elements 9, 10 do not obstruct each other.For example, the first upper force-transmitting element 9 and the second upper force-transmitting element 10 cross paths between their respective attachment points 18 on the respective flange 19 and support element 17. Therefore, the first force-transmitting element 9 runs ahead of the second force-transmitting element 10, and they do not interfere with each other within their respective ranges of motion. Furthermore, on the flange 19 of the first drive 5, there is a flat, disc-shaped / washer-shaped spacer 20 mounted below the attachment point to which the first force-transmitting elements 9 are attached in the first drive 5. The spacer 20 is approximately the sum of the thicknesses of the second force-transmitting elements 10 and the support element 17 to compensate for the resulting thickness difference. It is also possible to modify the distance d of the drive shafts 21, 22 or the distance between rollers 23, since the support element 17 can be moved up and down by means of the rotary mounting of the force transmitting elements 9, 10. The angular position of the two rollers 7, 8 can also be maintained when the distance between rollers is adjusted. Figures 8 and 9 show another embodiment of the invention, in which four rollers 7, 8, 30, 31 are arranged parallel to each other, forming three roller gaps 23, 32, 33. The adjacent rollers face in opposite directions. In particular, the arrangement shown includes three torque supports 1 with three support elements 17, each positioned below between two rollers. In this embodiment, two adjacent torque supports 1 are associated with each of the two internal shaft drives 6, 28. As a result, four force-transmitting elements 9, 10 are rotatably attached to the flanges 19 of the drives 6, 28, with the first two force-transmitting elements 9 being attached to a support element 17 positioned below and to the left, and the second two force-transmitting elements 10 being attached to a support element 17 positioned below and to the left. QQRRnn / ZZnZ / E / YIAI fixed to a support element 17 arranged at the bottom right. In the embodiment shown, the first force-transmitting elements 9 each run in a plane at the front of the support elements 17, and the second force-transmitting elements 10 run in a plane at the rear of the support elements 17. For this purpose, corresponding spacers 20 are installed on the drives 5, 6, 28, 29, through which different fixing planes are provided for the first and second force-transmitting elements 9, 10. Naturally, the principle of the illustrated embodiment can be applied alternatively to any number of shaft drives arranged side by side. The features of the invention described in the preceding description, in the figures, and in the claims may be essential to the implementation of the invention, both individually and in any combination. List of reference signs Torque support Torque Absorption force Reaction force at the drive First shaft drive Second shaft drive First roller Second roller First force transmitting element Second force transmitting element First end of the first force transmitting element Second end of the first force transmitting element First end of the second force transmitting element Second end of the second force transmitting element First drive shaft Second drive shaft Support element Fixing point Flange Spacer First drive shaft Second drive shaft QQRRnn / ZZnZ / E / YIAI Roller gap Traction force Compression force Lever arm Fixed bearing Third shaft drive Fourth shaft drive Third roller Fourth roller Second roller gap Third roller gap d Distance between drives / units a Angle between axes of fixing points

Claims

1. A torque support (1) for absorbing drive torques from at least one shaft drive (5), comprising a shaft drive (5) and two first force-transmitting elements (9), each of which is rotatably fixed to a first end (11) of the shaft drive (5) at a distance from each other, and comprising a support element (17) disposed at a distance from the shaft drive (5), wherein the first force-transmitting elements (9) are each rotatably fixed at a distance from each other to a second end (12) opposite the first end (12), and comprising a fixed element independent of the shaft drive (5) and two second force-transmitting elements (10),each of which is fixed to the support element (17) spaced apart from each other by a first end (13) and are each fixed at a distance from each other to the independent fixed element of the shaft drive (5) by a second end (14) opposite the first end in each case, characterized in that the two second force transmitting elements (10) are each rotatably fixed by the first end (13) to the support element (17) and are each rotatably fixed by the second end (14) to the independent fixed element of the shaft drive (5).

2. The torque support (1) according to claim 1, with a second shaft drive (6), in particular counter-rotating, arranged parallel to the first shaft drive (5), wherein the second ends (14) of the second force transmitting elements (10) can rotate about the second shaft drive (6) and are fixed and separated.

3. The torque support (1) according to claim 1 or 2, characterized in that the force transmitting elements (9, 10) are each rotatably housed around their respective fixing points (18).

4. The torque support (1) according to any of the preceding claims, with a first flange (19) surrounding the transmission shaft of the first shaft drive (5), wherein the first ends (11) of the first force-transmitting elements (9) are rotatably fixed to each other in the first flange (19).

5. The torque support (1) according to any of claims 2 to 4, having a second flange (19) surrounding the drive shaft of the second QQRRnn / ZZnZ / E / YIAI shaft drive (6), wherein the second ends (14) of the second force-transmitting elements (10) are rotatably fixed to each other in the second flange (19).

6. The torque support (1) according to any of claims 2 to 5, characterized in that a spacer (20) is additionally mounted on the flange (19) of the first or second drive (5, 6), in which the respective ends of the force-transmitting elements (9, 10) are fixed, such that the force-transmitting elements (9, 10) fixed to the spacer (20) and the force-transmitting elements (9, 10) fixed to the other drive run in different planes perpendicular to the axial direction of the transmission axes.

7. The torque support (1) according to claim 6, characterized in that the front force transmitting elements (9) are fixed at the front and the rear force transmitting elements (10) are fixed at the rear on the support element (17).

8. The torque support (1) according to any of the preceding claims, characterized in that the ends (12, 13) of the force transmitting elements (9, 10) fixed to the support element (17) are fixed to the support element (17) distributed over a circular circumference.

9. The torque support (1) according to any of the preceding claims, characterized in that the first force transmitting elements (9) and the second force transmitting elements (10) are arranged parallel to each other.

10. The torque support (1) according to any one of claims 2 to 9, characterized in that one of the first and one of the second force transmitting elements (9, 10) are crossed between the fixing points (18) on the drives (5, 6) and the fixing points (18) on the support element (17).

11. The torque support (1) according to any of claims 2 to 10, characterized in that the second ends (12) of the first force transmitting elements (9) and the first ends (13) of the second force transmitting elements (10) are fixed to each other and at regular intervals on the support element (17).

12. The torque support (1) according to any of claims 2 to 11, characterized in that by increasing the distance (d) between the two parallel drive shafts (21,22) of both drives (5, 6), the support element (17) moves in the direction of the drive shafts (21,22).

13. The torque support (1) according to any of the preceding claims, characterized in that the force transmitting elements (9, 10) are bar-shaped.

14. The torque support (1) according to any of the preceding claims, characterized in that the support element (17) is ring-shaped. QQRRnn / ZZnZ / E / YIAI 15. A roller arrangement with at least two parallel rollers, in particular counter-rotating (7, 8), between which a roller gap (23) is formed, wherein the rollers (7, 8) are driven by counter-rotating shaft drives (5, 6) arranged one next to the other having at least one torque support (1) according to any of the 5 preceding claims.

Images