Torque support for absorbing drive torques, and roll assembly with torque supports

Abstract

To provide a torque support reducing the influence of the torque support on a posture position of a roll bearing for a drive system.SOLUTION: A machine comprises: a frame; a roll set of four or more rolls horizontally arranged within the frame and turned by multiple drives, where the first and third rolls rotate in a first direction and the second and fourth rolls rotate in a second direction opposite to the first direction; and multiple torque supports. One of the torque supports comprises: a support element; a first force-conducting element connected to one of the drives and the support element; a second force-conducting element connected to the one of the drives and the support element and arranged in parallel to the first force-conducting element; a third force-conducting element connected to the support element and the frame; and a fourth force-conducting element connected to the support element and the frame and arranged in parallel to the third force-conducting element.SELECTED DRAWING: Figure 8

Description

[Technical field]

[0001] The present invention relates to a torque support device for capturing a driving torque of at least one shaft drive, comprising two first force-transmitting elements, each having a first end rotatably fixed to the shaft drive and spaced apart from each other, a support element arranged spaced apart from the shaft drive and fixing the first force-transmitting elements, each having a second end opposite the first ends, rotatably fixed to each other, and two second force-transmitting elements, each having a first end rotatably fixed to the support element and spaced apart from each other, and each having a second end opposite the first ends, rotatably fixed to each other, to a stationary element independent of the shaft drive. [Background technology]

[0002] In the calendar drives or rolling mill drives known from the prior art, the drive torque is captured via a simple torque support device, in which the drive is directly connected to the rolls, the torque is often captured via a connection to the machine frame, an external frame or by the mutual capture of two robust integral torque support devices. Torque support devices are known, for example, from German Utility Model No. 87 12 742.

[0003] With this type of torque support, which captures the torque on one side, forces are brought into the bearing. When torques appear, they are captured by the torque support, which acts as a lever arm that acts against the forces at its end. However, this generates reactive forces on the drive, which can push the rolls out of their position and have effects of varying magnitude on the accuracy of the plant depending on the captured drive torque. These reactive forces have a component in the same direction of action as the actual calendar, and therefore have a direct effect on the rolling force or the roll gap.

[0004] Another problem that arises, for example, with mutually connected torque support devices, is that if the rolls are displaced linearly in the horizontal direction, i.e. if the roll gap changes, the mutual angular position of the rolls changes. This problem also arises when the torque support device is externally connected, i.e. when the support points of the torque support device are fixed externally, the roll supports can only move freely to a limited extent.

[0005] When capturing the torque via two external points located on opposite sides of the drive, no reaction forces are certainly generated on the bearing or the drive, but the problem with this embodiment of the torque support is that, due to the use of two connection points, the drive is rotationally and linearly fixed in its position and therefore cannot fully compensate for the various movements acting on it or move relative to the other rolls. Summary of the Invention [Problem to be solved by the invention]

[0006] The object of the present invention is therefore to develop a torque support device in such a way that no reactive forces are transmitted to the drive system, while the influence of the torque support device on the attitude of the roll bearings is only slight. [Means for solving the problem]

[0007] This problem is solved by the proposal according to claim 1. Advantageous embodiments of the invention are respectively the subject of the dependent claims.

[0008] Accordingly, a torque support device is proposed for capturing the drive torque of at least one shaft drive, comprising two first force-transmitting elements, each of which is fixed at a first end to the shaft drive in a rotatable and spaced-apart relationship, a support element arranged at a distance from the shaft drive and fixing the first force-transmitting elements at a second end opposite the first ends, respectively, in a rotatable and spaced-apart relationship, and two second force-transmitting elements, each of which is fixed at a first end to the support element in a rotatable and spaced-apart relationship and fixed at a second end opposite the first ends to a stationary element independent of the shaft drive, respectively. When capturing the torque, one of the two first force-transmitting elements is a pressure element, the other is a tension element. The first ends of the first force-transmitting elements can in particular be arranged on opposite sides around the first drive axis. The support element can be formed as a flat element extending in substantially the same fastening plane as the fixing points of the force-transmitting elements. The second ends of the first force-conducting element can be arranged on opposite sides and the first ends of the second force-conducting element can be arranged on the support element. The fixing points of the force-conducting elements can in particular be arranged on the support element in such a way that they define corners of a square, whereby the corners of this square can be defined alternately by the first and the second force-conducting elements. The independent stationary element can in particular be a machine frame, a fixing point independent of the calendar, or another drive. The support element can in particular be arranged centrally below the drive and aligned in the plane of an end face of the drive or parallel to the end face.

[0009] The advantage of the torque support device according to the invention is that the torque is further conducted to the force-transmitting element via two rotatable bearings, which respectively fasten the force-transmitting element to one or more drives, one of which is in each case a tension element and the other a pressure element, depending on the direction of the torque. It is only possible to transmit the torque as tension or pressure force, restricted in a systematic way by the rotatable bearings. With this construction, the torque support device is only able to transmit the torque. No other forces are introduced into the system. Fluctuations in the drive torque thus do not lead to inaccuracies in the installation.

[0010] In particular, the second end of the second force-transmitting element can be rotatably fixed to a second shaft drive arranged parallel to the first shaft drive, spaced apart from one another. The second end of the second force-transmitting element can be arranged around the second drive shaft, in particular on opposite sides. This allows a mirror-symmetric arrangement of both drives and the first and second force-transmitting elements to result, in which the axis of symmetry runs vertically across the support element. Since the support element is free to move, a change in the roll spacing is also possible with the torque support device according to the invention. By changing the roll spacing, the support element may only move up or down. The angular orientation of both rolls remains the same when the roll position is changed.

[0011] Furthermore, the force-transmitting elements can be supported rotatably around the respective fixed point. In this way, only tensile and compressive forces are transferred via the force-transmitting elements to the external support element, which is supported or connected to the end of the force-transmitting element only by means of rotatable bearings. The force-transmitting elements are supported rotatably around the respective fixed point, which means that the force-transmitting elements can each rotate in a plane perpendicular to the axial direction of the associated drive. The force-transmitting elements can be fixed to the respective drive, in particular by means of a rotatable bolt connection. Alternatively, a bearing can be arranged between the respective drive and the force-transmitting elements. As a further alternative, the force-transmitting elements can be fixed to the respective drive via a hinge connection.

[0012] The first end of the first force-transmitting element can be rotatably fixed on the opposite side to a flange surrounding the drive shaft of the first shaft drive, or alternatively, a fastening disk can be attached to the flange of the first drive as an intermediate element, to which the force-transmitting element can also be fastened.

[0013] Furthermore, the second end of the second force-transmitting element can be rotatably fixed on the opposite side to a flange surrounding the drive shaft of the second shaft drive. Alternatively, the flange of the second drive can also be provided with a fastening disk as an intermediate element, to which the force-transmitting element is also fastened.

[0014] The force transmitting elements can each be fixed to the drive device such that a first line passing through a first end of the first force transmitting element and a second line passing through a second end of the second force transmitting element intersect at an angle of 60° to 120°, preferably 80° to 100°, particularly preferably 90°.

[0015] Furthermore, a spacer can be additionally attached to the flange of the first or second drive, to which each end of the force-transmitting element is fixed, so that the force-transmitting element fixed to the spacer and the force-transmitting element fixed to the other drive extend in different planes perpendicular to the axial direction of the drive shaft. Alternatively, if the flanges are provided with fastening disks, a spacer can be attached between each fastening disk and each flange. The fastening disks can be attached to each flange by means of bolts. The spacer can be fastened directly to the flange or can have holes aligned with the fastening disks, through which the spacer and the fastening disks laid thereon can be fastened together to the flange.

[0016] Furthermore, the front force-transmitting elements can be fixed to the support elements at their front side and the rear force-transmitting elements at their rear side, so that the drives can move freely relative to one another or the support elements can be moved up and down without any of the force-transmitting elements hindering any of said movements. Furthermore, the ends of the force-transmitting elements fixed to the support elements can be fixed to the support elements distributed over a circular periphery or can define the corner points of a square.

[0017] Furthermore, the first and second force conducting elements can be arranged parallel to each other, so that the distance between the fixing points of the first ends of the force conducting elements and the distance between the fixing points of the second force conducting elements are equal to each other.

[0018] Furthermore, one of the first and one of the second force-transmitting elements can cross between a fixed point at the drive and a fixed point at the support element. In particular, the first and second force-transmitting elements fixed on the side of the support element closer to the drive can cross between a fixed point at the drive and a fixed point at the support element, whereas the other first and second force-transmitting elements can be kept uncrossed. Furthermore, the second end of the first force-transmitting element and the first end of the second force-transmitting element can be fixed on the support element at regular intervals on opposite sides, respectively. Furthermore, the support element can be made movable in the direction of the drive axes by increasing the distance between the two parallel drive axes of the two drives.

[0019] Furthermore, the force conducting elements may be formed in a rod shape. In particular, the force conducting elements may be formed as flat bars. All the force conducting elements may have the same length. The first and second force conducting elements may have holes at their first and second ends, respectively, and the force conducting elements may be fixed at their respective fixing points via these holes. The spacing between the holes may be the same for all the force conducting elements. The ends of the force conducting elements may be rounded.

[0020] Furthermore, the support element can be ring-shaped. In particular, the circumferential surface of the support element, on which the ends of the force-conducting elements are fixed, can correspond to the circumferential surface of the flange of the first drive and / or the second drive, on which the opposite ends of the force-conducting elements are respectively fixed. In particular, the support element can have a complete flat ring, on which holes for fastening the force-conducting elements are arranged at regular intervals. Alternatively, the support element can have the form of a circular or polygonal disk, as long as the above-mentioned fastening of the force-conducting elements is ensured.

[0021] The invention further proposes a roll assembly having at least two parallel arranged, in particular counter-rotating, rolls with respective roll nips therebetween, the rolls being driven via juxtaposed counter-rotating shaft drives and having at least one torque support device as described above. Exemplary embodiments of the invention are explained on the basis of the following figures. [Brief description of the drawings]

[0022] [Figure 1] 1 is a perspective view of a known prior art embodiment of a mutually captive torque support device; FIG. [Diagram 2] FIG. 2 is a front view of a known prior art embodiment of the torque support device according to FIG. 1; [Diagram 3] FIG. 1 is a front view of a known embodiment of a torque support device having a double bearing according to the prior art; [Figure 4] FIG. 1 is a front view of a first embodiment of a torque support device according to the present invention. [Diagram 5] FIG. 11 is a front view of another embodiment of the torque support device according to the present invention. [Figure 6] FIG. 11 is a perspective view of another embodiment of a torque support device according to the present invention. [Figure 7] FIG. 7 is a front view of the embodiment of the torque support device according to the present invention shown in FIG. 6. [Figure 8] FIG. 11 is a perspective view of another embodiment of a torque support device according to the present invention. [Figure 9] FIG. 9 is a front view of the embodiment of the torque support device according to the present invention shown in FIG. 8. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0023] In the solution of the torque support device 1 for torque capture known from the prior art shown in Fig. 1, the drive torque appearing in the calendar or rolling mill drives 5, 6 is captured by means of mutually supporting torque support devices which are rigidly fastened on one side to the flanges 19 of the drives 5, 6 respectively and rotatably anchored to each other at a common fixing point on the other side. The drives 5, 6 are directly connected to the respective rolls 7, 8. The drive shafts 21, 22 are aligned parallel to one another and an equidistant roll gap 23 is formed between the rolls 7, 8.

[0024] As can be seen from Fig. 2, this one-sided capture of the forces ensures that the forces are always directed to the bearing. By way of example, only the right drive 5 is illustrated in Fig. 2. If a torque 2 is generated on the drive side, this torque 2 is captured by the torque support 1 of the right drive 5 via the force 3 and the lever arm 26. However, this results in a counteracting force 4 on the drive 5. This force 4 pushes the roll 7 out of its position and, depending on the strength of the drive torque, can have a differently strong effect on the accuracy of the plant. The counteracting force 4 has a component in the same direction of action as the calender feed direction and therefore has a direct effect on the rolling force or the roll gap 23.

[0025] 1 and 2, the torque support device 1 has two opposite lever arms 26 of equal length. By means of the torque support device 1 supported on both sides, the torque-capturing force 3 and the counteracting force 4 are counterbalanced, so that no forces act on the supports and no influence is exerted on the roll gap 23. However, the drive 5 is disadvantageously fixed in position at two points and thus cannot fully compensate for the various movements.

[0026] The first embodiment of the torque support device 1 according to the invention shown in FIG. 4 shows a shaft drive 5 with a first roll 7, in which the torque support is effected via a support element 17 which is connected on the one hand via two first force-transmitting elements 9 to a flange 19 of the drive and on the other hand via two second force-transmitting elements 10 to two fixed bearings 27. The fixed bearings 27 can be external elements, i.e. elements separated from the shaft drive 5, such as for example the machine frame of the machine or another structure suitable as a fixed bearing. The first force-transmitting element 9 is rotatably fastened with a first end 11 at a fixed point 18 to the flange 19 of the first shaft drive 5. Rotatable means in particular rotation in a plane perpendicular to the shaft drive axis 21. The first force-transmitting element is also rotatably fastened with a second end 12 at a fixed point 18 on the support element 17. The force-transmitting elements 9 run parallel to one another. This means that the fixed points 18 on the flange 19 on the one hand and the fixed points 18 on the support element on the other hand have the same mutual distance, respectively. The force-conducting elements are formed primarily as flat bars made of metal. The support elements 17 are formed in the form of rings, in particular from flat elements having the same width as the force-conducting elements. The diameter of the rings corresponds on average, in particular to the distance between the fixing points 18. The first force-conducting elements 9 are arranged on opposite sides on the support element 17. The second force-conducting elements 10 are preferably offset by 90° in each case with respect to the first force-conducting element 9 and are rotatably fastened at their first ends 13 to the fixing points 18 on the support element 17. The second force-conducting elements 10 are thus also arranged on opposite sides on the support element 17. The second force-conducting elements 10 are rotatably fastened at their second ends 14 to the fixing points 18, which are in particular formed as fixed bearings 27. The distance between the fixing points 18 of the second force-conducting elements 10 is also the same and the second force-conducting elements 10 also run parallel to one another. With this arrangement, it is achieved that only compressive or tensile stresses are transmitted by the force-conducting elements in each case, but no torques. This significantly reduces the risk of the drive device being deviated from its target position due to a large torque, as compared to conventional torque support devices.

[0027] In another embodiment of the torque support device 1 shown in FIG. 5, two shaft drives 5, 6 or two rolls 7, 8 driven by the shaft drives 5, 6 are arranged parallel to one another and form a common roll nip 23 between them. As a result, the drive directions of the drives 5, 6 are always opposite to one another. The drives 5, 6 each have a separate torque support device 1, i.e. each drive 5, 6 has a separate first and second force-transmitting element 9, 10 and a separate support element 17. The second force-transmitting element 10 is rotatably fixed at its second end 14 in a separate fixed bearing 27. The torque support device 1 prevents the drives 5, 6 from moving out of their target position even in the case of high torques, for example in the case of load fluctuations, so that the distance d between the shaft drives and thus the feed in the roll nip 23 remains the same.

[0028] In another embodiment of the torque support device 1 shown in Figures 6 and 7, the two counter-rotating drives 5, 6 have a common torque support device 1 so that the two drives 5, 6 support each other. The torque 2 is now discharged via two parallel force-transmitting elements 9, 10 fixed to the drives 5, 6, which are fixed at their opposite ends 12, 13 to a ring-shaped support element 17. The force-transmitting elements 9, 10, which are implemented as flat bars, are each rotatably supported at their fixing points 18. Thus, the force-transmitting elements 9, 10 serve only to transmit tensile or compressive forces and not to transmit torque to the support element 17. As a result, no counteracting forces act on the drives 5, 6, and the roll gap 23 is not influenced even in the case of strong torques.

[0029] In addition to this, the two first ends 11 of the first force conducting element 9 are rotatably fixed at radially opposite sides to a flange 19 of the first drive 5 at fixing points 18 at right angles to the first drive shaft 21. The first force conducting elements 9 are formed as flat bars, have the same length, and have opposite second ends 12, respectively, rotatably fixed to the ring-shaped support element 17 at respective fixing points 18 on the circumferential surface of the support element 17. The first force conducting elements 9 are rotatable 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 first force conducting elements 9 have the same distance between them, and both first force conducting elements 9 extend parallel to each other.

[0030] The two second ends 14 of the second force-conducting element 10 are rotatably fixed at radially opposite sides at fixed points 18 at right angles to the second drive shaft 22 to the flange 19 of the second drive 6. The second force-conducting element 10 is also formed as a flat bar, has the same length as the first force-conducting element 9, and has opposite first ends 13 rotatably fixed to the ring-shaped support element 17 at respective fixed points 18 on the circumferential surface of the support element 17. The second force-conducting element 10 is rotatable parallel to the plane in which the support element 17 extends. The fixed points 18 on the flange 19 and the fixed points 18 on the support element 17 of the second force-conducting element 10 are also spaced apart from each other at the same distance, and both second force-conducting elements 10 also extend parallel to each other. The straight line connecting the fixed points 18 of the first force-conducting element 9 on the flange 19 of the first drive 5 and the straight line connecting the fixed points 18 of the second force-conducting element 10 on the flange 19 of the second drive 6 intersect at an angle α above the roll assembly. By adjusting this angle, the vertical distance between the support element 17 and the parallel drive shafts 21, 22 of the roll assembly can be adjusted. The ring-shaped support element 17 is formed as a flat ring, on whose periphery the fastening points 18 of the first and second force-conducting elements 9, 10 are alternately distributed, the first force-conducting element 9 is fastened to the support element 17 on its front side, and the second force-conducting element 10 is fastened to the support element 17 on its back side, so that the force-conducting elements 9, 10 do not interfere with each other. For example, the upper first force-conducting element 9 and the upper second force-conducting element 10 cross each other in the respective sections between the fastening points 18 on the flanges 19 and the fastening points on the support element 17, and the first force-conducting element 9 passes in front of the second force-conducting element 10, so that they do not interfere with each other in the respective movement clearances. Accordingly, the flange 19 of the first drive 5 is provided with a spacer 20 in the form of a flat disk, which is attached below the fastening element that fastens the first force-conducting element 9 to the first drive 5. The spacer 20 has a thickness approximately equal to the sum of the thickness of the second force-conducting element 10 and the thickness of the support element 17 in order to compensate for any thickness differences that may occur.

[0031] A change in the distance d between the drive shafts 21, 22 or a change in the roll gap 23 is also possible since the support element 17 can be moved up and down by means of the rotatable bearings of the force-conducting elements 9, 10. The angular position of both rolls 7, 8 can be maintained even when the roll gap is changed.

[0032] In Fig. 8 and Fig. 9, which show another embodiment of the invention, four rolls 7, 8, 30, 31 are arranged parallel to one another and form three roll nips 23, 32, 33. Adjacent rolls rotate counter-rotatingly. In particular, in the illustrated arrangement, three torque support devices 1 are provided with three bracing elements 17, which are arranged below and between two rolls. In this embodiment, two adjacent torque support devices 1 are attached to both inner shaft drives 6, 28. Thus, four force-conducting elements 9, 10 are rotatably fastened to the flanges 19 of the drives 6, 28, respectively, with two first force-conducting elements 9 fastened to the bracing element 17 arranged at the bottom left and two second force-conducting elements 10 fastened to the bracing element 17 arranged at the bottom right. In the illustrated embodiment, the first force-conducting elements 9 each extend in a plane on the front side of the bracing element 17, and the second force-conducting elements 10 each extend in a plane on the rear side of the bracing element 17. In addition, the drives 5, 6, 28, 29 are provided with suitable spacers 20, which provide various fastening planes for the first and second force-transmitting elements 9, 10. It is self-evident that the principles of the illustrated embodiment can alternatively be applied to any number of juxtaposed shaft drives. The features of the invention disclosed in the above description, the drawings and the claims may be essential for realizing the invention both individually and in any combination. [Explanation of symbols]

[0033] 1 Torque support device 2 Torque 3. Capturing Power 4. Reactive forces on the drive unit 5 First shaft drive 6 Second shaft drive 7 First Roll 8 Second Roll 9. First Force-Transmitting Element 10 Second power transmission element 11 first end of first force conducting element 12 second end of the first force conducting element 13 First end of second force transmitting element 14 second end of second force conducting element 15 First drive shaft 16 Second drive shaft 17 Supporting Elements 18 Fixed points 19 Flange 20 Maza 21 First drive shaft 22 Second drive shaft 23 Roll gap 24 Tensile force 25 Pressure 26 Lever Arm 27 Fixed bearing 28 Third shaft drive 29 Fourth shaft drive 30 Third Roll 31 Fourth Roll 32 Second roll gap 33 Third roll gap d Distance between drives α angle between the axes of the fixed points

Claims

1. A frame, a roll set of four or more horizontally arranged rolls rotated within the frame by a corresponding plurality of drive devices, wherein a first roll and a third roll are rotated in a first direction by a first drive device and a third drive device, respectively, and a second roll and a fourth roll are rotated in a second direction opposite to the first direction by a second drive device and a fourth drive device, respectively; a plurality of torque support devices each associated with one of the horizontally arranged rolls; A machine comprising: One of the plurality of torque support devices is provided with Support elements and a first force-transmitting element connected to the support element and to one of the plurality of drives; a second force-transmitting element connected to the support element and the one drive device and arranged in parallel to the first force-transmitting element; a third force conducting element connected to the bracing element and to the frame; a fourth force conducting element connected to the support element and the frame and arranged parallel to the third force conducting element; A machine characterized in that it is equipped with:

2. 2. The machine according to claim 1, wherein the support element is polygonal.

3. 2. The machine according to claim 1, wherein the first force conducting element, the second force conducting element, the third force conducting element, and the fourth force conducting element are all formed in a rod shape.

4. 2. The machine of claim 1, wherein the first force conducting element, the second force conducting element, the third force conducting element, and the fourth force conducting element are all formed as flat bars.

5. 2. A machine according to claim 1, characterized in that the machine is a calender machine or a rolling machine.

6. 2. The machine according to claim 1, wherein the torque support device is associated with a first roll, and any roll other than the first roll among the four or more horizontally arranged rolls is associated with another torque support device similar to the torque support device.

7. 2. The machine according to claim 1, characterized in that the first and second force conducting elements belonging to a first torque support device are parallel to the first and second force conducting elements belonging to another torque support device, and the third and fourth force conducting elements belonging to the first torque support device are parallel to the third and fourth force conducting elements belonging to the another torque support device.

8. 2. The machine of claim 1, wherein the four or more horizontally disposed rolls are configured to move horizontally relative to one another to vary the gap between adjacent rolls.

9. 2. The machine according to claim 1, wherein the first and second force transmission elements are fixed to the support element on opposite sides.

10. 2. The machine according to claim 1, wherein the third and fourth force transmission elements are fixed to the support element on opposite sides.

11. 2. The machine of claim 1, wherein the first force transmitting element, the second force transmitting element, the third force transmitting element, and the fourth force transmitting element are all connected to a drive device, a support element, or a frame via bearings.

12. 2. The machine of claim 1, wherein the connections of the first force-transmitting element, the second force-transmitting element, the third force-transmitting element, and the fourth force-transmitting element to the support element are rotatable connections.

13. 2. The machine of claim 1, wherein adjacent force conducting elements connected to said support elements form an angle of 90 degrees.

14. 2. The machine of claim 1, wherein said first force conducting element, said second force conducting element, said third force conducting element, and said fourth force conducting element are all of the same length.

15. 2. The machine of claim 1, wherein said first force transmitting element and said second force transmitting element are connected to said one drive device via flanges.

16. 2. The machine of claim 1, wherein the roll set of four or more horizontally arranged rolls comprises more than four rolls.

17. 2. The machine of claim 1, wherein the third force conducting element and the fourth force conducting element are connected to the frame through one or more intermediate structures.

18. A torque support system comprising a plurality of torque support devices each associated with four or more horizontally arranged rolls rotated by a plurality of drive devices, the torque support device being provided with: Support elements and a first force-transmitting element connected to the support element and to one of the plurality of drives; a second force-transmitting element connected to the support element and the one drive device and arranged in parallel to the first force-transmitting element; a third force conducting element connected to the support element and to a stationary element; a fourth force conducting element connected to the support element and the stationary element and arranged parallel to the third force conducting element; A torque support system comprising:

19. 20. The torque support system of claim 18, wherein the support element is polygonal.

20. 20. The torque support system of claim 18, wherein the first force conducting element, the second force conducting element, the third force conducting element, and the fourth force conducting element are all formed in a rod shape.

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