Torque bearing for supporting drive torque and roller device having torque bearing

Abstract

The invention relates to a torque bearing for supporting a drive torque of at least one shaft drive, comprising two first force-conducting elements (9), each of which is fixed with a first end (11) rotatably and at a distance from one another on the shaft drive (5); a bearing element (17) arranged at a distance from the shaft drive, on which the first force-conducting elements are each rotatably fixed at a second end (12) opposite the first end and at a distance from each other; and two second force-conducting elements (10), each of which is fixed with a first end (13) so as to be rotatable and spaced apart from each other on the support element (17) and each of which is fixed with a second end (14) opposite the first end so as to be rotatable and spaced apart from each other on an independent fixing element relative to the shaft drive (5). The invention further relates to a corresponding roller device.

Description

[0001] This application is a divisional application of Chinese invention patent application No. 202180020740.X, entitled “Torque support for supporting driving torque and roller device having a torque support”, filed on January 5, 2021. The related applications of the parent case are incorporated herein by reference. Technical Field

[0002] The present invention relates to a torque support for supporting the driving torque of at least one shaft drive, comprising two first force transmission elements, which are respectively fixed to the shaft drive with first ends so as to be rotatable and spaced apart from each other; and a supporting element arranged spaced apart from the shaft drive, to which the first force transmission elements are respectively fixed with second ends respectively opposite to the first ends so as to be rotatable and spaced apart from each other; and comprising two second force transmission elements, which are respectively fixed to the supporting element with first ends so as to be rotatable and spaced apart from each other, and are respectively fixed with second ends respectively opposite to the first ends so as to be rotatable and spaced apart from each other on a fixing element independent of the shaft drive. Background Art

[0003] In calender drives or rolling mill drives known from the prior art, the drive torque is supported by a simple torque support, in which the drive is directly connected to the roll and the torque is often supported by a connection to the machine frame, an external frame or by two rigid, one-piece torque supports supporting each other. For example, a torque support is known from utility model DE 87 12 742 U1.

[0004] By means of such a torque support, which supports the moment on one side, forces are introduced into the support. When a torque occurs, it is supported by the torque support in that the torque support acts as a lever arm, at the end of which forces act in opposition. However, this forces react on the drive, which forces can force the rollers out of their position and can have varying degrees of influence on the precision of the device, depending on the supported drive torque. Since the reaction force has a component in the same direction of action as the actual calender, it directly influences the rolling force or the roll gap.

[0005] Another problem that exists, for example, in the case of mutually connected torque supports is that the angular position of the rollers relative to one another changes during a horizontal linear displacement of the rollers, that is, during a change in the roller gap. In addition, there is the problem of external connection of the torque supports, that is, when the bearing point of the torque support is fixed externally, the roller bearing can only move freely to a limited extent.

[0006] If the torque is supported via two external points, which are located on opposite sides of the drive, then no reaction forces are generated here that act on the support or the drive. However, the problem with this embodiment of the torque support is that the drive is fixed in its position both rotationally and linearly by using two connection points and therefore cannot completely compensate for movements acting on it or cannot be moved relative to the other roller. Summary of the invention

[0007] The object of the invention is therefore to improve the torque support in such a way that, on the one hand, no reaction forces are transmitted to the drive system via the torque support and, on the other hand, the influence of the torque support on the position of the roller bearing is reduced.

[0008] This object is achieved by a torque support or by a roller arrangement.

[0009] Therefore, a torque support for supporting the driving torque of at least one shaft drive is proposed, which comprises two first force transmission elements, which are each rotatably fixed to the shaft drive with a first end and spaced apart from each other; a support element arranged spaced apart from the shaft drive, to which the first force transmission elements are each rotatably fixed with a second end opposite to the first end and spaced apart from each other; and two second force transmission elements, which are each rotatably fixed to the support element with a first end and spaced apart from each other, and are each rotatably fixed with a second end opposite to the first end and spaced apart from each other on a fixing element independent of the shaft drive. In this case, in the support of the torque, one of the two first force transmission elements is a pressure element and the other is a tension element. The first ends of the first force transmission elements can be arranged opposite each other around a first drive axis, in particular. The support element can be designed as a planar element, which extends substantially in the same fastening plane as the fixing points of the force transmission elements. The second end of the first force transmission element can be arranged oppositely and the first end of the second force transmission element can be arranged oppositely on the support element. The fixing points of the force transmission element can be arranged on the support element in particular so that the fixing points define the corner points of a square. Thus, in this square, the corner points can be defined alternately by the first force transmission element and the second force transmission element. The independent fixing element can be in particular a machine frame, a fastening point independent of the calender or another drive. The support element can be arranged in particular centrally below the drive and oriented in the plane of the end face or parallel to the end face of the drive.

[0010] The advantage of the torque support according to the invention is that the torque is further guided via two rotatable bearings to a force transmission element, which is respectively fixed to one or more drives via these two rotatable bearings, and depending on the torque direction, one of these force transmission elements is a tension element and the other is a pressure element. Due to system conditions, only torque can be transmitted in the form of tension and pressure via the rotatable bearings. With this design, the torque support can only transmit torque. No other forces are introduced into the system. Therefore, fluctuations in the drive torque do not lead to inaccuracies in the device.

[0011] The second end of the second force transmission element can be fastened, in particular, rotatably and spaced apart from one another, to a second shaft drive arranged parallel to the first shaft drive. In this case, the second end of the second force transmission element can be arranged relative to one another, in particular, around the second drive axis. This results in a mirror-symmetrical arrangement of the two drives and the first force transmission element and the second force transmission element, in which the axis of symmetry extends perpendicularly through the support element. The torque support according to the invention can also be used to change the roller distance, since the support element can be freely moved. By changing the roller distance, the support element will only move up and down. The angular position of the two rollers also remains the same when adjusting the roller position.

[0012] The force transmission elements can also be supported rotatably around their respective fixing points. Thus, only the tensile forces and compressive forces are respectively directed via the force transmission elements to an externally arranged support element, which is supported or connected only by rotatable bearings at the ends of the force transmission elements. The fact that the force transmission elements are supported rotatably around their respective fixing points means that the force transmission elements are rotatable in a plane perpendicular to the axial direction of the assigned drive. The force transmission elements can be fixed to the respective drives in particular by rotatable screw connections. Alternatively, a bearing can be arranged between the respective drive and the force transmission element. Furthermore, alternatively, the force transmission element can be fixed to the respective drive by an articulated connection.

[0013] It can be provided that the first end of the first force transmission element is relatively and rotatably fixed on a flange around the drive shaft of the first shaft drive. Alternatively, a fastening disk can be mounted on the flange of the first drive as an intermediate element, on which the force transmission element is fixed.

[0014] It can also be provided that the second end of the second force transmission element is relatively and rotatably fixed on the flange of the drive shaft around the second shaft drive. Alternatively, a fastening disk can also be installed on the flange of the second drive as an intermediate element, on which the force transmission element is again fixed.

[0015] The force conducting elements can be fastened to the drive in each case such that a first line intersecting the first end of the first force conducting element and a second line intersecting the second end of the second force conducting element intersect at an angle of 60° to 120°, preferably 80° to 100°, and particularly preferably 90°.

[0016] Furthermore, a spacer can be additionally mounted on the flange of the first drive or the second drive, to which the respective end of the force-conducting element is fastened, so that the force-conducting element fastened to the spacer and the force-conducting element fastened to the other drive extend in different planes perpendicular to the axial direction of the drive shaft. Alternatively, in the case of a fastening disk arranged on the flange, the spacer is mounted between the respective fastening disk and the respective flange. The fastening disk can be mounted on the respective flange by means of screws. The spacer can be screwed directly to the flange by means of screws or have holes aligned with the fastening disk, through which the spacer and the associated fastening disk are screwed together to the flange by means of screws.

[0017] Furthermore, the front force transmission element can be fastened to the support element at the front and the rear force transmission element can be fastened to the support element at the rear. As a result, the drives can be freely moved relative to one another or the support element can be moved up and down without one of the force transmission elements hindering one of the mentioned movements.

[0018] The ends of the force conducting element which are fastened to the support element can also be fastened to the support element distributed over the circumference of a circle or define the corner points of a square.

[0019] Furthermore, it can be provided that the first force transmission element and the second force transmission element are each arranged parallel to one another. It follows that the distance between the fixing points of the first end of the force transmission element and the distance between the fixing points of the second force transmission element are each of the same size.

[0020] Furthermore, one of the first force transmission elements and one of the second force transmission elements between the fixing point on the drive and the fixing point on the support element can cross each other. In particular, the first force transmission elements and the second force transmission elements fixed to the side of the support element facing the drive between the corresponding fixing point on the drive and the corresponding fixing point on the support element can cross each other. Correspondingly, it can be provided that the corresponding other first force transmission elements and second force transmission elements do not cross each other.

[0021] Furthermore, the second end of the first force transmission element and the first end of the second force transmission element can each be fastened opposite each other and at a regular distance from each other on the carrier element.

[0022] Furthermore, by increasing the distance between two parallel drive axes of the two drives, the support element can be displaced in the direction of the drive axes.

[0023] Furthermore, the force transmission elements can be rod-shaped. In particular, they can be flat rods. In this case, all the force transmission elements can have the same length. Holes can be provided at the first end and the second end of the first force transmission element and the second force transmission element, respectively, through which the force transmission elements can be fastened to the corresponding fixing points. In this case, the hole spacing can be the same at all the force transmission elements. The ends of the force transmission elements can each be rounded.

[0024] The support element can also be designed in an annular manner. The circumference of the support element, to which the end of the force-conducting element is fixed, can correspond in particular to a circumference on the flange of the first drive and / or the second drive, to which the opposite end of the force-conducting element is respectively fixed. The support element can in particular have a flat, circumferential ring, on which holes for fixing the force-conducting element are arranged at regular intervals. Alternatively, the support element can have the shape of a circular or polygonal disk, as long as the above-mentioned fixing of the force-conducting element is ensured.

[0025] The invention further proposes a roller arrangement having at least two rollers arranged in parallel, in particular rotating in opposite directions, with a roller gap formed between each roller, wherein the rollers are driven by shaft drives arranged side by side and rotating in opposite directions, and the roller arrangement has at least one torque support as described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Exemplary embodiments of the present invention are described below with reference to the accompanying drawings.

[0027] FIG. 1 shows a perspective view of an embodiment of mutually supporting torque supports known from the prior art;

[0028] FIG. 2 shows a front view of an embodiment of the torque support according to FIG. 1 known from the prior art;

[0029] FIG3 shows a front view of an embodiment of a torque support with bearings on both sides known from the prior art;

[0030] Figure 4 shows a front view of a first embodiment of a torque support according to the invention;

[0031] Figure 5 shows a front view of another embodiment of a torque support according to the present invention;

[0032] Figure 6 shows a perspective view of another embodiment of a torque support according to the present invention;

[0033] Figure 7 Shown according to Figure 6A front view of an embodiment of a torque support according to the present invention;

[0034] Figure 8 shows a perspective view of another embodiment of a torque support according to the present invention;

[0035] Fig. 9 Shown according to Figure 8 A front view of an embodiment of a torque support according to the invention. DETAILED DESCRIPTION

[0036] FIG. 1 shows a solution of a torque support 1 for supporting torques known from the prior art, in which the drive torques occurring on the calender drive or rolling mill drive 5, 6 are supported by mutually supporting torque supports which are rigidly fastened to the flange 19 of the drive 5, 6 on the one hand and are rotatably anchored to each other in a common fixing point opposite one another. The drives 5, 6 are directly connected to the respective rollers 7, 8. The drive axes 21, 22 are oriented parallel to one another so that an equidistant roller gap 23 is formed between the rollers 7, 8.

[0037] As can be seen from FIG. 2 , this one-sided support of the forces always introduces forces into the corresponding bearings. FIG. 2 only illustrates the right drive side 5 by way of example. As soon as a torque 2 is generated on the drive side, it is supported by the torque support 1 of the right drive 5 via the force 3 and the lever arm 26. However, this generates a reaction force 4 acting on the drive 5. This force 4 causes the roller 7 to be squeezed out of its position and, depending on the size of the drive torque, has a different degree of effect on the precision of the device. Since the reaction force 4 has a component in the same direction of action as the feed direction of the calender, it directly affects the rolling force or the roll gap 23 here.

[0038] The embodiment of the torque support 1 shown in FIG. 3 has, in contrast to the example from FIGS. 1 and 2 , two-sided anchorings in which the torque support 1 has two opposing lever arms 26 of equal length. The torque support 1 supported on both sides achieves that the forces 3 of the support torque and the reaction forces 4 cancel each other out and thus no forces act on the support and no influence on the roller gap 23 occurs. However, the drive 5 is fixed in its position at two points in a disadvantageous manner and therefore cannot completely compensate for the movement.

[0039] Figure 4The first embodiment of the torque support 1 according to the invention shown in FIG. 1 shows a shaft drive 5 with a first roller 7, wherein the torque support is realized by a bearing element 17, which is connected to the flange 19 of the drive via two first force transmission elements 9 on the one hand and to two fixed bearings 27 via two second force transmission elements 10 on the other hand. The fixed bearing 27 can be an external element, that is to say an element decoupled from the shaft drive 5, such as a machine frame or another structure suitable as a fixed bearing. The first force transmission element 9 is rotatably fastened with a first end 11 to a fixing point 18 on the flange 19 of the first shaft drive 5, wherein rotatably here means, in particular, rotatable in a plane perpendicular to the shaft drive axis 21. The first force transmission element is also rotatably fastened with a second end 12 to a fixing point 18 on the bearing element 17. In this case, the force transmission elements 9 extend parallel to each other. This means that the fixing points 18 on the flange 19 on the one hand and on the bearing element 18 on the other hand are each at the same distance from each other. The force transmission elements are designed as flat rods, which are preferably made of metal. The support element 17 is formed in an annular shape by a flat part, which has in particular the same width as the force transmission element. The ring diameter corresponds in particular to the distance of the fixing points 18 on average. The first force transmission element 9 is arranged on the support element 17 in a relative manner. The second force transmission element 10 is preferably staggered 90° relative to the first force transmission element 9 and is rotatably fastened with the first end 13 on the fixing point 18 on the support element 17. Thus, the second force transmission element 10 is also arranged on the support element 17 in a relative manner. The second force transmission element 10 is rotatably fastened with the second end 14 on the fixing points 18, which are in particular configured as fixed bearings 27. The distances of the fixing points 18 of the second force transmission element 10 are also the same, so that the second force transmission elements 10 also extend parallel to each other. This arrangement achieves that these force transmission elements transmit only compressive stress or tensile stress respectively, but not torque. Thus, compared with conventional torque bearings, the deviation of the drive from its rated position due to large torque is significantly reduced.

[0040] Figure 5Another embodiment of a torque support 1 is shown, 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. As a result, the drive directions of the drives 5, 6 always run in opposite directions relative to each other. In this case, each of the drives 5, 6 has a separate torque support 1, that is, each drive 5, 6 has a separate first force transmission element 9 and a second force transmission element 10 and a separate bearing element 17. The second force transmission element 10 is each rotatably fixed with its second end 14 on a separate fixed bearing 27. The torque support 1 prevents the drives 5, 6 from their nominal position even at high torques, for example at load changes, so that the distance d between the shaft drive axes and the corresponding feed in the roller gap 23 remain unchanged.

[0041] exist Figure 6 and Figure 7 In another embodiment of the torque support 1 shown in FIG, two drives 5, 6 running in opposite directions have a common torque support 1, so that the two drives 5, 6 are supported relative to each other. Here, the torque 2 is now conducted via two force transmission elements 9, 10 respectively fixed in parallel to the drives 5, 6, which are each fixed with their opposite ends 12, 13 to an annular support element 17. Here, the force transmission elements 9, 10, which are designed as flat rods, are each rotatably supported in their fixing points 18. As a result, the force transmission elements 9, 10 are only used to transmit tensile or compressive forces to the support element 17, but not to transmit torque to the support element 17. Finally, this results in no reaction forces acting on the drives 5, 6, so that even in the case of high torques, no influence on the roller gap 23 occurs.

[0042] For this purpose, two radially opposite first ends 11 of the first force transmission element 9 on the flange 19 of the first drive 5 are rotatably fixed at a fixing point 18 orthogonally to the first drive axis 21. The first force transmission elements 9 are designed as flat rods and have the same length and are rotatably fixed to the support element 17 at the circumference of the annular support element 17 at the corresponding fixing point 18 with the opposite second ends 12. In this case, the first force transmission element 9 is rotatable parallel to the plane in which the support element 17 extends. The fixing points 18 on the flange 19 of the first force transmission element 9 and the fixing points 18 on the support element 17 are each at the same distance, so that the two first force transmission elements 9 extend parallel to each other.

[0043] The two radially opposite second ends 14 of the second force transmission element 10 on the flange 19 of the second drive 6 are rotatably fixed at the fixing point 18 orthogonally to the second drive axis 22. The second force transmission element 10 is also designed as a flat rod and has the same length as the first force transmission element 9 and is rotatably fixed to the support element 17 with the first opposite ends 13 on the circumference of the annular support element 17 at the corresponding fixing point 18. In this case, the second force transmission element 10 is rotatable parallel to the plane in which the support element 17 extends. The fixing points 18 on the flange 19 of the second force transmission element 10 and the fixing points 18 on the support element 17 are also at the same distance in each case, so that the two second force transmission elements 10 also extend parallel to each other. The straight line connecting the fixing points 18 of the first force transmission element 9 on the flange 19 of the first drive 5 and the straight line connecting the fixing points 18 of the second force transmission element 10 on the flange 19 of the second drive 6 intersect at an angle α above the roller arrangement. By adjusting this angle, the vertical distance of the support element 17 from the parallel drive axes 21, 22 of the roller arrangement can be adjusted. The annular support element 17 is formed by a flat ring, on the circumference of which the fixing points 18 of the first force transmission element 9 and the second force transmission element 10 are arranged alternately and distributed, wherein the first force transmission element 9 is fixed to the support element 17 at the front and the second force transmission element 10 is fixed to the support element 17 at the rear, so that the force transmission elements 9, 10 do not hinder each other. For example, the upper first force transmission element 9 and the upper second force transmission element 10 cross at the distance between the force transmission element located on the corresponding flange 19 and the corresponding fixing point 18 on the support element 17, wherein the first force transmission element 9 moves before the second force transmission element 10 and the two do not affect each other in their respective movement range. In conjunction with this, a spacer 20 in the form of a flat disk is provided on the flange 19 of the first drive 5, which is installed below the fastening element on which the first force transmission element 9 is fixed to the first drive 5. In this case, the spacer 20 has approximately the sum of the thicknesses of the second force conducting element 10 and the support element 17 in order to compensate for the resulting thickness differences.

[0044] A change in the distance d of the drive axes 21, 22 or the roller gap 23 is also possible because the support element 17 is moved up and down by the rotatable mounting of the force transmission elements 9, 10. In this case, the angular position of the two rollers 7, 8 can also be maintained when adjusting the roller distance.

[0045] Figure 8 and Fig. 9Another embodiment of the invention is shown, in which four rollers 7, 8, 30, 31 are arranged parallel to one another while forming three roller gaps 23, 32, 33. In this case, adjacent rollers each rotate in opposite directions. In particular, in the arrangement shown, three torque supports 1 are provided, which have three bearing elements 17, which are each located below between two rollers. In this embodiment, two adjacent torque supports 1 are each assigned to two built-in shaft drives 6, 28. As a result, four force transmission elements 9, 10 are each rotatably fastened to the flange 19 of the drive 6, 28, wherein the two first force transmission elements 9 are fixed to the bearing element 17 arranged at the bottom left and the two second force transmission elements 10 are fixed to the bearing element 17 arranged at the bottom right. In the embodiment shown, the first force transmission elements 9 extend in the plane of the front side of the bearing element 17 and the second force transmission elements 10 extend in the plane of the rear side of the bearing element 17. Corresponding spacers 20 are mounted on the drives 5, 6, 28, 29, by means of which different fastening planes are provided for the first force transmission element 9 and the second force transmission element 10. It will be appreciated that the principle of the illustrated embodiment can alternatively be applied to any number of adjacently arranged shaft drives.

[0046] The features of the invention disclosed in the above description and the drawings can be essential for the implementation of the invention both individually and in any combination.

[0047] Reference numerals list

[0048] 1 Torque support

[0049] 2 Torque

[0050] 3 Support force

[0051] 4 Reaction force on the driver

[0052] 5 First axis drive

[0053] 6 Second axis drive

[0054] 7 First Roll

[0055] 8 Second Roller

[0056] 9 First force transmission element

[0057] 10 Second force transmission element

[0058] 11 First end of the first force transmission element

[0059] 12 Second end of the first force transmission element

[0060] 13 First end of the second force transmission element

[0061] 14 Second end of the second force transmission element

[0062] 15 First drive shaft

[0063] 16 Second drive shaft

[0064] 17 Support element

[0065] 18 fixed points

[0066] 19 Flange

[0067] 20 Spacer

[0068] 21 First drive axis

[0069] 22 Second drive axis

[0070] 23 Roller gap

[0071] 24 Pull

[0072] 25 Pressure

[0073] 26 Lever arm

[0074] 27 Fixed bearing

[0075] 28 Third axis drive

[0076] 29 Fourth axis drive

[0077] 30 Third Roller

[0078] 31 Fourth Roller

[0079] 32 Second roller gap

[0080] 33 Third roller gap

[0081] d Distance between drivers

[0082] α Angle between the fixed point axes

Claims

1. A machine comprising: frame; a set of four or more horizontally aligned rollers within the frame, rotated by respective drives, the first and third rollers being rotated in a first direction by respective first and third drives, and the second and third rollers being rotated in an opposite second direction by respective second and fourth drives; A torque support system comprising a torque support associated with each horizontally aligned roller, a particular one of the torque supports comprising: Support elements; a first force conducting element connected to one of the actuators and the support element; a second force conducting element connected to the one driver and the support element, parallel to the first force conducting element; a third force conducting element connected to the support element and the frame; A fourth force conducting element connected to the support element and the frame is parallel to the third force conducting element.

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

3. The machine of claim 1, wherein the first, second, third and fourth force conducting elements are rod-shaped.

4. The machine of claim 1, wherein the first, second, third and fourth force conducting elements are flat rod-like elements.

5. The machine according to claim 1, wherein the machine is a calender or a rolling mill.

6. The machine of claim 1, wherein the torque support is associated with the first roller; Wherein an additional torque support similar to the one described is associated with each of the further four or more horizontally aligned rollers.

7. The machine of claim 1, wherein the first and second force conducting elements of a first torque support are parallel to the first and second force conducting elements of another torque support; and Therein, the third and fourth force transmission elements of the first torque support are parallel to the third and fourth force transmission elements of the other torque support.

8. The machine of claim 1, wherein four or more horizontally aligned rollers are configured to move horizontally relative to each other to vary the nip between adjacent rollers.

9. The machine of claim 1, wherein the first force conducting element is connected to the support element opposite the connection of the second force conducting element to the support element.

10. The machine of claim 1, wherein the third force conducting element is connected to the support element opposite the connection of the fourth force conducting element to the support element.

11. The machine of claim 1, wherein the first, second, third, and fourth force conducting elements are connected to the drive, the support element, or the frame via bearings, respectively.

12. The machine of claim 1, wherein the connection of the first, second, third and fourth force conducting elements to the support element is rotatable.

13. The machine of claim 1, wherein the angle between adjacent force conducting element connections to the support element is 90 degrees.

14. The machine of claim 1, wherein the first, second, third, and fourth force conducting elements have the same length.

15. The machine of claim 1, wherein the first and second force conducting elements are connected to one of the drivers via a flange.

16. The machine of claim 1, wherein a set of four or more horizontally aligned rollers includes more than four rollers.

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

18. A torque support system comprising: A torque support associated with one of a set of four or more horizontally aligned rollers rotated by a corresponding drive, a particular one of the torque supports comprising: Support elements; a first force conducting element connected to one of the actuators and the support element; a second force conducting element connected to the one driver and the support element, parallel to the first force conducting element; a third force conducting element connected to the support element and the base support structure; A fourth force conducting element connected to the support element and the base support structure is parallel to the third force conducting element.

19. A torque support system according to claim 18, wherein the support element is polygonal.

20. The torque support system of claim 18, wherein the first, second, third, and fourth force conducting elements are rod-shaped.

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