DE3227952C2 - Drive device for a rotary kiln - Google Patents

Abstract

The invention relates to a pivotable pinion arrangement to compensate for axial direction errors, which in rotary tubular drives with double helical gearing, in addition to the radial gear forces, also the axial frictional forces in the pinion bearings (7, 8) to support the setting movement by appropriate arrangement of the pendulum axis (11) and depending on the main direction of rotation Utilizes the directions of inclination of the teeth (21, 22) of the individual tooth tracks.

Description

a) the pendulum axis (11) runs approximately perpendicular to the connecting line (19, 20) between the centers of the ring gear (A) and the drive pinion (B, B ') and

b) through the oppositely directed double helical teeth formed tip of the toothing in the direction of the given direction of rotation eks ring gear (1) and the drive pinion ve? «Runs.

2. Drive device according to claim 1, characterized in that the pendulum axis (11) is arranged in an area which extends from the contact line (Z) of the rolling circles up to a distance of X , wherein

χ =

M ■ cos a μ ■ ctg a

30th

is with

χ = distance of the pendulum axis (11) from the contact line of the pitch circle (Z)

M = distance from the crack, center plane (10) to the center of a tooth trace

a = pressure angle

μ = coefficient of friction of the pinion bearing in the axial direction.

3. Drive device according to claim 2, characterized in that the pendulum axis (11) is arranged in an area which extends from the contact !: · never (Z) of the pitch circles to the distance X in the direction of the center A of the ring gear (1) .

4. Drive device with the features in the preamble of claim 1, characterized in that that

a) the pendulum axis (11) runs approximately perpendicular to the connecting line (19, 20) between the centers of the ring gear (A) and the drive pinion (B, B ') and

b) the pendulum axis is arranged on the side of the contact line (Z) of the pitch circles on which the center (A) of the gear rim (1) is located, but is at least a distance X from the contact line.

5. Drive device according to one of the preceding claims, characterized in that a plurality of drive pinions are arranged on the bearing block (9) and the pendulum axis (11 ) extends on average perpendicular to the connecting lines (AB, AB ') (Fig. 1).

The invention relates to a drive device for a rotary tube according to the preamble of claim 1 or 4, as it is used, for example, in rotary drum mills and rotary kilns Rotary tubes are often relatively large and run at low speed around.

Because of the large spans of the rotating tubes, caused by their own weight and filling, they bend Rotary tubes related to the usual ratios in gear drives, strong through. This causes especially if the ring gear of the rotary tube is arranged in the vicinity of a bearing point, an angular deviation of the Rotary tube and thus the ring gear from the central axis of the storage. This leads to the deviation of the Parallelism of the pinion axis and the ring gear axis, provided the pinion is below or above the ring gear is located so that the toothing is only supported on one side (corner girder). If the deviation were always constant, then let these balance each other out during assembly. However, since the degree of filling fluctuates strongly, the angular deviation shows strongly fluctuating values. If you prevent corner girders, the pinion with its axis must can follow the angular deviation. That the center distance and thus the depth of tooth engagement are slightly different changes, is mostly of no importance because of the large teeth.

Distortion of the rotary kiln and, above all, different thermal deformations occur in particular When starting from standstill and also temporarily tumbling movements of the rotary kiln during operation and thus the ring gear, which also interfere with the meshing of the teeth. The tumbling stroke is also periodic Axial movements of the ring gear result, which have to be taken into account with double helical gears is.

A gear arrangement is known (FR-PS 4 10 750) with double helical gearing, in which the pinion is driven by a pendulum axis perpendicular to the pinion axis, which is shown in the center plane of the drive pinion * runs, is arranged pendulum. The pendulum axis runs parallel to the Pinion axis and wheel axis plane. Thus, every pitch error causes the pinion and pinion to pivot this easily leads to vibrations. These are still favored by an elongated bearing block, the is also exposed to high bending stresses. This gear arrangement is also used in a special way the compensation of offset errors, while axis parallelism can only be compensated indirectly and partially by means of an axle set.

The object of the invention is to show a drive device according to the preamble of claim 1 or 4, which takes up little installation space with a relatively good compensation of tooth meshing errors, is flat, low-vibration and simple. Axial parallelism errors are to be preferred here be balanced and the compensatory movements favored, at least no more than inevitable be made more difficult if at the same time periodic axial displacements of the pinion take place.

This object is achieved, as indicated in the characterizing part of claims 1 and 4, respectively. The pivoting the pinion (s) around an axis results in a simple structure, but enables the compensation of axis parallelism errors directly and indirectly from set errors. Thus, great achievements can be achieved with good Load capacity of the gearing can be transferred. There can also be more than one pinion on a bracket

to be ordered. As with the size of the application upcoming sprockets and the pinions lying close to one another, the meshing errors for all pinions are almost the same in type and direction, they can all be balanced with the same pivoting movement.

Provided that the pendulum axis is the line of contact of the rolling cylinders cuts, axial movements of the pinion (s) do not affect the setting movements, since they do not Generate torque around the pendulum axis.

Refinements can be found in the further subclaims.

An exemplary embodiment is shown in the drawing and is explained below. It shows

F i g. 1 shows a drive device with two pinions in a side view,

F i g. 2 shows a section in the longitudinal plane of a pinion. A ring gear 1, which is attached to a rotating tube (not shown), is driven via two drive pinions 2, 3. The ring gear and pinion each have double helical teeth. In the main direction of rotation, the pinions turn clockwise 4. The pinions are driven by drive shafts 5, 6. Furthermore, the pinions are mounted in a bearing block 9 by means of bearings 7, 8. For the purpose of axial adjustment of the double helical toothing, the bearings 7, 8 are cylindrical roller bearings. The bearing block 9 is suspended in a pendulum fashion about a pendulum axis 11, which lies in the central plane 10 of the toothing and which runs perpendicular to the pinion axes. X denotes the distance that the contact line Z of the rolling circles has from the pendulum axis. M denotes the distance that the center of each tooth track of the double helical toothing has from the pinion means, which at the same time represents the central plane 10 of the toothing.

Since such drives normally run relatively slowly, dynamic forces can largely be ignored. The axial adjustable double helical toothing via the opposing axial thrusts.

Step now, conditional z. B. due to the deflection of the rotary tube, parallelism deviations in the axes of the ring gear and pinion, the meshing of the teeth is disturbed and corner girders appear first. That has with the result that the contact pattern of a tooth track is removed from the center plane 10, while the contact pattern of the other tooth trace approaches the midplane. Since with the contact patterns, the points of application of the radial forces of the gears move, they practice on the pendulum axle 11 due to their different distances also different moments, so that the bearing block 9 with the pinions 2, 3 is pivoted. Through this perfect tooth meshing is restored. In the case of axle offset errors that also affect corner girders lead, the same happens, so that at least the harmful corner beams are avoided.

If the contact lines Z of the rolling circles are at a distance X from the pendulum axis, axial displacements of the pinions cause z. B. as a result of wobbling of the ring gear 1 via the friction in the bearings 7, 8 also a torque on the bearing block'9 about the pendulum axis 11. This torque influences the setting of the toothings to each other described above due to parallelism and offset errors. Since mainly axial displacements and compensatory movements occur simultaneously as a result of parallelism or offset errors, the resulting torques can add up or be opposite, depending on the construction. If they add up, there are no disruptive influences. If they are in the opposite direction, at least the torque that results from an axial displacement of a pinion should be smaller than the torque that results from the radial force of the toothing, which is in the center of a tooth track, i.e. at a distance M from the center plane 10 of the toothing, attacking can be assumed. For ίο good compensation, it is better if the torque from an axial displacement is significantly smaller (approx. 50%) than that from the radial forces, but at least takes into account the friction of the bearings 14 and 15 of the pendulum axle 11. This can be achieved constructively by reducing X and / or increasing the pressure angle a . The influence of an axial displacement becomes zero if Χ becomes zero.

Since with a wobble of the ring gear, which is caused by an uneven deformation of the rotary tube, a certain direction of pendulum rotation of the pinion about the pendulum axis 1 r is always assigned a certain axial movement direction of the Rixz'is and such rotary tubes often have a certain working or main direction of rotation, there is the possibility by arranging certain tooth inclination directions: for the tooth tracks, that in each case the tooth track, which causes a certain axial thrust of the pinion through higher load absorption, is arranged to the pendulum axis 11 in such a way that due to the higher radial force of this track on the pendulum axis 11 a certain (favorable) torque is exerted. This is of particular interest when the axial forces are relatively large, e.g. B. due to high friction, large weights, etc. The direction of rotation of the torque from the radial force described must act opposite to the direction of rotation of the torque when the pendulum axis 11 is arranged on the side of the contact line Z of the rolling circles on which the Rilzel (s) are located is caused by the axial frictional forces, one wants to counteract corner girders.

When the pendulum axis 11 is arranged on the other side of the line of contact Z, the directions of rotation must of the torques around the pendulum axis must be rectified at least when the torque from the bearing friction is smaller than that from the radial gear forces.

While asymmetrical gear radial forces, regardless of the arrangement of the pendulum axes to the contact line Z, always exert a torque in the same direction around the pendulum axis depending on the bearing of the asymmetry, the bearing friction forces cause a torque around the pendulum axis depending on the arrangement of the pendulum axis to the contact line with a certain axial displacement of the pinion. The torque from the bearing friction forces is greater, the greater the distance X from the contact line. It supports pivoting of the bearing block and thus the pinion in the direction of improving the tooth engagement, provided the pendulum axis is arranged on the side of the contact line that faces the ring gear, or counteracts an improvement if the pendulum axis is on the side of the pinion .

The position of the asymmetry of the radial gear forces in the case of axial displacements caused by wobble ties pinion is determined by the choice of the tooth inclination directions (pitch direction) depending on the

Direction of movement and direction of rotation can be determined. In this way, a torque direction can be selected which contributes to improving the tooth engagement. While with the arrangement of the pendulum axis on the pinion side in an area that has a greater distance from the contact line than X , the disturbing influence of the bearing friction can only be reduced by the radial gear forces, it is possible in the remaining area to compensate it completely and even a positive one To achieve effect.

When the pendulum axis is arranged on the ring gear side, a positive effect can always be achieved, since the torque from the bearing friction always has a favorable direction and the torque can be chosen favorably from the gear axial forces. If the torque from the bearing friction is relatively large because of a large distance X from the contact line, it can be weakened by an opposing moment from the radial gear forces.

In the example shown, the direction of rotation 4 of the pinion 2, 3 is indicated with clockwise as the main direction of rotation and the front tooth trace of the pinion 2 in the viewing direction 18 (FIG. 2) with a right-handed tooth bevel direction intended.

If, for example, the ring gear 1 and pinion 2, 3 move in the axial direction as a result of wobble, the right tooth track 21 temporarily takes on a higher load share and thus exerts higher radial forces that cause the bearing block with the Ritzein to oscillate about the pendulum axis 11, namely in such a way that the right side of the pinion (FIG. 2) lowers, just as the ring gear does with the corresponding wobbling movement. The pendulum axis 11 lies in the example on the side of the pinion, so that the axial bearing frictional forces exert a torque in the opposite direction on the bearing block. However, since the distance X is made small, the iviomeni is nierauskiein, so that there are no corner girders.

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For this purpose 2 sheets of drawings

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Claims (1)

Patent claims: 1. Drive device for a rotary tube with at least a drive pinion arranged on a bearing block and a drive pinion attached to the rotary tube Ring gear with oppositely directed double helical teeth, the drive pinion to a pendulum axis perpendicular to the pinion axis, which runs in the center plane of the drive pinion, is arranged oscillating and axially freely movable, characterized in that