One embodiment of the invention is illustrated in the drawing that shows a schematic view of a planetary-gear transmission.
The only FIGURE shows a star wheel 10 with radial grooves 11 in an eccentric position in relation to a ring gear 12 with teeth 13. The eccentric displacement in the illustrated example is 10 mm. For simplicity reasons, only three planetary gears are shown, of which the two planetary gears 14 are free-running and in the overrunning mode because they run in the load-free path. The illustrated planetary gear 15 is shown in the load path entrance in the locking position. Of course corresponding to the nine radial grooves 11 nine planetary gears are provided.
As the drawing illustrates, the load path is defined by two boundary lines 16 that are positioned symmetrically to the displacement direction of the eccentricity (around 10 mm) and mark the load path entrance and the load path exit. The load path angle is 360°/9=40° for nine planetary gears. When the peripheral length 17 is located inside the load path at the height of the radius on which the teeth 13 is mounted, a whole-number multiple of the tooth peripheral length (about the tooth width) exists, i.e. a whole-number uninterrupted number of teeth inside this zone, the coupling of the subsequent planetary gear is not impaired. The planetary gear is then coupled directly in the vicinity of the load path entrance, and the load path shift and consequently the secondary fluctuation are minimized. All eccentric positions for which this state can be achieved are preferred positions for the gear transmission with optimal running properties.
Number | Date | Country | Kind |
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10 2004 004 850.9 | Jan 2004 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/EP05/00851 | 1/28/2005 | WO | 00 | 3/5/2007 |