inner rings 12 of conical roller bearings 10 are provided with a radially outwardly directed edge 13 against which the end wall of conical rollers 14 run through the pretensioned conical roller bearings 10 sliding friction develops between the end walls of conical rollers 14 and the inner surface of edge 13 which leads to wear through removal of material and has a negative effect on the final drive i e such support of the bevel pinion shaft 5 according to the state of the art involves a high frictional moment high bearing and oil temperatures as well as poor efficiency in addition the loss in pretensioning developing as a result of the wear of the conical rollers and edge surfaces leads to an increase in tooth play between bevel pinion 4 and ring gear 6 the bevel pinion shaft 5 of a differential shown in fig2 includes a stepped shank 15 on whose right side end lies bevel pinion 4 in housing 1 the bevel pinion shaft 5 is held by two spaced apart tandem angular contact ball bearings 16 and 17 which each include a one piece bearing inner ring 18 and a one piece bearing outer ring 19 with each ring having two shoulders 20 and 21 the bearing balls 22 and 23 are of the same size within bearings 16 and 17 and are guided in each case in bearing cages 24 one can further see from the figure that within a given bearing 16 and 17 the not more closely designated races of bearing balls 22 and 23 possess a different diameter since the greatest radial and axial stressing of bevel pinion shaft 5 occurs in the area of bevel pinion 4 tandem angular contact ball bearing.