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Viewing 161941 to 161970 of 170058
Technical Paper
1954-01-01
A. J. LAPOINTE
Technical Paper
1954-01-01
R. I. PETERS, H. W. REDSHAW
Technical Paper
1954-01-01
E. F. LEWIS
Technical Paper
1954-01-01
FRED M. GLASS
Technical Paper
1954-01-01
E. WALDEN
Technical Paper
1954-01-01
WILLIAM LITTLEWOOD
Technical Paper
1954-01-01
S. A. LIPPMANN
Technical Paper
1954-01-01
STEPHEN M. YOUNG
Technical Paper
1954-01-01
E. A. JAMISON, WILLIAM A. HOWE
Technical Paper
1954-01-01
MILTON S. BALD
Technical Paper
1954-01-01
ROBERT E. LaCROIX
Technical Paper
1954-01-01
W. M. HOLADAY
Technical Paper
1954-01-01
GEORGE W. LEWIS
Technical Paper
1954-01-01
E. M. JOHNSON
Technical Paper
1954-01-01
CLYDE S. BATCHELOR, EDWARD L. CAREY
Technical Paper
1954-01-01
W. H. SEACORD, F. L. HELMEL
Technical Paper
1954-01-01
F. W. FINK
Technical Paper
1954-01-01
HAROLD M. HARRISON
Technical Paper
1954-01-01
JOSEPH MARIN, ROBERT H. SHENK
SUMMARY Various types of power transmission systems such as for marine propulsion, aircraft and automotive applications utilize a planetary gear system as illustrated in Fig. 1(a). In this type of gear arrangement power is transferred from a center sun gear to a large stationary ring gear with internal teeth, by means of the three planet gears shown. The source of the power output is then obtained by the rotation of the planet gear carrier. The analysis of the stresses and deflection of this ring gear is the subject of this paper. The reason for making an accurate analysis of the stresses and deflection of the ring gear is that it is essential to provide the most flexible gear which has at the same time adequate strength. Flexibility in the gear is desired in order to make possible a uniform load distribution between the planet gears and thereby provide maximum power capactiy for the unit. The investigation made consists of the stress and deflection analysis of a circular ring gear subjected to forces P, Q and m as shown in Fig. 1(b).
Technical Paper
1954-01-01
Lt. Col. M. G. BEKKER

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