Machinery's Handbook, 31st Edition
Thrust Bearings
2423
. 10 13 35 10 0 1875 1 14 inches # = − = ^ h . .
6) Length of pad.
b
7) Actual unit load .
. . p 10 125 114 900 = # #
=
63psi
8) Pitch-line velocity.
. 12 1335 4000 4 430ft per min. # = = ,
U
9) Friction power loss. From Fig. 3, M = 0.19 . . .
. P 10 1 25 1 14 0 19 2 7 horsepower f # # # = =
10) Oil flow required.
. 35 40 424 27 082gallon per minute # # = = . . .
Q
(Assuming a temperature rise of 40 ° F—the maximum allowable according to the given condition—then the assumed operating temperature will be 120 ° F + 40 ° F = 160 ° F and the oil viscosity Z 2 is found from Fig. 6 to be 9.6 centipoises.) 11) Film flow. . . . . Q 96 15 10 10 1 0002 30 0038gpm F 5 3 # # # # # = = Because 0.038 gpm is a very small part of the required flow of 0.82 gpm, the bulk of the flow must be carried through the chamfers. 12) Required flow per chamfer. Assume that all the oil flow is to be carried through the chamfers. . . Q 10 0 82 0 082gpm c = = 13) Kinetic energy correction factor. If l , the length of chamfer is made 1 ⁄ 8 inch, then Z 2 l = 9.6 × 1 ⁄ 8 = 1.2. Entering Fig. 4 with this value and Q c = 0.082, 0.44 ξ = 14) Uncorrected required oil flow per chamfer. . . . Q 044 0 082 0 186gpm c 0 = = 15) Depth of chamfer. . . . . . g g 474 10 30 0186 0125 96 002inch 4 4 # # # # = = A schematic drawing of this bearing is shown in Fig. 5.
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