By Fowler R.H., Milne E.A.
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Additional info for A Note on the Principle of Detailed Balancing
12 Fig. 1 MN/mZ (z15 Ibf/in2) and 50°C 6000 8000 10000 20 000 40 000 \ LENGTHIDIAMETER, b/d fig. 7. 6 GUIDE TO POWER LOSS t. 1 I I MIN. FtLM THICKNESS DIAMETRAL CLEARANCE Fig. 8. 005. . 0001 , 2 . 2 --\ -. 000001 o,o, 30 000 50 DO0 Fig. 9. 4 AT EDGE (FOR MISALIGNED JOURNAL) DIAMETRAL CLEARANCE 0 I I I ? (LOAD POSITI e I MIN' (LOAD POSITI DIAMETRAL CLEARANCE 0 0 A R I I High speed bearings and rotor dynamics A10 Bearings in high speed m a c h i n e s t e n d to have high power losses and oil film t e m p e r a t u r e s .
Lightly loaded journal bearings tend therefore to generate shaft vibrationis with a frequency of about half the shaft rotational speed Fig. 2. 3 AI0 High speed bearing and rotor dynamics Lemon bore bearing I f the bearing is machined with shims between the joint faces, which are then removed for installation, the resultant bore is elliptical. When the shaft rotates, hydrodynamic clamping pressures are generated which restrain vibration Dammed groove bearing A wide and shallow central part circumferential groove in the upper half of the bearing terminates suddenly, and generates a hydrodynamic pressure which clamps downwards onto the shaft Offset halves bearing This can be made by machining the bore of two half bearing shells with a lateral offset and then rotating one shell about a vertical axis.
1 to assess whether the proposed design is likely to be critical for either load capacity or oil replenishment. With flanged bearings add together the duty of the cylindrical and thrust bearing surfaces. - 150 100 90 - 80 - 'O- N <60 2 50 - SHAFT VELOCITY, ft/rnin 0- 40- 30 20 - 2 10 'OO POROSITY, SHAFT VELOCITY, rn/s 1. A general guide to the severity of the duty. A t high pressures and particularly high velocities the running temperature increases, which requires provision for additional lubrication to give a satisfactory life.
A Note on the Principle of Detailed Balancing by Fowler R.H., Milne E.A.