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JOURNAL BEARINGS 19.27
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FIGURE 19.10 Friction variable versus Sommerfeld number for full and partial journal bearings, L/D = 1, Swift-Stieber boundary conditions. (From Raimondi and Boyd [19.7].)
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FIGURE 19.11 Flow variable versus Sommerfeld number for full and partial journal bearings, L/D = 1, Swift-Stieber boundary conditions. (From Raimondi and Boyd [19.7].)
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Downloaded from Digital Engineering Library @ McGraw-Hill (www.digitalengineeringlibrary.com) Copyright 2004 The McGraw-Hill Companies. All rights reserved. Any use is subject to the Terms of Use as given at the website.
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FIGURE 19.12 Side-leakage ratio versus Sommerfeld number for full and partial journal bearings, L/D = 1, Swift-Stieber boundary conditions. (From Raimondi and Boyd [19.7].)
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For slenderness ratios other than the four displayed ( , 1, 1 2, and 1 4), Raimondi and Boyd suggest the use of the following interpolation formula: yL/D = D L
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1 L 1 8 D
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1 L L y + 1 2 3 D D
L y1 D L y1/4 D
L 1 1 D 4
L 1 L y1/2 + 1 D 24 D
where y = any performance variable, that is, (R/C)(f ), h0 /C, etc., and the subscript of y is the L/D value at which the variable is being evaluated. For partial bearings with bearing arc angles other than the three displayed (180 , 120 , and 60 ), Raimondi and Boyd recommend using the following interpolation formula: y = 1 [( 120)( 60)y180 2( 180)( 60)y120 + ( 180)( 120)y60] 7200
where y = any performance variable and the subscript of y is the at which the variable is being evaluated. Some of the tedium associated with use of charts can be removed by employing curve fits of the data. Seireg and Dandage [19.8] have developed approximate equations for the full journal bearing data of the Raimondi and Boyd charts. Table 19.15 gives the coefficients to be used in these curve-fitted equations.
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JOURNAL BEARINGS 19.29
JOURNAL BEARINGS
FIGURE 19.13 Lubricant temperature-rise variable versus Sommerfeld number for full and partial journal bearings, L/D = 1, Swift-Stieber boundary conditions. (From Raimondi and Boyd [19.7].)
Example 2. For the following data N = 3600 r/min W = 7200 lbf D = 6 in L = 4 in C = 6.0 103 in Lubricant: SAE 20 oil Inlet temperature Ti = 110 F determine the isoviscous performance of a centrally loaded full journal bearing. The viscosity-temperature relation is contained in Table 19.16. Solution. Because the viscosity varies with temperature, an iterative procedure is required. By this procedure, a first-guess viscosity is used to determine the film temperature rise. From this an average film temperature is determined, which will permit a second film temperature rise to be determined, and so on, until a converged result is obtained.
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JOURNAL BEARINGS 19.30
BEARINGS AND LUBRICATION
TABLE 19.14 Performance Data for Full and Partial Journal Bearings, L/D = 1, SwiftStieber Boundary Conditions
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JOURNAL BEARINGS 19.31
JOURNAL BEARINGS
TABLE 19.14 Performance Data for Full and Partial Journal Bearings, L/D = 1, Swift-Stieber Boundary Conditions (Continued)
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JOURNAL BEARINGS 19.32
BEARINGS AND LUBRICATION
TABLE 19.14 Performance Data for Full and Partial Journal Bearings, L/D = 1, Swift-Stieber Boundary Conditions (Continued)
Since L/D = 2 3, the Raimondi and Boyd charts would require interpolation. Alternatively, the Seireg-Dandage curve-fitted equations are used. The unit load may be immediately computed: P= W 7200 = = 300 psi LD (6)(4)
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