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supporting axial loads In certain machines, two thrust bearings are used because axial loadings can arise in both directions, and the rotor must be located axially as precisely and rigidly as possible The greatest axial stiffness is realized if the two bearings are loaded against one another at the design condition Kg = 069 as shown in Figure 760 The design load, W* is given in Figure 761 and 762 and the stiffness provided is twice that of a single isolated thrust bearing under the same load When loaded, the pressure in each of the two bearings may be different, and the resultant ultimate load is 25% higher than the design load This value can be slightly increased by light preloading by utilizing an end float However, this can result in a higher gas flow, lower stiffness and a pneumatic hammer Sometimes, two unequal thrust bearings may be used The ultimate load in both directions = 125 W*, where W* is the design load of a single bearing at Kg = 069 Therefore, the equivalent load is given by
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Single bearing 10 +load 069 05 Combined characteristic
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05 069 load 10 h*
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Ultimate load in both directions = 125 W* where W * is the design load of a single bearing at Kg = 069 W* Stiffness kA = 288 at central position h*
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120 100 = 128 lbf 570 N 125 75 On referring to Figure 761, it can be concluded that an annular thrust bearing of a 3 in outside diameter and a 1 in inside diameter supplied at 100 lbf/in2 can carry a load of 195 lbf at the design clearance of 00005 in The load value is obtained from the intersection of the inside diameter and the outside diameter The airflow is determined in a similar manner The airflow at a 100 lbf/in2 gauge would be 074 scfm and at a 75 lbf/in2 gauge would be 074 0625 scfm = 0463 scfm (00131 m3/min) For this example, the annular air thrust bearings with rings of jets are chosen because the shaft is assumed to go through the bearings From Figure 762, it is seen that, in certain cases, a central feed hole arrangement can be used
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Fig 760: Combination of two thrust bearings [3]
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Fig 761: The general performance of annular air thrust bearings with a ring of jets [3]
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Fig 762: The general performance of air thrust bearings with a central feed hole and a circular pocket [3]
A comparison between the centre-fed and annular thrust bearings in terms of the load coefficient can be clearly seen in Figure 763 The variation of load coefficient with changes in the ratio of the outside to the inside radii is shown The high load coefficient for the centre-fed thrust bearing may not be applicable because of the instability due to the large pocket volume
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Thus, an annular thrust bearing can be designed to provide the necessary load capacity and from Figure 760, a combination of two identical bearings would provide an axial stiffness of
W* 288 75 = 195 = 1053000 lbf/in (184 000 N/mm) (125 ) * 4 h 100 5 10 This stiffness is up to the requirements and represents the maximum stiffness that is in operation near the point of equal clearance for the two thrust bearings However, two annular thrust bearings would require an airflow of 0926 scfm which is in excess of the design allowance Therefore, it may be necessary to increase the air flow rate capacity Another possibility is to consider using a thrust bearing with a central feed hole and a pocket to carry the load in one direction However, this is not possible since the shaft should protrude from the bearing assembly The initial design specifications are presented in Table 76 As the size and the shape of the bearing can be established from a consideration of the load capacity, stiffness, gas flow and friction power, the next crucial step will be to obtain the required jet diameter from Figure 764 The operating conditions are again indicated on the top left corner The diameters are indicated based Fig 763: The optimum load coefficient of thrust bearings [3, 31] on the design clearance and the ratio of the outside to the inside radii The correction factors for the supply pressure and the number of jets in annular bearings are given in Figure 765 It is noted that these figures are very similar to those used in the design of journal bearings The feed hole size and arrangement will have to be determined The ratio of the outside diameter to the pocket diameter is
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