Page 190 - Improving Machinery Reliability
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Machinery Reliability Audits and Reviews   161


                                       C


                     .- 6       B
                     c        20,000
                     E   A    15,000






                     .-        1,500
                     6  3,000
                     e
                               1.000
                     3   2,000  I
                     -
                                750
                        1,500
                     2   1,000   500
                         500    250
                             A. Radial ball bearings
                             B. Cylindrical roller bearings. needle roller bearings
                             C. Spherical roller bearings, taper roller bearings, thrust ball bearings

                     Figure 3-48. Relubrication interval. (Courtesy SKF Industries, King of Prussia, PA.)


                     A  close comparison  of  the bearing  housings  of  problem  pumps  with  those  of
                   pumps with low failure frequency can be quite revealing. Low bearing failure rates
                   are reported for the execution  shown in Figure 3-49. These axially preloaded bear-
                   ings are routinely used  by  a  German manufacturer. As  shown, they  elected to
                   achieve the proper  preloading  by  selectively different  dimensioning  the  width  of
                   spacers “A” and “B.” The pump manufacturer can thus control the preload by mak-
                   ing  appropriate  adjustments.  Flinger disc  “C” tosses  lube oil onto the surrounding
                   surfaces and from there it flows into trough “D’ and on  towards both inboard and
                   outboard bearing locations.
                     The periphery  of  flinger  “C” dips  into the lube oil  level;  however,  the  lube oil
                   level  is  generally  maintained  well  below  the center of  the  lowermost  ball. This
                   reduces oil churning and friction-induced heat-up of lube oil and bearings that would
                   be more likely to occur in the design shown in Figure 3-50.
                     There is a good reason to introduce the lube oil between the two back-to-back ori-
                   ented angular contact bearings. In this design, the cage inclination promotes through-
                   flow of  lubricant, whereas many  other designs attempt to introduce the lube oil  at
                   points that oppose through-flows. Figure 3-5 la allows us to see how the cage incli-
                   nation  of back-to-back  mounted  angular contact  bearings with  steeper angles  pro-
                   motes a centrifugal outward-oriented flinging action from side “a” to side “b.” Con-
                   versely,  if  conventionally  lubricated angular contact ball bearings are back-to-back
                   mounted as shown in Figure 3-51b, lubricant flow may become marginal or insuffi-
                   cient. Subject  to proper  selection  and  utilization  of  proper  installation  procedures,
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