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Jackson，..，""Radial and Thrust Bearing Practices with .aseHistories，'' Pro-ceedings of the 14th TurbomachinerySymposium， Texas A&MUniversity，
p.73， 1985.King，T.L.， and.apitao，J.W.， ""Impact on Recent Tilting Pad Thrust BearingTests on Steam Turbine .esign andPerformance，'' Proceedings of the 4thTurbomachinerySymposium， Texas A&MUniversity， October1975， pp. 1.8.Leopard，A.J.，""Principles of Fluid Film Bearing .esign andApplication，''Proceedings of the 6th TurbomachinerySymposium， Texas A&MUniversity，.ecember1977， pp. 207.230.Mayeux，T.，Paul， FeltmanJr.， andPaul，L.， "".esign Improvements Enhance.ry Gas Seal's Ability to Handle ReversePressurization，'' Proceedings of the25th TurbomachinerySymposium， Texas A&MUniversity， p.149， 1996.Richards，R.L.，.ance，J.M.，Paquette，..J.，Zeidan，F(xiàn).Y.， ""Using a .amper Seal to Eliminate Subsynchronous .ibrations in Three Back-to-Back.ompressors，''Proceedings of the 24th TurbomachinerySymposium， TexasA&MUniversity， p.59， 1995.Salamone，..J.， ""Journal Bearing .esign Types and Their Applications toTurbomachinery，'' Proceedings of the 13thTurbomachinerySymposium，Texas A&MUniversity， p.179， 1984.Scharrer，J.K.，Pelletti， andJoseph，M.， ""Leakage and Rotordynamic Effects of.ompressible AnnularSeals，'' Proceedings of the 24th Turbomachinery Sym-posium， Texas A&MUniversity， p.175， 1995.Shah，P.， "".ry Gas .ompressorSeals，'' Proceedings of the 17th TurbomachinerySymposium， Texas A&MUniversity， p.133， 1988.Shapiro，W.， and.olsher，R.， "".ynamic .haracteristics of Fluid Film Bear-ings，'' Proceedings of the 6th TurbomachinerySymposium， Texas A&M Uni-versity， .ecember1977， pp. 39.53.Southcott，J.F.，Sweeney，J.M.， FeltrnanJr.， andPaul，L.， "".ry Gas SealRetrofit，'' Proceedings of the 24th TurbomachinerySymposium， TexasA&MUniversity， p.221， 1995.Takeuchi，Takao，Kataoka，Tadashi，Nagasaka，Hiroshi，Kakutani，Momoko，Ito，Masanobu，Muraki， and Ryoji ""Advanced .ry Gas Seal by the .ynamic
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14

Gears

Gearing is one of the most important components between prime moversand driven units. If gearing is not selected properly， it can cause many problems. Gearing transmits great power at high rotational speeds. Recentadvances in turbomachinery technology， especially in turbines， compressors，couplings， and bearings， have required gearing to withstand high externalforces. To design problem-free equipment， it is important to consider theeffect of the external system on gearing.Thus， all the factors that influencedesign， application， and operation ofgear drives should be considered in the design phase.
Since problems encountered with gears are complex， it is unfair to blame them on the gear manufacturers alone. The gear supplier is much less informed about the package than any other group. Problems should be handled as a team effort between manufacturers and users. One factor causing problems is that the system is not timed in terms of spring constants and masses. The gear is usually the only item required to operate with metal parts in such close contact with other components. This setup can result in early failure. Gearing is also subjected to cyclic loading varying from0 to55，000 cycles per minute.
With current materials and heat-treating techniques， the use of high-hardness gearing with tooth loads of 1500-2000 pounds per inch of face atpitchlinevelocities of20，000-30，000feetperminute(6096-9144mpm)isnotat all uncommon. In turbine-driven test equipment， gear drives have beenbuiltwithpitchlinevelocitiesashighas55，000feetperminute(16，764mpm)and rotational speeds approaching100，000 rpm. The magnitude of internal forces and material stresses coupled with the high speeds has resulted in gear drives that are dynamically complicated and sensitive to influences from other components in the system.
　
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