agma pubs catalog february 2011

Technical Publications CatalogFebruary 2011

ii February 2011Publications Catalog

AGMACatalog of Technical Publications

TABLE OF CONTENTS

Topic Page

American Gear Manufacturers Association iii. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

How to Purchase Documents 1. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Index of AGMA Standards and Information Sheets by Number 1. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Index of AGMA Standards and Information Sheets by Topic 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Aerospace 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Calibration and Measurement Uncertainty 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Couplings 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design and Assembly -- Bevel 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Fine Pitch 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Spur and Helical 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Wormgear 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Drive Components 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Enclosed Drives 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Failure Modes 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .High Speed Units 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Inspection and Tolerances 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Lubrication 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Materials 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Metric Usage 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Mill Drives 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Nomenclature 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Plastics Gears 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Powder Metallurgy Gears 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Proportions 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Rating: Spur, Helical and Bevel Gears 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Sound and Vibration 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Style Manual 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Thermal 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Vehicle 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Wind Turbine Units 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Wormgears 8. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

AGMA Standards and Information Sheets 9. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

ISO Standards by Technical Committee 60 20. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Gear Software (for ANSI/AGMA 2001 and ISO 6336) 22. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .AGMA’s Gear Rating Suite 22. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .AGMA’s Bevel Gear Rating Suite 22. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Fall Technical Meeting Papers: 2000 -- 20010 24. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2010 Papers 24. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2009 Papers 29. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2008 Papers 33. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2007 Papers 37. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2006 Papers 41. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2005 Papers 43. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2004 Papers 47. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2002 Papers 50. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2001 Papers 52. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2000 Papers 53. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

iiiFebruary 2011 Publications Catalog

American Gear Manufacturers Association

AGMA is a voluntary association of companies, consultants and academicians with a direct interest in the design,manufacture, and application of gears and flexible couplings. AGMA was founded in 1916 by nine companies inresponse to the market demand for standardized gear products; it remains a member-- and market--drivenorganization to this day. AGMA provides a wide variety of services to the gear industry and its customers andconducts numerous programs which support these services. Some of these services and programs are:

D STANDARDS: AGMA develops all U.S. gear related standards through an open process under theauthorization of the American National Standards Institute (ANSI).

D ISO PARTICIPATION: AGMA is Secretariat to TC60, the committee responsible for developing allinternational gear standards. TC60 is an ISO (International Organization of Standardization) committee.

D MARKET REPORTS AND STATISTICS: AGMA’s Operating Ratio Report, Wage & Benefit Survey, andMonthlyMarket TrendReports help you stay competitive by giving you up--to--date information on the gearindustry.

D THE MARKETING AND STATISTICAL COUNCILS enhance your competitiveness by sharinginformation and by developing creative solutions to common industry problems.

D THEPUBLICAFFAIRSCOUNCIL gives you an active voice inWashington, promoting the gear industry toour nation’s legislators and regulators.

D GEAR EXPO: This is the only trade show dedicated solely to the gear industry.

D TECHNICAL COMMITTEEMEETINGS are the core of the open AGMA standard writing process keepingmembers abreast of new developments while ensuring that AGMA standards are kept current.

D THE AGMA TRAINING SCHOOL FOR GEAR MANUFACTURING uses current technology to offerhands--on training in hobbing, shaping, and inspection. At the ”Gear School”, operators learn how tomaximize their productivity. Enrollment is open to all.

D NEWS DIGEST, AGMA’s quarterly newsletter, offers you timely, useful information you can useimmediately.

If you would like additional information about our programs, or on how to become a member of AGMA, pleasecontact AGMA Headquarters.

American Gear Manufacturers Association500 Montgomery Street, Suite 350

Alexandria, VA 22314--1560

Phone: (703) 684--0211FAX: (703) 684--0242

E--Mail: [email protected]: www.agma.org

Leading the Gear Industry Since 1916

1February 2011 Publications Catalog

Obsolete documents should not be used, please use replacements. Most obsoleteand superseded documents are available for purchase. Contact AGMA Headquarters

for price and availability.

How to Purchase Documents

Unless otherwise indicated, all current AGMAStandards, Information Sheets and paperspresented at Fall Technical Meetings are

available for purchase, in electronic form,through the AGMA website, www.agma.org.

Index of AGMA Standards and Information Sheets by NumberItalicizing denotes a current standard

Number Page Title or reference

110.04 Replaced by 1010--E95

112.05 Incorporated into1012--G05

114.02 Replaced by 910--C90

115.01 Replaced by 933--A03

116.01 Incorporated into1012--G05


120.01 Withdrawn

121.02 Replaced by 120.01




141.01 Withdrawn


170.01 Replaced by 6002--B93

201.02 Withdrawn

202.03 Replaced by 2005--D03

203.03 Withdrawn

207.06 Replaced by 1003--G93

208.03 Replaced by 2005--D03

209.04 Replaced by 2005--D03


211.02A Replaced by 420.04

212.02 Replaced by 2003--B97

215.02 Replaced by 218.01 &2003--B97

216.01 Replaced by 2003--B97


217.01 Withdrawn

218.01 Replaced by 2001--D04 &908--B89




222.02 Replaced by 2003--B97


223.02 Replaced by 2003--B97

224.01 Incorporated into 240.01


226.01 Replaced by 908--B89

230.01 Replaced by 2007--C00

231.52 Replaced by 2002--B88

234.01 Replaced by 390.03a

235.02 Replaced by 2000--A88

236.05 Replaced by 390.03a


239.01 Replaced by 2000--A88

239.01A Replaced by 390.03a

240.01 Replaced by 2004--B89










246.02A Replaced by 926--A99




250.04 Replaced by 9005--E02



2 February 2011Publications Catalog


251.02 Replaced by 9005--E02



255.03 Replaced by 6001--D97

260.02 Replaced by 6001--D97

265.01 Replaced by 6001--D97



295.04 Replaced by 6025--D98

297.01 Replaced by 6025-- D98

298.01 Replaced by 6025-- D98


321.05 Replaced by 6004--F88

323.01 Replaced by 6005--B89

330.01 Replaced by 2005--D03

331.01 Replaced by 2008--C01

341.02 Replaced by 6022--C93

342.02 Replaced by 6035--A02

360.02 Withdrawn


374.04 Withdrawn

390.03 Replaced by 390.03a &2000--A88

390.03a Replaced by 2009--B01and 2011--A98


420.04 Replaced by 6010--F97

421.06 Replaced by 6011--i03

422.03 Withdrawn


424.01 Withdrawn


426.01 Replaced by 6000--B96

427.01 Incorporated into6011--H98


431.01 Withdrawn

440.04 Replaced by 6034--A87

441.04 Replaced by 6035--A02

442.01 Replaced by 6035--A02

460.05 Replaced by 6019--E89


461.01 Replaced by 6035--A02

480.06 Replaced by 6021--G89

481.01 Replaced by 6021--G89

510.03 Replaced by 9009--D02

511.02 Replaced by 9002--B04

512.03 Replaced by 9002--B04

513.01 Replaced by 9002--B04

514.02 Withdrawn

515.02 Replaced by 9000--C90

516.01 Replaced by 9008--B00


900--H06 9 Style Manual for thePreparation of Standards,Information Sheets andEditorial Manuals

901--A92 9 Procedure for thePreliminary Design ofMinimum Volume Gears

904--C96 9 Metric Usage

906--A94 Withdrawn

908--B89 9 Geometry Factors forDetermining the PittingResistance and BendingStrength of Spur, Helicaland Herringbone GearTeeth

909--A06 9 Specifications for MoldedPlastic Gears

910--C90 9 Formats for Fine--PitchGear Specification Data

911--A94 9 Design Guidelines forAerospace Gearing

912--A04 9 Mechanisms of Gear ToothFailure

913--A98 10 Method for Specifying theGeometry of Spur andHelical Gears

914--B04 10 Gear Sound Manual -- PartI: Fundamentals of Soundas Related to Gears; PartII: Sources, Specificationsand Levels of Gear Sound;Part III: Gear NoiseControl

915--1--A02 10 Inspection Practices -- Part1: Cylindrical Gears --Tangential Measurements

915--2--A05 10 Inspection Practices -- Part2: Cylindrical Gears --Radial Measurements





915--3--A99 10 Inspection Practices --Gear Blanks, Shaft CenterDistance and Parallelism

917--B97 10 Design Manual for ParallelShaft Fine--Pitch Gearing

918--A93 10 Numerical ExamplesDemonstrating theProcedures for CalculatingGeometry Factors for Spurand Helical Gears

920--A01 10 Materials for Plastic Gears

921--A97 Replaced by 6006--A03

922--A96 10 Load Classification andService Factors for FlexibleCouplings

923--B05 10 Metallurgical Specificationsfor Steel Gearing

925--A03 11 Effect of Lubrication onGear Surface Distress

926--C99 11 Recommended Practice forCarburized AerospaceGearing

927--A01 11 Load Distribution Factors --Analytical Methods forCylindrical Gears

929--A06 11 Calculation of Bevel GearTop Land and Guidance onCutter Edge Radius

930--A05 11 Calculated Bending LoadCapacity of PowderMetallurgy (P/M) ExternalSpur Gears

931--A02 Replaced by 10064--5--A06

932--A05 11 Rating the PittingResistance and BendingStrength of Hypoid Gears

933--A03 11 Basic Gear Geometry

935--A05 11 RecommendationsRelative to the Evaluationof Radial Composite GearDouble Flank Testers

938--A05 11 Shot Peening of Gears

939--A07 12 Austempered Ductile Ironfor Gears

1003--H07 12 Tooth Proportions forFine--Pitch Spur andHelical Gears

1006--A97 12 Tooth Proportions forPlastic Gears


1010--E95 12 Appearance of Gear Teeth-- Terminology of Wear andFailure

1012--G05 12 Gear Nomenclature,Definitions of Terms withSymbols

1102--A03 12 Tolerance Specification forGear Hobs

1103--H07 12 Tooth Proportions forFine--Pitch Spur andHelical Gears (MetricEdition)

1106--A97 12 Tooth Proportions forPlastic Gears

1328--1 Replaced by 2015--1--A01

1328--2 Replaced by 2015--2--A06

2000--A88 Replaced by 915--1--A02,915--2--A05, 2015--1--A01,and 2015--2--A06

2001--D04 13 Fundamental RatingFactors and CalculationMethods for Involute Spurand Helical Gear Teeth

2002--B88 13 Tooth ThicknessSpecification andMeasurement

2003--C10 13 Rating the PittingResistance and BendingStrength of GeneratedStraight Bevel, Zerol Bevel,and Spiral Bevel GearTeeth

2004--C08 13 Gear Materials, HeatTreatment and ProcessingManual

2005--D03 13 Design Manual for BevelGears

2007--C00 13 Surface Temper EtchInspection After Grinding

2008--C01 13 Assembling Bevel Gears

2009--B01 Replaced by 10064--6--A10and 17485--A08

2010--A94 Replaced by 18653--A06

2011--A98 13 Cylindrical WormgearingTolerance and InspectionMethods

2015--1--A01 13 Accuracy ClassificationSystem -- TangentialMeasurements forCylindrical Gears





2015--2--A06 14 Accuracy ClassificationSystem -- RadialMeasurements forCylindrical Gears

Supplementto 2015/915--1--A02

14 Accuracy ClassificationSystem -- TangentialMeasurement ToleranceTables for CylindricalGears

2101--D04 14 Fundamental RatingFactors and CalculationMethods for Involute Spurand Helical Gear Teeth(Metric)

2110--A94 Replaced by 18653--A06

2111--A98 14 Cylindrical WormgearingTolerance and InspectionMethods (Metric)

2113--A97 Replaced by 18653--A06

2114--A98 Replaced by 18653--A06

2116--A05 14 Evaluation of Double FlankTesters for RadialComposite Measurementof Gears

6000--B96 14 Measurement of LinearVibration on Gear Units

6001--E08 14 Design and Selection ofComponents for EnclosedGear Drives

6002--B93 14 Design Guide for VehicleSpur and Helical Gears

6004--F88 Replaced by 6014--A06

6005--B89 Withdrawn

6006--A03 14 Standard for Design andSpecification of Gearboxesfor Wind Turbines

6008--A98 15 Specifications for PowderMetallurgy Gears

6009--A00 Replaced by 6013--A06

6010--F97 Replaced by 6013--A06

6011--I03 15 Specification for HighSpeed Helical Gear Units

6013--A06 15 Standard for IndustrialEnclosed Gear Drives

6014--A06 15 Gear Power Rating forCylindrical Shell andTrunnion SupportedEquipment

6017--E86 Replaced by 6035--A02


6019--E89 Replaced by 6009--A00

6021--G89 Replaced by 6009--A00

6022--C93 15 Design Manual forCylindrical Wormgearing

6023--A88 Replaced by 6123--B06

6025--D98 15 Sound for EnclosedHelical, Herringbone andSpiral Bevel Gear Drives

6030--C87 Replaced by 6035--A02

6032--A94 15 Standard for Marine GearUnits: Rating

6033--C08 15 Materials for MarinePropulsion Gearing

6034--B92 16 Practice for EnclosedCylindrical WormgearSpeed Reducers andGearmotors

6035--A02 16 Design, Rating andApplication of IndustrialGloboidal Wormgearing

6101--E08 16 Design and Selection ofComponents for EnclosedGear Drives (Metric)

6109--A00 Replaced by 6113--A06

6110--F97 Replaced by 6113--A06

6113--A06 16 Standard for IndustrialEnclosed Drives (Metric)

6114--A06 16 Gear Power Rating forCylindrical Shell andTrunnion SupportedEquipment (Metric)

6123--B06 16 Design Manual forEnclosed Epicyclic MetricModule Gear Drives

6133--C08 16 Materials for MarinePropulsion Gearing(Metric)

6135--A02 16 Design, Rating andApplication of IndustrialGloboidal Wormgearing(Metric)

6336--6--A08 17 Calculation of LoadCapacity of Spur andHelical gears -- Part 6:Calculation of Service LifeUnder Variable Load

9000--C90 17 Flexible Couplings --Potential UnbalanceClassification

9001--B97 17 Flexible Couplings --Lubrication





9002--B04 17 Bores and Keyways forFlexible Couplings (InchSeries)

9003--B08 17 Flexible Couplings --Keyless Fits

9004--B08 17 Flexible Couplings -- MassElastic Properties andOther Characteristics

9005--E02 17 Industrial Gear Lubrication

9008--B00 17 Flexible Couplings – GearType – Flange Dimensions,Inch Series

9009--D02 17 Flexible Couplings --Nomenclature for FlexibleCouplings

9103--B08 18 Flexible Couplings --Keyless Fits (MetricEdition)

9104--A06 18 Flexible Couplings -- MassElastic Properties andOther Characteristics(Metric Edition)

9112--A04 18 Bores and Keyways forFlexible Couplings (MetricSeries)


10064--1 Replaced by 915--1--A02

10064--2 Replaced by 915--2--A05

10064--5--A06 18 Code of InspectionPractice -- Part 5:RecommendationsRelative to Evaluation ofGear MeasuringInstruments

10064--6--A10 18 Code of InspectionPractice – Part 6: BevelGear MeasurementMethods

14179--1 18 Gear Reducers -- ThermalCapacity Based on ISO/TR14179--1

17485--A08 18 Bevel Gears -- ISO Systemof Accuracy

Supplementto 17485--A08

18 Supplemental Tables forANSI/AGMA ISO17485--A08, Bevel Gears --ISO System of Accuracy --Tolerance Tables

18653--A06 19 Gears -- Evaluation ofInstruments for theMeasurement of IndividualGears

23509--A08 19 Bevel and Hypoid GearGeometry


Index of AGMA Standards and Information Sheets by Topic

Aerospace

AGMA 911--A94 Design Guidelines for AerospaceGearing

AGMA 926--C99 Recommended Practice forCarburized Aerospace Gearing

Calibration and Measurement Uncertainty

AGMA 935--A05 Recommendations Relative to theEvaluation of Radial Composite Gear Double FlankTesters

ANSI/AGMA 2116--A05, Evaluation of Double FlankTesters for Radial Composite Measurement of Gears

AGMA ISO 10064--5--A06, Code of InspectionPractice -- Part 5: Recommendations Relative toEvaluation of Gear Measuring Instruments

ANSI/AGMA 18653--A06, Gears -- Evaluation ofInstruments for the Measurement of Individual Gears

Couplings

AGMA 922--A96 Load Classification and ServiceFactors for Flexible Couplings

ANSI/AGMA 9000--C90 Flexible Couplings --Potential Unbalance Classification

ANSI/AGMA 9001--B97 Flexible Couplings --Lubrication

ANSI/AGMA 9002--B04 Bores and Keyways forFlexible Couplings (Inch Series)

ANSI/AGMA 9003--B08 Flexible Couplings -- KeylessFits

ANSI/AGMA 9004--B08 Flexible Couplings -- MassElastic Properties and Other Characteristics

ANSI/AGMA 9008--B00 Flexible Couplings – GearType – Flange Dimensions, Inch Series

ANSI/AGMA 9009--D02 Flexible Couplings --Nomenclature for Flexible Couplings

ANSI/AGMA 9103--B08 Flexible Couplings -- KeylessFits (Metric Edition)

ANSI/AGMA 9104--A06 Flexible Couplings -- MassElastic Properties and Other Characteristics (MetricEdition)

ANSI/AGMA 9112--A04 Bores and Keyways forFlexible Couplings (Metric Series)

Design and Assembly - Bevel

AGMA 929--A06 Calculation of Bevel Gear Top Landand Guidance on Cutter Edge Radius

AGMA ISO10064--6--A10Codeof InspectionPractice– Part 6: Bevel Gear Measurement Methods

ANSI/AGMA 2005--D03 Design Manual for BevelGears

ANSI/AGMA 2008--C01 Assembling Bevel Gears

ANSI/AGMA ISO 17485--A08 Bevel Gears -- ISOSystem of Accuracy

ANSI/AGMA ISO 23509--A08 Bevel and Hypoid GearGeometry

Design - Fine Pitch

AGMA 910--C90 Formats for Fine--Pitch GearSpecification Data

AGMA 917--B97 Design Manual for Parallel ShaftFine--Pitch Gearing

Design - Spur and Helical

AGMA 901--A92 A Rational Procedure for thePreliminary Design of Minimum Volume Gears

AGMA 913--A98Method for Specifying the Geometryof Spur and Helical Gears

Design - Wormgear

ANSI/AGMA6022--C93DesignManual for CylindricalWormgearing

Drive Components

ANSI/AGMA 6001--E08 Design and Selection ofComponents for Enclosed Gear Drives

ANSI/AGMA 6101--E08 Design and Selection ofComponents for EnclosedGearDrives (MetricEdition)

Enclosed Drives

AGMA ISO 14179--1 Gear Reducers -- ThermalCapacity Based on ISO/TR 14179--1

ANSI/AGMA 6013--A06 Standard for IndustrialEnclosed Gear Drives

ANSI/AGMA 6113--A06 Standard for IndustrialEnclosed Gear Drives (Metric)

ANSI/AGMA 6123--B06 Design Manual for EnclosedEpicyclic Gear Drives (Metric)

Failure Modes

AGMA 912--A04, Mechanisms of Gear Tooth Failure

ANSI/AGMA 1010--E95 Appearance of Gear Teeth --Terminology of Wear and Failure

High Speed Units

ANSI/AGMA 6011--I03 Specification for High SpeedHelical Gear Units


Inspection and Tolerances

AGMA 915--1--A02 Inspection Practices -- Part 1:Cylindrical Gears -- Tangential Measurements

AGMA 915--2--A05 Inspection Practices -- Part 2:Cylindrical Gears -- Radial Measurements

AGMA 915--3--A99 Inspection Practices -- GearBlanks, Shaft Center Distance and Parallelism

ANSI/AGMA 1102--A03, Tolerance Specification forGear Hobs

ANSI/AGMA 2002--B88 Tooth ThicknessSpecification and Measurement

ANSI/AGMA 2007--C00 Surface Temper EtchInspection After Grinding

ANSI/AGMA 2011--A98 Cylindrical WormgearingTolerance and Inspection Methods

ANSI/AGMA 2015--1--A01 Accuracy ClassificationSystem -- Tangential Measurements for CylindricalGears

ANSI/AGMA 2015--2--A06 Accuracy ClassificationSystem -- Radial Measurements for Cylindrical Gears

ANSI/AGMA 2111--A98 Cylindrical WormgearingTolerance and Inspection Methods (Metric)

Supplemental Tables for AGMA 2015/915--1--A02Accuracy Classification System -- TangentialMeasurement Tolerance Tables for Cylindrical Gears

Lubrication

ANSI/AGMA 9005--E02 Industrial Gear Lubrication

Materials

AGMA 920--A01 Materials for Plastic Gears

AGMA 923--B05Metallurgical Specifications for SteelGearing

AGMA 938--A05, Shot Peening of Gears

ANSI/AGMA 939--A07, Austempered Ductile Iron forGears

ANSI/AGMA 2004--C08 Gear Materials, HeatTreatment and Processing Manual

ANSI/AGMA 6033--C08 Materials for MarinePropulsion Gearing

ANSI/AGMA 6133--C08 Materials for MarinePropulsion Gearing (Metric)

Metric Usage

AGMA 904--C96 Metric Usage

Mill Drives

ANSI/AGMA 6014--A06 Gear Power Rating forCylindrical Shell and Trunnion Supported Equipment

ANSI/AGMA 6114--A06 Gear Power Rating forCylindrical Shell and Trunnion Supported Equipment(Metric)

Nomenclature

AGMA 933--A03 Basic Gear Geometry

ANSI/AGMA 1012--G05 Gear Nomenclature,Definitions of Terms with Symbols

Plastics Gears

AGMA 909--A06 Specifications for Molded PlasticGears

AGMA 920--A01 Materials for Plastic Gears

ANSI/AGMA 1006--A97 Tooth Proportions for PlasticGears


Powder Metallurgy Gears

AGMA930--A05CalculatedBendingLoadCapacity ofPowder Metallurgy (P/M) External Spur Gears

ANSI/AGMA 6008--A98 Specifications for PowderMetallurgy Gears

Proportions

ANSI/AGMA 1003--H07 Tooth Proportions forFine--Pitch Spur and Helical Gears


ANSI/AGMA 1103--H07 Tooth Proportions forFine--Pitch Spur and Helical Gears (Metric Edition)

ANSI/AGMA 1106--A97 Tooth Proportions for PlasticGears (Metric Edition)

Rating: Spur, Helical and Bevel Gears

AGMA 908--B89 Information Sheet--GeometryFactors for Determining the Pitting Resistance andBending Strength of Spur, Helical and HerringboneGear Teeth

AGMA 918--A93 A Summary of Numerical ExamplesDemonstrating the Procedures for CalculatingGeometry Factors for Spur and Helical Gears

AGMA925--A03Effect of Lubrication onGear SurfaceDistress

AGMA 927--A01 Load Distribution Factors --Analytical Methods for Cylindrical Gears

AGMA 932--A05 Rating the Pitting Resistance andBending Strength of Hypoid Gears


ANSI/AGMA 2001--D04 Fundamental Rating Factorsand Calculation Methods for Involute Spur and HelicalGear Teeth

ANSI/AGMA 2003--C10 Rating the Pitting Resistanceand Bending Strength of Generated Straight Bevel,ZEROL Bevel, and Spiral Bevel Gear Teeth

ANSI/AGMA 2101--D04 Fundamental Rating Factorsand Calculation Methods for Involute Spur and HelicalGear Teeth (Metric Edition)

ANSI/AGMA 6032--A94 Standard for Marine GearUnits: Rating

ANSI/AGMA ISO 6336--6--A08 Calculation of LoadCapacity of Spur and Helical Gears -- Part 6:Calculation of Service Life Under Variable Load

Sound and Vibration

AGMA 914--B04 Gear Sound Manual -- Part I:Fundamentals of Sound as Related to Gears; Part II:Sources, Specifications and Levels of Gear Sound;Part III: Gear Noise Control

ANSI/AGMA 6000--B96 Specification forMeasurement of Linear Vibration on Gear Units

ANSI/AGMA 6025--D98 Sound for Enclosed Helical,Herringbone, and Spiral Bevel Gear Drives

Style Manual

AGMA 900--G00 Style Manual for the Preparation ofStandards and Editorial Manuals

Thermal

AGMA ISO 14179--1 Gear Reducers -- ThermalCapacity Based on ISO/TR 14179--1

Vehicle

ANSI/AGMA 6002--B93 Design Guide for VehicleSpur and Helical Gears

Wind Turbine Units

ANSI/AGMA/AWEA 6006--A03 Standard for Designand Specification of Gearboxes for Wind Turbines

Wormgears

ANSI/AGMA 6034--B92 Practice for EnclosedCylindrical Wormgear Speed Reducers andGearmotors

ANSI/AGMA 6035--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing

ANSI/AGMA 6135--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing(Metric)

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AGMA Standards and Information Sheets

Many standards require additional documents for their proper use. A list of these standards are normallysupplied after the scope, in the normative references section of a document. Be sure to inquire whether thestandard you need requires other documents listed herewith.

AGMA 900--H06 Style Manual for the Preparationof Standards, Information Sheets and EditorialManuals

Presents the requirements for preparing AGMAstandards, editorial manuals, and other technicalliterature. A new annex ”ISO symbols used in metricdocuments”, has been added, which includes acomprehensive listing of the symbols used in ISOgear rating standards. Revision of AGMA 900--G00.ISBN: 1--55589--775--4 Pages: 38

AGMA 901--A92 A Rational Procedure for thePreliminary Design of Minimum Volume Gears

Presents a simple, closed--form procedure as a firststep in the minimum volume spur and helical gearsetdesign. Includes methods for selecting geometry anddimensions, considering maximum pitting resistance,bending strength, and scuffing resistance, andmethods for selecting profile shift.ISBN: 1--55589--579--4 Pages: 37

AGMA 904--C96 Metric UsageServes as a guide in preparing AGMA metricstandards.ISBN: 1--55589--681--2 Pages: 20

AGMA 908--B89 Information Sheet - GeometryFactors for Determining the Pitting Resistanceand Bending Strength of Spur, Helical andHerringbone Gear Teeth

Gives the equations for calculating the pittingresistance geometry factor, I, for external and internalspur and helical gears, and the bending strengthgeometry factor, J, for external spur and helical gearsthat are generated by rack--type tools (hobs, rackcutters or generating grinding wheels) or pinion--typetools (shaper cutters). Includes charts which providegeometry factors, I and J, for a range of typical gearsets and tooth forms.ISBN: 1--55589--525--5 Pages: 78

AGMA 909--A06, Specifications for Molded PlasticGears

The objective of this information sheet is to inform theplastic gear designer of the importance to clearly andthoroughly define the gear specifications to the plastic

gear producer. It discusses the specifications for geartooth geometry, inspection, other gear features andmanufacturing considerations for involute externaland internal spur and helical gears. Suggested dataforms are provided in the annexes.ISBN: 1--55589--889--8 Pages: 25

AGMA 910--C90 Formats for Fine-Pitch GearSpecification Data

Consists of a series of printed forms for gear drawingsthat contain the appropriate data the gear designermust tabulate for the gear manufacturer. Includes aseries of definitions of the various tabulated items.Appendix contains blank, pre--printed forms that caneasily be copied for the user’s drawings.ISBN: 1--55589--571--9 Pages: 29

AGMA 911--A94Guidelines for Aerospace GearingCovers current gear design practices as they areapplied to air vehicles and spacecraft. Goes beyondthe design of gear meshes. Presents the broadspectrum of factors which combine to produce aworking gear system, whether it be a powertransmission or special purpose mechanism. Coversonly spur, helical and bevel gears. (Does not coverwormgears, face gears, and various proprietary toothforms). Replaces AGMA 411.02.ISBN: 1--55589--629--4 Pages: 97

AGMA 912--A04, Mechanisms of Gear ToothFailure

This information sheet describes many of the ways inwhich gear teeth can fail and recommends methodsfor reducing gear failure. It provides guidance forthose attempting to analyze gear failures. It should beused in conjunction with ANSI/AGMA 1010--E95 inwhich the gear tooth failure modes are defined. Theyare described in detail to help investigatorsunderstand failures and investigate remedies. Thisinformation sheet does not discuss the details ofdisciplines such as dynamics, material science,corrosion or tribology. It is hoped that the materialpresented will facilitate communication in theinvestigation of gear operating problems.Supplement to ANSI/AGMA 1010--E95.ISBN: 1--55589--838--6 Pages: 22



AGMA 913--A98 Method for Specifying theGeometry of Spur and Helical Gears

Provides information to translate tooth thicknessspecifications which are expressed in terms of tooththickness, center distance or diameter into profile shiftcoefficients. It describes the effect that profile shifthas on the geometry and performance of gears.Annexes are provided which contain practicalexamples on the calculation of tool proportions andprofile shift.ISBN: 1--55589--714--2 Pages: 25

AGMA 914--B04, Gear Sound Manual - Part I:Fundamentals of Sound as Related to Gears; PartII: Sources, Specifications and Levels of GearSound; Part III: Gear Noise Control

This information sheet discusses how noisemeasurement and control depend upon the individualcharacteristics of the prime mover, gear unit, anddriven machine, as well as their combined effects in aparticular acoustical environment. It indicates certainareas that might require special attention. Thisdocument is a revision of AGMA 299.01 to includeupdated references and a discussion of Fast FourierTransform analysis. Replaces AGMA 299.01.ISBN: 1--55589--820--3 Pages: 37

AGMA 915--1--A02 Inspection Practices - Part 1:Cylindrical Gears - Tangential Measurements

Provides a code of practice and measuring methodsdealing with inspection relevant to tangential elementand composite deviations of cylindrical involute gears(measurements referred to single flank contact).Replaces elemental measurement section ofAGMA 2000--A88.ISBN: 1--55589--798--3 Pages: 39

AGMA 915--2--A05 Inspection Practices - Part 2:Cylindrical Gears - Radial Measurements

This information sheet discusses inspection ofcylindrical involute gears using the radial (doubleflank) composite method, with recommendedpractices detailed. Also included is a clause on runoutand eccentricity measurement methods. Thisinformation sheet is a supplement to the standardANSI/AGMA 2015--2--A06. It replaced AGMA ISO10064--2 and replaces double flank compositemeasurement section of AGMA 2000--A88.ISBN: 1--55589--843--2 Pages: 24

AGMA 915--3--A99 Inspection Practices - GearBlanks, Shaft Center Distance and Parallelism

Provides recommended numerical values relating tothe inspection of gear blanks, shaft center distanceand parallelism of shaft axes. Discussions includesuch topics as methods for defining datum axes oncomponents; the use of center holes and mountingsurfaces during manufacturing and inspection; and,

recommended values of in--plane and out--of--planedeviations of shaft parallelism. Modified adoption ofISO/TR 10064--3:1996.ISBN: 1--55589--738--X Pages: 9

AGMA 917--B97 Design Manual for Parallel ShaftFine-Pitch Gearing

Provides guidance for the design of spur and helicalgearing of 20 through 120 diametral pitch includinginternal and rack forms. Manual contains suchspecialized subjects as inspection, lubrication, gearload calculation methods, materials, including a widevariety of plastics. Replaces AGMA 370.01.ISBN: 1--55589--694--4 Pages: 84

AGMA 918--A93 A Summary of NumericalExamples Demonstrating the Procedures forCalculatingGeometry Factors for Spur andHelicalGears

Provides numerical examples for calculating thepitting resistance geometry factor, I, and bendingstrength geometry factor, J, for typical gearsets thatare generated by rack-- type tools (hobs, rack cuttersor generating grinding wheels) or pinion--type tools(disk--type shaper cutters). Supplement to AGMA908--B89.ISBN: 1--55589--617--0 Pages: 42

AGMA 920--A01 Materials for Plastic GearsThis document serves to aid the gear designer inunderstanding the unique physical, mechanical andthermal behavior of plastic materials. Topics coveredinclude general plastic material behavior, gearoperating conditions, plastic gear manufacturing,tests for gear related material properties, and typicalplastic gear materials.ISBN: 1--55589--778--9 Pages: 40

AGMA 922--A96 Load Classification and ServiceFactors for Flexible Couplings

This Information Sheet provides load classificationsand related service factors that are frequently used forvarious flexible coupling applications. Typicalapplications using smooth prime movers and specialconsiderations involving unusual or more severeloading are discussed. Replaces AGMA 514.02.ISBN: 1--55589--680--4 Pages: 6

AGMA 923--B05 Metallurgical Specifications forSteel Gearing

This document identifies metallurgical qualitycharacteristics which are important to theperformance of steel gearing. The AGMA gear ratingstandards identify performance levels of gearing byheat treatment method and grade number. For eachheat treatment method and AGMA grade number,acceptance criteria are given for various metallurgicalcharacteristics identified in this document. Revisionof AGMA 923--A00.ISBN: 1--55589--848--3 Pages: 31



AGMA 925--A03 Effect of Lubrication on GearSurface Distress

This document provides currently availableinformation pertaining to oil lubrication of industrialgears for power transmission applications. It isintended to serve as a general guideline and source ofinformation about gear oils, their properties, and theirtribological behavior in gear contacts. Equationsprovided allow the calculation of specific filmthickness and instantaneous contact (flash)temperature for gears in service, and to help assessthe potential risk of surface distress (scuffing,micropitting and macropitting, and scoring) involvedwith a given lubricant choice. Supplement toANSI/AGMA 2001--D04.ISBN: 1--55589--815--7 Pages: 51

AGMA 926--C99 Recommended Practice forCarburized Aerospace Gearing

Establishes recommended practices for materialcase and core properties, microstructure andprocessing procedures for carburized AISI 9310aerospace gears. This document is not intended to bea practice for any gears other than those applied toaerospace. Replaces AGMA 246.02a.ISBN: 1--55589--758--4 Pages: 9

AGMA 927--A01 Load Distribution Factors -Analytical Methods for Cylindrical Gears

Describes an analytical procedure for the calculationof face load distribution factor. The iterative solutionthat is described is compatible with the definitions ofthe term face loaddistribution of AGMAstandards andlongitudinal load distribution of the ISO standards.The procedure is easily programmable and flowcharts of the calculation scheme, as well as examplesfrom typical software are presented. Supplement toANSI/AGMA 2001--D04.ISBN: 1--55589--779--7 Pages: 31

AGMA 929--A06 Calculation of Bevel Gear TopLand and Guidance on Cutter Edge Radius

Has the calculations for bevel gear top land andguidance for selection of cutter edge radius fordetermination of tooth geometry. It integrates variouspublications with modifications to include facehobbing. It adds top land calculations fornon--generated manufacturing methods. It isintended to provide assistance in completing thecalculations requiring determination of top lands andcutter edge radii for gear capacity in accordance withANSI/AGMA 2003--B97. This information sheet is asupplement to standard ANSI/AGMA 2005--D03ISBN: 1--55589--873--4 Pages: 38

AGMA 930--A05 Calculated Bending LoadCapacity of PowderMetallurgy (P/M) External SpurGears

This information sheet describes a procedure forcalculating the load capacity of a pair of powdermetallurgy external spur gears based on toothbending strength. Two types of loading areconsidered: 1) repeated loading over many cycles;and 2) occasional peak loading. It also describes anessentially reverse procedure for establishing aninitial design from specified applied loads. As part ofthe load capacity calculations, there is a detailedanalysis of the gear teeth geometry, including toothprofiles and various fillets.ISBN: 1--55589--845--9 Pages: 78

AGMA 932--A05 Rating the Pitting Resistance andBending Strength of Hypoid Gears

This information sheet provides a method by whichdifferent hypoid gear designs can be compared. Theformulas are intended to establish a uniformlyacceptable method for calculating the pittingresistance and bending strength capacity of bothcurved and skewed tooth hypoid gears. They applyequally to tapered depth and uniform depth teeth.Annexes contain graphs for geometry factors and asample calculation to assist the user. Supplement toANSI/AGMA 2003--B97.ISBN: 1--55589--869--6 Pages: 18

AGMA 933--B03 Basic Gear GeometryThis information sheet illustrates importantgeometrical relationships which provide a soundbasis for a thoroughly logical and comprehensivesystem of gear geometry. Replaces AGMA 115.01.ISBN: 1--55589--814--9 Pages: 18

AGMA 935--A05Recommendations Relative to theEvaluation of Radial Composite Gear DoubleFlank Testers

The condition and alignment of gear measuringinstruments can greatly influence themeasurement ofproduct gears. This information sheet providesqualification procedures for double flank testers thatare used for the evaluation of radial compositedeviations of gears. It discusses guidelines foralignment of double flank tester elements such ascenters, ways, probe systems, etc. It also covers theapplication of artifacts to determine instrumentaccuracy. This information sheet is a supplement tostandard ANSI/AGMA 2116--A05.ISBN: 1--55589--872--6 Pages: 11

AGMA 938--A05 Shot Peening of GearsThis information sheet provides a tool for geardesigners interested in the residual compressivestress properties produced by shot peening and itsrelationship to gearing. It also discusses shot mediamaterials, delivery methods and process controls.ISBN: 1--55589--847--5 Pages: 14



AGMA 939--A07, Austempered Ductile Iron forGears

This information sheet gives the background andbasic guidelines to consider the feasibility ofaustempered ductile iron (ADI) for gear applications. Itcontains experimental, experiential and anecdotalinformation to assist in the specification, purchaseand manufacture of ADI components. The metallurgyof ADI, relevant factors in its production, allowablestress numbers, and stress cycle curves arereviewed. It also has references, relevant standards,and evaluation methods used in the manufacture ofADI components.ISBN: 978--1--55589--901--1 Pages: 10

ANSI/AGMA 1003--H07 Tooth Proportions forFine-Pitch Spur and Helical Gears

Tooth proportions for fine--pitch gearing are similar tothose of coarse pitch gearing except in the matter ofclearance. This standard is applicable to externalspur and helical gears with diametral pitch of 20through 120 and a profile angle of 20 degrees. Itprovides a system of enlarged pinions which use theinvolute form above 5 degrees of roll. Data on 14--1/2and 25 degree profile angle systems, and adiscussion of enlargement and tooth thicknesses areprovided in annexes. In addition, it addresses, in anew annex, an analysis of comparative systems ofselecting tooth thicknesses of pinions. Revision ofANSI/AGMA 1003--G93.ISBN: 978--1--55589--902--8 Pages: 25

ANSI/AGMA 1006--A97 Tooth Proportions forPlastic Gears

Presents a new basic rack, AGMA PT, which, with itsfull round fillet, may be preferred in many applicationsof gears made from plastic materials. It contains adescription, with equations and sample calculations,of how the proportions of a spur or helical gearmay bederived from the design tooth thickness and the basicrack data. In several annexes, there are discussionsof possible variations from the basic rack and also aprocedure for defining tooth proportions without usingthe basic rack concept.ISBN: 1--55589--684--7 Pages: 47

ANSI/AGMA 1010--E95 Appearance of Gear Teeth-Terminology of Wear and Failure

This standard provides nomenclature for generalmodes of gear tooth wear and failure. It classifies,identifies and describes the most common types offailure and provides information which will, in manycases, enable the user to identify failure modes andevaluate the degree or progression of wear.Replaces AGMA 110.04.ISBN: 1--55589--665--0 Pages: 40

ANSI/AGMA 1012--G05 Gear Nomenclature,Definitions of Terms with Symbols

This standard establishes the definitions of terms,symbols and abbreviations which may be used tocommunicate the technology and specifications ofexternal and internal gear teeth. it provides definitivemeanings by the use of words and illustrations, forcommonly used gearing terms. Revision ofANSI/AGMA 1012--F90.ISBN: 1--55589--846--7 Pages: 72

ANSI/AGMA 1102--A03, Tolerance Specificationfor Gear Hobs

Provides specifications for nomenclature,dimensions, equation based tolerances, andinspection practices for gear hobs. Defines aclassification system for accuracy grades D throughAAA, in order of increasing precision. The standarddescribes hob identification practices, manufacturingand purchasing considerations, and hob designparameters. An informative annex is included whichprovides the reader with a basic understanding of howthe different elements of a hob can affect the accuracyof the gear being machined. Replaces AGMA120.01.ISBN: 1--55589--816--5 Pages: 49

ANSI/AGMA 1103--H07 Tooth Proportions forFine-Pitch Spur and Helical Gears (Metric Edition)

Tooth proportions for fine--pitch gearing are similar tothose of coarse pitch gearing except in the matter ofclearance. This standard is applicable to externalspur and helical gears with diametral pitch of 1.25through 0.2 and a profile angle of 20 degrees. Itprovides a system of enlarged pinions which use theinvolute form above 5 degrees of roll. Data on 14--1/2and 25 degree profile angle systems, and adiscussion of enlargement and tooth thicknesses areprovided in annexes. In addition, it addresses, in anew annex, an analysis of comparative systems ofselecting tooth thicknesses of pinions. Metricversion of ANSI/AGMA 1003--H07.ISBN: 978--1--55589--903--5 Pages: 25

ANSI/AGMA 1106--A97 Tooth Proportions forPlastic Gears

Presents a new basic rack, AGMA PT, which, with itsfull round fillet, may be preferred in many applicationsof gears made from plastic materials. It contains adescription, with equations and sample calculations,of how the proportions of a spur or helical gearmay bederived from the design tooth thickness and the basicrack data. In several annexes, there are discussionsof possible variations from the basic rack and also aprocedure for defining tooth proportions without usingthe basic rack concept. Metric edition ofANSI/AGMA 1006--A97.ISBN: 1--55589--685--5 Pages: 47



ANSI/AGMA 2001--D04 Fundamental RatingFactors andCalculationMethods for InvoluteSpurand Helical Gear Teeth

Presents a comprehensive method for rating thepitting resistance and bending strength of spur andhelical involute gear pairs. Contains detaileddiscussions of factors influencing gear survival andcalculation methods. Revisions reflected in thisversion include incorporating the latest AGMAaccuracy standard (ANSI/AGMA --A01) into thedetermination of dynamic factor, and change to therelationship between service factor and stress cyclefactor. Revision of ANSI/AGMA 2001--C95.ISBN: 1--55589--839--4 Pages: 56

ANSI/AGMA 2002--B88 Tooth ThicknessSpecification and Measurement

Presents procedures for determining tooth thicknessmeasurements of external and internal cylindricalinvolute gearing. Includes equations and calculationprocedures for commonly used measuring methods.ISBN: 1--55589--503--4 Pages: 47

!! NEW !!

ANSI/AGMA 2003-C10 Rating the PittingResistance and Bending Strength of GeneratedStraight Bevel, Zerol Bevel and Spiral Bevel GearTeeth

This standard specifies a method for rating the pittingresistance and bending strength of generated straightbevel, zerol bevel and spiral bevel gear teeth. Adetailed discussion of factors influencing gearsurvival and a calculation method are provided.Revision of ANSI/AGMA 2003-B97.ISBN: 978-1-55589-975-2 Pages: 71

ANSI/AGMA 2004--C08 Gear Materials, HeatTreatment and Processing Manual

This standard provides information pertaining toferrous and nonferrous materials used in gearing.Factors inmaterial selection, includingmaterial forms,properties, and associated processing and heattreatments are discussed. Manufacturing proceduresto prepare materials for machining and final heattreatment are included. Heat treating proceduresused for gearing are covered in detail, includingprocess description, product specifications, processcontrols, and characteristics of heat treated gearing.Post--heat treatment processes to meet gearingrequirements are discussed. Product inspectionmethods and documentation are covered. Termdefinitions, test methods, distortion and residualstress, sources for additional information andbibliography are included. Revision of ANSI/AGMA2004--B89.ISBN: 978--1--55589--904--2 Pages: 68

ANSI/AGMA 2005--D03 Design Manual for BevelGears

Provides the standards for designing straight bevel,zerol bevel, spiral bevel and hypoid gears along withinformation on fabrication, inspection and mounting.Covers preliminary gear design parameters, blankdesign including standard taper, uniform depth,duplex taper and tilted root. Also includes drawingformat, inspection, materials, lubrication, mountingsand assembly. An Annex contains examples for easeof understanding. Revision of ANSI/AGMA2005--C96.ISBN: 1--55589--667--7 Pages: 94

ANSI/AGMA 2007--C00 Surface Temper EtchInspection After Grinding [Same as New ISO14104]

Explains the materials and procedures to determineand evaluate localized overheating on groundsurfaces. Includes a system to describe and classifythe indications produced during this inspection.However, does not provide specific acceptance orrejection criteria. Revision of ANSI/AGMA2007--B92.ISBN: 1--55589--761--4 Pages: 6

ANSI/AGMA 2008--C01 Assembling Bevel GearsPrepared expressly for the assembly man in thefactory and the service man in the field. Eachdefinition, explanation, and instruction is directedtoward the physical appearance of the gears as theyare inspected and assembled by these personnel.Revision of ANSI/AGMA 2008--B90.ISBN: 1--55589--795--9 Pages: 30


Establishes a classification system for thegeometrical accuracy specification of wormgearing. Italso provides uniform measurement proceduresincluding discussions on single and double flankcomposite testing and tooth thicknessmeasurements. The standard establishes tenaccuracy grades, W3 through W12, based on therelative effect of geometrical errors on conjugateaction for wormgear sets.ISBN: 1--55589--716--9 Pages: 43

ANSI/AGMA 2015--1--A01 Accuracy ClassificationSystem - TangentialMeasurements forCylindricalGears

This standard, for spur and helical gearing, correlatesgear accuracy grades with gear tooth tolerances andgeometry. It provides information on minimumrequirements for accuracy by elementalmeasurement methods. Annex material providesguidance on measurement filtering influences andinformation on comparison of gear inspectionmethods. Users of this standard should have a copyof the companion information sheet, AGMA915--1--A02. Replaceselemental tolerancesectionof AGMA 2000--A88.ISBN: 1--55589--797--5 Pages: 37



ANSI/AGMA 2015--2--A06 Accuracy ClassificationSystem - Radial Measurements for CylindricalGears

This standard establishes a classification systemrelevant to radial (double flank) composite deviationsof individual cylindrical involute gears. It serves as aconcise means of specifying gear accuracy withoutthe needof supplying individual element tolerances. Itsimplifies discussions of gear accuracy between gearmanufacturer and purchaser. It specifies theappropriate definitions of gear tooth accuracy terms,the structure of the gear accuracy system, and thetolerances (allowable values of deviations). Annex Aprovides information on the accuracy ofmaster gears.Annex B provides information on runout tolerancevalues. Replaces double flank compositetolerance section of AGMA 2000--A88.ISBN: 1--55589--874--2 Pages: 13

Supplemental Tables for AGMA 2015/915--1--A02Accuracy Classification System - TangentialMeasurement Tolerance Tables for CylindricalGears

Only provides tolerance tables as a supplement toAGMA 2015--1--A01, Accuracy Classification System-- Tangential Measurements for Cylindrical Gears.ISBN: 1--55589--813--0 Pages: 101

ANSI/AGMA 2101--D04 Fundamental RatingFactors andCalculationMethods for InvoluteSpurand Helical Gear Teeth (Metric Edition)

Presents a comprehensive method for rating thepitting resistance and bending strength of spur andhelical involute gear pairs. Contains detaileddiscussions of factors influencing gear survival andcalculation methods. Revisions reflected in thisversion include incorporating the latest AGMAaccuracy standard (ANSI/AGMA 2015--1--A01) intothe determination of dynamic factor, and change tothe relationship between service factor and stresscycle factor. Revision of ANSI/AGMA 2101--C95.ISBN: 1--55589--840--8 Pages: 56


Establishes a classification system for thegeometrical accuracy specification of wormgearing. Italso provides uniform measurement proceduresincluding discussions on single and double flankcomposite testing and tooth thicknessmeasurements. The standard establishes tenaccuracy grades, W3 through W12, based on therelative effect of geometrical errors on conjugateaction for wormgear sets. Metric edition ofANSI/AGMA 2011--A98.ISBN: 1--55589--717--7 Pages: 43

ANSI/AGMA 2116--A05 Evaluation of Double FlankTesters for Radial Composite Measurement ofGears

This standard provides the evaluation criteria fordouble flank testers. Recommended artifact sizesand geometry are provided along with measurementsystem conditions. Annexes contain methods forestimating calibration uncertainty and specifyingartifact.ISBN: 1--55589--871--8 Pages: 9

ANSI/AGMA 6000--B96 Specification forMeasurement of Linear Vibration on Gear Units

Presents amethod for measuring linear vibration on agear unit. Recommends instrumentation, measuringmethods, test procedures and discrete frequencyvibration limits for acceptance testing. Annexes listsystem effects on gear unit vibration and systemresponsibility. The ISO vibration rating curves fromISO 8579--2, Acceptance code for gears -- Part 2:Determination of mechanical vibrations of gear unitsduring acceptance testing are introduced.ISBN: 1--55589--666--9 Pages: 21

ANSI/AGMA 6001--E08, Design and Selection ofComponents for Enclosed Gear Drives

This standard outlines the basic practices for thedesign and selection of components, other thangearing, for use in commercial and industrial enclosedgear drives. Fundamental equations provide for theproper sizing of shafts, keys, and fasteners based onstated allowable stresses. Other components arediscussed in a manner to provide an awareness oftheir function or specific requirements. This standardapplies to the following types of commercial andindustrial enclosed gear drives, individually or incombination: spur, helical, herringbone, bevel andworm. Revision of ANSI/AGMA 6001--D97.ISBN: 978--1--55589--951--6 Pages: 44

ANSI/AGMA 6002--B93 Design Guide for VehicleSpur and Helical Gears

A guide to the design, fabrication, and inspection ofspur and helical gears for vehicles and for powertransmission on vehicles.ISBN: 1--55589--616--2 Pages: 38

ANSI/AGMA/AWEA 6006--A03 Standard for Designand Specification of Gearboxes for Wind Turbines

This standard is intended to apply to wind turbinegearboxes. It provides information for specifying,selecting, designing, manufacturing, procuringoperating and manufacturing reliable speedincreasing gearboxes for wind turbine generatorsystem service.Annex information is supplied on: wind turbinearchitecture, wind turbine load description, qualityassurance, operation and maintenance, minimumpurchaser gearbox manufacturing ordering data,lubrication selection and monitoring, determination of



an application factor from a load spectrum usingequivalent torque, and bearing stress calculations.Replaces AGMA 921--A97.ISBN: 1--55589--817--3 Pages: 94

ANSI/AGMA 6008--A98 Specifications for PowderMetallurgy Gears

Defines the minimum detailed information to beincluded in the powder metallurgy gear specificationssubmitted by the gear purchaser to the gear producer.Specifications on gear tooth geometry are describedin detail for external spur and helical gears and forstraight bevel gears. In addition, there arediscussions on specifications for gear drawings andgear material data. The standard applies to gearsmade by the conventional P/M process consisting ofcompaction followed by sintering and, in some cases,by post sintering treatments.ISBN: 1--55589--713--4 Pages: 17

ANSI/AGMA 6011--I03 Specification for HighSpeed Helical Gear Units

This standard includes information on design,lubrication, bearings, testing and rating for single anddouble helical external tooth, parallel shaft speedreducers and increasers. Units covered include thoseoperating with at least one stage having a pitch linevelocity equal to or greater than 35meters per secondor rotational speeds greater than 4500 rpm and otherstages having pitch line velocities equal to or greaterthan 8 meters per second. Annex material includesdiscussions on service factors, rotor dynamics,efficiency and newly configured purchaser’s datasheets. Revision of ANSI/AGMA 6011--H98.ISBN: 1--55589--819--X Pages: 51

ANSI/AGMA 6013--A06 Standard for IndustrialEnclosed Gear Drives

This standard includes design, rating, lubrication,testing and selection information for enclosed geardrives, including foot mounted, shaft mounted, screwconveyor drives and gearmotors. These drivesinclude spur, helical, herringbone, double helical, orbevel gearing in single or multistage arrangements,and wormgearing in multistage drives, as eitherparallel, concentric or right angle configurations. Thisstandard combines and replaces the informationpreviously found in ANSI/AGMA 6009--A00 andANSI/AGMA 6010--F97.ISBN: 1--55589--822--X Pages: 60

ANSI/AGMA 6014--A06 Gear Power Rating forCylindrical Shell and Trunnion SupportedEquipment

This standard specifies methods for rating the pittingresistance and bending strength of open orsemi--enclosed spur, single helical, double helical,and herringbone gears made from steel andspheroidal graphitic iron for use on cylindrical shell

and trunnion supported equipment, such ascylindrical grinding mills, kilns, coolers and dryers.This standard provides a design comparison methodfor different open or semi--enclosed gears, where thegear reaction forces are transmitted through astructure which provides independent bearingsupport for the gear and pinion. Annexes coverinstallation, alignment, maintenance, lubrication, anda ratingmethod for gearsmade fromausferritic ductileiron. Supersedes ANSI/AGMA 6004--F88.ISBN: 1--55589--876--9 Pages: 71

ANSI/AGMA 6022--C93 Design Manual forCylindrical Wormgearing

Covers the design of general industrial coarse----pitchcylindrical worms and throated gears mounted withaxes at a 90 degree angle and having axial pitches of3/16 inch and larger..ISBN: 1--55589--041--5 Pages: 10

ANSI/AGMA 6025--D98 Sound for EnclosedHelical, Herringbone and Spiral Bevel Gear Drives

Describes a recommended method of acceptancetesting and reporting of the sound pressure levelsgenerated by a gear speed reducer or increaser whentested at the manufacturer’s facility. The resultsobtained through the use of this standard shouldrepresent only the sound of the gear unit, as othersystem influences, such as prime mover or drivenequipment are minimized. Annexes to the standardpresent sound power measurement methods for usewhen required by specific contract provisionsbetween the manufacturer and purchaser. Revisionof ANSI/AGMA 6025--C90.ISBN: 1--55589--718--5 Pages: 21

ANSI/AGMA 6032--A94 Standard for Marine GearUnits: Rating

Considers rating practices for marine mainpropulsion, power take--off and auxiliary propulsionservice. Allowable contact stress numbers andallowable bending stress numbers for materials areincluded. Also addresses bearings, clutches,lubricating oil systems, shafts and certain aspects ofvibration.ISBN: 1--55589--633--2 Pages: 57


This standard identifies commonly used alloy steels,heat treatments and inspection requirements forthrough hardened and surface hardened gearing formain propulsion marine service over 1500 hp. Forgedand hot rolled alloy steel bar stock are specified to twometallurgical quality grades (1 and 2) according tocleanliness and test requirements. Cast steel gearingis specified to a single metallurgical quality level.Mechanical, metallurgical and nondestructive testrequirements are provided for various heat treatmentprocesses and metallurgical quality grades ofgearing. Revision of ANSI/AGMA 6033--B98.ISBN: 978--1--55589--929--5 Pages: 34



ANSI/AGMA 6034--B92 Practice for EnclosedCylindrical Wormgear Speed Reducers andGearmotors

Covers the design and rating of cylindrical-- wormgearspeed reducers, having either solid or hollow outputshafts of the following specific types: single reduction;double reduction incorporating cylindricalwormgearing for each reduction; and doublereduction incorporating cylindrical wormgearing asfinal and helical gearing as initial reduction.ISBN: 1--55589--494--1 Pages: 37

ANSI/AGMA 6035--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing

This standard provides guidelines for the design,rating and application of globoidal wormgearingmounted at a 90 degree angle. Specific definitions forgloboidal wormgearing terms are presented, alongwith formulas for determining the geometric sizes ofthe major features for the worm and gear. Designconsiderations, design procedures, gear blanks andself--locking conditions are also discussed.Procedures for rating the load capacity of globoidalwormgearing are included. Replaces ANSI/AGMA6017--E86 and ANSI/AGMA 6030--C87.ISBN: 1--55589--792--4 Pages: 45

ANSI/AGMA 6101--E08, Design and Selection ofComponents for Enclosed Gear Drives (MetricEdition)

This standard outlines the basic practices for thedesign and selection of components, other thangearing, for use in commercial and industrial enclosedgear drives. Fundamental equations provide for theproper sizing of shafts, keys, and fasteners based onstated allowable stresses. Other components arediscussed in a manner to provide an awareness oftheir function or specific requirements. This standardapplies to the following types of commercial andindustrial enclosed gear drives, individually or incombination: spur, helical, herringbone, bevel andworm. Metric Edition of ANSI/AGMA 6001--E08.ISBN: 978--1--55589--952--3 Pages: 42

ANSI/AGMA 6113--A06 Standard for IndustrialEnclosed Gear Drives (Metric Edition)

This standard includes design, rating, lubrication,testing and selection information for enclosed geardrives, including foot mounted, shaft mounted, screwconveyor drives and gearmotors. These drivesinclude spur, helical, herringbone, double helical orbevel gearing in single or multistage arrangements,and wormgearing in multistage drives, as eitherparallel, concentric or right angle configurations. Thisstandard combines and replaces the informationpreviously found in ANSI/AGMA 6109--A00 andANSI/AGMA 6110--F97. Metric version ofANSI/AGMA 6013--A06.ISBN: 1--55589--823--8 Pages: 60

ANSI/AGMA 6114--A06 Gear Power Rating forCylindrical Shell and Trunnion SupportedEquipment (Metric Edition)

This standard specifies methods for rating the pittingresistance and bending strength of open orsemi--enclosed spur, single helical, double helical,and herringbone gears made from steel andspheroidal graphitic iron for use on cylindrical shelland trunnion supported equipment, such ascylindrical grinding mills, kilns, coolers and dryers.This standard provides a design comparison methodfor different open or semi--enclosed gears, where thegear reaction forces are transmitted through astructure which provides independent bearingsupport for the gear and pinion. Annexes coverinstallation, alignment, maintenance, lubrication, anda ratingmethod for gearsmade fromausferritic ductileiron. SupersedesANSI/AGMA 6004--F88 and is themetric edition of ANSI/AGMA 6014--A06.ISBN: 1--55589--877--7 Pages: 71

ANSI/AGMA 6123--B06 Design Manual forEnclosed Epicyclic Gear Drives

This standard provides the user of enclosed epicyclicgear drives with advanced methods of specifying andcomparing proposed designs to help predict therelative performance of different drive systems. Itprovides guidelines for epicyclic gear meshing andassembly requirements, tooth geometry, load sharingbetween planets, circulating power, componentdesign, thermal rating and lubrication. Annexesprovide complete example calculations, anddiscussions on special design considerations forepicyclic drives. Replaces ANSI/AGMA 6023--A88and ANSI/AGMA 6123--A88.ISBN: 1--55589--875--0 Pages: 97


This standard identifies commonly used alloy steels,heat treatments and inspection requirements forthrough hardened and surface hardened gearing formain propulsion marine service over 1500 hp. Forgedand hot rolled alloy steel bar stock are specified to twometallurgical quality grades (1 and 2) according tocleanliness and test requirements. Cast steel gearingis specified to a single metallurgical quality level.Mechanical, metallurgical and nondestructive testrequirements are provided for various heat treatmentprocesses and metallurgical quality grades ofgearing. Metric version of ANSI/AGMA 6033--C08.ISBN: 978--1--55589--930--1 Pages: 34

ANSI/AGMA 6135--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing(Metric Version)

This standard provides guidelines for the design,rating and application of globoidal wormgearingmounted at a 90 degree angle. Specific definitions forgloboidal wormgearing terms are presented, alongwith formulas for determining the geometric sizes of



the major features for the worm and gear. Designconsiderations, design procedures, gear blanks andself--locking conditions are also discussed.Procedures for rating the load capacity of globoidalwormgearing are included. Replaces ANSI/AGMA6017--E86 and ANSI/AGMA 6030--C87. Metricedition of ANSI/AGMA 6035--A02.ISBN: 1--55589--793--2 Pages: 45

ANSI/AGMA ISO 6336--A08 Calculation of LoadCapacity of Spur and Helical Gears - Part 6:Calculation of Service Life Under Variable Load

This standard specifies the information andstandardized conditions necessary for the calculationof the service life (or safety factors for a required life)of gears subject to variable loading. While themethodis presented in the context of ISO 6336 and thecalculation of load capacity for spur and helical gears,it is equally applicable to other types of stress.Identical adoption of ISO 6336--6:2006.ISBN: 978--1--55589--928--8 Pages: 20

ANSI/AGMA 9000--C90 Flexible Couplings -Potential Unbalance Classification

Offers standard criteria for the unbalanceclassification of flexible couplings. Considers theeffects of hardware and eccentricity to give a moreaccurate value. Presents revised examples in theappendices that illustrate the calculation methods.Replaces AGMA 515.02.ISBN: 1--55589--549--2 Pages: 41

ANSI/AGMA 9001--B97 Flexible Couplings -Lubrication

Examines proper lubrication and why it is an essentialelement for satisfactory performance and long life.Looks at the requisites for proper lubrication,including: selection of proper lubricant, awell--designed lubrication system, and an adequatemaintenance program, are discussed in this standard.Revision of ANSI/AGMA 9001--A86.ISBN: 1--55589--686--3 Pages: 6

ANSI/AGMA 9002--B04 Bores and Keyways forFlexible Couplings (Inch Series)

This standard describes sizes and tolerances forstraight and tapered bores and the associated keysand keyways, as furnished in flexible couplings. Thedata in the standard considers commercially standardcoupling bores and keyways, not special couplingbores and keyways that may require specialtolerances. Annexes provide material on inspectionmethods and design practices for tapered shafts.Revision of ANSI/AGMA 9002--A86.ISBN: 1--55589--841--6 Pages: 22

ANSI/AGMA 9003--B08 Flexible Couplings -Keyless Fits

This standard presents information on design,dimensions, tolerances, inspection, mounting,removal, and equipment that is in common use withkeyless tapered and keyless straight (cylindrical) borehubs for flexible couplings. Example calculations ofimportant design issues are provided in an annex.Revision of ANSI/AGMA 9003--A91.ISBN: 1--55589--572--7 Pages: 21

ANSI/AGMA 9004--B08 Flexible Couplings - MassElastic Properties and Other Characteristics

This standard provides calculationmethods related tomass elastic properties of flexible couplings.Properties discussed include coupling mass, polarmass moment of inertia (WR2), center of gravity, axialstiffness, axial natural frequency, lateral stiffness,lateral natural frequency, and torsional stiffness.Calculation examples are provided in informativeannexes. Revision of ANSI/AGMA 9004--A99.ISBN: 978--1--55589--973--8 Pages: 33

ANSI/AGMA 9005--E02 Industrial Gear LubricationThis standard provides the end user, originalequipment builder, gear manufacturer and lubricantsupplier with guidelines for minimum performancecharacteristics for lubricants suitable for use withenclosed and open gearing which is installed ingeneral industrial power transmission applications. Itprovides recommendations for selecting lubricantsbased on current theory and practice in the industry,and attempts to align with current ISO standards. It isnot intended to supplant specific instructions from thegear manufacturer. Replaces ANSI/AGMA9005--D94.ISBN: 1--55589--800--9 Pages: 31

ANSI/AGMA 9008--B00 Flexible Couplings – GearType – Flange Dimensions, Inch Series

Defines the North American industry practice for theinterface dimensions of the sleeve and rigid hubs ofboth shrouded and exposed bole, inch series, geartype couplings.ISBN: 1--55589--736--3 Pages: 3

ANSI/AGMA 9009--D02 Flexible Couplings -Nomenclature for Flexible Couplings

Presents the nomenclature common to flexiblecouplings as used in mechanical power transmissiondrives. It was prepared to reduce the languagebarriers that arise between designers, manufacturersand users when attempting to designate various typesof flexible couplings and their elements. It does notaddress nomenclature for flexible shafts, quill shafts,universal joints or devices which exhibit slip such asclutches, fluid couplings, magnetic couplings ortorque converters.ISBN: 1--55589--796--7 Pages: 17



ANSI/AGMA 9103--B08 Flexible Couplings -Keyless Fits (Metric Edition)

This standard presents information on design,dimensions, tolerances, inspection, mounting,removal, and equipment that is in common use withkeyless tapered and keyless straight (cylindrical) borehubs for flexible couplings. Example calculations ofimportant design issues are provided in an annex.Metric version of ANSI/AGMA 9003--B08.ISBN: 978--1--55589--925--7 Pages: 22

ANSI/AGMA 9104--A06 Flexible Couplings - MassElastic Properties and Other Characteristics(Metric Edition)

This standard provides calculationmethods related tomass elastic properties of flexible couplings.Properties discussed include coupling mass, polarmass moment of inertia, center of gravity, axialstiffness, axial natural frequency, lateral stiffness,lateral natural frequency, and torsional stiffness.Calculation examples are provided in informativeannexes. Metric edition of ANSI/AGMA 9004--A99.ISBN: 1--55589--900--4 Pages: 32

ANSI/AGMA 9112--A04 Bores and Keyways forFlexible Couplings (Metric Series)

This standard describes sizes and tolerances forstraight and tapered bores and the associated keysand keyways, as furnished in flexible couplings. Thedata in the standard considers commercially standardcoupling bores and keyways, not special couplingbores and keyways that may require specialtolerances. Annexes provide material on inspectionmethods and design practices for tapered shafts.Metric edition of ANSI/AGMA 9002--B04.ISBN: 1--55589--842--4 Pages: 35

AGMA ISO 10064--5--A06, Code of InspectionPractice - Part 5: Recommendations Relative toEvaluation of Gear Measuring Instruments

This information sheet provides methods andexamples to support the implementation ofANSI/AGMA ISO 18653--A06. It includes evaluationand calibration procedures for involute, helix, runout,and tooth thickness measurement processes.Methods are given for the evaluation of condition andalignment of instrument elements such as centers,guideways, probe systems, etc. Recommendationsinclude statistical data evaluation procedures.Guidance is given on the application of measurementprocesses to the inspection of product gears,including fitness for use and the recommended limitsof U95 uncertainty based on the accuracy tolerancesof product gears to be inspected. Many of itsrecommendations could be applied to themeasurement of worms, worm wheels, bevel gearsand gear cutting tools. Replaces AGMA 931--A02.ISBN: 1--55589--881--5 Pages: 62

!! NEW !!

AGMA ISO 10064-6-A10 Code of InspectionPractice – Part 6: Bevel Gear MeasurementMethods

This document provides information on measuringmethods and practices of unassembled bevel andhypoid gears and gear pairs. Tolerances are providedin ISO 17485:2006, for calculating the maximumvalues allowed by the specific tolerance grade. Thesemethods and practices are intended to promoteuniform inspection procedures which are accurateand repeatable to a degree compatible with thespecified tolerance grade. Replaces ANSI/AGMA2009-B01.ISBN: 978-1-55589-994-3 Pages: 28

AGMA ISO 14179--1, Gear Reducers - ThermalCapacity Based on ISO/TR 14179-1

This information sheet utilizes an analytical heatbalance model to provide a means of calculating thethermal transmittable power for a single-- ormulti--stage gear drive lubricatedwithmineral oil. Thecalculation is based on standard conditions of 25Cmaximumambient temperature and 95Cmaximumoilsump temperature in a large indoor space, butprovides modifiers for other conditions. Differencesfrom ISO/TR 14179--1 are: a) errors were identifiedand corrected, b) text was added to clarify thecalculation methods, and c) an illustrative examplewas added to assist the reader. Modified adoptionof ISO/TR 14179--1.ISBN: 1--55589--821--1 Pages: 26

ANSI/AGMA ISO 17485-A08 Bevel Gears - ISOSystem of Accuracy

This standard establishes a classification system thatcan be used to communicate geometrical accuracyspecifications of unassembled bevel gears, hypoidgears, and gear pairs. It defines tooth accuracy terms,specifies the structure of the gear accuracy gradesystem, and provides allowable values. The standardprovides the gear manufacturer and the gear buyerwith a mutually advantageous reference for uniformtolerances. Ten grades are defined, numbered 2 to 11in order of decreasing precision. Equations fortolerances and their ranges of validity are provided forbevel and hypoid gearing. Identical adoption of ISO17485:2006.ISBN: 978--1--55589--926--4 Pages: 23

Supplemental Tables for ANSI/AGMA ISO17485--A08,BevelGears - ISOSystemofAccuracy- Tolerance Tables

This information sheet contains tolerance tablesdealing with the measurements of bevel gear toothflanks. While the tables may be used to estimate thetolerance, the actual tolerances are provided inANSI/AGMA ISO 17485--A08.ISBN: 978--1--55589--950--9 Pages: 39



ANSI/AGMA ISO 18653--A06 Gears - Evaluation ofInstruments for the Measurement of IndividualGears

This International Standard specifies methods for theevaluation ofmeasuring instruments used tomeasurecylindrical gear involute, helix, pitch and runout. Itincludes instruments that measure runout directly, orcompute it from index measurements. Of necessity, itincludes the estimation of measurement uncertaintywith the use of calibrated gear artifacts. It also givesrecommendations for the evaluation of tooththickness measuring instruments. The estimation ofproduct gear measurement uncertainty is beyond itsscope (see AGMA ISO 10064--5--A06 forrecommendations). This standard is an identicaladoption of ISO 18653:2006. Replaces ANSI/AGMA

2010--A94, ANSI/AGMA 2110--A94, ANSI/AGMA2113--A97 and ANSI/AGMA 2114--A98.ISBN: 1--55589--882--3 Pages: 14

ANSI/AGMA ISO 23509--A08 Bevel and HypoidGear Geometry

This standard specifies the geometry of bevel gears.The term bevel gears is used to mean straight, spiral,zerol bevel and hypoid gear designs. The standardintegrates straight bevel gears and the three majordesign generation methods for spiral bevel gears intoone complete set of formulas. The formulas of thethree methods are developed for the general case ofhypoid gears and calculate the specific cases of spiralbevel gears by entering zero for the hypoid offset.Identical adoption of ISO 23509:2006.ISBN: 978--1--55589--927--1 Pages: 138


ISO Standards by Technical Committee 60

Technical Committee 60 is responsible for the development of all international gear--related standards.

Many standards require additional documents for their proper use. A list of these standards are normally supplied after thescope, in the normative references section of a document. Be sure to inquire whether the standard you need requiresother documents listed herein.

53:1998 Cylindrical gears for general and heavyengineering – Standard basic rack tooth profile

54:1996Cylindrical gears for general engineering and forheavy engineering -- Modules

677:1976 Straight bevel gears for general engineeringand heavy engineering -- Basic rack

678:1976 (1996) Straight bevel gears for generalengineering and heavy engineering -- Modules anddiametral pitches

701:1998 International gear notation -- Symbols forgeometric data

1122--1:1998Glossary of gear terms -- Part 1: Definitionsrelated to geometry

1122--2:1999 Vocabulary of gear terms -- Part 2:Definitions related to worm gear geometry

1328--1:1995Cylindrical gears -- ISO system of accuracy-- Part 1: Definitions and allowable values of deviationsrelevant to corresponding flanks of gear teeth (SeeANSI/AGMA ISO 1328--1)

1328--2:1997Cylindrical gears -- ISO system of accuracy-- Part 2: Definitions and allowable values of deviationsrelevant to radial composite deviations and runoutinformation (See ANSI/AGMA ISO 1328--2)

1340:1976 Cylindrical gears -- Information to be given tothe manufacturer by the purchaser in order to obtain thegears required

1341:1976 Straight bevel gears -- Information to be givento themanufacturer by the purchaser in order to obtain thegears required

2490:1996Single--start solid (monoblock) gear hobs withtenon drive or axial keyway, 1 to 40 module -- Nominaldimensions

4468:2009 Gear hobs -- Accuracy requirements

6336--1:2006 Calculation of load capacity of spur andhelical gears -- Part 1: Basic principles, introduction andgeneral influence factors

6336--2:2006 Calculation of load capacity of spur andhelical gears -- Part 2: Calculation of surface durability(pitting)

6336--3:2006 Calculation of load capacity of spur andhelical gears -- Part 3: Calculation of tooth bendingstrength

6336--5:2003 Calculation of load capacity of spur andhelical gears -- Part 5: Strength and quality of materials

6336--6:2006 Calculation of load capacity of spur andhelical gears -- Part 6: Calcultion of service life undervariable load

8579--1:2002 Acceptance code for gears -- Part 1:Determination of airborne sound power levels emitted bygear units

8579--2:1993 Acceptance code for gears -- Part 2:Determination ofmechanical vibration of gear units duringacceptance testing

9083:2001 Calculation of load capacity of spur andhelical gears -- Application to marine gears

9085:2002 Calculation of load capacity of spur andhelical gears -- Application for industrial gears

TR10064--1:1992 Cylindrical gears -- Code of inspectionpractice -- Part 1: Inspection of corresponding flanks ofgear teeth (See AGMA ISO 10064--1)

TR10064--2:1996 Cylindrical gears -- Code of inspectionpractice -- Part 2: Inspection related to radial compositedeviations, runout, tooth thickness and backlash (SeeAGMA ISO 10064--2)

TR10064--3:1996 Cylindrical gears -- Code of inspectionpractice -- Part 3: Recommendations relative to gearblanks, shaft centre distance and parallelism of axes

TR10064--4:1998 Cylindrical gears -- Code of inspectionpractice -- Part 4: Recommendations relative to surfacetexture and tooth contact pattern checking

TR10064--5:2005/Cor 1:2006 Code of inspectionpractice ---- Part 5: Recommendations relative toevaluation of gear measuring instruments ---- TechnicalCorrigendum 1

TR10064--6:2009 Code of inspection practice -- Part 6:Bevel gear measurement methods

10300--1:2001 Calculation of load capacity of bevelgears -- Part 1: Introduction and general influence factors

10300--2:2001 Calculation of load capacity of bevelgears -- Part 2: Calculation of surface durability (pitting)

10300--3:2001 Calculation of load capacity of bevelgears -- Part 3: Calculation of tooth root strength


TR10495:1997 Cylindrical gears-- Calculation of servicelife under variable loads -- Conditions for cylindrical gearsaccording to ISO 6336

10825:1995 Gears -- Wear and damage to gear teeth --Terminology

TR10828:1997Wormgears -- Geometry of worm profiles

TR13593:1999 Enclosed gear drives for industrialapplications

13691:2001 Petroleum and natural gas industries -- Highspeed special--purpose gear units

TR13989--1:2000 Calculation of scuffing load capacity ofcylindrical, bevel and hypoid gears – Part 1: Flashtemperature method

TR13989--2:2000 Calculation of scuffing load capacity ofcylindrical, bevel and hypoid gears – Part 2: Integraltemperature method

14104:1995 Gears -- Surface temper etch inspectionafter grinding

TR14179--1:2001 Gears -- Thermal capacity -- Part 1:Rating gear drives with thermal equilibrium at 95C sumptemperature

TR14179--2:2001 Gears -- Thermal capacity -- Part 2:Thermal load--carrying capacity

14635--1:2000 Gears – FZG test procedures – Part 1:FZG method A/8, 3/90 for relative scuffing load carryingcapacity of oils

14635--3:2005 Gears -- FZG test procedures -- Part 3:FZG test method A/2,8/50 for relative scuffingload--carrying capacity and wear characteristics ofsemifluid gear greases

17485:2006 Bevel gears -- ISO system of accuracy

18653:2003 Gears ---- Evaluation of instruments for themeasurement of individual gears

TR18792:2009 Lubrication of industrial gear drives

21771:2007 Gears -- Cylindrical involute gears and gearpairs -- concepts and geometry

23509:2006 Bevel and hypoid gear geometry


Gear Software(for ANSI/AGMA 2001 and ISO 6336)

AGMA’s Gear Rating SuiteBeginning with AGMA’s ISO6336 Software , which wasdeveloped and tested over several years by a group ofAGMA men and women working closely with thedevelopers of the international standard, the softwareaddresses ISO 6336method B, themost comprehensive,analytical calculation method. It has gained internationalacceptance since its release in 1998 and enables you to:

S determine gear capacity in accordance with the ISO6336 standard quickly and accurately;

S compare your own design and practices with ISO6336 results;

S understand your competitor’s ratings.

The manual alone is worth the price! In addition toexplaining the software, this handy document is a greattool for learning how to use ISO6336, guiding you throughthe complexities and teaching you the correct inputs,especially in the exacting areas of tooth geometry andtooling.

Two of the most recognized standards in the world todayfor determining the rating of spur and helical gears areANSI/AGMA 2001--C95 and ISO 6336. Now for the firsttime, software to calculate ratings in accordance witheach standard is available in one package from AGMA.Entitled the Gear Rating Suite, the software allows theuser to input data once for each gearset, and obtainratings to both standards. Among the many features ofthe software package are:

S An in--depth User’s Manual, and all required AGMAand ISO standards.

S User friendly I/O that provides an intuitive userinterface, with drop--down boxes, look--up tables,and graphical guides used to assist in data entry.

S Dual input units which allow the user to switchbetween SI and inch units.

S Error and warning messages are provided withinboth the input and rating routines to help identifyproblems.

S A help program is incorporated within the software.

S Long and short form outputs are provided.

In addition to the gear rating routines and aids, thepackage also provides:

S A Geometry Checker for checking input data toensure they are within allowable ranges. TheGeometry Checker will help identify data entry errorsand unusual gear designs.

S Tolerance worksheets which allow the user tocalculate tooth tolerances from quality numbers,convert quality numbers between AGMA and ISO,and to display tolerances for adjacent grades.

The potential of the Gear Rating Suite to improve yourefficiency and save you time in performing these rigorouscalculations makes this a “must have” tool for all gearengineers.

There are two purchasing options available:

S OPTION I – Software with help file and an electronic(read-only) copy of the referenced standards.

S OPTION II – Software with help file only (standardsnot included)

AGMA’s Bevel Gear Rating SuiteLooking for an easy tool to calculate complex bevel geargeometry? Would you like to compare your designagainst standards and understand your competitors’ratings? Then AGMA’s Bevel Gear Rating Suite isthe-must-have software for you.

TheBevel Gear Rating Suite (currently v.1.1.1) calculatesgeometry and ratings for straight, spiral, skew, and zerolbevel gears according to ANSI/AGMA standards. Theprogram strictly follows these standards without imposingdesign rules. It allows the user to analyze a full range ofgears accurately.

Enter bevel gear parameters quickly in the manner and inthe units you prefer. It can calculate the geometry factorsfor you or accept factors that have been calculatedoutside the program. Tooth thickness can be entered,calculated by balancing geometry factors or from AGMAor ISO thickness factors.

Not only can this software calculate ratings, it will alsoallow you to easily enter or calculate geometry accordingto either current or old standards plus load capacities.

The program covers material from the followingstandards:

S ANSI/AGMA2003,Rating thePittingResistance andBending Strength of Generated Straight Bevel,Zero1Bevel and Spiral Bevel Gear Teeth

S ANSI/AGMA 2005, Design Manual for Bevel Gears

S AGMA 208.03, System for Straight Bevel Gears(1978)

S AGMA209.03,System for Spiral Bevel Gears (1964)

S AGMA209.04,System for Spiral Bevel Gears (1982)

S AGMA 202.03, System for Zerol Bevel Gears (1965)


S ANSI/AGMA 2009, Bevel Gear Classification,Tolerances, and Measuring Methods

S AGMA 390.03a, Gear Handbook GearClassification, Materials and Measuring Methods forBevel, Hypoid, Fine Pitch Wormgearing and RacksOnly as Unassembled Gears (1988)

S AGMA 929, Calculation of Bevel Gear Top Land andGuidance on Cutter Edge Radius

Enjoy user‐friendly, efficient screens for data input andoutput. In fact, the input data can be customized to defaultto the input methods and bevel types used by yourcompany.

There are two purchasing options available:

S OPTION I – Software with help file and an electronic(read-only) copy of the referenced standards.

S OPTION II – Software with help file only (standardsnot included)



Fall Technical Meeting Papers: 2000 -- 2010

2010 PAPERS

10FTM01. Complete Machining of Gear Blank andGear TeethAuthor: C. Kobialka

Demands for increased throughput, with smallerlot sizes at lower cost have led to the development ofan innovative approach to machining both: the gearbland and gear teeth on a single machine.

This paper will concentrate on the potentials andrisks of combined process machines what are capableof turning, hobbing, drilling, milling, chamfering anddeburring of cylindrical gears. The same machineconcept can be used for singular operations of eachmanufacturing technology on the same designconcept. This leads to reduced amounts of differentspare parts, increases achievable workpiece qualityand harmonizes on a commonuser friendliness. In theend the economical potential of combined processtechnology anda vision for integratedheat treatment isshown.ISBN: 978--1--55589--976--9 Pages: 8

10FTM02. ImprovingHeat Treating Flexibility forWindTurbine Gear Systems Through Carburizing,Quenching and Material Handling AlternativesAuthor: W. Titus

Part handling and processes for heat treatinglarge gears have created challenges for decades.Growth in wind energy technology has focused moreattention on this issue in recent years. The vastmajority of installations processing such large partsutilize conventional methods via pit furnace systems.Such equipment has inherent limitations with respectto quench flow and part handling, making trueimprovements in areas such as distortion controldifficult due to physical limitations of this processingapproach. This presentation will explain alternativemethods for heat treating large components that allowpart distortion to be minimized. Benefits will bequantified regarding cost savings to produce suchgearing and quality.ISBN: 978--1--55589--977--6 Pages: 19

10FTM03. A Novel Approach to the Refurbishment ofWind Turbine GearsAuthors: M. Michaud, G.J. Sroka and R.E. Benson

Multi--megawatt wind turbine gearboxes operateunder demanding environmental conditions includingconsiderable variation in temperature, wind speed,and air quality. It is not uncommon for gearboxes ratedfor a maintenance free 20--year lifespan to fail afteronly a few years. These gearboxes experience severaltypes of repairable damage including micropitting or“gray staining”, abrasive wear, foreign object debris(FOD) damage, surface corrosion and frettingcorrosion. Wear is greatest on the input stage,especially on the sun pinion gear. Historically, grindingis utilized to refurbish these damaged gears. However,

there are numerous drawbacks including but notlimited to high capital investment and the extraordinaryamount of time and skill involved in the grindingprocess. Moreover, nitrided gears cannot be groundand must be scrapped. However, chemicallyaccelerated vibratory finishing, or isotropicsuperfinishing (ISF), represents a value adding,low--cost option for refurbishing both case carburizedand nitrided gears. Isotropic superfinishing removeslight to moderate gear flank surface damage. Theresult is a surface with a non--directional pattern with aroughness of approximately 0.08 mm or less.Moreover, evidence suggests that isotropicsuperfinishing imparts a finish that increases geardurability and service life in the field. A case study on asun pinion gear is presented.ISBN: 978--1--55589--978--3 Pages: 10

10FTM04. Low Distortion Heat Treatment ofTransmission ComponentsAuthors: V. Heuer, K. Löser, D.R. Faron and D. Bolton

In many applications the high demands regardingservice life of transmission components can bereached only by the application of a customized casehardening. This case hardening process results in awear resistant surface--layer in combination with atough core of the component. However as aside--effect the components get distorted during heattreatment. This distortion has a significantcost--impact, because distorted components oftenneed to be hard--machined after heat treatment.Therefore the proper control of distortion is animportant measure to minimize production costs.

By applying the technology of low pressurecarburizing (LPC) and high pressure gas quenching(HPGQ) heat treat distortion can be significantlyreduced. HPGQ provides a very uniform heat transfercoefficient. The predictability of movement duringquenching is more certain and uniform throughout theload. Further improvements can be achieved by“Dynamic Quenching” processes where thequenching severity is varied during the quenchsequence by step control of the gas velocity. Properfixturing is another factor for distortion control. ModernCFC--materials (carbon reinforced carbon) are wellsuited as fixture--material for gas quenching.

The paper presents how LPC and HPGQprocesses are successfully applied on Internal ringgears for a 6 speed automatic transmission. Thespecific challenge in the heat treat process was toreduce distortion in such a way that subsequentmachining operations are entirely eliminated. As aresult of extensive development in the quenchingprocess and the use of specialized CFC-- fixtures itwas possible to meet the design metrologicalrequirements.

The Internal ring gears addressed in this reporthave been in continuous production since 2006.Subsequent testing and monitoring over a two yearperiod progressively demonstrated that consistent



metrology was achieved and quality inspection wasreduced accordingly.ISBN: 978--1--55589--979--0 Pages: 16

10FTM05. Comparison of the AGMA and FEACalculations of Gears and Gearbox ComponentsApplied in the Environment of Small Gear CompanyAuthor: V. Kirov

The current AGMA standards provide a lot ofinformation about the calculations of loose gears andgearbox components – shafts, splines, keys, etc.These recommendations are based mostly on the“traditional” methods of mechanical engineering,found in many classical textbooks and researchpapers. Their accuracy and reliability have beenproven in many years of gearbox design and fieldtests. They are clear, concise, in most cases easy toprogram and apply even by a small gear company withlimited resources. However new methods forcalculations of mechanical engineering componentslike FEA (finite element analysis) are becoming widespread. Once these techniques were used only by bigcompanies because of their complexity and price butwith the development of the computer technology theybecome more and more accessible to small gearcompanies which are themajority of participants in themarket.

Nowadays, in the gear business, even a smallgear company is usually in possession of a modernCAD system which always includes a basic oradvanced FEA package. Such CAD systems aremostoften run by one gear engineer whomakes 3Dmodels,engineering calculations and production drawings.The level of the FEA packages is such that it allows thegear engineer to be able to do componentscalculations without deep knowledge in the FEA itself.

So the question about the effectiveness of thetraditional AGMA calculations and the new FEAmethods becomes of vital importance particularly forsmall firms.ISBN: 978--1--55589--980--6 Pages: 9

10FTM06. Finite Element Analysis of High ContactRatio GearAuthors: M. Rameshkumar, G. Venkatesan andP. Sivakumar

Modern day vehicles demandhigher load carryingcapacity with less installed volume and weight. Thegears used in the vehicles should also have lessernoise and vibration. Even though helical gears willmeet the requirement, they are prone for additionalaxial thrust problem. High contact ratio (HCR) is onesuch gearing concept used for achieving high loadcarrying capacity with less volume and weight.Contact ratio greater than 2.0 inHCRgearing results inlower bending and contact stresses. Previouslypublished literature deal with studies on variousparameters affecting performance of HCR gears but a

comparison of HCR and normal contact ratio (NCR)gears with same module and center distance has notbeen carried out so for. This paper deals with finiteelement analysis of HCR,NCR gears with samemodule, center distance and the comparison ofbending, contact stress for both HCR, NCR gears. Atwo dimensional deformable body contact model ofHCR and NCR gears is analyzed in ANSYS software.ANSYS Parametric Design language (APDL) is usedfor studying the bending and contact stress variationon complete mesh cycle of the gear pair for identicalload conditions. The study involves design, modeling,meshing and post processing of HCR and NCR gearsusing single window modeling concept to avoidcontact convergence and related numerical problems.ISBN: 978--1--55589--981--3 Pages: 12

10FTM07. A New Statistical Model for PredictingTooth Engagement and Load Sharing in InvoluteSplinesAuthors: J. Silvers, C.D. Sorensen and K.W. Chase

Load--sharing among the teeth of involute splinesis little understood. Designers typically assume only afraction of the teeth are engaged and distribute theload uniformly over the assumed number of engagedteeth. This procedure can widely over-- orunderestimate tooth loads.

A new statistical model for involute spline toothengagement has been developed and presentedearlier, which takes into account the random variationof gear manufacturing processes. It predicts thenumber of teeth engaged and percent of load carriedby each tooth pair. Tooth--to--tooth variations cause theclearance between each pair of mating teeth to varyrandomly, resulting in a sequential, rather thansimultaneous tooth engagement. The sequencebegins with the tooth pair with the smallest clearanceand proceeds to pick up additional teeth as the load isincreased to the maximum applied load. The newmodel can predict the number of teeth in contact andthe load share for each at any load increment.

This report presents an extension of the newsequential engagement model, which morecompletely predicts the variations in the engagementsequence for a set of spline assemblies. A statisticaldistribution is derived for each tooth in the sequence,alongwith itsmean, standard deviation and skewness.Innovative techniques for determining the resultingstatistical distributions are described. The results of anin--depth study are also presented, which verify thenew statisticalmodel. MonteCarlo Simulation of splineassemblies with randomerrors was performed and theresults compared to the closed--form solution.Extremely close agreement was found. The newapproach shows promise for providing keener insightsinto the performance of spline couplings and will serveas an effective tool in the design of power transmissionsystems.ISBN: 978--1--55589--982--0 Pages: 17



10FTM08. Calculation of Load Distribution inPlanetary Gears for an Effective Gear Design ProcessAuthors: T. Schulze, C. Hartmann--Gerlach, B.Schlecht

Thedesign of gears -- especially planetary gears --can just be carried out by the consideration ofinfluences of the whole drive train and the analysis ofall relevant machine elements. In this case the gear ismore than the sum of its machine elements. Relevantinteractions need to be considered under realconditions. The standardized calculations are decisivefor the safe dimensioning of the machine elementswith the consideration of realistic load assumptions.But they need to be completed by extended analysis ofload distribution, flank pressure, root stress,transmission error and contact temperature.ISBN: 978--1--55589--983--7 Pages: 11

10FTM09. Reverse EngineeringAuthor: C.D. Schultz

As America’s manufacturing base has contractedthe need for reverse engineering has grown. Wellestablished suppliers have disappeared, often leavingcustomers with no source of spare parts or technicalsupport. Over time certain pieces of equipment requirechanges to output speeds or power levels and newparts have to be designed, built, and installed. Andunfortunately, some pieces of equipment don’tmeasure up to the demands they are subjected to andneed redesign or improvement. Inmanyways, reverseengineering is just as demanding a discipline asoriginal product development with many of the samechallenges but plus the additional restrictions of fittinginside of an existing envelope.

The typical reverse engineering project beginswith very limited information on the existing piece ofequipment. This paper will describe a methodology forthe reliable measurement, evaluation, re--design, andmanufacture of replacement parts for gearboxes andindustrial machinery. A step--by--step example will beprovided.ISBN: 978--1--55589--984--4 Pages: 9

10FTM10. Evaluation of Methods for CalculatingEffects of Tip Relief on Transmission Error, Noise andStress in Loaded Spur GearsAuthor: D. Palmer and M. Fish

The connection between transmission error andnoise and vibration during operation has long beenestablished. Calculation methods have developed todescribe the influence such that it is possible toevaluate the relative effect of applying a specificmodification at the design stage. The calculations canallow the designer to minimize the excitation from thegear pair engagement at a specific load. This paperexplains the theory behind transmission error and thereasoning behind the method of applying themodifications through mapping the surface profilesand deducing the load sharing. It can be used toexplain the results of later experimental validation onvarious types of tip relief in low contact ratio (LCR)

gears, from very long to very short. The paper will alsodemonstrate that though the effects of modification inany specific case can bemodeled with some certainty,the same modifying strategy can not be applieduniversally but must consider the required operatingconditions. It illustrates that the effect of tip relief ontransmission error and load sharing is not a black artbut can be fully explained by applying existing theory.

A study of high contact ratio (HCR) gears will bepresented to demonstrate why it is often necessary toapply different amounts and extents of tip relief in suchdesigns, and how these modifications affect loadsharing and highest point of tooth loading. Specificattention will be paid to the phenomenon of extendedcontact, where if nomodification or insufficient tip reliefis applied, contact does not stop at the end of activeprofile but continues beyond this point as the gearrotates resulting in contact on the tip. This effectivelyincreases contact ratio and has implications for thetooth load and in particular how this may affect theloading position, highest point of single tooth contact(HPSTC), which is relevant to both ISO and AGMAstandard rating. The paper will consider 3 methodscommonly employed in the industry; a simple 2Dmapping procedure carried out on graph paper, a 3Dlinear tooth stiffness computation method, and a 3Dfinite element analysis (FEA) calculation. The paperwill demonstrate that though in some cases thesemethods can produce similar results, albeit withvarying degrees of accuracy, further examples will bepresentedwhich demonstrate behavior which can onlybe detected using some of the more complex analysismethods. The commercial viability of implementing abetter quality models against the time constraints inthe development process will be discussed andconclusions drawn.ISBN: 978--1--55589--985--1 Pages: 15

10FTM11. Point--Surface--Origin, PSO, MacropittingCaused by Geometric Stress Concentration, GSCAuthors: R.L. Errichello, C. Hewette, and R. Eckert

Point--Surface--Origin, PSO, macropitting occursat sites ofGeometric StressConcentration, GSC, suchas discontinuities in the gear tooth profile caused bymicropitting, cusps at the intersection of the involuteprofile and the trochoidal root fillet, and at edges ofprior tooth damage such as tip--to--root interference.When the profile modifications in the form of tip relief,root relief, or both are inadequate to compensate fordeflection of the gear mesh, tip--to--root interferenceoccurs. The interference can occur at either end of thepath of contact, but the damage is usually more severenear the start--of--active--profile, SAP, of the drivinggear.

An FZG--C gearset (with no profile modifications)was tested at load stage 9 and three pinion teeth failedby PSOmacropitting. It is shown that the root cause ofthe PSOmacropitting was GSC created by tip--to--rootinterference.ISBN: 978--1--55589--986--8 Pages: 11



10FTM12. Flank Load Carrying Capacity and PowerLoss Reduction by Minimized LubricationAuthors: B.--R. Höhn, K. Michaelis and H.--P. Otto

The lubrication of gears has two major functions:Reducing friction and wear as well as dissipating heat.The power losses, especially the no--load losses,decrease with decreasing immersion depth using diplubrication. The load--dependent gear power lossesare nearly unaffected by minimized lubrication.However, the gear bulk temperatures rise dramaticallyby using minimized lubrication due to a lack of heatdissipation.

With minimized lubrication the scuffing loadcarrying capacity decreased by up to morethan60%compared to rich lubrication conditions. Thedominating influence of the bulk temperature istherefore very clear. Starved lubrication leads to morefrequent metal -- to contact and the generation of highlocal flash temperatures must be considered. Anadditional factor for the scuffing load carrying capacitycalculation in case of minimized lubrication conditionsis proposed.

Concerning pitting damage test runs showed thatby lowering the oil level the load cycles without pittingdamage decreased by approximately 50% up to 75%for minimized lubrication compared to the results withrich lubrication conditions. The allowable contactstress is clearly reduced (up to 30%) by minimizedlubrication. A reduced oil film thickness as aconsequence of increased bulk temperatures resultsin more frequent metal--to--metal contacts causing ahigher surface shear stress. In combination with adecreased material strength due to a possibletempering effect at high bulk temperatures the failurerisk of pitting damage is clearly increased. Thecommon pitting load carrying capacity calculationalgorithms according to DIN/ISO are only valid formoderate oil temperatures and rich lubricationconditions. For increased thermal conditions, thereduction of the pitting endurance level at increasedgear bulk temperatures can be approximated with themethod of Knauer (FZG TU München, 1988). Anadvanced calculation algorithm for pitting load carryingcapacity calculation at high gear bulk temperatures(valid for high oil temperatures as well as forminimizedlubrication) is proposed.

The micropitting risk was increased by low oillevels, especially at high loads and during theendurance test. Themicropitting damage is causedbypoor lubrication conditions which are characterized bya too low relative oil film thickness due to high bulktemperatures. Again, the actual bulk temperatures areof major significance for calculation of the micropittingload carrying capacity.

The wear rate of the gears is almost unaffected bythe oil level. Only a slight increase of wear could beobserved with minimized lubrication. This increasecan be explained by the higher bulk temperature of thegears running under minimized lubrication conditions.The investigations showed that there exists a naturallimitation for lowering the oil quantity in transmissionswithout detrimental influence on the load carrying

capacity. Knowing these limitations enables the user todetermine the possible potential benefits of reduced oillubrication. The correct prediction of the actual gearbulk temperatures is of major importance in thiscontext. A method for the estimation of the gear bulktemperature at reduced immersion depth respectivelypoor lubrication conditions is proposed.ISBN: 978--1--55589--987--5 Pages: 15

10FTM13. Gear Design for Wind Turbine Gearboxesto Avoid Tonal Noise According to ISO/IEC 61400--11Author: J. Litzba

Present wind turbine gearbox design usuallyincludes one or two planetary gear stages and at leastone high speed helical gear stage, which play animportant role regarding noise and vibration behavior.Next to the overall noise of the gearbox and thestructure--born noise on the gearbox housing alsotonal noise is becoming a much more important issuein recent years. Since tonal noise is problematic due tothe human perception as “uncomfortable”, avoidanceis important. Conventional theories regarding lownoise gear design are not developed in view of tonalnoise. This leads to the question: How to deal withtonal noise in the design stage and which gearparameters can be used for an optimization regardinggood tonal noise behavior?

Within a research project measurements havebeen performed on different gearboxes using differentgear designs. These measurements have beenevaluated according to ISO/IEC 61400--11 and theresults have been analyzed in view of the influence ofdifferent gear parameters. It was also investigated if itis possible to rank gearboxes in wind turbinesaccording to their tonal noise behavior as observed onthe test rig.

The paper will give an introduction into thedefinition of tonal noise according to ISO/IEC61400--11 and give insight in measurement resultsfrom test rigs and from gearboxes in the field, wherenoise behavior is also evaluated according to ISO/IEC61400--11. Furthermore, the paper will show anddiscuss the link between measurement results anddifferent gear parameters, which are affecting tonalnoise behavior. In addition simulation results will bepresented, showing how tonal noise can be estimatedwithin the design stage using state--of--the–artcalculation software.

The paper will give recommendations regarding agear design process that is considering tonal noise inthe design stage and will compare an, regarding tonalnoise, improved gear set with an older one.ISBN: 978--1--55589--988--2 Pages: 19

10FTM14. Analysis and Testing of Gears withAsymmetric Involute Tooth Form and Optimized FilletForm for Potential Application in Helicopter MainDrivesAuthors: F.W. Brown, S.R. Davidson, D.B. Hanes,D.J. Weires and A. Kapelevich

Gears with an asymmetric involute gear toothform were analyzed to determine their bending andcontact stresses relative to symmetric involute gear



tooth designs which are representative of helicoptermain drive gears. Asymmetric and baseline(symmetric) toothed gear test specimens weredesigned, fabricated and tested to experimentallydetermine their single--tooth bending fatigue strengthand scuffing resistance. Also, gears with ananalytically optimized root fillet form were tested todetermine their single--tooth bending fatiguecharacteristics relative to baseline specimens with acircular root fillet form. Test results demonstratedhigher bending fatigue strength for both theasymmetric tooth form and optimized fillet formcompared to baseline designs. Scuffing resistancewas significantly increased for the asymmetric toothform compared to a conventional symmetric involutetooth design.ISBN: 978--1--55589--989--9 Pages: 15

10FTM15. Drive Line Analysis for Tooth ContactOptimization of High Power Spiral Bevel GearsAuthors: J. Rontu, G. Szanti and E. Mäsä

It is a common practice in high power gear designto apply relieves to tooth flanks. They are meant toprevent stress concentration near the tooth edges.Gears with crownings have point contact without load.When load is applied, instantaneous contact turnsfrom point into a Hertzian contact ellipse. The contactarea grows and changes location as load increases. Toprevent edge contact, gear designer has to choosesuitable relieves considering contact indentations aswell as relative displacements of gearmembers. In themajority of spiral bevel gears spherical crownings areused. The contact pattern is set to the center of activetooth flank and the extent of crownings is determinedby experience. Feedback from service, as well as fromfull torque bench tests of complete gear drives haveshown that this conventional design practice leads toloaded contact patterns, which are rarely optimal inlocation and extent. Too large relieves lead to smallcontact area and increased stresses and noise;whereas too small relieves result in a too sensitivetooth contact.

Today it is possible to use calculative methods topredict the relative displacements of gears underoperating load and conditions. Displacements anddeformations originating from shafts, bearings andhousing are considered. Shafts aremodeled based onbeam theory. Bearings are modeled as 5--DOFsupports with non--linear stiffness in all directions.Housing deformations are determined byFEM--analysis and taken into account as translationsand rotations of bearing outer rings. The effect oftemperature differences, bearing preload andclearances are also incorporated.

With the help of loaded tooth contact analysis(LTCA), it is possible to compensate for thesedisplacements and determine a special initial contactposition that will lead to well centered full torquecontact utilizing a reasonably large portion of theavailable tooth flank area. At the same time, crowningscan be scaled to theminimumnecessary amount. Thissystematic approach leads to minimum tooth

stressing, lower noise excitation as well as increasedreliability and/or power density as compared toconventional contact design method.

During recent years ATA Gears Ltd. has gainedcomprehensive know--how and experience in suchanalyses and advanced contact pattern optimization.The methodology and calculation models have beenverified in numerous customer projects and casestudies.ISBN: 978--1--55589--990--5 Pages: 14

10FTM16. Analysis of Load Distribution inPlanet--Gear BearingsAuthors: L. Mignot, L. Bonnard and V. Abousleiman

In epicyclic gear sets aimed at aeronauticalapplications, planet--gears are generally supported byspherical roller bearings with bearing outer race beingintegral to the gear hub. This paper presents a newmethod to compute roller load distribution in suchbearings where the outer ring can’t be consideredrigid. Based on well known Harris method, a modifiedformulation enables to account for centrifugal effectsdue to planet--carrier rotation and to assess rollerloads at any position throughout the rotation cycle.New model load distribution predictions showdiscrepancies with results presented by Harris, but arewell correlated with 1D and 3D Finite Element Models.Several results validate the use of simplified analyticalmodels to assess the roller load distribution instead ofmore time consuming Finite element Models. Theeffects of centrifugal effects due to planet--carrierrotation on roller loads are also analyzed. Finally theimpact of the positions of rollers relative to the gearmesh forces on the load distribution is shown.ISBN: 978--1--55589--991--2 Pages: 11

10FTM17. Self-Locking Gears: Design andPotential ApplicationsAuthors: A.L. Kapelevich and E. Taye

Inmost of the gear drives, when the driving torqueis suddenly reduced as a result of power off, torsionalvibration, power outage or any mechanical failure atthe transmission input side, then gears will be rotatingeither in the same direction driven by the systeminertia, or in the opposite direction driven by theresistant output load due to gravity, spring load, etc.The latter condition is known as backdriving. Duringinertial motion or backdriving, the driven output shaft(load) becomes the driving one and the driving inputshaft (load) becomes the driven one. There are manygear drive applications where the output shaft drivingis less desirable. In order to prevent it, different types ofbrake or clutch devices are used. However, there arealso solutions in gear transmission that prevent inertialmotion or backdriving using self--locking gears withoutany additional devices. The most common one is aworm gear with a low lead angle. In self--locking wormgears, torque applied from the load side (worm gear) isblocked, i.e. cannot drive the worm. However, theirapplication comes with some limitations: the crossedaxis shafts’ arrangement, relatively high gear ratio, low



speed, low gear mesh efficiency, increased heatgeneration, etc.

The paper describes the design approach as wellas potential applications of the parallel axisself--locking gears. These gears, unlike the wormgears don’t have suchapplication limitations. They canutilize any gear ratio from 1:1 and higher. They can beexternal, internal, or incorporated into the planetarygear stage ormultistage gear system. Their gearmeshefficiency is significantly higher than the worm gearsand closer to conventional gears. As a result theygenerate less heat. The self--locking can be designedto prevent either the inertia driving, or backdriving, orboth. The paper explains the principle of theself--locking process for gears with symmetric andasymmetric teeth profile, and shows their suitability fordifferent applications. It defines the main parametersof gear geometry and operating conditions. It alsodescribes potential self--locking gear applications andreferences to related publications.ISBN: 978--1--55589--992--9 Pages: 8

2009 PAPERS

09FTM01. Influence of theResidual Stresses Inducedby Hard Finishing Processes on the Running Behaviorof GearsAuthors: V. Vasiliou, C. Gorgels and F. Klocke

Low noise and high load carrying capacity are twoimportant characteristics of competitive powertransmissions. The challenge in the development,design and manufacturing of these powertransmissions is to meet these requirementseconomically. One of the ways to meet both of theserequirements is through a process known as hardfinishing. There are various types of hard finishing andit is important to know which process produces whichrequirement.

The aim of this research project is to induceresidual stresses in the edge of the work pieces bydifferent hard finishing processes and to analyze theirinfluence on the durability of the gears. The testedgears are manufactured by profile grinding, gearhoning and generating grinding. The gear deviationsand the finish quality have to be comparable. Throughthis the influence of the residual stresses on thedurability can be analyzed independent from thegeometrical conditions. The presentation will show theresults of the load carrying capacity tests dependingon the values of the residual stresses.ISBN: 978--1--55589--954--7 Pages: 11

09FTM02. Implementing ISO 18653, Evaluation ofInstruments for the Measurement of GearsAuthors: R.C. Frazer and S.J. Wilson

A trial test of the calibration procedures outlined inISO 18653, Gears-- Evaluation of instruments for themeasurement of individual gears, showed that the

results are reasonable, but a minor change to theuncertainty formula is recommended.

Gearmeasuringmachine calibrationmethods arereviewed. The benefits from using work--piece likeartifacts are discussed and a procedure forimplementing the standard in the work place ispresented.

Problems with applying the standard to large gearmeasuring machines are considered and somerecommendations are offered.ISBN: 978--1--55589--955--2 Pages: 15

09FTM03. Producing Profile and Lead Modificationsin Threaded Wheel and Profile GrindingAuthor: A. Türich

Modern gear boxes are characterized by hightorque load demands, low running noise, and compactdesign. In order to fulfill these demands, profile andlead modifications are being applied more and more.The main reason for the application of profile and orleadmodification is to compensate for the deformationof the teeth due to load, thus ensuring proper meshingof the teeth which will result in optimized tooth contactpattern.

This paper will focus on how to produce profileand leadmodifications by using the twomost commongrinding processes, threaded wheel and profilegrinding. In addition, more difficult modifications, suchas defined flank twist or topological flank corrections,will also be described in this paper.ISBN: 978--1--55589--956--1 Pages: 16

09FTM04. New Developments in Gear HobbingAuthor: O. Winkel

Several innovations have been introduced to thegear manufacturing industry in the past few years. Inthe case of gear hobbing, dry cutting technology andthe ability to do it with powder--metallurgicalHSS--materials might be two of the most impressiveones. But the technology is still moving forward. Theaim of this paper is to present recent developments inthe field of gear hobbing, focusing on innovationsregarding tool materials, process technology andprocess integration.ISBN: 978--1--55589--957--8 Pages: 18

09FTM05. HYPOLOIDt Gears with Small ShaftAngles and Zero to Large OffsetsAuthor: H. Stadtfeld

Beveloid gears are used to accommodate a smallshaft angle. The manufacturing technology used forbeveloid gearing is a special set up of cylindrical gearcutting and grinding machines.

A new development, called Hypoloid gearing,addresses the desire of gear manufacturers for morefreedom in shaft angles. Hypoloid gear sets can realizeshaft angles between zero and 20 and at the sametime allow a second shaft angle (or an offset) in spacewhich provides the freedom to connect two points inspace.

In all wheel driven vehicles that traditionally use atransfer case with a pinion/idler/gear arrangement or achain, the exit of the transfer case needs to beconnected with the front axle. This connection



necessitates the use of two CV joints, because thefront axle input point has a vertical offset and is shiftedsideways with respect to the transfer case exit.Compared to a single CV joint, the twoCVconnectionsare more costly and less efficient.

However, the newly developed Hypoloids canremedy the situation by offering more freedom in shaftangle and additional offset which eliminates the needfor an additional CV joint. Moreover, the Hypoloidtechnology offers enhancedperformance compared tobeveloids with straight teeth. In addition to theautomotive drive trains, Hypoloid technology can beapplied to aircraft as well as general gearboxmanufacturing.ISBN: 978--1--55589--958--5 Pages: 15

09FTM06. Dependency of the Peak--to--PeakTransmission Error on the Type of Profile Correctionand Transverse Contact Ratio of the Gear PairAuthor: U. Kissling

Profile corrections on gears are a commonly usedmethod to reduce transmission error, contact shock,and scoring risk. There are different types of profilecorrections. It is a known fact, that the type of profilecorrection used will have a strong influence on theresulting transmission error. The degree of thisinfluence may be determined by calculating toothloading during mesh. The current method for thiscalculation is very complicated and time consuming;however, a new approach has been developed whichcould reduce the calculation time.

This approach uses an algorithm which includesthe conventional method for calculating tooth stiffnessin regards to bending and shearing deformation,flattening due to Hertzian pressure, and tilting of thetooth in the gear body. The newmethod was tested bycomparing its results with FEM and LVR.

This paper illustrates and discusses the results ofthis study. Furthermore the maximum local powerlosses are compared with the scoring safetycalculated following the flash temperature criteria ofAGMA 925 and DIN 3990.ISBN: 978--1--55589--959--2 Pages: 19

09FTM07. Optimizing Gear Geometry for MinimumTransmission Error, Mesh Friction Losses andScuffing RiskAuthors: R.C. Frazer,B.A. Shaw,D. Palmer andM.Fish

Minimizing gear mesh friction losses is importantif plant operating costs and environmental impact areto beminimized. This paper describes how a validated3D FEA and TCA can be used to optimize cylindricalgears for low friction losses without compromisingnoise and power density. Some case studies arepresented and generic procedures for minimizinglosses are proposed. Future development and furthervalidation work is discussed.ISBN: 978--1--55589--960--8 Pages: 20

09FTM08. Load Sharing Analysis of High ContactRatio Spur Gears in Military Tracked VehicleApplicationAuthors:M. Rameshkumar, P. Sivakumar, K. Gopinathand S. Sundaresh

Military tracked vehicles demand a very compacttransmission to meet mobility requirements. Some ofthe desirable characteristics of these transmissionsinclude: increased rating, improved power to weightratio, low operating noise and vibration, and reducedweight. Toachieve all or someof these characteristics,it is has been decided to apply a High Contact Ratio(HCR) spur gearing concept which will improve loadcarrying capacity, lower vibration, and reduce noise.Similar to helical gears, the load in HCR gearing isshared by minimum two pair of teeth. Therefore, loadsharing analysis was conducted on Normal ContactRatio (NCR) gearing used in sun -- planet gears of anexisting drive.

This paper deals with analysis of load sharing ofindividual teeth in mesh for different load conditionsthroughout the profile for both sun and planet gears ofNCR/HCR gearing using Finite Element Analysis.Also, the paper reveals the variation of bending stressand deflection along the profile of both gearingdesigns.ISBN: 978--1--55589--961--5 Pages: 12

09FTM09. Designing for Static and Dynamic Loadingof a Gear Reducer Housing with FEAAuthors: M. Davis, Y. S. Mohammed, A.A. Elmustafa,P.F. Martin and C. Ritinski

A recent trend has been towardmore user friendlyproducts in the mechanical power transmissionindustry. One of these products is a high horsepower,right angle, shaft mounted drive designed to minimizeinstallation efforts. Commonly referred to as“alignment free” type, this drive assembly offers quickinstallationwithminimum level of expertise required. Itis also more cost effective. These characteristicsmake this type of drive ideal for use in applicationssuch as underground mining where there is little roomto maneuver parts.

An alignment free drive is direct coupled to thedriven shaft only; it is not firmly attached to afoundation or rigid structure. A connecting link ortorque arm connects the drive to a fixed structure,which limits the drive’s rotational movement about thedriven shaft. The electric motor is supported by thereducer housing through a fabricated steel motoradapter; the coupling connecting the motor shaft andreducer shaft is enclosed by this motor adapter.

FEA was used to test the cast iron housing todetermine any potential problem areas beforeproduction began. Once analyses were completed,the motor adaptor was redesigned to lower stressesusing the information from the FEA and comparing it tothe infield test data.ISBN: 978--1--55589--962--2 Pages: 9



09FTM10. The Effect of Flexible Components on theDurability, Whine, Rattle and Efficiency of aTransmission Geartrain SystemAuthor: A. Korde and B.K. Wilson

Gear Engineers have long recognized theimportance of considering system factors whenanalyzing a single pair of gears inmesh. These factorsinclude: load sharing in multi--mesh gear trains,bearing clearances, andeffects of flexible componentssuch as housings, gear blanks, shafts, and carriers forplanetary gears. Quality requirements andexpectations in terms of durability, lower operatingnoise and vibration, and efficiency have increased.With increased complexity and quality requirements, agear engineermust use advanced systemdesign toolsto ensure a robust gear train is delivered on time,meeting all quality, cost, and weight requirements.

As a standard practice, finite element modelshave traditionally been used for analyzingtransmission system deflections, but this modelingenvironment does not always include provisions foranalysis of vibration, efficiency, or any considerationsfor attribute variation. And that often requires manyruns of the test to ensure all variations have beenincluded and tested.

An advanced software tool is available for theanalysis of transmission system durability, noise,vibration, and efficiency, all within a singleprogramming environment, including the effects offlexible components such as housings, gear blanks,and shafting, while also allowing manufacturingvariation studies to be performed. This paper includesthe results of a case study of this program.ISBN: 978--1--55589--963--9 Pages: 13

09FTM11. Unique Design Constraints for MoldedPlastic TransmissionsAuthors: R. Kleiss and E. Wiita

Molded plastic gears and transmissions mustwork effectively in extremely variable conditions just astheir counterparts in steel. Plastics have the addedvariables of large thermal expansion and contraction,moisture absorption, greater tolerance variation, lowerstrength, and form deviations due to the moldingprocess. The design of a molded transmission mustconsider these effects and characteristics. This paperwill offer an example of the development of a moldedplastic gear pump intended for the very steady deliveryof 50 psi water pressure for amedical application. It willpresent our approach in design, tolerancing, materialselection, molding procedure, and testing to achieveand verify an effective as--molded transmission.ISBN: 978--1--55589--964--6 Pages: 7

09FTM12. The Anatomy of a Micropitting InducedTooth Fracture Failure -- Causation, Initiation,Progression and PreventionAuthors: R.J. Drago, R.J. Cunningham, andS. Cymbala

Micropitting has become a major concern incertain classes of industrial gear applications,especially wind power and other relatively highlyloaded somewhat slow speed applications, where

carburized gears are used to facilitate maximum loadcapacity in a compact package. While by itself theappearance of micropitting does not generally causemuch perturbation in the overall operation of a gearsystem, the ultimate consequences of a micropittingfailure can, and frequently are, much morecatastrophic.

Micropitting is most often associated with parallelaxis gears (spur and helical) however, the authorshave also found this type of distress when evaluatingdamage to carburized, hardened and hard finishedspiral bevel gears.

This paper presents a discussion of the initiation,propagation and ultimate tooth fracture failuremechanism associated with amicropitting failure. Thesubject is presented by way of the discussion ofdetailed destructive metallurgical evaluations ofseveral example micropitting failures that the authorshave analyzed on both parallel axis and bevel gears.ISBN: 978--1--55589--965--3 Pages: 12

09FTM13. Bending Fatigue, Impact Strength andPitting Resistance of Ausformed Powder Metal GearsAuthors: N. Sonti, S. Rao and G. Anderson

Powder metal (P/M) process is making inroads inautomotive transmission applications because ofsubstantially lower cost of P/M steel components forhigh volume production as compared to wrought orforged steel parts. Although P/M gears areincreasingly used in powered hand tools, gear pumps,and as accessory components in automotivetransmissions, P/M steel gears are currently in limiteduse in vehicle transmission applications.

The primary objective of this project was todevelop high strength P/M steel gears with bendingfatigue, impact, and pitting fatigue performanceequivalent to current wrought steel gears. Ausformfinishing tools and process were developed andapplied to powder forged (P/F) steel gears in order toenhance the strength and durability characteristics ofP/M gears, while maintaining the substantive costadvantage for vehicle transmission applications.

This paper presents the processing techniquesused to produce Ausform finished P/F steel gears, andcomparative bending fatigue, impact and surfacedurability performance characteristics of Ausformfinished P/F steel gears, as well as conventionalwrought steel gears.ISBN: 978--1--55589--966--0 Pages: 14

09FTM14. Design Development and Application ofNew High--Performance Gear SteelsAuthors: J.A. Wright, J.T. Sebastian, C.P. Kern, andR.J. Kooy,

A new class of high strength, secondaryhardening gear steels that are optimized forhigh--temperature, low--pressure (i.e., vacuum)carburization is being developed. These alloys werecomputationally designed as secondary--hardeningsteels at three different levels of case hardness. Theexceptional case hardness, in combination with highcore--strength and toughness properties, offer thepotential to reduce drive trainweight or increase power



density relative to incumbent alloys such as AISI 9310or Pyrowear X53.

This new class of alloys utilizes an efficientnano--scale M2C carbide strengthening dispersion,and their key benefits include: high fatigue resistance(contact, bending, scoring); high hardenabilityachieved via low--pressure carburization (thusreducing quench distortion and associatedmanufacturing steps); a tempering temperature of>900F to provide up to a 500F increase in thermalstability relative to incumbent alloys; and core tensilestrengths in excess of 200 ksi. Ferrium C69t, is onealloy in this family that can achieve a carburizedsurface hardness of HRC 67 (with a microstructuresubstantially free of primary carbides), hasexceptionally high contact fatigue resistance whichmake it an excellent candidate for applications such ascamshafts and bearings as well as gear sets.ISBN: 978--1--55589--967--7 Pages: 14

09FTM15. High Performance Industrial GearLubricants for Optimal ReliabilityAuthors: K.G. McKenna, J. Carey, N.Y. Leon, andA.S. Galiano--Roth

In recent years gearbox technology hasadvanced and Original Equipment Manufacturershave required gear oils to meet the lubricationrequirements of these new designs. Moderngearboxes operate under severe conditions andmaintain their reliability to ensure end--userproductivity. The latest generation of industrial gearlubricants can provide enhanced performance evenunder extreme operating conditions for optimalreliability and reduced cost of operation.

This paper describes how gear lubricants functionin gearboxes and discusses the facts vs. myths ofindustrial gear lubricants. The paper will show howadvanced gear lubricant technology can optimize thelife of the gears, bearings and seals, resulting inreduced cost of operation. Opportunities to useadvanced synthetic gear lubricants to achieveoperational benefits in the areas of improved energyefficiency, wider operating temperature ranges,extended oil drain intervals and equipment life will bediscussed.ISBN: 978--1--55589--968--4 Pages: 16

09FTM16. Allowable Contact Stresses of JackingGear Units Used in the Offshore IndustryAuthor: A. Montestruc

An offshore jack--up drilling rig is a barge uponwhich a drilling platform is placed. The barge has legswhich can be lowered to the sea floor to support the rig.Then the barge can be “jacked--up” out of the waterproviding a stable work platform from which to drill foroil and gas. The rack and pinion systems used to raiseand lower the rig are enormous in terms of gear pitch ormodule by gear industry standards. Quarter pitch(101.6 module) pinions are common. Lifetime numberof cycles for these units are -- again, by gear industrystandards – small, as rack teeth typically have 25 yearlifetime cycles measured in the low hundreds. That is

off the charts for AGMA (and ISO or DIN) design ruleswhich draw a straight line to zero cycles for contactstress cycles less than 10,000. Use of any standardswas abandoned from the start in the offshore industryfor jacking applications. The author presentsmethods,and experience of that industry and suggestedallowable contact stresses in such applications.ISBN: 978--1--55589--969--1 Pages: 8

09FTM17. Variation Analysis of Tooth Engagementand Load--Sharing in Involute SplinesAuthors: K. Chase, C. Sorenson and B. DeCaires

Involute spline couplings are used to transmittorque from a shaft to a gear hub or other rotatingcomponent. External gear teeth on the shaft engagean equal number of internal teeth in the hub. Becausemultiple teeth engage simultaneously, they cantransmit much larger torques than a simple key andkeyway assembly. However, due to manufacturingvariations, the clearance between each pair of matingteeth varies, resulting in only partial engagement.

A new model for tooth engagement, based onstatistics, predicts that the teeth engage in asequence, determined by the individual clearances.As the shaft load is applied, the tooth pair with thesmallest clearance engages first, then deflects as theload increases, until the second pair engage. Thus,only a subset of teeth carry the load. In addition, theload is non--uniformly distributed, with the first toothcarrying the biggest share. As a consequence, theload capacity of spline couplings is greatly reduced,though still greater than a single keyway.

This paper discusses the results of a statisticalmodel which predicts the average number of teethwhich will engage for a specified load, plus or minusthe expected variation. The model quantitativelypredicts the load and stress in each engaged pair.Critical factors in the model are the stiffness anddeflection of a single tooth pair and thecharacterization of the clearance. Detailed finiteelement analyses were conducted to verify the toothdeflections and engagement sequence. The closedform statistical results were verified with intensiveMonte Carlo simulations.ISBN: 978--1--55589--970--7 Pages: 14

09FTM18. Does the Type of Gear Action Affect theAppearance of Micro--Pitting and Gear Life?Authors: A. Williston

Early results from testing conducted have raisedquestions concerning the role of gear action with theappearance of micropitting as well as surface fatigue(macropitting). Comparisons between similar gearsets with the same loads, speeds, and lubrication butoperated either as speed increasers or as speedreducers have yielded strikingly different propensitiesfor wear. Further, these observations are not limited tolubrication based failures such as micropitting, but, sofar, have applied to traditional surface fatigue failures(macropitting) as well.

Findings point to an increase in the presence ofmicropitting on gearing operated as speed reducers.All components are operating at the same speed and



load, yet wear is greatly reduced for the drivencomponents.

Perhaps more intriguing is that to date allmacropitting failures have occurred to the drivingpinions of gear sets operated as speed reducers.While the number of samples is decidedly small, thelength of life for these components is much less thanwould be anticipated under smooth loadcircumstances. The other gear sets (operated asspeed increasers) do not show any fatigue wear.

In addition to how gear action affects micropittingin gearing is the question of how the gear action affectsfatigue life. Current gear rating standards are basedupon statistical analysis of real--world experience andmathematical stress--versus--cycle calculations. Ifgear action affects how gearing fails in fatigue, theremay be significant ramifications in the industry.However, before any such conclusion may be made,additional testing is necessary.ISBN: 978--1--55589--971--4 Pages: 30

09FTM19. The Effect of Gearbox Architecture onWind Turbine Enclosure SizeAuthor: C.D. Schultz

Gearbox architecture -- the type of gearing used,the overall gear ratio, the number of increaser stages,the number of meshes, the ratio combinations, and thegear proportions-- can have a profound effect on the”package” size of a wind turbine. In this paper theauthor applies a common set of requirements to avariety of potential gearbox designs for a 2.0 MWwindturbine and compares the resulting ”gearedcomponent” weights, gearbox envelope sizes,generator sizes, and generator weights. Each designoption is also evaluated for manufacturing difficulty viaa relative cost estimate.ISBN: 978--1--55589--972--1 Pages: 19

2008 PAPERS

08FTM01. Parametric Study of the Failure of PlasticGearsAuthors: M. Cassata and Dr. M. Morris

This paper presents the results of collaboration todevelop tools for the prediction of plastic gear toothfailure for any given set of operating conditions and toclassify failure modes of these gears. The goal of theproject is to characterize and predict the failure ofplastic gears over a range of given parameters.

A test plan was developed to explore the effect ofrotational speed, root stress, and flank temperature onthe life of plastic gears. The dependent variable for theexperiments was the number of cycles (or rotations)until failure.ISBN: 978--1--55589--931--8 Pages: 7

08FTM02. A Methodology for Identifying DefectiveCycloidal Reduction Components Using VibrationAnalysis and TechniquesAuthors: V. Cochran and T. Bobak

For several years predictive maintenance hasbeen gaining popularity as method for preventingcostly and time consuming machine breakdowns.Vibration analysis is the cornerstone of predictivemaintenance programs, and the equations forcalculating expected vibration frequencies forbearings and toothed gear sets are widely available.Cycloidal reducers present a special case due to thenature of their reduction mechanism. This paper willdescribe a method for utilizing vibration analysis inorder to identify a defective Cycloidal ring gearhousing, disc, and eccentric bearing.ISBN: 978--1--55589--932--5 Pages: 25

08FTM03. Effects of Gear Surface Parameters onFlank WearAuthors: J.C. Wang, J. Chakraborty, and H. Xu

Non--uniform gear wear changes gear topologyandaffects the noise performanceof a hypoid gear set.This paper presents the effects of gear surfaceparameters on gear wear and themeasurement/testing methods used to quantify theflank wear in laboratory tests. Gear tooth profile,transmission error, gear tooth surface finishdetermined by cutting, and gear tooth surface finishdetermined by other processes are the factorsconsidered in this paper. The measurements includetransmission error, pattern rating, and surfaceroughness before and after test. The effects andinteraction between controlled factors provided theinformation for product improvement. The actionresulted from this study is anticipated to significantlyimprove product reliability and customer satisfaction.ISBN: 978--1--55589--933--2 Pages: 15

08FTM04. The Effect of ManufacturingMicrogeometry Variations on the Load DistributionFactor and on Gear Contact and Root StressesAuthors: D. Houser

Traditionally, gear rating procedures directlyconsider manufacturing accuracy in the application ofthe dynamic factor, but only indirectly through the loaddistribution consider such errors in the calculation ofstresses used in the durability and gear strengthequations. This paper discusses howaccuracy affectsthe calculation of stresses and then uses bothstatistical design of experiments and Monte Carlosimulation techniques to quantify the effects ofdifferent manufacturing and assembly errors on rootand contact stresses. Manufacturing deviations to beconsidered include profile and lead slopes andcurvatures, as well as misalignment. The effects ofspacing errors, runout and center distance variationwill also be discussed.ISBN: 978--1--55589--934--9 Pages: 15



08FTM05. Gear Failure Analysis Involving GrindingBurnAuthors: G.Blake, M. Margetts, and W. Silverthorne

Aerospace gears require post case--hardeninggrinding of the gear teeth to achieve their necessaryaccuracy. Tempering of the case hardened surface,commonly known as grinding burn, occurs in themanufacturing process when control of the heatgeneration at the surface is lost.

A gearboxwithminimal service timewas removedin service from an aircraft, disassembled, and visualinspection performed. Linear cracks along thededendumof theworking gear tooth facewere found inthree adjacent teeth. A detailed inspection of thegearbox found no other components with distress.

AGMA 2007--C00 provides details of the temperetch process and exclusively uses a Nitric acid etchprocess, which is typically used in production qualityinspections. The incident gear was processed forgrinding burn using an Ammonium Persulfate etchsolution. Quality records documented variation inchemical concentration levels during the time thefailed gear was manufactured. A design ofexperiments was conducted to understand the effectsof the factors and interactions that impact thecapability of the Ammonium Persulfate process usedin production to detect griding burn.

Presented are the metallurgical findings, loaddistribution analysis of actual geometry, crackpropagation analysis, and design of experimentresults of the Ammonium Persulfate etch process.ISBN: 978--1--55589--935--6 Pages: 10

08FTM06. Tooth Fillet Profile Optimization for Gearswith Symmetric and Asymmetric TeethAuthors: A. Kapelevich and Y. Shekhtman

Involute flanks are nominally well described andclassified by different standard accuracy grades,depending on gear application and defining theirtolerance limits for such parameters as runout, profile,lead, pitch variation, and others.

The gear tooth fillet is an area of maximumbending stress concentration. However, its profile istypically marginally described as a cutting tool tiptrajectory. Its accuracy is defined by a usuallygenerous root diameter tolerance. The most commonway to reduce bending stress concentration isapplication of the basic (or generating) rack with fullradius.

This paper presents a fillet profile optimizationtechnique based on the FEA and random searchmethod, which allows for a substantial bending stressreduction, by 15 to 30% compared to traditionallydesigned gears. This reduction results in higher loadcapacity, longer lifetime, and lower cost. It includesnumerical examples confirming the benefits of filletoptimization.ISBN: 978--1--55589--936--3 Pages: 11

08FTM07. Planetary Gearset LubricationRequirement Estimation Based on Heat GenerationAuthors: H. Kim, D. Zini, J. Chen and N. Anderson

A planetary gearset is composed of sun gear,planet gears, ring gear, carrier and bearings. As thegearset is in motion under torque, heat is generated atall sliding and rolling contacts for gear meshes andbearing surfaces as lubricant is supplied. Withoutlubrication the gearset cannot operate properlybecause all contact surfaces are influended by heatand subsequent damages. On the other hand,excessive lubrication could cause a significant heatgeneration as churning or dragging losses increase. Itis very important to predict a right amount of lubricationrequired for each component and to supply anecessary amount of lubricant in an effective way.

Empirical data of temperature increase inside aplanetary gearset at different inlet lubricationtemperature, torque and speed are presented withphysical explanation. It has been attempted to utilizeheat generation data as an indicator for requiredlubrication measure and also for gearset efficiencymeasure. Heat generation sources are classified toexamine largest and smallest contributors and thenproject a better way to effective lubrication for theplanetary gearset. Some published gear efficiencyequations are examined with power loss calculationsbased on gearset heat generations which areempirically measured in the present study.ISBN: 978--1--55589--937--0 Pages: 17

08FTM08. PM Materials for Gear ApplicationsAuthors: S. Dizdar, A. Flodin, U. Engström, I. Howeand D. Milligan

The latest material and process developments inpowder metal (PM) gears have increased their loadcapacity. These new developments allow PM to fullycompete with hardened machined wrought gears in avariety of power transmission applications. Newgrades of PM materials that can be case hardenedusing the same conditions as wrought materialsimprove their load capacity. Increased load capacity isalso achieved by surface densifying gear teeth deeperthan case hardened depth requirements. Since toothHertzian and bending stress gradients are within thefully dense layer, PM gears are virtually equivalent towrought gears. The performance is demonstrated bygear tooth bending and RCF data on prototype gears.ISBN: 978--1--55589--938--7 Pages: 9

08FTM09. Concept for aMulti MegawattWind TurbineGear and Field ExperienceAuthors: T. Weiss and B. Pinnekamp

The increasing call for the use of renewableenergy in all industrial countries demands for theextension of wind power generation capacity. Incentral Europe, as in parts of the Americas and Asia,such further expansion is only possible byre--powering -- replacement of existing turbines byhigher rated ones -- or by developing locations in the



open sea -- offshore. To this end, the gear industryworldwide is challenged to develop and supply therequired number of reliable 5 MW class wind turbinegears.

This paper summarizes the concept evaluationand design of the 5 MW MultibridE wind turbinetransmission arrangement, test bed measurementswith the prototype, as well as field experience over atest period of 3 years.ISBN: 978--1--55589--939--4 Pages 11

08FTM10. The Effect of Superfinishing on FZG GearMicropitting – Part IIAuthors: L. Winkelmann and M. Bell

The most common failure mechanism of highlystressed case carburized gears is micropitting (greystaining). The standard FZG gear test (FVA WorkSheet 54) is generally used to determine themicropitting load capacity of gear lubricants. In recentyears, FZG gear testing has also demonstrated itsusefulness for evaluating the effect of superfinishingon increasing the micropitting load capacity of gears.Results from the Technical University of Munich werepreviously presented in Part 1 of this paper. Part II willpresent the results of Ruhr University Bochum. Bothresearch groups concluded that superfinishing is oneof the most powerful technologies for significantlyincreasing the load carrying capacity of gear flanks.ISBN: 978--1--55589--940--0 Pages: 10

08FTM11. Bending Fatigue Tests of Helicopter CaseCarburized Gears: Influence of Material, Design andManufacturing ParametersAuthors: G. Gasparini, U. Mariani, C. Gorla,M. Filippini, and F. Rosa

For helicopter gears many aspects of design andmanufacturing must be analyzed, such as materialcleanliness, case depth and hardness, tooth rootshape and roughness, and compressive residualstresses. Moreover, these gears are designed towithstand loads in the gigacycle field, but are alsosubjected to short duration overloads. Therefore aprecise knowledge of the shape of the S--N curve is ofgreat importance for assessing their in--service life.

A single tooth bending (STB) test procedure hasbeen developed to optimally map gear designparameters and a test program on case carburized,aerospace standard gears has been conceived andperformed in order to appreciate the influence ofvarious technological parameters on fatigueresistance, and to draw the curve shape up to thegigacycles region.

The program has been completed by failureanalysis on specimens and by static tests. Someaccessory investigations, like roughness andmicro--hardness measurements, have also beenperformed. Gigacycle tests confirm the estimationsdone on the basis of the shorter tests, both in term offatigue limit and of curve shapes.ISBN: 978--1--55589--941--7 Pages: 12

08FTM12. In--situ Measurement of Stresses inCarburized Gears via Neutron DiffractionAuthors: R. LeMaster, B. Boggs, J. Bunn, J. Kolwyck,C. Hubbard, and W. Bailey

The total stresses in a mating gear pair arise fromtwo sources: 1) externally induced stressesassociated with the transmission of power, and 2)residual stresses associated with the heat treatmentand machining of the tooth profiles. The stresses dueto power transmission are the result of complex normaland shearing forces that develop during the meshingsequence. The total stress from these two sourcescontributes to the life of a gear.

This paper, funded by the AGMA Foundation,presents the results of research directed at measuringthe total stress in a pair of statically loaded andcarburized spur gears. Measurements were madeusing neutron diffraction methods to examine thechange in total stress as a function of externallyapplied load and depth below the surface. The paperincludes a summary of the various test methods thatwere used and a discussion of their applicability tocarburized gears.ISBN: 978--1--55589--942--4 Pages: 10

08FTM13. Hydrogen & Internal Residual Stress GearFailures -- Some Failure Analyses and Case StudiesAuthor: R. Drago

Hydrogen and internal stress failures arerelatively rare; however, when they occur they areoften very costly and sometimes quite catastrophic.While hydrogen and internal stress issues aregenerally recognized as significant in the design andmanufacture of larger gears, they are also importantfor smaller gears as well.

This paper presents, via illustrated actual casestudies, the mechanisms by which these failure occur,the manner in which they progress, and methods fortesting finished gears for the possibility of internalproblems. In addition, precautionary steps that can betaken during design, manufacture, heat treatment andquality control to minimize the possibility of theseproblems occurring in a finished part along with similarsteps required to prevent any flawed gears fromentering service are also presented and discussed.ISBN: 978--1--55589--943--1 Pages: 11

08FTM14. Effects of Axle Deflection and Tooth FlankModification on Hypoid Gear Stress Distribution andContact Fatigue LifeAuthors: H. Xu, J. Chakraborty, and J.C. Wang

Flank modifications are often made to overcomethe influences of errors coming from manufacturingand assembly processes, as well as deflections of thesystem. This paper presents a semi--analyticalapproach on estimating the axle system deflections bycombining computer simulations and actual loadedcontact patterns obtained from lab tests. By using anexample hypoid gear design, influences of axledeflections and typical flank modifications (lengthwisecrowning, profile crowning and twist) on stressdistribution of the hypoid gear drive are simulated.Finally, several experimental gear samples are made



and tested. Tooth surface topography is examined byusing a Coordinate Measuring Machine. Test resultsare reported to illustrate the effect of tooth flankmodifications on contact fatigue life cycles.ISBN: 978--1--55589--944--8 Pages: 11

08FTM15. Extending the Benefits of Elemental GearInspectionAuthor: I. Laskin

It may not be widely recognized that most of theinspection data supplied by inspection equipmentfollowing the practices of AGMA Standard 2015 andsimilar standards are not of elemental accuracy,deviations but of some form of composite deviations.This paper demonstrates the validity of this“composite” label by first defining the nature of a trueelemental deviation, and then, by referring to earlierliterature, demonstrating how the common inspectionpractices for involute, lead (on helical gears), pitch,and in some cases, total accumulated pitch, constitutecomposite measurements. The paper further explainshowsuchmeasurements often obscure the truenatureof the individual deviations. It also containssuggestions as to some likely source of the deviation invarious gear manufacturing processes, and how thatdeviation may affect gear performance. It furtherraises the question of the likely inconsistencies ofsome of these inspection results and of inappropriatejudgments of gear quality, even to the point of therejection of otherwise satisfactory gears. Finally, thereare proposals for modifications to inspection software,possibly to some inspection routines, all to extendingthe benefits of the basic elemental inspection process.ISBN: 978--1--55589--945--5 Pages: 12

08FTM16. Hob Tool Life Technology UpdateAuthor: T. Maiuri

The method of cutting teeth on a cylindrical gearby the hobbing process has been in existence sincethe late 1800’s. Advances have been made over theyears in both the machines and the cutting tools used.This paper will examine hob tool life and the manyvariables that affect it. It will cover the state of the artcutting tool materials and coatings, hob tool designcharacteristics, process speeds and feeds, hobshifting strategies, wear characteristics, etc. Thepaper will also discuss the use of a commondenominator method for evaluating hob tool life interms of meters [or inches] per hob tooth as analternative to tool life expressed in parts persharpening.ISBN: 978--1--55589--946--2 Pages: 15

08FTM17. Innovative Concepts for Grinding WindPower Energy GearsAuthor: C. Kobialka

Over the past years wind power energy hasgained greater importance to reduce CO2 emissionsand thus antagonize global warming. The

development of wind power is driven by increasedperformance, which requires larger wind turbines andgear boxes. The quality demands of those gears areincreasing while the production cost must decrease.This requires new production methods to grind thegears. Profile grinding is known as a process toachieve highest possible quality, even for complexflank modifications, while threaded wheel grinding isknown for high productivity. New machine conceptsmake it now possible to use both advantages at thesame time.

This paper will show the newest developments forcycle time reduction and increased workpiece qualityusing tool change systems to be able to use differentgrinding wheels for rough and finishing operation,workpiece clamping systems, and concepts ofprocess integration for one workpiece flow.ISBN: 978--1--55589--947--9 Pages: 12

08FTM18. Gear Corrosion During the ManufacturingProcessAuthors: G. Blake and G. Sroka

No matter how well gears are designed andmanufactured, gear corrosion can occur that mayeasily result in catastrophic failure. Since corrosion isoften difficult to observe in the root fillet region or in finepitched gears with normal visual inspection, it maywellgo undetected. This paper presents the results of anincident that occurred in a gear manufacturing facilityseveral years ago that resulted in pitting corrosion andintergranular attack (IGA). It shows that superfinishingcan mitigate the damaging effects of IGA and pittingcorrosion, and suggests that the superfinishingprocess is a superior repair method for corrosionpitting versus the current practice of glass beading.ISBN: 978--1--55589--948--6 Pages: 13

08FTM19. How Are You Dealing With The Bias ErrorIn Your Helical Gears?Author: J. Lange

Using illustrations this paper explains that biaserror (“the twisted tooth phoneme”) is a by--product ofapplying conventional radial crowning methods toproduced crowned leads on helical gears. Themethods considered are gears that are finished,shaped, shaved, form and generated ground. Thepaper explains why bias error occurs in thesemethods, and then addresses what techniques areused to limit/eliminate bias error. Profile and leadinspection charts will be used to detail bias error andthe ability to eliminate it.

The paper details the simultaneous interpolationof multiple axes in the gear manufacturing machine toachieve the elimination of bias error. It also explainsthat CNCmachine software canbeused to predict biaserror, and equally important that it could be used tocreate an “engineered bias correction” to increase theload carrying capacity of an existing gear set.ISBN: 978--1--55589--949--3 Pages: 14



2007 PAPERS

07FTM01. Estimation of Lifetime of Plastic GearsAuthor: S. Beermann

This paper gives an overview on the state of art inplastic gear resistance calculation. The main problemwith plastics is the dependency of the stress cyclecurve (Woehler line) with temperature. Today, moreplastic gears (as in automobile headlights) are used ina high temperature range. Furthermore, flankresistance depends strongly on lubrication (lifetimemay vary by a factor of ten and more, if oil, greaselubricated or dry running).

As no secure data for plastic gears is available,how can nevertheless plastic gear design and life timeprediction be improved?The best strategy is to use thefeedback of existing reducers. Plastic gearboxes,before starting production in big series, are normallysubmitted to endurance tests. If these tests are used tocheck also the real lifetime limits — or by increasingtest length, or by increasing applied torque — theseresults can be used to define the required safetyfactors for future gear design. This procedure hasbeen very successful, and will be described with someexamples.ISBN: 978--1--55589--905--9 Pages: 14

07FTM02. Study of the Correlation BetweenTheoretical and Actual Gear Fatigue Test Data on aPolyamideAuthor: S. Wasson

Fatigue tests have been run on actual moldedgears in order to provide design data, using fullylubricated, plastic on plastic spur gears in atemperature controlled experiment. The purpose ofthe testing is to see if there is a good correlationbetween fatigue data, generated in a lab on test bars,versus the actual fatigue performance in a gear.

In order to do this, the theories of gear calculationsto get root stresses also had to be examined.Advanced FEA showed that there are correctionsneeded to account for high loading or hightemperatures in plastic gears. The chemistry ofvarious nylons used in gears is explained. A highcrystalline nylon has been found which is an excellentmaterial for gears in demanding applications and canwithstand high torques and operating temperatures.The material has very good wear properties andexcellent retention of mechanical properties (strength,stiffness, and fatigue) especially at elevatedtemperatures. Several commercial gear applicationsare currently utilizing these properties. These will beshown to demonstrate the benefits andmanufacturability of this material.ISBN: 978--1--55589--906--6 Pages: 6

07FTM03. Material Integrity in Molded Plastic Gearsand Its Dependence on Molding PracticesAuthor: T. Vale

The quality of molded plastic gears is typicallyjudged by dimensional feature measurements only.This practice overlooks potential deficiencies in the

plastic injection molding process and its effect on theintegrity of the plastic material. These deeper issuesare often not given proper consideration until a relatedgear failure demands its study and evaluation. Thispaper identifies some of these oversights in themolding process, the resultant effect on the plasticmaterial, and discusses their likely effect on short andlong term gear performance.ISBN: 978--1--55589--907--3 Pages: 11

07FTM04. Applying Elemental Gear Measurement toProcessing of Molded Plastic GearsAuthor: G. Ellis

Although elemental gear inspection is rarelyspecified for molded plastic gears, the measurementequipment and practices can be valuable in advancingthe molding processes and improving quality. After abrief description of plastic gear tooling and molding,this paper gives examples of specific elementalmeasurements and relates them to process changesand quality improvements. Such examples for spurand helical gears include: profile measurements,leading to gear mesh noise reduction; leadmeasurement, leading to increased face width loaddistribution and, continuing from that, even to themolding of crowned gears; and index measurement,leading to improved roundness of gears molded fromfiber reinforced plastic materials.ISBN: 978--1--55589--908--0 Pages: 10

07FTM05. Vacuum Carburizing Technology forPowder Metal Gears and PartsAuthors: J. Kowalewski and K. Kucharski,

Carburizing is one of the leading surfacehardening processes applied to the sintered,low--alloyed steel gears in the automotive industry.While diffusion of carbon in wrought steel is welldocumented, this is not the case for PMsteel subject tocarburizing in vacuum furnaces. This paper presentsresults that show that the density of the powder metalis the main factor for the final carbon content anddistribution. Also important is the state of the surface ofthe part; either sintered with open porosity ormachined with closed porosity. The way thecarburizing gasmoves through the furnacemight be ofsome influence as well.ISBN: 978--1--55589--909--7 Pages: 5

07FTM06. Using Barkhausen Noise Analysis forProcess andQualityControl in theProduction ofGearsAuthors: S. Kendrish, T. Rickert and R. Fix

The use of magnetic Barkhausen Noise Analysis(BNA) has been proven to be an effective tool for thenon--destructive detection of microstructuralanomalies in ferrousmaterials. Used as an in--processtool for the detection of grinding burn, heat treatdefects and stresses, BNA is a quick comparative andquantitative alternative to traditional destructivemethods.

This paper presents examples that demonstratehow BNA is used to evaluate changes inmicrostructual properties. Quantitative resultscorrelate BNA test values to X--Ray diffraction valuesfor the detection of changes in residual stress.



Qualitative results correlate BNA test values to acidetch patterns/colors for the detection of grinding burndefects.ISBN: 978--1--55589--910--3 Pages: 5

07FTM07. Grinding Induced Changes in ResidualStresses of Carburized GearsAuthors: R. LeMaster, B. Boggs, J. Bunn, C. Hubbard,and T. Watkins

This paper presents the results of a studyperformed to measure the change in residual stressthat results from the finish grinding of carburizedgears. Residual stresses were measured in five gearsusing the x--ray diffraction equipment in the LargeSpecimen Residual Stress Facility at Oak RidgeNational Laboratory. Two of the gears were hobbed,carburized, quenched and tempered, but not finished.The remaining three gears were processed similarly,but were finish ground. The residual stresses weremeasuredat 64different locations ona tooth fromeachgear. Residual stresses were also measured at fewerpoints on other teeth to determine the tooth--to--toothvariation. Tooth profile measurements were made ofthe finished and unfinished gear samples.

The results show a fairly uniform and constantcompressive residual field in the nonfinished gears.There was a significant reduction in the averageresidual stress measured in the finished gears.Additionally, there was a significant increase in thevariability of the residual stress that was introduced bythe grinding process. Analysis of the data suggests alinear relationship between the change in averageresidual stress and the amount of material removed bythe grinding process.ISBN: 978--1--55589--911--0 Pages: 14

07FTM08. Manufacturing Net Shaped Cold FormedGearsAuthor: D. Engelmann

An innovative metal forming process has beendeveloped for manufacturing quality, durable and costefficient gears for high volume production. In thispaper, the development of net shaped Cold FormedGears (CFG) is presented along with their suitableapplications. The manufacturing technique andequipment is introduced, as well as the advantagesand limitations. Applicable materials and heattreatment practices are also discussed. Gear toothinspection charts are presented and compared toconventional manufacturing methodologies.ISBN: 978--1--55589--912--7 Pages: 7

07FTM09. The Ikona Clutch and DifferentialAuthors: J. Colbourne, V. Scekic, and S. Tesic

This paper describes two devices, a clutch and adifferential, which are based on the Ikona CVT. ThisCVT is essentially an internal gear pair, in which thepinion is mounted on an eccentric that can drive or bedriven by an electric motor/generator, thus providing avariable ratio. Since this arrangement allows for

“branching” of energy flow(s), it can be classified assummation--type CVT.

When theCVT is usedas a clutch, it would replacethe friction--plate clutch in vehicles with standardtransmissions, and the fluid torque converter inautomatic transmissions. The new clutch will bereferred to as the electric torque converter. Any excessenergy is converted into electrical energy, and eitherstored in the battery, or reintroduced into the systemthrough the motor/generator. Modulation of the clutchcan be very smooth which is particularlyadvantageous when the vehicle starts from rest onuphill slopes. Since no friction element is involved, andonly a fraction of torque is being manipulated, themodulation can be repeatable regardless ofconditions. Finally, in a hybrid--vehicle arrangement,the clutch can be used to maintain the engine at itsoptimum speed (within limits), regardless of the roadspeed and the gearbox ratio.

Similar principals apply to the Ikona differential.Unlike today’s limited slip differentials, the Ikonadifferential allows full torque to be transmitted throughone drive wheel, even though the other drive wheelmay have completely lost traction. Unlike traditionaldifferentials that allow wheels to rotate at differentspeeds, the Ikona differential forces the wheels to doso. Accordingly when the vehicle is changing direction,thedifferential canbeused to control the speedof eachdrive wheel, thus providing active torque steering.ISBN: 978--1--55589--913--4 Pages: 6

07FTM10. The Gear Dynamic Factor, Historical andModern PerspectiveAuthors: D. Houser and D. Talbot

The dynamic factor has been included in geardesign and rating formulas since the 1930’s. Itsoriginal formulation was based on an assessment ofentering tooth impacts, but in modern gear designprocedures, where tip relief and leadmodifications arecommon, these impacts may be virtually eliminated.With this elimination, one finds that gear dynamics aremainly excited by steady state phenomena such astransmission error, friction and axial shuttling of themesh force. This paper will first provide a historicalprogression of the dynamic factor equations that arebased on impact theory and will define when thismethodology is appropriate. The paper will thendiscuss the various steady statemodeling approachesand will use one of these approaches to demonstratethe effects of manufacturing deviations on predicteddynamic loads.ISBN: 978--1--55589--914--1 Pages: 11

07FTM11. Helicopter Accessory Gear FailureAnalysis Involving Wear and Bending FatigueAuthors: G. Blake and D. Schwerin

Gear tooth wear is a very difficult phenomenon topredict analytically. The failure mode of wear is closelycorrelated to the lambda ratio, and can manifest intomore severe failure modes, such as bending.Presented is a failure analysis inwhich this occurred. Alegacy aerospace gear mesh experienced ninefailures within a two year time period. The failures



occurred after more than eight years in service andwithin tight range of cycles to one another. Each failureresulted in the loss of all gear teeth with originsconsistent with classic bending fatigue.

Non--failed gears, with slightly lower time than thefailed gears, were removed from service andinspected. Gear metrology measurements quantifieda significant amount of wear. The flank form of theseworn gears was measured and the measured dataused to analytically predict the new dynamic loaddistribution and bending stress. To predict if the failuremode of wear was expected for this gear mesh, anempirical relationship of wear to lambda ratio wascreated using field data from multiple gear meshes inmultiple applications. Presented are the metallurgicalfailure analysis findings, dynamic gear mesh analysis,the empirical wear rate curve developed, and designchanges.ISBN: 978--1--55589--915--8 Pages: 12

07FTM12. The Effect of Start--Up Load Conditions onGearboxPerformanceandLife—FailureAnalysis andCase StudyAuthor: R.J. Drago

Whengearboxes are used in applications inwhichthe connected load has high inertia, the starting torquetransmitted by the gearbox can be much higher thanthe rated load of the prime mover. Power plants oftenrequire several evaporative cooling towers or largebanks of air cooled condensers (ACC) to dischargewaste heat. Because of the very large size of the fansused in these applications, they fall into this category ofhigh inertia starting load devices. When started fromzero speed, a very high torque is required to acceleratethe fan to normal operating speed. If the fan is startedinfrequently and run continuously for long periods oftime, this high starting torque is of minimalsignificance. However, when the fan is started andstopped frequently, the number of cycles at the highstarting torque can accumulate to a point where theycan cause extensive fatigue damage, even if the gearsystem is adequately rated.

Where the gear unit ismarginally rated, very early,catastrophic gear failure is often the result. As part ofthe overall investigation of several failures in suchgearboxes, we measured starting torque on a typicalinstallation, examined many failed gears, andcalculated the load capacity ratings for the gearboxesunder actual operating conditions. This paperdescribes the failures observed, the testingconducted, the data analyses and the effect of the highmeasured starting torque on the life and performanceof the gear systems. The test results revealedsurprising results, especially during starts where thefan was already wind--milling due to natural air flow inthe ACC bank.ISBN: 978--1--55589--916--5 Pages: 12

07FTM13. Influence of Grinding Burn on the LoadCarrying Capacity of Parts under Rolling StressAuthors: F. Klocke, T. Schröder and C. Gorgels

The demand for continuous improvementconcerning economic efficiency of products and

processes leads to an increasing cost pressure inmanufacturing and design of power transmissions.Also, the power density of gears has been increasedwhich leads to a demand for higher gear quality. Inmore and more cases this can only be achieved usinghard finishing processes.

The demand for higher gear qualities leads to anincreased use of gear grinding, which incurs the risk ofthermal damage, such as grinding burn on the gearflank. The influence of thermal damage on the set inoperation is nevertheless hard to judge so thatdamaged gears are often scrapped. This leads toincreasing failure costs.

The lack of knowledge of the effect of grindingburn on the load carrying capacity of gears leads to thepoint that the same degree of damage is judgeddifferently by different companies. Therefore it isnecessary to do trials with thermally damaged parts inorder to know how much a certain degree of thermaldamage influences the load carrying capacity.

The investigations described in this report areaimed at determining the load carrying capacity ofparts under rolling stress. Thermally damaged rollersare employed on a roller test rig, since with thisanalogy process the part geometry is easier todescribe and easier to damage reproducibly.ISBN: 978--1--55589--917--2 Pages: 10

07FTM14. Roughness and Lubricant ChemistryEffects in MicropittingAuthors: A. Olver, D. Dini, E. Lainé, D. Hua, and T.Beveridge

Micropitting has been studied using a discmachine in which a central carburized steel test rollercontacts three, harder, counter--rollers with closelycontrolled surface roughness. Roughness was variedusing different finishing techniques, and the effects ofdifferent oil base--stocks and additives wereinvestigated.

Damage on the test rollers included densemicropitting and “micropitting erosion” in which tens ofmicrons of the test surface were completely removed.This phenomenon is particularly damaging in gearteeth where it has the potential to destroy profileaccuracy. It was found that anti--wear additives led to ahigh rate of micropitting erosion, and the effectcorrelated more or less inversely with simple slidingwear results. There were also appreciable effects frombase--stock chemistry.

The key parameter affecting the severity ofdamage seemed to be the near--surface shear stressamplitude arising from the evolved roughness;different chemistries led to the evolution of differentroughness during initial running and to differentcontact stresses and levels of damage.ISBN: 978--1--55589--918--9 Pages: 8

07FTM15. Experience with a Disc Rig MicropittingTestAuthors: M. Talks and W. Bennett

The experimental work carried out was aimed atdeveloping a test method that was able to consistentlyproduce micropitting damage and could discriminate



between a good oil (i.e., one that rarely producesmicropitting in service) and a poor oil (i.e., one thatdoes produce micropitting in service).

The disc rig control systemallows test parameterssuch as entrainment velocity, contact stress andslide/roll ratio at the disc/roller contacts to beaccurately and independently controlled. This enablesthe effect of key parameters to be studied in isolation,which is something that cannot be easily achievedusing conventional gear test rigs.

A test procedure has been developed whichprovides a good level of repeatability anddiscrimination between oils. In addition, a study of theeffect of slide/roll ratio (SRR) has shown that theseverity of micropitting damage increases as SRRincreased, whereas at 0% SRR no micropittingoccurred, and, at negative SRRs, microcrackingoccurred, but notmicropitting. This is theway that SRRseems to affect micropitting in gears.ISBN: 978--1--55589--919--6 Pages: 9

07FTM16. Straight Bevel Gear Cutting and Grindingon CNC Free Form MachinesAuthor: H. Stadtfeld

Manufacturing of straight bevel gears was in thepast only possible on specially dedicated machines.One type of straight bevel gears are those cut with acircular cutter with a circumferential bladearrangement. The machines and the gears theymanufacture have theGleason trade nameConiflex.The cutters are arranged in the machine under anangle in an interlocking arrangement which allows acompleting cutting process. The two interlockingcutters have to be adjusted independently duringsetup, which is complicated and time consuming.

The outdated mechanical machines have neverbeen replaced by full CNCmachines, but there is still aconsiderable demand in a high variety of low quantitiesof straight bevel ears. Just recently it was discoveredthat it is possible to connect one of the interlockingstraight bevel gear cutter disks to a free form bevelgear generator and cut straight bevel gears of identicalgeometry compared to the dedicated mechanicalstraight bevel gear generator. A conversion based onavector approach delivers basic settings as they areused in modern free form machines. The advantagesare quick setup, high accuracy, easy corrections andhigh repeatability.ISBN: 978--1--55589--920--2 Pages: 10

07FTM17. Simulation Model for the Emulation of theDynamic Behavior of Bevel GearsAuthors: C. Brecher, T. Schröder and A. Gacka

The impact of bevel gear deviations on the noiseexcitation behavior can only be examined undervarying working conditions such as different rotationalspeed and torque. The vibration excitation of bevelgears resulting from the tooth contact is primarilydetermined by the contact conditions and the stiffness

properties of the gears. By the use of a detailed toothcontact analysis, the geometry based gear propertiescan be developed and provided for a dynamicalanalysis of the tooth mesh.

A model has been developed for the simulation ofthe dynamic behavior of bevel gears. With the aid of aload--free tooth contact analysis, the geometry--basedpart of the path excitation is determined. With a toothcontact analysis under load, the path excitationcaused by deflections can be calculated. Thegeometry based part of the path excitation and acharacteristic surface of the excitation values iscreated and provided for dynamic simulation.

This dynamic model is able to consider everydeviation of the micro-- and macrogeometry from theideal flank topography, i.e., waves and/or grooves inthe surface structure, in combination with two andthree dimensional flank deviations like profiledeviations, helix deviations and twists. It is alsopossible to consider the influence of friction and thecontact impact caused by load and/or manufacturingerrors with a test rig to verify the calculations.ISBN: 978--1--55589--921--9 Pages: 8

07FTM18. Bevel Gear ModelAuthor: Ted Krenzer

The paper presents a method for developing anaccurate generic bevel gear model including both theface milling and face hobbing processes. Starting withgear blank geometry, gear and pinion basic generatormachine settings are calculated. The contact patternand rolling quality are specified and held to the secondorder in terms of pattern length, contact bias andmotion error. Based on the setup, a grid of tooth pointsare found including the tooth flank, fillet and, if it exists,the undercut area. It is proposed as the model for thenext generation of bevel gear strength calculations inthat the procedure produces true bevel gear geometry,uses blank design parameters as input and is vendorindependent except for cutter diameter.ISBN: 978--1--55589--922--6 Pages: 10

07FTM19. How to Determine theMTBF of GearboxesAuthor: G. Antony

Mean Time Between Failures (MTBF) became afrequently used value describing reliability ofcomponents, assemblies, and systems. While MTBFwas originally introduced and used mainly inconjunction with electronic components and systems,the definition and application for mechanicalcomponents, such as gearboxes, is not broadlyavailable, used, or recognized. In the field of gears it isdifficult to obtain an MTBF from the manufacturer dueto the lack of applicable, generally recognizeddefinitions and standards. The paper will evaluate,compare and suggest ways in determining a gearboxMTBF based on the already established, proven,design calculation standards and test methods used inthe gear design.ISBN: 978--1--55589--923--3 Pages: 9



2006 PAPERS

06FTM01. The Effects of Super Finishing on BendingFatigueAuthor: G. Blake

A super finishing study was designed andconducted for bending fatigue. AMS6265 parts werecreated: with and without super finishing. Bendingfatigue was tested using Single Tooth Fatigue (STF)and RRMoore rotating beammethods. The STF partswere designed with tooth geometry replicating a spiralbevel gear section. Two lots of material wereprocessed. Thus, a minimum of two carburized andhardened lots, two shot peen batches and two superfinishing cycles (if applicable) were processed persample group. A detailed metallurgical evaluation wasperformed to characterize thematerial and compare toactual spiral bevel gears. Analysis of the test dataconcluded no statistical difference in bending fatiguestrength.ISBN: 1--55589--883--1 Pages: 14

06FTM02. Isotropic Superfinishing of S--76C+ MainTransmission GearsAuthors: B. Hansen, M. Salerno and L. Winkelmann

Isotropic superfinishing was applied to the thirdstage spur bull gear and mating pinions along with thesecond stage bevel gears of a Sikorsky S--76C+ maingearbox. The gearbox completed the standardAcceptance Test Procedure (ATP) and a 200--hourendurance test. During these tests noise, vibration,and operating temperatures were shown to besignificantly reduced due to lower friction. Adescription of the tests, performance data and ageneral description of the process is presented.ISBN: 1--55589--884--X Pages: 12

06FTM03. Detailed Procedure for the OptimumDesign of an Epicyclic Transmission Using PlasticGearsAuthors: I. Regalado and A. Hernández

Shows the steps to get an optimum (volumebased) design for an epicyclic transmission usingplastic materials, the tooth proportions of ANSI/AGMA1006--A97, the recommendations given inANSI/AGMA 6023--A88, and ANSI/AGMA 2101--C95.It gives the effect of changing the number of planets,the bending fatigue and contact strength of the plasticmaterials, and the temperature effects on the size ofthe gears. The design procedure starts with apreliminary analysis of gear performance in aproposed (not optimized) transmission, going step bystep to an optimumdesign for thegiven load conditionsand expected minimum life.ISBN: 1--55589--885--8 Pages: 11

06FTM04. Precision Planetary Servo GearheadsAuthors: G.G. Antony and A. Pantelides

Automatedmachines use servomotors to performcomplex motions. Planetary gearheads are frequentlyused in conjunction with servomotors to match theinertias, lower the speed, boost the torque, and at thesame time provide a mechanical interface for pulleys,

cams, drums and other mechanical components. Thispaper covers topics such as: reasons why planetarygear systems are chosen for “servo applications”;what influences the planetary servo gear positioningaccuracy and repeatability; rating practices toestablish a “comparability” of different torques; and, anintroduction of a simple method to determine therequired gearbox torque rating for a servo--applicationbased on motor torque data.ISBN: 1--55589--886--6 Pages: 11

06FTM05. Development of a Gear Rating Standard --A Case Study of AGMA 6014--A06Author: F.C. Uherek

The AGMA Mill Gearing Committee completedAGMA 6014 for grinding mill and kiln service gearrating. The approach the committee took in thedevelopment of this standard to determine the contentis reviewed. Through a review of previous standards,the performance history of applications for long life(over 20 years), and considering the large gear size,the committee achieved consensus on a ratingmethod, which was derived from ANSI/AGMA2001--D04. A factor comparison between 6014 and2001 is presented, as well as their interaction, toexplain the goal of the committee to develop adocument that reflects actual field experience ofin--service operating gear sets.ISBN: 1--55589--887--4 Pages: 8

06FTM06. An Analytical Approach to the Prediction ofMicropitting on Case Carburised GearsAuthors: D. Barnett, J.P. Elderkin and W. Bennett

Micropitting is an area of gear failure thatinfluences gear noise and transmission error. Thispaper outlines an approach to analysing micropittingby looking at the critical factors for a given gear design.A practical procedure, which incorporates athree--dimensional spring model, was used to predictthe micropitting wear rate and the position that wearwould take place on test gear pairs. Case studies havebeen included that directly compare the predictedlevels of micropitting with those actually measured. Asimplified formulation suitable for manual calculationsare also discussed.ISBN: 1--55589--888--2 Pages: 15

06FTM07. Improvement of Standardized TestMethods for Evaluating the Lubricant Influence onMicropitting and Pitting Resistance of CaseCarburized GearsAuthors: B.--R. Höhn, P. Oster, T. Radev, G.Steinberger and T. Tobie

Micropitting and pitting are fatigue failures thatoccur on case carburized gears. The performance oflubricants in regard to micropitting and pitting can beevaluated by test methods. TheFVA--FZG--micropitting test consists of two parts: aload stage test followed by an endurance test. Thetests require relatively high costs and are timeconsuming. Therefore an analogous short test methodwas developed to classify candidate lubricants, andsupplement the existing test. The results of the shorttestmethodaregiven. TheFVA--FZG--pitting test is for



limited--life using test gears, which are ground withoutcontrolled profile or helix modifications. Although theflank roughness is restricted, the appearance ofmicropitting can cause a wide statistical spread ofpitting test life. Thus, therewas potential improvementin the test results reproducibility. In the test gears weresuperfinished to prevent micropitting, and given flankmodifications for improved test relevance. The paperdescribes test procedures and shows basic examplesof test results.ISBN: 1--55589--889--0 Pages: 11

06FTM08. An Evaluation of FZG Micropitting TestProcedures and Results for the Crowned AGMA TestGearsAuthors: D.R. Houser, S. Shon and J. Harianto

This paper reports on surface fatigue testing. Thegoal was to develop models for predicting wear. Aspart of this goal, the study reports on developing anunderstanding of the stresses and wear predictorsusing FZG tests. Since the focus was on micropitting,the first tests used the method described in FVAInformation Sheet No. 54/I--IV. Later, the procedurewas modified to account for higher contact stresslevels that are predicted for the heavily crownedand tiprelievedAGMA test gears that weremanufactured as apart of the AGMA tribology test program. This paperprovides extensive analysis that includes detailedtopography measurements of the tooth profiles,predictions of contact stresses and contact patterns. Itdiscusses factors that affect contact stresses, flashtemperatures, and test film thickness.ISBN: 1--55589--890--4 Pages: 12

06FTM09. Opportunities to Replace Wrought Gearswith High Performance PM Gears in AutomotiveApplicationsAuthors: U. Engström, D. Milligan, P. Johansson andS. Dizdar

Powder metallurgy (PM) enables production ofcomponents with complex geometries such as gears.The cost effective use of PM components inautomotive applications has showed a continuousgrowth. This growth is due to the the net shapecapability, while maintaining performance. Gears forautomotive applications are complex in shape andrequire both geometrical accuracy and highmechanical performance in terms of tooth durability.By utilizing selective densification of the teeth, theseperformance requirements can bemet at a low cost. Inthis paper a PM process consisting of compaction,sintering, surface densification, and finally heattreatment has been studied to assess the feasibility ofproduction. Helical and spur gears were used wherethe densification, as well as the resulting gear qualityand durability, were tested.ISBN: 1--55589--891--2 Pages: 7

06FTM10. Fabrication, Assembly and Test of a HighRatio, Ultra Safe, High Contact Ratio, Double HelicalPlanetary Transmission for Helicopter ApplicationsAuthors: F.W. Brown, M.J. Robuck, M. Kozachyn, J.R.Lawrence and T.E. Beck

An ultra--safe, high ratio planetary transmission,for application as a helicopter main rotor final drive,has been designed, fabricated and tested. Thetransmission improvements are reduced weight,reduced noise and improved fail--safety and efficiency.This paper discusses the fabrication, assembly andtesting of the planetary transmission. An existingplanetary transmission utilized a two--stageconventional spur gear design with fixed internal ringgears. The newdouble helical planetary (DHP) systemdesign uses a compound planetary arrangement withstaggered planets and high contact ratio gearing in aunique configuration. Double helical gears in theplanet to ring meshes balance axial tooth forceswithout axial planet bearing reactions. The spur gearsun to planet meshes are staggered to achieve acompact arrangement. The sun gear is fully floating.ISBN: 1--55589--892--0 Pages: 12

06FTM11. On Tooth Failure Analysis in Small--Teeth--Number Gearing: An Analytical ApproachAuthor: S.P. Radzévich

This paper is an analytical study of tooth failure ingearing having small numbers of teeth. For theanalysis, tooth contact stresses and combined shearstresses are investigated. The study is based on geartooth loading, accounting for load variations with timeand other gear parameters in various phases of toothmeshing. The contact and shear stresses are bysimultaneous: (a) contact stresses together with (b)stresses caused by the pinion and gear sliding. Whiledeveloped for use in gearing with low numbers ofteeth, the method can be used for computation ofstresses in gearing having more teeth. The results ofthe research could be used with AGMA 908--B89 forgears having less than 12 teeth.ISBN: 1--55589--893--9 Pages: 22

06FTM12. A Crane Gear Failure Analysis -- CaseStudy, Observations, Lessons Learned,RecommendationsAuthor: R.J. Drago

The gearboxes used in cranes have proventhemselves to be reliable. However, some gearfailures have caused a reevaluation of the design,configuration, and manufacture of gearboxes in largecranes. Since crane gearboxes do not operatecontinuously, gear system fatigue characteristics havenot been in the forefront of system operation. Studieshave indicated that in many cases usage rates,loading, and in many cases both, have increased. Insome applications, crane usage has increased byfactors of two, or three, or evenmore, and gear loadinghas similarly increased. This higher usage makes thecumulative effects of fatigue much more important.



This paper presents a case study of one particularcrane gear failure, including failure analysis andresultant remedial actions, along with a discussion ofthe results and implications from extensive gearboxinspections that were conducted as a result of theinitial failure.ISBN: 1--55589--894--7 Pages: 10

06FTM13. Economic Aspects of Vacuum CarburizingAuthor: J. Kowalewski

This paper presents the aspects of vacuumcarburizing technology that have an impact on processcosts and quality improvements in the final product.There is an interest in furnaces for vacuum carburizingdue to the demand for products with overallmetallurgical quality and low unit cost. Vacuumcarburizing technology produces work with minimumdistortion, and desired surface metallurgy. Systemscanprovide “cold to cold” (coldwork going in, coldworkcoming out) and fully automatic operation that reducesoperator involvement, thus minimizing labor.Considering upstreamand downstream requirements,vacuum carburizing can provide a total reduction ofcosts. This technology differs considerably fromtraditional gas carburizing both in the equipment usedand in the process economy.ISBN: 1--55589--895--5 Pages: 6

06FTM14. The Optimal High Speed Cutting of BevelGears -- New Tools and New Cutting ParametersAuthor: H.J. Stadtfeld

High speed carbide dry cutting improvementshave a dependency of many important parametersupon the particular job situation, which makes itdifficult for a manufacturing engineer to establish anoptimal cutting scenario. An analysis of the differentparameters and their influence on the cutting process,allows the establishment of five, nearly independentareas of attention: blade geometry and placement inthe cutter head; cutting edge micro geometry; surfacecondition of front face and side relief surfaces; speedsand feeds in the cutting process; and, kinematicrelationship between tool and work (climb orconventional cutting, vector feet). This paper presentsexplanations and guidelines for optimal high speedcutting depending on cutting method, part geometryand manufacturing environment. Also, how to choosethe blade system, thus giving the manufacturingengineer information to support optimizing cutterperformance, tool life and part quality.ISBN: 1--55589--896--3 Pages: 13

06FTM15. Optimal ToothModifications in Spiral BevelGears Introduced by Machine Tool Setting VariationAuthor: V. Simon

A method for the determination of optimal toothmodifications in spiral bevel gears based on loaddistribution, minimized tooth root stresses, andreduced transmission errors is presented.Modifications are introduced into the pinion toothsurface considering the bending and shearingdeflections of gear teeth, local contact deformations ofmating surfaces, gear body bending and torsion,

deflections of the supporting shafts, andmanufacturing and alignment of mating members. Byapplying a set of machine tool setting parameters, themaximum tooth contact pressure can be reduced by5.4%, the tooth fillet stresses in the pinion by 8% andthe angular position error of the driven gear by 48%,based on a spiral bevel gear pair manufactured bymachine tool settings determined by a commonly usedmethod.ISBN: 1--55589--897--1 Pages: 12

06FTM16. Certificate for Involute Gear EvaluationSoftwareAuthor: F. Härtig

A test for the verification of involute gear softwarehas been developed at the Physikalisch--TechnischeBundesanstalt (PTB). This paper shows the criticalinfluence on measurement uncertainty of uncertifiedinvolute evaluation software. Beside the testparameter information, the most dominant effects ofsoftware errors will be explained. The algorithmsdeveloped during this project should influence andhelp complete the existing standards and theirguidelines.ISBN: 1--55589--898--X Pages: 5

2005 PAPERS

05FTM01. Fine Pitch, Plastic Face Gears: Design andManufactureAuthors: I. Laskin and E. Reiter

Face gear technology has attracted attention.Products benefiting include those which use moldedplastic gears. More applications could benefit,justifying the need for more information on the specialfeatures of face gears, their design and manufacture,in comparison to other non--parallel--shaft gears. Adescription of manufacturing methods, particularly inplastic molding is given with inter--related design andgear performance issues. New methods of graphicmodeling are included with descriptions of face gearconfigurations and applications.ISBN: 1--55589--849--1 Pages: 11

05FTM02. The Effects of Pre Rough MachineProcessing on Dimensional Distortion DuringCarburizingAuthor: G. Blake

A study to isolate the influence of pre--roughmachine processing on final dimensional distortion.Methods are discussed to aid process developmentand minimize dimensional change during carburizing.The study examined the distortion during carburizingbetween five possible rawmaterial starting conditions.Coupons were used and manufactured from eachpopulation of material processing. Dimensions weremade before and after carburizing using a scanningcoordinate measurement machine. The results showthat dimensional distortion during carburizingincreases with mechanical and thermal processing.ISBN: 1--55589--850--5 Pages: 18



05FTM03. Modelling Gear DistortionAuthor: P.C. Clarke

Dealing with carburize case hardened geardistortion and growth is a challenge for the global gearindustry. Attempts started in 1978 with computerprograms to calculate distortion and growth, plusresidual stress distributions for a gear and evolved bygathering distortion data for a wide range of sizes,shapes, grinding allowances with trends for differentgeometries. A spread sheet program with geardimensional input, calculates the distortions andgrowths, and then calculates the modified dimensionsfor required protuberance and the minimumcarburized case depth. Case histories illustrate theconsequences of various geometries and futuredevelopments are discussed.ISBN: 1--55589--851--3 Pages: 12

05FTM04. Tooth Meshing Stiffness OptimisationBased on Gear Tooth Form Determination for aProduction Process Using Different ToolsAuthors: U. Kissling, M. Raabe, M. Fish

The variation of the tooth meshing stiffness is asource of noise and the exact calculation of tooth formis important for the stiffness determination. For thispurpose, software was written with the concept of anunlimited number of tools such as hobs, grinding disk,and honing defining a manufacturing sequence.Stiffness variation can be improved by optimization offinal gear geometry with a calculation of the contactpath under load. The meshing stiffness is derivedmaking it possible to study the effect of a proposedprofile correction of a gear under different loads.Calculations with AGMA2001 or ISO6336 check thepoint with the highest root stress. Effect of a grindingnotch is also included.ISBN: 1--55589--852--1 Pages: 11

05FTM05. Computerized Design of Face HobbedHypoid Gears: Tooth Surface Generation, ContactAnalysis and Stress CalculationAuthors: M. Vimercati and A. Piazza

Face milled hypoid gears have been widelystudied. Aim of this paper is just to propose anaccurate tool for computerized design of face hobbedhypoid gears. A mathematical model able to computedetailed gear tooth surface is presented. Then, theobtained surfaces will be employed as input for anadvanced contact solver that, using a hybrid methodcombining finite element techniquewith semianalyticalsolutions, is able to efficiently carry out contactanalysis under light and heavy loads and stresscalculation of these gears.ISBN: 1--55589--853--X Pages: 13

05FTM06. A Model to Predict Friction Losses ofHypoid GearsAuthors: H. Xu, A. Kahraman and D.R. Houser

A model to predict friction--related mechanicalefficiency losses of hypoid gear pairs is proposed,which combines a commercial available finite elementbased gear contact analysis model and a frictioncoefficient model with a mechanical efficiency

formulation. The contact analysis model is used toprovide contact pressures and other contactparameters required by the friction coefficientmodel.The instantaneous friction coefficient is computed byusing a validated formula that is developed based on athermal elastohydrodynamic lubrication (EHL) model.Computed friction coefficient distributions are thenused to calculate the friction forces and the resultantinstantaneous mechanical efficiency losses of thehypoid gear pair at a given mesh angle. The model isapplied to study the influence of speed, load, surfaceroughness, and lubricant temperature as well asassembly errors on the mechanical efficiency of anexample face--hobbed hypoid gear pair.ISBN: 1--55589--854--8 Pages: 15

05FTM07. Spiral Bevel and Hypoid Gear CuttingTechnology UpdateAuthor: T.J. Maiuri

Spiral bevel and hypoid gear cutting technologyhas changed significantly over the years. Themachines, tools, materials, coatings and processeshave steadily advanced to the current state of the art.This paper will cover the progression frommechanicalmachines with complex drive trains using the five cutmethod of cutting gears with coolant, to machines withdirect drive CNC technology dry cutting gears by thecompleting method with carbide and high speed steeltools. The latest cutting toolmaterials and tool coatingswill be discussed. Production examples from theautomotive and truck industries will be provided, aswell as examples from the gear jobbing industry.ISBN: 1--55589--855--6 Pages: 20

05FTM08. New Developments in Tooth ContactAnalysis (TCA) and Loaded TCA for Spiral Bevel andHypoid Gear DrivesAuthors: Q. Fan and L. Wilcox

Tooth Contact Analysis (TCA) and Loaded ToothContact Analysis (LTCA) are two powerful tools for thedesign and analysis of spiral bevel and hypoid geardrives. TCA and LTCA respectively simulate gearmeshing contact characteristics under light load andunder significant load. Application of CNC hypoid geargenerators has brought new concepts in design ofspiral bevel and hypoid gears with sophisticatedmodifications. This paper presents new developmentsin TCAand LTCAof spiral bevel and hypoid gears. Thefirst part of the paper describes a new universal toothsurface generation model with consideration ofcapabilities of CNC bevel gear generators. Theuniversal model is based on the kinematical modelingof the basic machine settings and motions of a virtualbevel gear generator which simulates the hypoid geargenerator and integrates both face milling and facehobbing processes. Mathematical descriptions of geartooth surfaces are represented by a series ofcoordinate transformations in terms of surface pointposition vector, unit normal, and unit tangent.Accordingly, a generalized TCA algorithm andprogram are developed. In the second part of thispaper the development of a finite element analysis(FEA) based LTCA is presented. The LTCA contact



model is formulated using TCA generated toothsurface and fillet geometries. The FEA modelsaccommodate multiple pairs of meshing teeth toconsider a realistic load distribution among theadjacent teeth. An improved flexibility matrix algorithmis formulated by introducing specialized gap elementswith considerations of deflection and deformation dueto tooth bending, shearing, local Hertzian contact, andaxle stiffness. Two numerical examples, aface--hobbing design and a face milling design, areillustrated to verify the developed mathematicalmodels and programs.ISBN: 1--55589--856--4 Pages: 12

05FTM09.Hypoid Gear LappingWear Coefficient andSimulationAuthors: C. Gosselin, Q. Jiang, K. Jenski andJ. Masseth

Hypoid gears are usually hard finished after heattreatment using lapping. Because of the rolling andsliding motion inherent to hypoid gears, the lappingcompound abrades and refines the tooth surface toachieve smoothness in rolling action and produce highquality gear sets. The pinions and gears are lapped inpairs and must therefore remain as coordinated pairsfor the rest of their lives. However, heat treatmentdistortion can vary significantly. Thus, developing alapping sequence for manufacturing requires bothtime and experienced technicians who can establishlapping operating positions and sequence times toproduce quality gear sets both in terms of performanceand cost. This development is generally trial and error.In this paper, the lapping process is simulated usingadvanced modelling tools such as gear vectorialsimulation for the tooth surfaces and path of contactand reverse engineering to analyze the tooth contactpattern of existing gear sets under load (static LTCA).Test gear sets are measured using a CMM prior to aspecial lapping cycle where the position of the gearsets on the lapper does not change, and thenre--measured after lapping in order to establish howmuch, and where, material was removed. A wearconstant named ”wear coefficient” specific to thelapping compound composition is then calculated.Based on the obtained wear coefficient value, analgorithm for simulating the lapping process ispresented. Gear sets lapped on the production line areused for simulation case studies.Results show that it ispossible to predict how much and where material willbe removed, thereby opening the door to betterunderstanding of the lapping process.ISBN: 1--55589--857--2 Pages: 16

05FTM10. Finite Element Study of the Ikona GearTooth ProfileAuthors: J.R. Colbourne and S. Liu

The Ikona gear tooth profile is a patentednon--involute tooth profile for internal gear pairs.Gearswith this profile have the following properties: the teethare conjugate; the contact ratio is very high; there is notip interference, even when only a one--toothdifference between the pinion and internal gear; thereis minimal backlash; and the gears can be cut on

conventional gear--cutting machines. Large reductionratios can be achieved by a single gear pair and a highcontact ratio results in lower tooth stresses than for asimilar involute gear. Plus, minimal backlash makesthe Ikona profile ideal for many applications, such asservo--drives, medical prostheses, and robots. Stressanalysis of these gears assumes that the contact forceis equal at each contacting tooth pair. Finite elementresults demonstrate how the number of tooth pairs incontact may increase under load. Finally, an estimatewill be presented, showing the variation of tooth forcebetween the contacting teeth.ISBN: 1--55589--858--0 Pages: 9

05FTM11. Low Loss GearsAuthors: B.--R. Höhn, K. Michaelis and A. Wimmer

In most transmission systems one power losssources is the loaded gear mesh. High losses lead tohigh energy consumption, high temperatures, early oilageing, increased failure risk and high coolingrequirements. In many cases high efficiency is not themain focus and design criteria as load capacity orvibration excitation predominate the gear shapedesign. Those design criteria can counteract highefficiency. The influences of gear geometryparameters on gear efficiency, load capacity, andexcitation are shown. Design preference guidelinescanbe followed to a varying extent which leads tomoreor less unconventional, but more efficient gear design.Low loss gears can save substantial energy incomparison to conventional gears. The power lossreduction is dependent on the operating conditionsand can add up to 70% of the power loss ofconventional gears. Such low loss gears havesignificant advantages in terms of energyconsumption, heat development, and coolingrequirements.ISBN: 1--55589--859--9 Pages: 11

05FTM12.Modal Failure Analysis of a Gear and DriveRing AssemblyAuthor: D.D. Behlke

After years of successful reliable applications, acomponent failure on a new application cannot beexplained with static stress analyses,modal failureanalyses may be required. Finite element modalanalyses was used to identify the mode and itsfrequency that cause a high range gear and drive ringassembly to fail prematurely. ACampbell Diagramwasused to identify modes in the operating range of asix--speed transmission that could cause the drive ringto fail. Redesigning the assembly to move the criticalmodes out of the operating range is described.ISBN: 1--55589--860--2 Pages: 8

05FTM13. Evaluation of the Scuffing Resistance ofIsotropic Superfinished Precision GearsAuthors: P.W. Niskanen, B. Hansen andL. Winkelmann

Aerospace gears are often engineered to operatenear the upper bounds of their theoretical designallowables. Due to this, scuffing is a primary failuremode for aerospace gears. Isotropic superfinishingimproved Rolling/Sliding Contact Fatigue up to nine



times that of baseline test specimens. Testsdemonstrated the ability to successfully carry 30percent higher loads for at least three times the life ofthe baseline samples. A study was conducted onactual gears having an isotropic superfinish. Thisstudy showed superfinishing technology increased agear’s resistance to contact fatigue by a factor of three,and increased bending fatigue resistance by at least10 percent. The paper discusses an additional studywhich is underway to determine the scuffing resistanceof isotropic superfinished aerospace gears to that ofbaseline ground gears. These tests were conductedusing a method that progressively increases lubricanttemperature until scuffing occurs, rather than thetraditional load increasingmethod used in FZG testingrigs. The results of the current testing reveals thatisotropic superfinished SAE 9310 specimens show atleast a 40 Fhigher lubricant temperature at the point ofscuffing compared to as--ground baseline gears.ISBN: 1--55589--861--0 Pages: 10

05FTM14. Determining the Shaper Cut Helical GearFillet ProfileAuthor: G. Lian

This paper describes a root fillet form calculatingmethod for a helical gear generated with a shapercutter. The shaper cutter considered has an involutemain profile and elliptical cutter edge in the transverseplane. Since the fillet profile cannot be determinedwithclosed form equations, a Newton’s approximationmethod was used in the calculation procedure. Thepaper will also explore the feasibility of using a shapertool algorithm for approximating a hobbed fillet form.Finally, the paper will also discuss some of theapplications of fillet form calculation procedures suchas form diameter (start of involute) calculation andfinishing stock analysis.ISBN: 1--55589--862--9 Pages: 16

05FTM15. Repair of Helicopter GearsAuthors: S. Rao, D. McPherson and G. Sroka,

In order to reduce costs by extending theoperational life of the sun and input pinion gears of ahelicopter transmission, scraped gears were subjectto a superfinishing process. This process was found toremove minor foreign object damage by uniformlyremoving a minimal amount of material on the gearteeth, while meeting original manufacturingspecifications for geometry. The process also resultedin enhanced surface quality and did not exhibitdetrimental metallurgical effects on the surface orsub--surface of the teeth. The process was also foundto eliminate gray staining, an early precursor to pitting.This paper describes the results of the helicopter gearrepair project and includes the geometry andmetallurgical evaluations on the repaired gear. Furthereffort to characterize the durability and strengthcharacteristics of the repaired gear is ongoing.ISBN: 1--55589--863--7 Pages: 9

05FTM16. CH47D Engine Transmission Input PinionSeeded Fault TestAuthors: J.P. Petrella, J.S. Kachelries and S.M. Holder,and T.E. Neupert

This paper summarizes an Engine TransmissionInput Pinion Seeded Fault Test that was accomplishedas a portion of the validation process for theTransmission Vibration Diagnostic System (TVDS)Analyzer. The test specimen was a high speed enginetransmission input pinion with a known defect (i.e.,seeded fault) machined into a high stress area of agear tooth root. During the testing, the TVDS analyzermonitored the test pinion real time to provide asufficient warning time of the impending failure. TheTVDS data was evaluated along with a post--testevaluation of the fatigue crack. During the post--testfractographic evaluation, arrest lines and fatiguestriations were analyzed to develop crack propagationdata as a function of the number of applied load cycles.This data was then correlated to better understand thepotential warning signals the TVDS system couldprovide that would allow the pilot enough time tounload the suspect engine transmission.ISBN: 1--55589--864--5 Pages: 11

05FTM17. Influences of Bearing Life Considerationson Gear Drive DesignAuthor: F.C. Uherek

Historically, catalog gear drives have beendesigned with 5000 hours of L10 bearing life at servicefactor 1.0 power. Advances in bearing analysismethods have brought new considerations to thedesign and selection process. The impact of newmodeling techniques, additional considerations, andvarious extensions to the traditional bearing fatiguecalculations are explored. The modeling of thesevarious additions to a traditional catalog L10calculation is illustrated by bearing selections forcases of single, double, and triple reduction geardrives. A roadmap is presented listing criticalconsiderations when applying various bearingmanufacturer recommendations.ISBN: 1--55589--865--3 Pages: 13

05FTM18. Planet Pac: Increasing Epicyclic PowerDensity and Performance through IntegrationAuthor: D.R. Lucas

Epicyclical gear systems are typically equippedwith straddle--mounted planetary idlers and aresupported by pins on the input and output sides of acarrier. These carriers can be either one--piece ortwo--piece carrier designs. Traditionally many of thehigher power rated epicyclic gear systems usecylindrical roller bearings to support the planetarygears. This paper will demonstrate that using apreloaded taper roller bearing in an integratedpackage should be the preferred choice for thisapplication to increase the bearing capacity, powerdensity, and fatigue life performance. Based onDIN281--4 calculations, this patented [1], fullyintegrated solution allows for calculated bearingfatigue lives to be 5 times greater than a



non--integrated solution and more than 1.5 timesgreater than a semi--integrated solution, withoutchanging the planet gear envelope.ISBN: 1--55589--866--1 Pages: 7

05FTM19. The Application of Very Large, WeldFabricated, Carburized, Hardened & Hard FinishedAdvanced Technology Gears in Steel Mill Gear DrivesAuthors: R.J. Drago, R. Cunningham and S. Cymbala

In the 1980’s, Advanced Technology Gear (ATG)steel rolling mill gear drives consisting of carburizedpinions in mesh with very large, weld fabricated, highthrough hardened gears were introduced to improvecapacity. Recently, even the improvements obtainedfrom these ATG gear sets were not sufficient to meethigher production rates and rolling loads. For greaterload capacity ATG sets have been developedconsisting of carburized, hardened pinions in meshwith very large, weld fabricated, carburized and hardfinished gears. Single and double helical gears of thistype, ranging in size from 80 to 136 inches pitchdiameter have been implemented in several steelrolling applications. This paper describes theconditions that require the use of these gears and thetechnology required to design, manufacture, and,especially, heat treat, these very special, very largegear sets.ISBN: 1--55589--867--X Pages: 16

05FTM20. Dual Drive Conveyor Speed ReducerFailure AnalysisAuthor: M. Konruff

With increasing requirements, many conveyorsystems utilize dual drive arrangements to increaseoutput. Dual drives canprovide aneconomical solutionby utilizing smaller, more efficient, systemdesigns.However,multiple drive conveyorsmust proportion theload between drives and load sharing without sometype of control is difficult to achieve. This paperpresents a case study on a failure analysis of a coalmine dual drive conveyor system that experiencedgear reducer failures between 2 to 18months. Physicaland metallurgical inspection of failed gearing did notindicate material or workmanship defects, butindicated overload. In order to determine the cause ofthe failures, strain gage load testing was performed.The testing of the conveyor drives revealed loadsharing problems which that will be reviewed.ISBN: 1--55589--868--8 Pages: 9

2004 PAPERS

04FTM1.Gear Noise -- Challenge and Success Basedon Optimized Gear GeometriesAuthors: F. Hoppe and B. Pinnekamp

Airborne and structure borne noise behaviourbecomes more and more an important feature forindustrial applications. Noise excitation requirementsmay differ with applications. Industrial conveyor beltsor cement mills are less sensitive with respect to noiseemission than military applications, such as navy ship

propulsion. This paper describes requirements andsolutions with regard to noise behaviour focussing onexamples taken from wind turbine gear transmissionsand navy applications. The individual approacheshave to be a suitable compromise to meet thechallenge of noise requirement and cost optimizationwithout restrictions on gear load carrying capacity.Therefore, the paper shows requirements andmeasurements examples from shop and field tests incomparison to gear micro geometry and calculationresults.ISBN: 1--55589--824--6 Pages: 15

04FTM2. Noise Optimized Modifications:Renaissance of the Generating Grinders?Author: H. Geiser

While load and stress optimized toothmodifications may be normal in production, noise andvibration optimized tooth modifications need higherproduction accuracies and more complexmodifications than with crowning and root or tip relief.Topological modifications show advantages for lownoise and vibration behavior due to the highervariability in direction of contact pattern. Unfortunately,a load optimized tooth flank modification is not alwaysa noise optimized modification -- a compromisebetween optimized load distribution and low noise hasto be found. In a practical example the calculationpossibilities will be demonstrated on how an optimizedtooth modification can be found. To satisfy the newrequirements the gear grinder manufacturers neededto improve their machines. This improvement waspossible with the substitution for the mechanicaltransmissions in the grinder with the modern CNCcontrols. By introducing a torque motor as the maintable drive of a grinder, together with the directmounted encoder, an advantage is offered incomparison to the mechanical drive. Problems likeworm gear wear, backlash and deviations areeliminated. This, and the possibility of topologicalmodifications, could now lead to a renascence of thegenerating grinders.ISBN: 1--55589--825--4 Pages: 9

04FTM3. A Method to Define Profile Modification ofSpur Gear and Minimize the Transmission ErrorAuthors: M. Beghini, F. Presicce, C. Santus

The object of this presentation is to propose asimple method to reduce the transmission error for agiven spur gear set, at a nominal torque, by means ofprofile modification parameters. Iterative simulationswith advanced software are needed. A hybrid methodhas been used, combining the finite element techniquewith semi analytical solutions. A two dimensionalanalysis is thought to be adequate for this kind of work;in fact, the resulting software does not require muchtime for model definition and simulations, with veryhigh precision in the results. The starting configurationis presented. At each subsequent step, little alterationof one parameter is introduced, and the bestimprovement in terms of static transmission error isfollowed, until a minimum peak--to--peak value isachieved. At the end a check is needed to verify that



the tip relief is enough to avoid the non--conjugatecontact on the tip corner for a smooth transfer load.ISBN: 1--55589--826--2 Pages: 11

04FTM4. Influence of Surface Roughness on GearPitting BehaviorAuthors: T.C. Jao, M.T. Devlin, J.L. Milner, R.N. Iyer,and M.R. Hoeprich

In earlier studies, surface roughness had beenshown to have a significant influence on gear pittinglife. Within a relatively small range of surfaceroughness (Ra = 0.1 -- 0.3 micron), gear pitting life asmeasured by the FZG pitting test decreases as thegear surface roughness increases. This inverserelationship between gear surface roughness andpitting life is well understood in the field. To determinewhether this inverse relationship is applicable to awider range of surface roughness values, a pittingstudy was conducted using gears whose surfaceroughness ranges from 0.1 -- 0.6 micron. The resultswere not completely expected. The study showed thatthe micropitting area is radically expanded when thegear surface roughness is close to the upper limit of therange studied. At the same time, the formation ofmacropitting is also greatly delayed. Not only is thepitting life significantly longer, but the initiation ofmacropitting can occur near or slightly beyond thepitch line. The paper discusses how high surfaceroughness introduces a wear mechanism that delaysthe formation of macropits.ISBN: 1--55589--827--0 Pages: 12

04FTM5. Investigations on the Micropitting LoadCapacity of Case Carburized GearsAuthors: B.--R. Höhn, P. Oster, U. Schrade and T. Tobie

Micropitting is fatigue damage that is frequentlyobserved on case carburized gears. It is controlled byconditions of the tribological system of tooth flanksurface and lubricant. The oil film thickness has beenfound to be a dominant parameter. Based on theresults of investigations a calculation method toevaluate the risk of micropitting respectively todetermine a safety factor for micropitting on casecarburized gears was developed. The calculationmethod is based on the result of themicropitting test asa lubricant tribological parameter, but enables the geardesigner to take major influences such as operatingconditions, gear geometry and gear size of the actualapplication into consideration. The paper summarizesimportant results of the continuous experimentalinvestigations and introduces the proposedcalculation method for rating the micropitting loadcapacity of case carburized gears.ISBN: 1--55589--828--9 Pages: 15

04FTM6. The Effect of a A ZnDTP Anti--wear AdditiveonMicropitting Resistance of Carburised Steel RollersAuthors: Chi--Na Benyajati and Andrew V. Olver

Zinc di--alkyl dithio--phosphate (ZnDTP)compounds are widely used in engine andtransmission oils both as anti--oxidants and asanti--wear additives. However, recent work has shownthat many anti--wear additives appear to have a

detrimental effect on the resistance of gears and othercontacting components to various types of rollingcontact fatigue, including micropitting. The paperexamines the effect of a secondary C6 ZnDTPpresence in low viscosity synthetic base oil on theresistance to micropitting and wear of carburized steelrollers, using a triple--contact disk tester. It was foundthat the additive caused severe micropitting andassociated wear, whereas the pure base oil did notgive rise to any micropitting. It was further found thatthe additive was not detrimental unless it was presentduring the first 100 000 cycles of the test when it wasfound to exert a strong effect on the development ofroughness on the counter--rollers. It is concluded thatthe additive is detrimental to micropitting resistancebecause it retards wear--in of the contact surfaces,favoring the development of damaging fatigue cracks.This contrasts with some earlier speculation thatsuggested a direct chemical effect could beresponsible.ISBN: 1--55589--829--7 Pages: 10

04FTM7. A Short Procedure to Evaluate MicropittingUsing the New AGMA Designed GearsAuthors: Kevin J. Buzdygon and Angeline B. Cardis

At the 1998 AGMA Fall Technical Meeting,encouraging results of a prototype micropitting testusing specially designed gears on the standard FZGtest rig were reported. Additional gear sets becameavailable from AGMA in 2000. Subsequently, severalsets of these experimental AGMA test gears wereused in an attempt to develop a relatively short testprocedure to evaluate micropitting. The detailedresults of these tests are discussed in the paper. Theprocedure involved running the test gears on thestandard FZG test rig with oil circulation for 168 hours.At the end of test, the gears are rated for micropitting,weight loss, pitting, and scuffing. Five commerciallyavailable ISO VG 320 gear oils, with performance inthe FVA Procedure 54 micropitting test ranging fromFLS 9--low to FLS >10--high, were evaluated using thisprocedure. The degree of micropitting coverageranged from 34% to 7% in the new test procedure.Micropitting generally originated in the middle of thegear tooth, instead of the root or tip. Overall, there wasexcellent correlation of the degree of micropittingdamage between the new test procedure and FVAProcedure 54.ISBN: 1--55589--830--0 Pages: 8

04FTM8. Generalized Excitation of Traveling WaveVibration in GearsAuthor: Paul B. Talbert

Rotation of gears under load creates dynamicloading between the gears at tooth mesh frequencyand its harmonics. The dynamic loading can excitetraveling wave vibration in the gears. The strainassociated with the traveling wave vibration can beexcessive and result in high cycle fatigue of the gears.Prior investigations have examined traveling waveexcitation for specific configurations, such as asequential star system with a fixed planetary carrier.Gear mesh excitation of traveling wave vibration can



be generalized to include the following: (1) any numberof gears surrounding the center gear, (2)non--symmetric spacing of the surrounding gears, (3)non--equal power transfer of the surrounding gears,and (4) theeffect of periodic features in the center gear.A closed form expression is developed to quantify therelative excitation of traveling wave vibration for eachnodal diameter. This expression for the relativeexcitation is verified using analytical finite elementexamples.ISBN: 1--55589--831--9 Pages: 13

04FTM9. Design of a High Ratio, Ultra Safe, HighContact Ratio, Double Helical Compound PlanetaryTransmission for Helicopter ApplicationsAuthors: Frederick W. Brown, Mark J. Robuck,G. Keith Roddis and Timothy E. Beck

An ultra--safe, high ratio planetary transmission,for application as a helicopter main rotor drive, hasbeen designed under the sponsorship of NRTC--RITA.It is anticipated that this new planetary transmissionoffers improvements relative to the currentstate--of--the--art including, reduced weight, reducedtransmitted noise and improved fail--safety. This paperdiscusses the analysis and design results for thesubject planetary transmission. Fabrication andtesting of the transmission will be conducted insubsequent phases of the project. Typically, the finalstage in helicopter main rotor transmission is the mostcritical and usually the heaviest assembly in the drivesystem for any rotarywing aircraft. The newultra--safe,high ratio planetary transmission design utilizes acompound planetary configuration with a 17.5:1reduction ratiowhichwould replace a conventional twostage simple planetary transmission. The new designuses split--torque paths and high combined contactratio gearing.ISBN: 1--55589--832--7 Pages: 12

04FTM10.The Failure Investigation andReplacementof a Large Marine GearAuthors: Peter Hopkins, Brian Shaw, J. Varo, andA. Kennedy

The paper presents details of a recent gearboxproblem encountered on a Naval ship and the finalsolution bringing the ship back to full ability. Theproblem occurred on the main wheel of a large, highpower Naval gearbox. The investigation showed thatpitting damage had developed as a result of loose sideplate bolts, which led on to bending fatigue cracking.Additional investigations and monitoring establishedthat the damage had been assisted by increasedusage at high power levels, as well as a small numberof significant overloads. Assessment of the gearboxdesign was that it had been running very close tooriginal design limits. Repairs were then carried out toremove and arrest any damage present, andmonitoring procedures were put in place to ensure nofurther damage developed. Risk assessments wereperformed to allow the ship to continue to meet itsdemands. Full repair options were then consideredand replacement gear elements designed andproduced to increase future abilities and safety factors.

The paper covers the discovery of the problem, failureinvestigation, the in--situ repair, risk assessment ofcontinued running, prevention of further damage,damage monitoring, the permanent repairassessment, design, manufacture and installation ofreplacement gears, and trials.ISBN: 1--55589--833--5 Pages: 11

04FTM11. Gear Lubrication as a Reliability PartnerAuthor: Michael Holloway

Performance lubrication is quickly becoming acomponent of preventive, predictive, proactive andreliability based maintenance programs. Using thebest gear lubricant, coupled with system condition,monitoring and analysis, actually reduces overalloperating expenses dramatically. Various techniquessuch as system conditioning, oil and equipmentanalysis, along with product selection andmanagement are valuable tools which convert manymaintenance departments into reliability centers.These concepts and others are discussed in thisinformative, hands on discussion which will reviewbest maintenance practices from various companiesand review how to implement similar programs.ISBN: 1--55589--834--3 Pages: 8

04FTM12. Improved Tooth Load Distribution in anInvolute Spline Joint Using Lead Modifications Basedon Finite Element AnalysisAuthors: Frederick W. Brown, Jeffrey D. Hayes andG. Keith Roddis

Involute splines are prone to non--uniform contactloading along their length, especially in lightweight,flexible applications such as a helicopter main rotorshaft--to--rotor hub joint. A significantly improved toothload distribution is achieved by applying, to theinternally splined member, complex lead correctionswhich vary continuously along the length of the spline.Rotor hub splines with analytically determined leadcorrections were manufactured and tested underdesign load conditions. A standard rotor shaft--to--hubjoint, which uses a step lead correction betweensplines, was also tested as a baseline. Test dataindicated that the complex lead corrections resulted ina nearly uniform contact load distribution along thelength of the spline at the design torque load. The dataalso showed that the load distribution for the splineswith the complex lead corrections was significantlyimproved relative to the baseline splines.ISBN: 1--55589--835--1 Pages: 16

04FTM13. Superfinishing Motor Vehicle Ring andPinion GearsAuthors: Lane Winkelmann, Jerry Holland andRussell Nanning

Today, the automotive market is focusing on”lubed for life” differentials requiring no service for thelife of the vehicle. Premature differential failure can becaused by bearing failures as well as ring and pinionfailure. By super finishing the lapped ring and piniongear sets to a surface roughness less than 10 microinch, lubricant, bearing and gear lives can besignificantly increased because of the concomitantelimination of wear and the temperature spike



associated with break--in. It was assumed that superfinishing technology could not preserve the contactpattern of the lapped andmatched gear set. This paperdiscusses a mass finishing operation whichovercomes these obstacles and meets the needs of amanufacturing facility. Gear metrology, contactpatterns, transmission error and actual performancedata for super finished gear sets will be presentedalong with the super finishing process.ISBN: 1--55589--836--X Pages: 16

04FTMS1. Stress Analysis of Gear Drives Based onBoundary Element MethodAuthor: Daniele Vecchiato

The stress analysis is performed as a part of TCA(Tooth Contact Analysis) for a gear drive. Unlike theexisting approaches, the proposed one does notrequire application of commercial codes (like ANSYSor ABAQUS) for derivation of contact model anddetermination of contact and bending stresses. Thecontacting model is derived directly by using theequations of tooth surfaces determined analytically.The boundary element approach allows to reducesubstantially the number of nodes of the model.Determination of stresses caused by applied load isobtained directly for the applied contacting model forany position of meshing. The developed approach isillustrated by stress analysis of helical gears withmodified geometry.ISBN: 1--55589--837--8 Pages: 16

2002 PAPERS

02FTM1. The Effect of Chemically AcceleratedVibratory Finishing on Gear MetrologyAuthors: Lane Winklemann, Mark Michaud, GarySroka, Joseph Arvin and Ali Manesh

Chemically accelerated vibratory finishing is acommercially proven process that is capable ofisotropically superfinishing metals to an Ra < 1.0 in.Gears have less friction, run significantly cooler andhave lower noise and vibration when this technology isapplied. Scuffing, contact fatigue (pitting), and bendingfatigue are also reduced or eliminated both inlaboratory testing and field trials. This paper presentsstudies done on aerospace Q13 spiral bevel gearsshowing that the amount of metal removed tosuperfinish the surface is both negligible andcontrollable. Media selection and metal removalmonitoring procedures are described ensuringuniform surface finishing, controllability andpreservation of gear metrology.ISBN: 1--55589--801--7 Pages: 18

02FTM2. Development and Application ofComputer--Aided Design and Tooth Contact Analysisof Spiral--Type Gears with Cylindrical WormAuthors: V.I. Goldfarb and E.S. Trubachov

This paper presents the method of step--by--stepcomputer--aided design of spiroid--type gears, which

involves gear scheme design, geometric calculation ofgearing, drive design, calculation of machine settingsand tooth--contact analysis. Models of operating andgenerating gearing have been developed, includingmodels ofmanufacture andassembly errors, forceandtemperature deformations acting in real gearing, anddrive element wear. Possibilities of CAD--techniqueapplication are shown to solve design andmanufacture tasks for gearboxes and gear--motorswith spiroid--type gears.ISBN: 1--55589--802--5 Pages: 15

02FTM3. The Application of Statistical Stability andCapability for Gear Cutting Machine AcceptanceCriteriaAuthor: T.J. (Buzz) Maiuri

Over the years the criteria for gear cuttingmachine acceptance has changed. In the past, cuttinga standard test gear or cutting a customer gear to theirspecification was all that was expected for machineacceptance. Today, statistical process control (SPC) isrequired for virtually every machine runoff. This paperwill cover the basic theory of stability and capabilityand its application to bevel and cylindrical gear cuttingmachine acceptance criteria. Actual case studies willbe presented to demonstrate the utilization of theseSPC techniques.ISBN: 1--55589--803--3 Pages: 26

02FTM4. Multibody--System--Simulation of DriveTrains of Wind TurbinesAuthor: Berthold Schlecht

During the last years a multitude of wind turbineshave been put into operation with continuouslyincreased power output. Wind turbines with 6 MWoutput are in the stage of development, a simpleextrapolation to larger dimensions of wind turbines onthe basis of existing plants and operationalexperiences is questionable. This paper deals with thesimulation of the dynamic behavior of the completedrive train of a wind turbine by using a detailedMulti--System--Model with special respect of the gearbox internals. Starting with the model creation and theanalysis of the natural frequencies, various load casesin the time domain will be discussed.ISBN: 1--55589--804--1 Pages: 13

02FTM5.Crack Length andDepth Determination in anIntegrated Carburized Gear/BearingAuthors: Raymond Drago and James Kachelries

In an effort to determine if processing cracksposed a safety of flight concern, several gears thatcontained cracks were designated to undergo arigorous bench test. Prior to the start of the test, it wasnecessary to document, nondestructively, all of thecrack dimensions. This paper will present a speciallymodified magnetic rubber inspection technique todetermine crack lengths as short as 0.006 inch, and aunique, highly sensitive, laboratory eddy currentinspection technique to estimate crack depths up to+/-- 0.003 inch.ISBN: 1--55589--805--X Pages: 9



02FTM6. Contemporary Gear Hobbing -- Tools andProcess StrategiesAuthor: Claus Kobialka

Gear manufacturing without coolant lubrication isgetting more and more important. Modern hobbingmachines are designed to cope with dry hobbing. Inthe last years, carbide hobs were prevailing inhigh--speed hobbing due to their excellent thermalstability. Today, this high performance rate isconfronted with rather high tool costs and critical toolhandling. Powder metallurgical HSS combined withextremely wear resistant coating on the base of (Ti,Al)N offer interesting alternatives for dry hobbing. It isevident that existing conventional hob geometries canbe optimized respecting limiting factors like maximumchip thickness and maximum depth of scallops.ISBN: 1--55589--806--8 Pages: 11

02FTM7. Selecting the Best Carburizing Method forthe Heat Treatment of GearsAuthors: Daniel Herring, Gerald Lindell, David Breuerand Beth Madlock

Vacuum carburizing has proven itself a robustheat treatment process and a viable alternative toatmosphere carburizing. This paper will presentscientific data in support of this choice. A comparisonof atmosphere carburized gears requiring pressquenching to achieve dimensional tolerances in a “onepiece at a time” heat treating operation, with a vacuumcarburized processing a full load of gears that havebeen high gas pressure quenched within requiredtolerances.ISBN: 1--55589--807--6 Pages: 13

02FTM8. Compliant Spindle in Lapping and TestingMachinesAuthor: Bill McGlasson

This paper presents theory, analysis and resultsof a novel spindle design with application to bevel gearlapping and testing machines. The spindle designincludes a rotationally compliant element which cansubstantially reduce the dynamic forces inducedbetween the gear members while rolling under load.The theory of this spindle concept is presented usingsimplified models, providing the explanation for theprocess benefits it brings. Analysis and simulationsgive additional insight into the dynamics of the system.Finally, actual lapping and testing machine results arepresented.ISBN: 1--55589--808--4 Pages: 11

02FTM9. Gear RollScan for High Speed GearMeasurementAuthor: Andreas Pommer

This presentation features a revolutionary newmethod for the complete topographical measurementof gears. The Gear RollScan system is similar toone--flank gear rolling inspection. However, themastergear has measuring tracks on selected flanks. Withtwo master gears in roll contact, both the left and rightflanks of the specimen can be inspected

simultaneously. After a specified number of rotations,everymeasuring track on themaster gears will contactevery flank of the specimen this measuring device willalways find the worst tooth.ISBN: 1--55589--809--2 Pages: 10

02FTM10. Comparing the Gear Ratings from ISO andAGMAAuthor: Octave LaBath

In the early 1980’s several technical papers weregiven comparing gear ratings from ISO and AGMAshowing some interesting and diverse differences inthe trends when the gear geometry was changedslightly. These changes included addendummodification coefficients and helix angle. Differencesalso existed when the hardness and hardeningmethods were changed. This paper will use ratingprograms developed by an AGMA committee tocompare AGMA and ISO ratings while having thesame gear geometry for both ratings. This will allowconsistent trend analysis by only changing one geargeometry parameter while holding other geometryitems constant.ISBN: 1--55589--810--6 Pages: 17

02FTM11. Gear Design Optimization Procedure thatIdentifies Robust, Minimum Stress and MinimumNoise Gear Pair DesignsAuthor: Donald Houser

Typical gear design procedures are based on aniterative process that uses rather basic formulas topredict stresses. Modifications such as tip relief andlead crowning are based on experience and thesemodifications are usually selected after the design hasbeen considered. In this process, noise is usually anafter thought left to be chosen by the designer after thegeometric design has been established. This paperstarts with micro--topographies in the form of profileand lead modifications. Then, evaluations are madeon the load distribution, bending and contact stresses,transmission error, film thickness, flash temperature,etc. for a large number of designs. The key to thisanalysis is the rapid evaluation of the load distribution.ISBN: 1--55589--811--4 Pages: 15

02FTMS1Design and Stress Analysis of New Versionof Novikov--Wildhaber Helical GearsAuthor: Ignacio Gonzalez--Perez

This paper covers design, generation, toothcontact analysis and stress analysis of a new type ofNovikov--Wildhaber helical gear drive. Greatadvantages of the developed gear drive in comparisonwith the previous ones will be discussed, including:reduction of noise and vibration caused by errors ofalignment, the possibility of grinding, and applicationofhardened materials and reduction of stresses. Theseachievements are obtained by application of: newgeometry based on application of parabolicrack--cutters, double--crowning of pinion and parabolictype of transmission errors.ISBN: 1--55589--812--2 Pages: 25



2001 PAPERS

01FTM1. Carbide Hobbing Case StudyAuthor: Yefim Kotlyar

Carbide hobbing improves productivity and cost,however many questions remain regarding the bestapplication, carbide material, hob sharpening, coatingand re--coating, hob handling, consistency andoptimum hob wear, best cutting conditions, andconcerns for the initial cutting tool investment. Thispaper is a case study of a successful implementationof carbide hobbing for an annual output of 250,000gears, average lot size of about 200--300 gears,producing gears of about 150 different sizes andpitches, with 4 setups per day on average.ISBN: 1--55589--780--0 Pages: 16

01FTM2. The Ultimate Motion Graph for “Noiseless”GearsAuthors: Hermann J. Stadtfeld and Uwe Gaiser

Gear noise is a common problem in all bevel andhypoid gear drives. A variety of expensive geargeometry optimizations are applied daily in all hypoidgear manufacturing plants, to reduce gear noise. Inmany cases those efforts have little success. Thispaper will present ”The Ultimate Motion Graph”, aconcept for modulating the tooth surfaces that usesmodifications to cancel operating dynamicdisturbances that are typically generated by any geartypes.ISBN: 1--55589--781--9 Pages: 16

01FTM3. Automated Spiral Bevel Gear PatternInspectionAuthors: S.T. Nguyen, A. Manesh, K. Duckworth andS. Wiener

Manufacturing processes for precision spiralbevel gears are operator intensive, making themparticularly costly in today’s small lot productionenvironment. This problem is compounded byproduction requirements for replacement parts thathave not beenproduced formany years. Thepaperwillintroduce a new closed loop system capable ofreducing development costs by 90% and bevel geargrinder setup time by 80%. In addition, a capability toproduce non--standard designs without part datasummaries is reviewed. Advancements will also bepresented for accepting precision gears using anelectronic digital master in lieu of a physical master.ISBN: 1--55589--782--7 Pages: 15

01FTM4. How to Inspect Large Cylindrical Gears withan Outside Diameter of More Than 40 InchesAuthor: Güenter Mikoleizig

This paper discusses the design and function ofthe relevant machines used for individual errormeasurements such as lead andprofile formaswell asgear pitch and runout. The author will cover differenttypes of inspection machines such as: stationary,CNC--controlled gear measuring centers, andtransportable equipment for checking individual

parameters directly on the gear cutting or gear grindingmachine.ISBN: 1--55589--783--5 Pages: 20

01FTM5. Traceability of Gears -- New Ideas, RecentDevelopmentsAuthors: Frank Härtig and Franz Wäldele

Some national standard tolerances for cylindricalgears lie in, and even below, the range of instrumentmeasurement uncertainties. This paper presents aconcept based on three fundamental goals: reductionof measurement uncertainty, construction ofworkpiece--like standards, and shortening of thetraceability chain. One of the focal points is thedevelopment of a standard measuring device as anadditional metrological frame integrated into acoordinate measuring machine.ISBN: 1--55589--784--3 Pages: 6

01FTM6.Performance--BasedGear--Error Inspection,Specification, andManufacturing--Source DiagnosticsAuthors: William D. Mark and Cameron P. Reagor

This paper will show that a frequency--domainapproach for the specification of gear tooth tolerancelimits is related to gear performance and transmissionerrors. In addition, it is shown that one can compute,from detailed tooth measurements, the specific tootherror contributions that cause any particularlytroublesome rotational harmonic contributions totransmission error, thereby permitting manufacturingsource identification of troublesome operation.ISBN: 1--55589--785--1 Pages: 15

01FTM7. Chemically Accelerated Vibratory Finishingfor the Elimination of Wear and Pitting of Alloy SteelGearsAuthors: Mark Michaud, Gary Sroka and LaneWinkelmann

Chemically accelerated vibratory finishingeliminates wear and contact fatigue, resulting in gearssurviving higher power densities for a longer lifecompared to traditional finishes. Studies haveconfirmed this process is metallurgically safe for boththrough hardened and case carburized alloy steels.The superfinish can achieve an Ra < 1.5 minch, whilemaintaining tolerance levels. Metrology, topography,scanning electron microscopy, hydrogenembrittlement, contact fatigue and lubrication resultsare presented.ISBN: 1--55589--786--X Pages: 16

01FTM8. The Effect of Spacing Errors and Runout onTransverse Load Sharing and the Dynamic Factor ofSpur and Helical GearsAuthors: Husny Wijaya, Donald R. Houser and JonnyHarianto

This paper addresses the effect of two commonmanufacturing errors on the performance of spur andhelical gears; spacing error and gear runout. Inspacing error analysis, load sharing for twoworst--case scenarios are treated, onewhere a tooth isout of position and the second where stepped indexerrors are applied. The analyzed results are then used



as inputs to predict gear dynamic loads, dynamic toothstresses and dynamic factors for gear rating.ISBN: 1--55589--787--8 Pages: 16

01FTM9. New Opportunities with Molded GearsAuthors: Roderick E. Kleiss, Alexander L. Kapelevichand N. Jack Kleiss Jr.

Unique tooth geometry that might be difficult oreven impossible to achieve with cut gears can beapplied to molded gears. This paper will investigatetwo types of gears that have been designed, moldedand tested in plastic. The first is an asymmetric meshwith dissimilar 23 and 35 degree pressure angles. Thesecond is an orbiting transmission with a 65 degreepressure angle. Both transmissions have higher loadpotential than traditional design approaches.ISBN: 1--55589--788--6 Pages: 11

01FTM10. Design Technologies of High Speed GearTransmissionAuthor: Jeff Wang

This paper discusses a few critical factors andtheir effects on high speed gear transmissions. Thefirst factor is centrifugal force and its effect on toothroot strength, tooth expansion and backlash and theinterference fit between gear and shaft. The second issystem dynamics, including critical speed, dynamicbalancing and the torsional effects of flexiblecouplings. The third is the windage loss with differentcombinations of helix and rotation direction, lubricantflow rate, flow distribution and their effects on toothbulk temperature field and tooth thermal expansion.ISBN: 1--55589--789--4 Pages: 8

01FTM11. Kinematic and Force Analysis of a SpurGear System with Separation of Sliding and Rollingbetween Meshing ProfilesAuthor: D. E. Tananko

This paper describes a comprehensive study ofthe novel gear design with physical separationbetween sliding and rolling motions of the mesh gearcontact point. The sliding motion is accommodated byshear deformation of a thin--layered rubber--metallaminate allowing very high compression loads.Several important advantages will be presented whencomparing the composite gear design to theconventional involute profile.ISBN: 1--55589--790--8 Pages: 50

01FTMS1. Optical Technique for Gear ContouringAuthor: Federico Sciammarella

This paper presents an optical technique(projection moiré) that is compact and can provide aquick full field analysis of high precision gears.Comparisons are made between mechanical andoptical profiles obtained of a gear tooth.ISBN: 1--55589--791--6 Pages: 12

2000 PAPERS

2000FTM1. Minimization of In--Process Corrosion ofAerospace GearsAuthors: S.T. Nguyen, A. Manesh, and J. Reeves

This paper discusses problems and root causesassociated with the corrosion of aerospace gearsduring the manufacturing process.

Specimens of common base materials used inprecision gearing were subjected to processconditions that contribute to corrosion initiationincluding: different coolant types and concentrations,material heat treat conditions, base materialmagnetism, surface finish and iron particles in coolant.ISBN: 1--55589--762--2 Pages: 7

2000FTM2. The Calculation of Optimum SurfaceCarbon Content for CarburizedCaseHardenedGearsAuthor: P.C. Clarke

At present, there is not a method to calculateeutectoid carbon from chemical analysis and theeutectoid carbon is not the best element upon which tobase surface carbon requirements. This paper willdefine the conditions and propose a method tocalculate an optimum carbon level to minimize thepossibilities of retained austenite, cementite andbainite.ISBN: 1--55589--763--0 Pages: 8

2000FTM3. Comparison of New Gear MetallurgyDocuments, ISO 6336--5 and AGMA 923 with GearRating Standards AGMA 2001 and 2003Author: A.A. Swiglo

This paper will compare and contrast these fourdocuments. What’s new, what’s different and what’shidden in the footnotes. Knowing the differences willbe important to the users of these documents.ISBN: 1--55589--764--9 Pages: 110

2000FTM4. Parametric Influences in the ISO ProjectConcerning Worm Gear RatingAuthor: M. Octrue

This paper analyzes the influence of differentparameters in CD ISO 14561 Load CapacityCalculation of Worm Gears such as; efficiency, wearload capacity, pitting, deflection and tooth root stress.The influencing parameters are divided into differentcategories such as external parameters of loadingconditions, environmental parameters of lubricanttemperature and driving and driven machines.ISBN: 1--55589--765--7 Pages: 10

2000FTM5. Systematic Investigations on theInfluence of Viscosity Index Improvers on EHL--FilmThicknessAuthors: B.--R. Hohn, K. Michaelis and F. Kopatsch

This paper compares film thickness calculationsto measurements taken using polymer containing oilsin a twin disk machine. Results will show all polymercontaining oils form lower film thicknesses thanstraight mineral oils of the same viscosity aftershearing. A polymer correction factor is derived from



test results improving the accuracy of film thicknesscalculation.ISBN: 1--55589--766--5 Pages: 11

2000FTM6. Did the Natural Convection Exist inMechanical Power Transmissions? Theoretical andExperimental ResultsAuthor: M. Pasquier

ISO TR14179 parts 1 and 2, give values of totalheat exchange coefficients in the case of naturalconvection and forced convection. This paper willcompare the values of total heat exchange obtainedfrom a theoretical study to the values given in the ISOTechnical Reports.ISBN: 1--55589--767--3 Pages: 10

2000FTM7. An Analytical -- FEM Tool for the Designand Optimization of Aerospace Gleason Spiral BevelGearsAuthor: C. Gorla, F. Rosa, and P.G. Schiannini

To save time and money during the designprocess a tool based on analytical algorithms and onFEM models is introduced. As a first step, theconjugate surfaces theory is applied to a bevel set. Ananalytical tooth contact analysis is performed todetermine the theoretical contact points on flanksurfaces versus the meshing points. Information isthen derived by the contact analysis and used togenerate Finite Element models of the gear pair on thebasis of the theoretical contact pattern. A finalsimulation by means of FEM models takes intoaccount load sharing between tooth pairs.ISBN: 1--55589--768--1 Pages: 12

2000FTM8. Stock Distribution Optimization in FixedSetting Hypoid PinionsAuthor: C. Gosselin and J. Masseth

This paper presents an algorithmused to optimizethe stock distribution between the roughing andfinishing cuts for fixed setting spiral bevel and hypoidmembers. The optimization is based on the SurfaceMatch algorithm, where differences between theroughing and finishing spiral angle, pressure angleand tooth taper are minimized in order to obtain roughand finished tooth flanks that are parallel.ISBN: 1--55589--769--X Pages: 8

2000FTM9. Cylindrical Gear Inspection and BevelGear Inspection -- A Simple Task by Means ofDedicated CNC--Controlled Gear InspectionMachinesAuthor: G. Mikoleizig

This paper will discuss the design, function,software management and probe systems of theinspection machines. Analytical tooth contact analysisof a cylindrical gear set by means of the combinedeffects of gear and pinion is shown on the basis ofindividual profile and alignment measurements. A fullyautomatic correction system will be introduced forchecking the flank form on spiral bevel gears.ISBN: 1--55589--770--3 Pages: 25

2000FTM10. Bending Fatigue Investigation underVariable Load Conditions on Case Carburized GearsAuthors: B.--R. Hohn, P. Oster, K. Michaelis,Th. Suchandt and K. Stahl

Variable load spectrum tests are carried out atdifferent load levels in a step program and at randomloading. The results of step programmed tests show asubstantial influence of the period of the programmedsubsequence of fatigue life. Fatigue life decreaseswhen the subsequence period is shortened. Withsubstantially shortened subsequences in stepprogrammed test nearly the same fatigue life isreached as in random load tests.ISBN: 1--55589--771--1 Pages: 14

2000FTM11. UltraSafe Gear Systems -- Single ToothBending Fatigue Test ResultsAuthors: R.J. Drago, A. Isaacson and N. Sonti

This paper will discuss a system from a point ofview of ”what happens when a failure occurs”. Gearswere manufactured with seeded faults to simulateunexpected defects in various portions of the highlyloaded gear tooth and rim sections. Crack propagationwas monitored by measuring effective mesh stiffnessand applied loading to provide both warning of animpending failure and a reasonable period operationafter initiation of a failure for a safe landing.ISBN: 1--55589--772--X Pages: 9

2000FTM12. The Finite Strips Method as anAlternative to the Finite Elements in Gear Tooth Stressand Strain AnalysisAuthors: C. Gosselin and P. Gagnon

The Finite Strip Method (FSM), which may beconsidered a subset of the Finite Element Method(FEM), is presented as an alternative to (FEM) thatrequires very littlemeshing effort and can be applied tovirtually any tooth geometry while offering precisioncomparable to that of Finite Elements. This paper willcover the (FSM) model for spur and helical gears,plates of variable thickness such as the teeth of facegear members and for spiral bevel and hypoid gears.ISBN: 1--55589--773--8 Pages: 11

2000FTMS1. Effects of Helix Slope and FormDeviation on the Contact and Fillet Stresses of HelicalGearsAuthors: R. Guilbault

An investigation is conducted on the effects ofhelix slope and form deviation tolerances specified forgrades 5 and 7 of the ANSI/AGMA ISO 1328--1 forcylindrical gears. The results show and almost linearcorrespondence between deviation amplitude andtooth load and fillet stress increases: using grade 7instead of grade 5 can double the tooth flank loadincrease and associated fillet stress increase. Resultsalso show that effects are evenmore significant on themaximum contact pressure.ISBN: 1--55589--774--6 Pages: 21


Price List

Full Set of Current Standards (CD) $4297.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Priced separately: $6455.00)

Full Set of Current Standards (Printed copy) $5450.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

NUMBER TITLE LIST PRICE900--H06 Style Manual for the Preparation of Standards $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .901--A92 A Rational Procedure for the Preliminary Design of Minimum Volume Gears $32.00. . . .904--C96 Metric Usage $40.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .908--B89 Information Sheet -- Geometry Factors for Determining the Pitting Resistance

and Bending Strength of Spur, Helical and Herringbone Gear Teeth $80.00. . . . . . . . . . .909--A06 Specifications for Molded Plastic Gears $45.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .910--C90 Formats for Fine--Pitch Gear Specification Data $48.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .911--A94 Guidelines for Aerospace Gearing $91.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .912--A04 Mechanisms of Gear Tooth Failure $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .913--A98 Method for Specifying the Geometry of Spur and Helical Gears $55.00. . . . . . . . . . . . . . .914--B04 Gear Sound Manual -- Part I: Fundamentals of Sound as Related to Gears; Part II:

Sources, Specifications and Levels of Gear Sound; Part III: Gear Noise Control $72.00915--1--A02 Inspection Practices -- Part 1: Cylindrical Gears -- Tangential Measurements $55.00. . .915--2--A05 Inspection Practices -- Part 2: Cylindrical Gears -- Radial Measurements $44.00. . . . . . .915--3--A99 Inspection Practices -- Gear Blanks, Shaft Center Distance and Parallelism $30.00. . . . .917--B97 Design Manual for Parallel Shaft Fine--Pitch Gearing $80.00. . . . . . . . . . . . . . . . . . . . . . . .918--A93 A Summary of Numerical Examples Demonstrating the Procedures for

Calculating Geometry Factors for Spur and Helical Gears $64.00. . . . . . . . . . . . . . . . . . . .920--A01 Materials for Plastic Gears $55.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .922--A96 Load Classification and Service Factors for Flexible Couplings $38.00. . . . . . . . . . . . . . . .923--B05 Metallurgical Specifications for Steel Gearing $75.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .925--A03 Effect of Lubrication on Gear Surface Distress $65.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .926--C99 Recommended Practice for Carburized Aerospace Gearing $45.00. . . . . . . . . . . . . . . . . .927--A01 Load Distribution Factors -- Analytical Methods for Cylindrical Gears $65.00. . . . . . . . . . .929--A06 Calculation of Bevel Gear Top Land and Guidance on Cutter Edge Radius $75.00. . . . .930--A05 Calculated Bending Load Capacity of Powder Metallurgy (P/M) External

Spur Gears $83.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .932--A05 Rating the Pitting Resistance and Bending Strength of Hypoid Gears $60.00. . . . . . . . . .933--B03 Basic Gear Geometry $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .935--A05 Recommendations Relative to the Evaluation of Radial Composite Gear Double

Flank Testers $40.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .938--A05 Shot Peening of Gears $45.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .939--A07 Austempered Ductile Iron for Gears $55.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1003--H07 Tooth Proportions for Fine--Pitch Spur and Helical Gears $69.00. . . . . . . . . . . . . . . . . . . . .1006--A97 Tooth Proportions for Plastic Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1010--E95 Appearance of Gear Teeth --Terminology of Wear and Failure $91.00. . . . . . . . . . . . . . . . .1012--G05 Gear Nomenclature, Definitions of Terms with Symbols $78.00. . . . . . . . . . . . . . . . . . . . . .1102--A03 Tolerance Specification for Gear Hobs $78.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1103--H07 Tooth Proportions for Fine--Pitch Spur and Helical Gears (Metric Edition) $64.00. . . . . . .1106--A97 Tooth Proportions for Plastic Gears $59.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Catalog of Technical Publications


AGMA Standards (continued)

2000--A88 Gear Classification and Inspection Handbook -- Tolerances and MeasuringMethods for Unassembled Spur and Helical Gears (Including MetricEquivalents) $133.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2001--D04 Fundamental Rating Factors and Calculation Methods for Involute Spur andHelical Gear Teeth $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2002--B88 Tooth Thickness Specification and Measurement $85.00. . . . . . . . . . . . . . . . . . . . . . . . . . . .2003--C10 NEW Rating the Pitting Resistance and Bending Strength of Generated Straight

Bevel, Zerol Bevel, and Spiral Bevel Gear Teeth $145.00. . . . . . . . . . . . . . . . . . . . . . . . . . .2004--C08 Gear Materials, Heat Treatment and Processing Manual $98.00. . . . . . . . . . . . . . . . . . . . .2005--D03 Design Manual for Bevel Gears $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2007--C00 Surface Temper Etch Inspection After Grinding $38.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2008--C01 Assembling Bevel Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2011--A98 Cylindrical Wormgearing Tolerance and Inspection Methods $80.00. . . . . . . . . . . . . . . . . .2015--1--A01 Accuracy Classification System -- Tangential Measurements for Cylindrical

Gears $60.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2015--2--A06 Accuracy Classification System -- Radial Measurements for Cylindrical Gears $40.00. . .Supp to Accuracy Classification System -- Tangential Measurement Tolerance Tables2015/915 for Cylindrical Gears $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2101--D04 Fundamental Rating Factors and Calculation Methods for Involute Spur and

Helical Gear Teeth $133.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2111--A98 Cylindrical Wormgearing Tolerance and Inspection Methods $70.00. . . . . . . . . . . . . . . . . .2116--A05 Evaluation of Double Flank Testers for Radial Composite Measurement of Gears $38.006000--B96 Specification for Measurement of Linear Vibration on Gear Units $69.00. . . . . . . . . . . . . .6001--E08 Design and Selection of Components for Enclosed Gear Drives $90.00. . . . . . . . . . . . . . .6002--B93 Design Guide for Vehicle Spur and Helical Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . .6006--A03 Standard for Design and Specification of Gearboxes for Wind Turbines $198.00. . . . . . .6008--A98 Specifications for Powder Metallurgy Gears $53.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6011--I03 Specification for High Speed Helical Gear Units $95.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .6013--A06 Standard for Industrial Enclosed Gear Drives $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6014--A06 Gear Power Rating for Cylindrical Shell and Trunnion Supported Equipment $115.00. . .6022--C93 Design Manual for Cylindrical Wormgearing $69.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6025--D98 Sound for Enclosed Helical, Herringbone and Spiral Bevel Gear Drives $75.00. . . . . . . .6032--A94 Standard for Marine Gear Units: Rating $95.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6033--C08 Materials for Marine Propulsion Gearing $85.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6034--B92 Practice for Enclosed Cylindrical Wormgear Speed Reducers and Gearmotors $53.00. .6035--A02 Design, Rating and Application of Industrial Globoidal Wormgearing $75.00. . . . . . . . . . .6101--E08 Design and Selection of Components for Enclosed Gear Drives (Metric) $85.00. . . . . . .6113--A06 Standard for Industrial Enclosed Gear Drives (Metric) $135.00. . . . . . . . . . . . . . . . . . . . . . .6114--A06 Gear Power Rating for Cylindrical Shell and Trunnion Supported Equipment

(Metric) $100.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6123--B06 Design Manual for Enclosed Epicyclic Gear Drives $140.00. . . . . . . . . . . . . . . . . . . . . . . . .6133--C08 Materials for Marine Propulsion Gearing $75.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6135--A02 Design, Rating and Application of Industrial Globoidal Wormgearing (Metric) $70.00. . . .6336--6--A08 Calculation of Load Capacity of Spur and Helical Gears -- Part 6: Calculation of

Service Life Under Variable Load $100.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9000--C90 Flexible Couplings -- Potential Unbalance Classification $59.00. . . . . . . . . . . . . . . . . . . . . .9001--B97 Flexible Couplings -- Lubrication $38.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9002--B04 Bores and Keyways for Flexible Couplings (Inch Series) $52.00. . . . . . . . . . . . . . . . . . . . .9003--B08 Flexible Couplings -- Keyless Fits $55.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .


AGMA Standards (concluded)

9004--B08 Flexible Couplings -- Mass Elastic Properties and Other Characteristics $65.00. . . . . . . .9005--E02 Industrial Gear Lubrication $80.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9008--B00 Flexible Couplings – Gear Type – Flange Dimensions, Inch Series $38.00. . . . . . . . . . . .9009--D02 Flexible Couplings -- Nomenclature for Flexible Couplings $46.00. . . . . . . . . . . . . . . . . . .9103--B08 Flexible Couplings -- Keyless Fits (Metric Edition) $52.00. . . . . . . . . . . . . . . . . . . . . . . . . . .9104--A06 Flexible Couplings -- Mass Elastic Properties and Other Characteristics

(Metric Edition) $60.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9112--A04 Bores and Keyways for Flexible Couplings (Metric Series) $50.00. . . . . . . . . . . . . . . . . . . .10064--5--A06 Cylindrical Gears -- Code of Inspection Practice -- Part 5: Recommendations Relative

to Evaluation of Gear Measuring Instruments $145.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .10064--6--A10NEW Code of Inspection Practice – Part 6: Bevel Gear Measurement Methods $120.00. .14179--1 Gear Reducers -- Thermal Capacity Based on ISO/TR 14179--1 $65.00. . . . . . . . . . . . . . .17485--A08 Bevel Gears -- ISO System of Accuracy $110.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Supp to17485--A08 Bevel Gears -- ISO System of Accuracy Tables $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .18653--A06 Gears -- Evaluation of Instruments for the Measurement of Individual Gears $75.00. . . .23509--A08 Bevel and Hypoid Gear Geometry $210.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

ISO STANDARDS BY TECHNICAL COMMITTEE 60

53:1998 Cylindrical gears for general and heavy engineering – Standard basic racktooth profile $41.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

54:1996 Cylindrical gears for general engineering and for heavy engineering -- Modules $30.00.677:1976 Straight bevel gears for general engineering and heavy engineering -- Basic

rack $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .678:1976 Straight bevel gears for general engineering and heavy engineering -- Modules

and diametral pitches $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .701:1998 International gear notation -- Symbols for geometric data $35.00. . . . . . . . . . . . . . . . . . . . .1122--1:1998 Glossary of gear terms -- Part 1: Definitions related to geometry $139.00. . . . . . . . . . . . .1122--2:1999 Vocabulary of gear terms -- Part 2: Definitions related to worm gear geometry $82.00. .1328--1:1995 Cylindrical gears -- ISO system of accuracy -- Part 1: Definitions and allowable

values of deviations relevant to corresponding flanks of gear teeth (SeeANSI/AGMA ISO 1328--1) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1328--2:1997 Cylindrical gears -- ISO system of accuracy -- Part 2: Definitions and allowablevalues of deviations relevant to radial composite deviations and runoutinformation (See ANSI/AGMA ISO 1328--2) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1340:1976 Cylindrical gears -- Information to be given to the manufacturer by thepurchaser in order to obtain the gears required $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1341:1976 Straight bevel gears -- Information to be given to the manufacturer by thepurchaser in order to obtain the gears required $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2490:2007 Single--start solid (monoblock) gear hobs with tenon drive or axial keyway,1 to 40 module -- Nominal dimensions $54.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

4468:2009 Gear hobs -- Accuracy requirements $122.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6336--1:2006 Calculation of load capacity of spur and helical gears -- Part 1: Basic

principles, introduction and general influence factors $170.00. . . . . . . . . . . . . . . . . . . . . . . .6336--2:2006 Calculation of load capacity of spur and helical gears -- Part 2: Calculation of

surface durability (pitting) $107.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6336--3:2006 Calculation of load capacity of spur and helical gears -- Part 3: Calculation of

tooth bending strength $117.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6336--5:2003 Calculation of load capacity of spur and helical gears -- Part 5: Strength and

quality of materials $117.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Catalog of Technical Publications


6336--6:2006 Calculation of load capacity of spur and helical gears -- Part 6: Calculation of service lifeunder variable load $92.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

8579--1:2002 Acceptance code for gears -- Part 1: Determination of airborne sound powerlevels emitted by gear units $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

8579--2:1993 Acceptance code for gears -- Part 2: Determination of mechanical vibration ofgear units during acceptance testing $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

9083:2001 Calculation of load capacity of spur and helical gears -- Application to marinegears $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

9085:2002 Calculation of load capacity of spur and helical gears -- Application forindustrial gears $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

TR10064--1:1992 Cylindrical gears -- Code of inspection practice -- Part 1: Inspection ofcorresponding flanks of gear teeth (See AGMA ISO 10064--1) -- --. . . . . . . . . . . . . . . . . . . .

TR10064--2:1996 Cylindrical gears -- Code of inspection practice -- Part 2: Inspection related toradial composite deviations, runout, tooth thickness and backlash (See AGMAISO 10064--2) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

TR10064--3:1996 Cylindrical gears -- Code of inspection practice -- Part 3: Recommendationsrelative to gear blanks, shaft centre distance and parallelism of axes $41.00. . . . . . . . . . .

TR10064--4:1998 Cylindrical gears -- Code of inspection practice -- Part 4: Recommendationsrelative to surface texture and tooth contact pattern checking $92.00. . . . . . . . . . . . . . . . .

TR10064--5:2005 Code of inspection practice ---- Part 5: Recommendations relative to evaluation ofgear measuring instruments ---- Technical Corrigendum 1 $160.00. . . . . . . . . . . . . . . . . . . . . .

TR10064--6:2009 Code of inspection practice -- Part 6: Bevel gear measurement methods $135.00. . . . . .10300--1:2001 Calculation of load capacity of bevel gears -- Part 1: Introduction and general

influence factors $124.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .10300--2:2001 Calculation of load capacity of bevel gears -- Part 2: Calculation of surface

durability (pitting) $77.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .10300--3:2001 Calculation of load capacity of bevel gears -- Part 3: Calculation of tooth root

strength $112.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR10495:1997 Cylindrical gears-- Calculation of service life under variable loads -- Conditions

for cylindrical gears according to ISO 6336 $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .10825:1995 Gears -- Wear and damage to gear teeth -- Terminology $139.00. . . . . . . . . . . . . . . . . . . . .TR10828:1997 Wormgears -- Geometry of worm profiles $82.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR13593:1999 Enclosed gear drives for industrial applications $150.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .13691:2001 Petroleum and natural gas industries -- High speed special--purpose gear units $139.00TR13989--1:2000 Calculation of scuffing load capacity of cylindrical, bevel and hypoid gears –

Part 1: Flash temperature method $112.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR13989--2:2000 Calculation of scuffing load capacity of cylindrical, bevel and hypoid gears –

Part 2: Integral temperature method $124.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .14104:1995 Gears -- Surface temper etch inspection after grinding $41.00. . . . . . . . . . . . . . . . . . . . . . .14179--1:2001 Gears -- Thermal capacity -- Part 1: Rating gear drives with thermal equilibrium

at 95C sump temperature -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR14179--2:2001 Gears -- Thermal capacity -- Part 2: Thermal load--carrying capacity $102.00. . . . . . . . . .14635--1:2000 Gears – FZG test procedures – Part 1: FZG method A/8, 3/90 for relative

scuffing load carrying capacity of oils $77.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .14635--3:2005 Gears -- FZG test procedures -- Part 3: FZG test method A/2,8/50 for relative scuffing

load--carrying capacity and wear characteristics of semifluid gear greases $82.00. . . . . .17485:2006 Bevel gears ---- ISO system of accuracy $98.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .18653:2003 Gears ---- Evaluation of instruments for the measurement of individual gears $82.00. . .TR18792:2009 Lubrication of industrial gear drives $157.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .21771:2007 Gears -- Cylindrical involute gears and gear pairs -- concepts and geometry $160.00. . .23509:2006 Bevel and hypoid gear geometry $180.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .


TECHNICAL PAPERS

2010 Full Set of Fall Technical Meeting Papers (17 papers on CD) $550.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2009 Full Set of Fall Technical Meeting Papers (19 papers on CD) $500.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2008 Full Set of Fall Technical Meeting Papers (19 papers on CD) $425.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2007 Full Set of Fall Technical Meeting Papers (19 papers on CD) $375.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2006 Full Set of Fall Technical Meeting Papers (16 papers on CD) $275.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2005 Full Set of Fall Technical Meeting Papers (20 papers on CD) $175.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2004 Full Set of Fall Technical Meeting Papers (14 papers on CD) $125.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2002 Full Set of Fall Technical Meeting Papers (12 papers on CD) $125.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2001 Full Set of Fall Technical Meeting Papers (12 papers on CD) $125.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1990--2000 AGMA Fall Technical Meeting Papers -- Millennium CD $200.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

All Individual Technical Papers $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .For titles and authors of papers from FTM Meetings prior to 1990, please send for our “TECHNICAL PAPERS CATALOG”.

GEAR SOFTWARE(See software descriptions for Option information)

Gear Rating SuiteOPTION I (includes electronic set of reference standards)

(AGMA Members) $1195.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Non Members) $1495.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

OPTION II (does not include reference standards)(AGMA Members) $495.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Non Members) $750.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Bevel Gear Rating SuiteOPTION I (includes electronic set of reference standards)

(AGMA Members) $1695.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Non Members) $2195.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

OPTION II (does not include reference standards)(AGMA Members) $995.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Non Members) $1495.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .