AGMA 01FTM6-2001 Performance - Based Gear - Error Inspection Specification and Manufacturing - Source Diagnostics《性能.基础齿轮.检验误差和制造规范.来源诊断学》.pdf
《AGMA 01FTM6-2001 Performance - Based Gear - Error Inspection Specification and Manufacturing - Source Diagnostics《性能.基础齿轮.检验误差和制造规范.来源诊断学》.pdf》由会员分享,可在线阅读,更多相关《AGMA 01FTM6-2001 Performance - Based Gear - Error Inspection Specification and Manufacturing - Source Diagnostics《性能.基础齿轮.检验误差和制造规范.来源诊断学》.pdf(15页珍藏版)》请在麦多课文档分享上搜索。
1、01FTM6Performance-Based Gear-ErrorInspection, Specification, andManufacturing-Source Diagnosticsby: W.D. Mark and C.P. Reagor, Penn State UniversityTECHNICAL PAPERAmerican Gear ManufacturersAssociationPerformance-Based Gear-Error Inspection,Specification, and Manufacturing-Source DiagnosticsWilliam
2、D. Mark and Cameron P. Reagor, Penn State UniversityThestatementsandopinionscontainedhereinarethoseoftheauthorandshouldnotbeconstruedasanofficialactionoropinion of the American Gear Manufacturers Association.AbstractPerformance-relevant imperfections in gear manufacturing machines, cutting tools, an
3、d operations are exhibited asmanufacturingerrorsingear-toothworkingsurfaces. Detailedmeasurementsofsuchgear-tootherrorscanbeobtainedutilizing present-day dedicated CNC gear measurement machines. The effects of such gear-tooth errors on gearperformance are usefully described in the frequency domain b
4、y their rotational harmonic contributions to thetransmissionerror. Using sucha frequency-domainrepresentation, therotational-harmonic tooth-errorcontributionscanbeseparatedfromtheattenuatingeffectsonsucherrorscausedbythesimultaneousmultipletoothcontactofmeshinggear teeth, which can greatly attenuate
5、 the contribution of such errors to the transmission error of helical gears. It isshownthatthisfrequency-domainapproachallowsspecificationoflimitsonthefeaturesofgear-tootherrorsthatrelateto gear performance as described by the transmission error. In addition, it is shown that one can compute, from s
6、uchdetailed tooth measurements, the specific error contributions on the teeth that cause any particularly troublesomerotationalharmonic contributionsto thetransmission error,thereby permitting manufacturing-source identification ofsuch troublesome harmonics. Examples are given illustrating the above
7、-described approach to gear-tooth errormeasurement, specification, and manufacturing source diagnostics.CopyrightGe32001American Gear Manufacturers Association1500 King Street, Suite 201Alexandria, Virginia, 22314October, 2001ISBN: 1-55589-785-11Performance-Based Gear-Error Inspection, Specification
8、, and Manufacturing-Source Diagnostics William D. Mark* and Cameron P. Reagor#*Drivetrain Technology Center, Applied Research Laboratory, and Graduate Program in Acoustics, The Pennsylvania State University #Graduate Program in Acoustics, The Pennsylvania State University 1. Introduction This paper
9、describes an approach to measuring, characterizing, specifying, and diagnosing manufacturing errors on spur and helical gears with nominally equispaced involute teeth in a manner that can be related to gear performance as described by the “static” transmission error 1-7. The methods to be described
10、are potentially useful for characterizing and diagnosing errors generated by gear manufacturing machines and their operation, gear cutting and finishing tools, and possibly for spot checking individual gears. The static transmission error contributions from an individual gear have two fundamental so
11、urces: elastic deformations of the teeth and gearbodies, and geometric deviations of the tooth working surfaces from equispaced perfect involute surfaces. (From this juncture onward, we shall refer to such deviations only as geometric deviations of the teeth or, simply, deviations.) Since the static
12、 transmission error is the principal source of vibrations and noise generated by the meshing action of gear pairs 1-3, it is both useful and convenient to utilize its representation in the frequency domain. 1.1 Transmission error representation in the frequency domain Because a gear is circular, its
13、 static transmission error contributions are periodic with a period of one revolution of the gear. Let Rbdenote the base-cylinder radius of the gear, and its rotational position in radians. Then bRx =is an obvious choice 4-7 for an independent variable in which to describe transmission error contrib
14、utions in the “time” domain. (The base pitch G29 of both gears of a meshing pair is the same when measured in units of x; it is ,/2 NRb= where N is the number of teeth on each gear of base-cylinder radius Rb.) It follows from equation (1) that the fundamental period in x of the static transmission e
15、rror contributions from a single gear is 2G42 Rb, the base-cylinder circumference. In the following discussion, it is assumed that the geometric deviations of the working surfaces of all teeth on a gear may differ from one another. It follows 4-7 that rotational harmonic contributions to the transmi
16、ssion error can occur at all integer multiples n of the fundamental n=1 rotational harmonic with period in x of .2 = NRb Typically, the strongest rotational harmonics, other than the tooth-meshing harmonics, ,.,2,1, = ppNn are the first few rotational harmonics (once-per-revolution, twice-per-revolu
17、tion, etc.), the so-called sidebands around the tooth-meshing harmonics, and “ghost tone” harmonics 3,7,8 when they are present. Besides vibration and noise considerations, there are other reasons why transmission error analysis in the frequency domain is useful. If the stiffness of every tooth and
18、its supporting structure is the same as that of every other tooth on a gear, then the contributions to the transmission error from elastic tooth deformations are provided only to the tooth-meshing harmonics, equation (4). Furthermore, let us conceptually measure, in complete detail, the geometric de
19、viations of every point on the working surface of every tooth on a gear, as a function of axial location and roll angle. Next, conceptually place these N measured surfaces in a stack and form the arithmetic average of these N surfaces, which creates a deviation surface expressed as a function of axi
20、al location and roll angle. (If the geometric deviations of the working surface of every tooth on the gear were the same, then each such deviation surface would coincide with the above-described average deviation surface.) The contributions to the static transmission error from the above-described a
21、verage deviation surface are provided only to the tooth-(1)(2)(3)(4)2meshing harmonics, equation (4), along with contributions from elastic deformations of the teeth. For high-quality gears, the contributions from the above-described average deviation surface usually are dominated by intentional wor
22、king surface modifications from perfect involute surfaces. Next, conceptually form the difference between the deviation surface measured for each tooth on a gear and the above-described average deviation surface for that gear. The resulting “difference surfaces” clearly are a result of manufacturing
23、 errors. (From this juncture onward, we shall refer to these surfaces only as geometric “difference surfaces” or, simply, “difference surfaces”.) For gear pairs rotating at constant speed and transmitting constant torque, the above-described difference surfaces provide the contributions to the rotat
24、ional harmonics of the static transmission error 4-8, excluding the tooth-meshing harmonics, equation (4). In what follows, it is shown that these rotational harmonic contributions to the transmission error can be computed from detailed gear tooth measurements made on a single gear, and that the uni
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