AGMA 01FTM8-2001 The Effect of Spacing Errors and Runout on Transverse Load Sharing and the Dynamic Factor of Spur and Helical Gears《正齿轮和螺旋齿轮的横向负载分配上间距误差和弯曲及动力因素的影响》.pdf
《AGMA 01FTM8-2001 The Effect of Spacing Errors and Runout on Transverse Load Sharing and the Dynamic Factor of Spur and Helical Gears《正齿轮和螺旋齿轮的横向负载分配上间距误差和弯曲及动力因素的影响》.pdf》由会员分享,可在线阅读,更多相关《AGMA 01FTM8-2001 The Effect of Spacing Errors and Runout on Transverse Load Sharing and the Dynamic Factor of Spur and Helical Gears《正齿轮和螺旋齿轮的横向负载分配上间距误差和弯曲及动力因素的影响》.pdf(16页珍藏版)》请在麦多课文档分享上搜索。
1、01FTM8The Effect of Spacing Errors and Runout onTransverse Load Sharing and the DynamicFactor of Spur and Helical Gearsby: H. Wijaya, D.R. Houser and J. Harianto,The Ohio State UniversityTECHNICAL PAPERAmerican Gear ManufacturersAssociationThe Effect of Spacing Errors and Runout onTransverse Load Sh
2、aring and the Dynamic Factor ofSpur and Helical GearsHusny Wijaya, Donald R. Houser and Jonny Harianto, The Ohio StateUniversityThestatementsandopinionscontainedhereinarethoseoftheauthorandshouldnotbeconstruedasanofficialactionoropinion of the American Gear Manufacturers Association.AbstractThispape
3、raddressestheeffectsoftwocommonmanufacturingerrorsontheperformanceofspurandhelicalgears. Thefirst error to be considered will be tooth spacing error. First the transverse load sharing for two types of worst casescenarios,onewhereonetoothisoutofpositionandthesecondwherethereisastepindexerrorisapplied
4、(allsubsequentteeth areoutofposition).Theresultsoftheseanalysesarethen used asinputto asimulation program that predictsgeardynamic loads, dynamic contact stresses and dynamic root stresses and generalized dynamic factor information isgenerated. Runout, which results in a sinusoidal spacing error is
5、the second type of error that is analyzed. When thedynamic simulation is run with runout, there is much modulation of the meshing forces and again dynamic loads andstresses are presented as a function of rotating speed.Inallcases,resultsarerunforgearsthathaveprofilemodificationsthatinitiallyminimize
6、dynamicload,thusminimizingdynamics due to mesh stiffness variations. This allows the isolation of spacing error effects while at the same timeminimizestoothcornercontact. Sinceitisdifficultinthesesituationstoseparatethetransverseloadsharingeffectsfromthe dynamic effects, they will be simultaneously
7、considered in all of the analyses.CopyrightGe32001American Gear Manufacturers Association1500 King Street, Suite 201Alexandria, Virginia, 22314October, 2001ISBN: 1-55589-787-81The Effect of Spacing Errors and Runout on Transverse Load Sharing and Dynamic Factor of Spur and Helical Gears Dr. D. R. Ho
8、user Professor, Department of Mechanical Engineering The Ohio State University Columbus, OH 43210 and Husni Wijaya Graduate Research Associate, Department of Mechanical Engineering The Ohio State University Columbus, OH 43210 and Jonny Harianto Research Engineer, Department of Mechanical Engineering
9、 The Ohio State University Columbus, OH 43210 INTRODUCTION The dynamic factor used in gear design has been the subject of many studies, most of them being analytical in format. Buckinghams first formulation 1 of a dynamic factor was based on entering contact impacts due to spacing errors and subsequ
10、ent work by Tuplin 2, and Houser and Seireg 3, 4 continued applying this approach. However, in modern gear design, these impacts are eliminated through the use of tip relief and lead crowning so that the later formulations of Harianto and Houser 5, 6 and Lin 7 have been based on errors in the tooth
11、form that result in a transmission error excitation. Three types of dynamic factors defined by Harianto and Houser 5 are the “dynamic load factor” which is the same as the factor used by AGMA 8, the “dynamic root stress factor” and the “dynamic contact stress factor”. In this paper, spacing errors a
12、nd runout will be introduced and further analyzed using these three dynamic factor definitions. However, the static changes in the transverse load sharing (TLS) sometimes are much greater than the dynamic effect, so we shall define two new factors that combine the static and dynamic effects as follo
13、ws: errorwithoutvaluestaticMaximumerrorspacingwithvaluestaticMaximumFactorDynamicFactorSpacing=spacingTLSSpacingTLSrunoutwithoutvaluestaticMaximumrunoutwithvaluestaticMaximumFactorDynamicFactorRunout=runoutTLSrunoutTLSThe “static value” depends on the type of analysis, namely load, pinion root stres
14、s, gear root stress or contact stress, and these two factors give the net static and dynamic effect of the respective spacing errors and runout. The procedure for determining these factors is first to use the Load Distribution Program (LDP) 9 to obtain the static transmission error and mesh stiffnes
15、s as functions of gear rotation. These parameters are then used as excitations to the Dynamic Transmission Error Program (DYTEM) that uses a six degree-of-freedom 2non-linear time domain model to simulate gear dynamics 10. Dynamic loads are predicted from the DYTEM program and then fed back to LDP t
16、o calculate the values of both root and contact stresses at each contact position. The procedures used in this paper for predicting dynamic load, root stress and contact stress are similar to those presented by Harianto and Houser 5, 6. A description of each of these programs is provided in the APPE
17、NDIX. SPACING ERROR AND RUNOUT Spacing error is the circumferential position error of one gear tooth with respect to the previous tooth. Runout is an eccentricity that can be described over one revolution of the gear as a sinusoidal spacing error function. Spacing errors and runout have a significan
18、t effect on gear dynamics, and many studies have been conducted in this area. Houser and Seireg 3, 4 have done experimental and analytical studies on the influence of different pitch errors and profile modifications on the dynamic factors of spur and helical gears. The studies were limited to gear s
19、ystems that operate at low speed or non-resonant speeds and concentrated on the entering tooth impact that occurs due to corner contact. Today, this corner contact effect can be avoided or minimized by providing adequate tip relief and lead crowning. Umezawa, Sato and Kohno 11 studied the rotational
20、 vibration of gears with pitch errors on every other tooth and on every third tooth, and their results show that low contact ratio gears are more sensitive to pitch error than are high contact ratio gears. Kohler 12 examined the effect of spacing error on the gear transmission error. Padmasolala and
21、 Lin 13 investigated the effectiveness of profile modification for reducing dynamic loads on the gears using long span and short span spacing error over several teeth, but the magnitudes of spacing errors used are very low and are close to the highest quality (quality 15) rated gear tolerances presc
22、ribed by AGMA. Briere and Sabot 14 investigated the eccentricity faults in spur gears and their results show amplitude modulation and a resulting periodicity of kinematic transmission errors. The proper means of simulating spacing errors would be to apply the errors over the total rotation of both p
23、inion and gear. This would require running the gears through their total hunting period. Instead, we have found that the worst-case spacing errors occur when the respective worst-case errors of the pinion and gear match up. Therefore, we are only going to study the worst-case combinations of spacing
24、 errors, first with errors in the positive direction and second with errors in the negative direction. Even so, there are two ways errors can occur that give high dynamic responses. The first, called case A, is when one tooth is out of position and all other teeth are in their original locations. Th
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