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1、#215;sin（146°/2）=1968N2、齿轮传动的设计计算1选定齿轮材料及精度等级及齿数1）机器为一般工作机器，速度不高，故选用7级精度（GB10095-88）。2）材料选择。由表课;98×0.5/)(mN?VAR=VBR=0.5rF=0.5×566.909=283.455)(mN?VCM=0.5VARL=283.455×98×0.5/)(mN?转矩T=161.182)(mN?校核CM=22VCHCMM?=.38?=40.697)(mN?eM=??22aTMC?=??.0697.40??=104.923)(mN?由图表查得，??b1??=55MPad≥10??beM131.0??=3.(mm)考虑键槽d=26.72mm&39mm则强度足够计算及说明结果42第六章轴承、键和联轴器的选择6.1轴承的选择及校核考虑轴受力较小且主要是径向力，故选用单列深沟球轴承主动轴承根据轴颈值查《机械零件设计手册》选择62072个（GB/T276-1993）从动轴承62092个（GB/T276-1993）寿命计划：两轴承受纯径向载荷P=rF=Y=0从动轴轴承寿命：深沟球轴承6209，基本额定功负荷rC。2、一级圆柱齿轮减速器的设计计算（最终版）本表10-1选择小齿轮和大齿轮材料为45钢（调质）硬度为280HBS。3）选小齿轮齿数z1=24，大齿轮齿数z2=24×3.86=92.64，取93。2按齿面接触疲劳强度设计由设计计算公式（10-9a）d1≥2.32(KT1(u+1)ZE2/φdu[σH]2)1/3(1)确定公式内的各计算数值1）试选载荷系数Kt=1.32）计算小齿轮传递的转矩T1=9.55×106×P1/n1=95.5×106×4.92/342.86=137041N·mm3)由课本表10-7选取齿款系数φd=14)由课本表10-6查得材料的弹性影响系数ZE=189.8MPa1/25)由课本tu10-21按齿面硬度查得小齿轮的接触疲劳强度极限σHlim1=600MPa；打齿轮的接触疲劳强度极限σHlim2=550MPa；6）由课本式10-13计算应力循环次数NLNL1=60n1jLh=60×342.86×1×(16×300×10)=9.874×108NL2=NL1/i=9.874×108/3.86=2.558×1087）由图课本10-19取接触疲劳寿命系数KHN1=0.96KHN2=0.988）计算解除疲劳许用应力。取失效概率为1%，安全系数S=1.0[σH]1=KHN1σHl。3、5;1.7/π×300=108.2r/min按手册P7表1推荐的传动比合理范围，取圆柱齿轮传动一级减速器传动比范围I’a=3~6。取V带传动比I’1=2~4，则总传动比理时范围为I’a=6~24。故电动机转速的可选范围为n’d=I’a×n筒n筒=（6~24）×108.2=649.4~2597.4r/min符合这一范围的同步转速有750、1000、和1500r/min。根据容量和转速，由有关手册查出有三种适用的电动机型号：因此有三种传支比方案：由《机械设计手册》查得。综合考虑电动机和传动装置尺寸、重量、价格和带传动、减速器的传动比，可见第3方案比较适合，则选n=1000r/min。4、确定电动机型号根据以上选用的电动机类型，所需的额定功率及同步转速，选定电动机型号为Y13M2-6。其主要性能：额定功率：5.5KW，满载转速960r/min，三、计算总传动比及分配各级的传动比1、总传动比：i总=n电动/n筒=960/108.2=8.872、分配各级伟动比（1）据指导书P7表1，取齿轮i带=2.3（V带传动比I’1=2~4合理）（2）∵i总=i齿轮×i带∴i齿轮=i总/i带=8.87/2.3=3.86四、运动参数及动力参数计算1、计算各轴转速（r/min）nI=n电机=960r/minnII=nI/i带=960/2.3=417.39(r/min)n。4、一级圆柱齿轮减速器的设计计算.doc分度圆直径d1=z1m=30×2.5=75mmd2=z1m=116×2.5=290mm（2）计算中心距a=（d1+d2）/2=（75+290）/2=183mm（3）计算齿轮宽度b=φdd1=1×75=75mm取B2=75mm，B1=80mm六、轴的设计计算输出轴的设计计算1、两轴输出轴上的功率P、转数n和转矩TPII输=4.67×0.98=4.58kwn2=n1/i=417.39/3.86=108.13r/minT2=397656N·mmPI输=4.92×0.98=4.82kwn1=417.39r/minT1=100871N·mm2、求作用在齿轮上的力因已知低速大齿轮的分度圆直径为d2=355mmFt2=2T2/d2=2×=2011NFr2=Ft2tan20°=.N因已知低速大齿轮的分度圆直径为d1=84mmFt1=2T1/d1=2×=2401NFr1=Ft1tan20°=.、初步确定轴的最小直径先按课本式（15-2）初步估算轴的最小直径。选取的材料为45钢，调制处理。根据课本表15-3，取A0=112，于是得dmin2=A0（PII输/n2）1/3=112。5、圆柱齿轮减速器,doc,圆柱齿轮减速器设计,减速器设计,齿轮减速器设计计算,减速器设计计算,减速器,一级圆柱齿轮减速器的设计,设计一级,一级圆柱齿轮减速机,设计计算,一级圆柱齿轮减速器,圆柱齿轮减速器的设计221111mmmhZhddaaa????????????)((222222mmmhZhddaaa??????????齿距P=2×3.14=6.28(mm)齿根高??)(5.2mmmchhaf?????齿顶高)(221mmmhhaa?????齿根圆直径fd)(435.2248211mmhddff??????)(2mmhddff??????4.3齿轮的结构设计小齿轮采用齿轮轴结构，大齿轮采用锻造毛坯的腹板式结构大齿轮的关尺寸计算如下：轴孔直径d=?50)(mm轮毂直径1D=1.6d=1.6×50=80)(mm轮毂长度)(482mmBL??轮缘厚度δ0=(3～4)m=6～8(mm)取0?=8轮缘内径2D=2ad-2h-20?=204-2×4.5-2×8强度足够ad=54mm2ad=204mmh=4.5mmS=3.14mmP=6.28mmhf=2.5mmha=2mmdf1=43mmdf2=199mm计算及说明结果36=179(mm)取D2=180(mm)腹板厚度c=0.32B=0.3×48=14.4取c=15(mm)腹板中心孔直径0D=0.5(1D+2D)=0.5(80+180)=130(mm)腹板孔直径0d=0.25（2D-1D）=0.25（180-80）=25(mm)取0d=25(mm)齿轮。6、#215;sin（146°/2）=1968N2、齿轮传动的设计计算1选定齿轮材料及精度等级及齿数1）机器为一般工作机器，速度不高，故选用7级精度（GB10095-88）。2）材料选择。由表课;98×0.5/)(mN?VAR=VBR=0.5rF=0.5×566.909=283.455)(mN?VCM=0.5VARL=283.455×98×0.5/)(mN?转矩T=161.182)(mN?校核CM=22VCHCMM?=.38?=40.697)(mN?eM=??22aTMC?=??.0697.40??=104.923)(mN?由图表查得，??b1??=55MPad≥10??beM131.0??=3.(mm)考虑键槽d=26.72mm&39mm则强度足够计算及说明结果42第六章轴承、键和联轴器的选择6.1轴承的选择及校核考虑轴受力较小且主要是径向力，故选用单列深沟球轴承主动轴承根据轴颈值查《机械零件设计手册》选择62072个（GB/T276-1993）从动轴承62092个（GB/T276-1993）寿命计划：两轴承受纯径向载荷P=rF=Y=0从动轴轴承寿命：深沟球轴承6209，基本额定功负荷rC（全文完）
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/FileRoot2//96d71a7d-772a-4ab4-b532-b017aeaA7D-772A-4AB4-B532-B017AEA1446465.swf10-2110-2110-2110-2110-2110-2110-2110-2110-2110-21最新范文01-0101-0101-0101-0101-0101-0101-0101-0101-0101-0101-0101-0101-0101-0101-01近日，《辉煌中国》在央视热播，广大人民群众反响强烈。国家的飞速发展让我们感到骄傲和自豪，祖国为世界和平作出的巨大贡献让我们深感荣幸。这个国庆长假，焦点不应只放在“八天”。别忘了享受和平年代繁荣昌盛的同时，去看看《辉煌中国》，感受这部让我们热血沸腾的纪录片。
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