二级标准圆柱斜齿轮减速器设计

目录1前言······························································································12电动机选择计算···············································································22.1选择电动机类型和结构形式····························································22.2选择电动机的容量·········································································22.3确定电动机转速············································································23计算传动装置的运动和动力参数·························································33.1计算总传动比及分配各级传动比······················································33.2计算各轴的转速：·········································································33.3计算各轴的输入功率：···································································43.4计算各轴的输入转距：···································································44齿轮转动设计··················································································54.1齿轮的选择··················································································54.2按齿面接触疲劳强度设计齿轮························································54.3确定主要参数及计算主要几何尺寸···················································74.4按齿根弯曲疲劳强度校核······························································105轴的设计计算················································································125.1轴Ⅰ的设计················································································125.2轴Ⅱ的设计················································································145.3轴Ⅲ的设计················································································186轴承的校核···················································································216.17308B型轴承校核······································································216.27212C型轴承校核······································································247键连接的校核计算··········································································267.1Ⅱ轴齿轮键选择校核····································································267.2Ⅲ轴齿轮键选择校核····································································278联轴器的标记················································································279传送带速度校核·············································································27设计小结·························································································29参考文献·························································································30附录·························································································31致谢·························································································33广西农业职业技术学院毕业论文11前言毕业设计是对前面所学知识作一次大的总结和综合应用能力的考察。本毕业设计的设计内容是用于带式传送机的二级圆柱斜齿轮减速器的设计。减速机是一种动力传达机构，利用齿轮的速度转换器，将马达的回转数减速到所要的回转数，并得到较大转矩的机构。它具有稳定的传动比、可靠的工作性能和使用寿命长等特点，是一种适用范围很广的机械设备。所以，在机械设计领域中，减速器的设计具有一定的代表性。二级减速器的设计汇集了机械设计基础、机械制造基础、机械制图、标准件的选型方法等方面的知识。是综合运用机械设计基础、机械制造基础的知识和制图技能，完成传动装置的分析和设计的过程。通过这一过程全面了解机械产品所涉及的结构、强度、制造、装配以及表达等方面知识，培养我们的综合分析能力、动手能力。提高了我们的综合素质。广西农业职业技术学院毕业论文22电动机选择计算2.1选择电动机类型和结构形式按工作条件和要求，选用一般用途的Ｙ系列三相异步电动机，为卧式封闭结构。2.2选择电动机的容量电动机所需的实际功率即电动机输出功率Pd为：awdPP/而工作机的输出功率1000/FVPwadFVP1000/卷联齿承223a查《机械设计基础课程设计》P22表2—3得：99.0承，97.0齿，99.0联，96.0卷则：a=99.03×97.02×99.02×96.0＝0.8667.786.01000/1.161000/103FVPwKW2.3确定电动机转速nu'＝60×1000V／D＝6×1000×1.1／D×400＝52.55（r／min）为便于选择电动机转速，需先推算出电动机转速可选范围。单级圆柱齿轮传动比范围为i齿＝3—6，则电动机转速选择范围为：nd'＝nnnniuuuu2222/'//'36963齿＝473—1892（r/min）符合这一转速范畴的转速有730r/min、970r/min、1460r/min，根据容量和转速，由广西农业职业技术学院毕业论文3《机械零件设计手册》表19—11查出有三种适用的电动机型号，如下表2-1：表2-1三种传动方案方案电动机型号额定功率（Ped／KW）电动机转速（r/min）电动机质量（㎏）效率（%）1Y160M—4111460123882Y160L—611970147873Y180L—81173018486.5由表中数据可知，三种方案均可行，但考虑到电动机和传动装置尺寸、结构。认为方案三比较合适，所以选定电动机的型号为Y180L—8。3计算传动装置的运动和动力参数3.1计算总传动比及分配各级传动比总传动比ia为：89.1355.52730'iiiuma同时iiia齿齿21按展开式布置，考虑润滑条件，为使两级大齿轮直径相近，取减速器中高速级齿轮41i齿低速级齿轮传动比为：47.3489.1312iiia齿齿3.2计算各轴的转速：Ⅰ轴730nnmⅠ(r/min)广西农业职业技术学院毕业论文4Ⅱ轴5.18247301inn齿ⅠⅡ(r/min)Ⅲ轴59.5247.35.1822inn齿ⅡⅢ(r/min)卷筒轴59.52nnⅢ卷(r/min)3.3计算各轴的输入功率：Ⅰ轴59.799.067.7联Ⅰppd(kw)Ⅱ轴29.799.097.059.7承齿ⅠⅡpp(kw)Ⅲ轴)(00.799.097.029.7kwpp承齿ⅡⅢ卷筒轴)(68.699.099.000.7kwpp承联Ⅲ卷3.4计算各轴的输入转距：电动机所需的实际转距即电动机的输出转距npTmdd9550＝73067.79550＝100.34(mN)Ⅰ轴联ⅠTTd100.340.99=99.34(mN)Ⅱ轴37.39399.00434.991承齿ⅠⅡiTT(mN)Ⅲ轴承齿ⅡⅢiTT2=393.3799.047.3=1353.34(mN)卷筒轴45.132499.099.034.1350联承Ⅲ卷TT(mN)将运动和动力参数计算结果进行整理并列表如表2-2：表2-2运动和动力参数计算结果广西农业职业技术学院毕业论文5轴名功率T/Nm转速min1rn转动比i输入输出输入输出电机轴7.67100.341Ⅰ轴7.5999.344Ⅱ轴7.29393.373.47Ⅲ轴7.001351.341卷筒轴6.861324.454齿轮转动设计减速器是闭式传动，通常采用HBS≤350的软齿面铜制齿轮。根据计算准则，应按齿面接触疲劳强度设计，确定齿轮的参数，然后验算齿根弯曲疲劳强度。4.1齿轮的选择⑴齿轮编号定高速级轴Ⅰ上的小齿轮为1齿；中速级轴Ⅱ上的大齿轮为2齿；小齿轮为3齿；低速级轴Ⅲ为4齿。⑵材料热处理方法对齿轮转动无特殊要求，可选一般齿轮材料如下：小齿轮1、3选用45号钢，调质处理，HB1=280，HB3=300；大齿轮选用45号钢，正火处理，HB2=HB4=260。⑶选择精度等级为8级4.2按齿面接触疲劳强度设计齿轮由于是软齿面的闭式齿轮传动，齿轮的承载能力应由齿面接触疲劳强度决定。广西农业职业技术学院毕业论文6321115.76HkdTd⑴.载荷系数：《机械零件设计手册》图15—21，取k=1.1⑵.转距T：34.991TmNmNT37.3932⑶.接触疲劳许应力H：SZHHimNH由《机械零件设计手册》图15—20查得：PMaHim5601；pMaHim5202；PM