塑料包装机构主传动机构设计-二级展开式圆柱圆锥齿轮减速器【说明书+CAD】
塑料包装机构主传动机构设计-二级展开式圆柱圆锥齿轮减速器【说明书+CAD】,说明书+CAD,塑料包装机构主传动机构设计-二级展开式圆柱圆锥齿轮减速器【说明书+CAD】,塑料包装,机构,传动,设计,二级,展开式,圆柱,圆锥,齿轮,减速器,说明书,仿单,cad
1 塑料包装机构主传动机构设计 二级展开式圆柱圆锥齿轮减速器 任务说明书 系 别: 机电工程系 专 业: 机械设计制造及其自动化 姓 名: 荆伟泽 学 号: 2005090221 指导教师: 贾毅超 2 目 录 一 设计题目 .3 1塑料包装机的传动示意如图所示。 .3 2已知条件 .3 3设计内容 .3 二 传动装置总体设计 .4 三 电动机的选择 .4 四 运动和运动参数计算: .4 1分配传动比 .4 2计算传动装置的运动和动力参数 .4 五 传动零件的设计计算 .6 1普通 V带的设计计算 .6 2闭式直齿轮圆锥齿轮传动的设计计算 .8 3闭式直齿圆柱齿轮设计计算 .13 4.轴的设计 .17 1)高速轴的设计 .17 2) .中间轴的设计 .20 3)低速轴的设计 .24 六 轴承的校核 .27 1高速轴轴承的校核 .27 2.中速轴轴承校核 .28 3.高速轴轴承的校核 .30 七.减速器机体结构 .31 八键的设计 .33 1.高速轴键的设计与校核 .33 2.中间轴键的设计与校核 .33 3.低速轴键的设计与校核 .34 九减速器的各部位附属零件的设计. .34 十防滑方式的确定 .35 1滚动轴承的润滑 .35 2齿轮的润滑 .35 3 一 设计题目 1塑料包装机的传动示意如图所示。 2已知条件 1)凸轮的转速 n/(r/min) 35 电动机的功率/KW 0.25 2)工作情况:两班制,连续单向运转,载荷有轻微冲击,室内工作。 3)使用期限:10 年; 4)生产条件:一般机械厂,单件生产; 5)动力来源:电力,三项交流,电压 380220V; 6)检修间隔:三年一大修,二年一中修,半年一小修 3设计内容 1)拟定工作机构和传动方案 2) 工作机构和运动学动力学分析 3)设计绘制减速器装配图一张 4)设计绘制零件图三张 5)编写设计计算说明书一份 4 二 传动装置总体设计 1) 组成:传动装置由电机、减速器、工作机组成。 2)特点:齿轮相对于轴承不对称布置,因而沿齿向载荷分布不均匀,要求轴有较大的刚 度 3)传动系统的作用:介于机械中原动机与工作机之间,主要将原动机的运动和动力传给 工作机,在此起减速作用,并协调二者的转速和转矩。 三 电动机的选择 查手册 选电动机型号 YS7114 功率 0.25kw 380V 转速 1400r/min 四 运动和运动参数计算: 1分配传动比 分配传动比:查手册第十三章,表 132知 V带 i7,开式圆柱齿轮 i8,圆锥齿 轮 i5;总传动比:i =40;取 (带轮) 04i带 , (减速器)0/4/1i减 取 (锥齿轮) 12.5 (柱齿轮)2/i 2计算传动装置的运动和动力参数 (1)0 轴电动机的转速 =350r/min140 nIinI =140r/min 352.Ii I =35r/min140 nIinI 5 (2)各轴的功率 传动总效率 带的传动效率: 0.961 轴圆锥滚子轴承的效率: 82 圆锥齿轮啮合的效率: .53 轴圆锥滚子轴承的效率: 094 齿轮啮合的效率: .75 轴圆锥滚子轴承的效率: 6 联轴器的传动效率: 0.97 总的传动效率 1234567总 .8326总 各轴的功率: 012.5096.8IPKW0.5PKWI 34I219 2567.7II .8I 各轴的转矩: 60.3539.109.51PITIn6417.mTNI 6.296.5.4II 938.I 0.189.109.53PITIn542.TNI 6 五 传动零件的设计计算 1普通 V带的设计计算 (1)确定 V带的型号和带轮的直径 工况系数 由(设计说明书)11.5 K1.2A 计算功率 选取带型由0K1.25ACP03PWC (设计说明书)11.15 Y 型 小带轮的直径 同理由表 11.6 取 125mD 大带轮的直径 取210i54D0 (2)计算带长 求 m2 62.5m 求 1052 37. 初取中心距 120a 带长 2LDam48L 基准长度 50m (3)求中心距和包角 中心距 12()84LaLDm 5062. 2(4506.)37.5 1am 小轮包角 2118aa 0542.801 7 (4)求带根数 带速 1.83m/s 160nvDv 传动比 i=4 带的根数 由表 11.8 由表 11.7 .4P0.89K 由表 11.20 由表 11.10 1.0LK0.1PW Z= pck = =4.76 取 Z=5 根0.3.619. 张紧力 20 25CKPFqvVZ =500 +(0.04 ) .318.08921.835 (由表 11.4 q=0.04/m) .0FN 轴上载荷 2sin0FZQ 142.85.Si 26.3Q 带轮的结构 由 YS741电动机 知轴的直径 14dm 故小带轮的孔径 V带的尺寸 顶宽 6b 节宽 5.3p 高 4hm 轮缘尺寸 =4.7mm =1.6mmminhfinh e=8mm f=7mm =5mmm 带轮计算直径 D 大带轮 214D102D 8 带轮的外径 0D10251.6ha1028.Dm 2 23 带轮的宽度 B()2(51)827zef46B6.3 2闭式直齿轮圆锥齿轮传动的设计计算 选材: 直齿锥齿轮的加工多为刨齿,不宜采用硬齿面,小齿轮用 45 钢调质处理, 硬度为 取平均硬度为 ,大齿轮选用 45 钢正火处理,2175HB230HB 硬度为 ,取平均硬度为 。619 齿面接触强度计算(由于小齿轮更容易失效故按小齿轮设计): 齿数 Z和精度等级 工业用齿应大于等于 14 选取小齿轮齿数 16Z 则大齿轮的齿数为 初取 ,2.501iZ 16Z240Z 估计 左右 由表 12.9 选 8级精度/Vms 使用系数 由表 12.9 KA 1.25KA 动载系数 由图 12.9 0V 齿间载荷分配系数 kh 估计 10/KFAtNmb = = =0.928cos2i.5 9 = = =0.371cos21i2.51 = = =17.24ZVcs1z60.98 = = =107.822o4.37 =1.661.8cos2z =0.88 4.63Z 由此得 =1.285120.8KHz 齿向载荷分布系数 查课本表 及注释 =1.9 2KH 载荷系数 KAV 1.25.3193.42 0.25669.0PTNmn6587TI 弹性系数 查课本表 ZE1189.ZMPa 节点区域系数 查课本图 H262.5ZH 接触最小安全系数 查课本表 limS1410limS 总工作时间 th83080th 应力循环次数 NL 96143.3011nt 10 993.01.321052NLi 接触寿命系数 查课本图 12-18 Z 12.NZ 接触应力 =638.1H 670lim1.5ZSH H =590.521li2.N2 小齿轮大端分度圆的直径 1d 1d24.73205.3ZKTEHR = 2.61.89.50.3245.8 演算圆周速度及 KFAtb =(1-0.50.3)45.84=39mm10.54ddmR =0.714m/s3.950661 nmvs =329.1N 247.1TFNtdm =221cos dRb0.35421981.6m.539./0/846KFAtNmb 确定传动主要尺寸 11 大端模数 m = = =2.865 取 m=31dZ45.86 实际大端分度圆的直径 =48mm2.0mz1d =120mm 5d2 锥距 R = 21Z23640.Rm 齿宽 b 0.39.87b9b 按齿根弯曲疲劳强度计算 齿形系数 查课本图 12-30 =2.66 =2.31YFa1YFa2YFa 应力修正系数 查课本表 12-22 =1.64 =2.02 重合度系数 =0.710.750.75.2.21 齿间载荷分布系数 查课本表 12-10KF = 1.440.71YKF 载荷系数 KAVF 1.250.493.08 弯曲疲劳极限 查课本表 limF3()c6lim1MpaF =570Mpa2 弯曲最小安全系数 查课本表 12-14 =1.60liSliS 应力循环次 NL601350841nth8.061NL 8.62.2Li 83.2 弯曲寿命系数 查课本图 12-24 = =1.0Y 1Y 12 尺寸系数 查课本图 12.25 =1.0YX XY 许用弯曲应力 Flim1YFNS =420.160.MPa1FMPa li2 YXSF =396.75701.6a2a 验算 4.123051KTYSFZmiR .73861.607. 5 1542Mpa 1F = F2.310546Ys 16.pa2F 传动无严重过载,故不做静强度校核 锥齿轮结构 148dm210d11(0.5).48.mRm221arcos.9.21068arctn/arctn3/4.2.6hR 13 arctn/arctn3.6/42.ffhRm19.b 3闭式直齿圆柱齿轮设计计算 材料的选取:小齿轮用 钢调质处理,硬度 ,平均取为 。大452175HB230HB 齿轮用 钢正火处理,硬度 ,平均取为 。619 齿面接触疲劳计算: (1)初步计算: 轴的转矩 1T 1438.TNm 查课本表 12-3,取齿宽系数 d0d 接触疲劳极限应力 由课本图 limH12.7()c67li1MpaH =620Mpa2 初步计算的许用接触应力 0.90.9681li1MPaH 6031paH 52m2 2M 由表 取Ad85Ad 初步计算小齿轮直径 1 14938.12531 20Tid mH = 取.7135dm 齿宽 b1035d6b (2)校核计算: 圆周速度 v1.466nms0.24v 14 精度等级 查课本表 12-6 选 8级精度 齿数 Z 初取 =181Z =722 模数 = 由表 12.3 取1dmZ368m 使用系数 查课本表 =1.25KA129KA 动载系数 查课本图 =1.10VV 齿间载荷分布系数 查课本表 12-10,先求H 214938.29.46TFNtd829.4FNt 1.2589.4.36KAtNmb 8.m10 =1.65811.cos.83272z 4.3Z0.84Z 由此得 =1.28120.86KHzKH 齿向载荷分布系数 HK 310.61bABCbd =1.33621.70.0KH 载荷系数 K AV .51.836 2.35 15 弹性系数 查课本表 ZE12189.ZMPaE 节点区域系数 查课本图 H62.5H 接触最小安全系数 查课本表 limS40limS 接触寿命系数 查课本图 ZN1281.8ZN25 许用接触应力 H6701.25lim1ZSH7.9MpaH.li2N 38.1 验算 : 21KTiZHEbd .35498.1189.250.8 a 7.6Mp H2 计算结果表明,触疲劳强度较为合适,齿轮尺寸无需调整 (3)确定传动主要尺寸实际分度圆直径 D 因模数取标准值时,齿数已重新确定,但并未圆整。 故分度圆直径不会改变,即 实际分度圆直径 218dmz361dm 742 中心距 a12()()za 9090a 齿宽 取b36dm14bm236 16 (4)齿根弯曲疲劳强度验算: 重合度系数 Y0.750.75.2.2168Y0.72Y 齿间载荷分布系数 查课本表KF1 =1.4240.72YKF 齿向载荷分布系数 358(.4)bh 查课本图 12-14 =1.24 载荷系数 KKAVF 1.250.41.22.57K 齿形系数 查课本图 YFa.Ya18Fa 应力修正系数 查课本表 = 1.82S159s2S 弯曲疲劳极限 查课本表 lim123()c7limMp 50aF 弯曲最小安全系数 查课本表 liSF41.2liS 弯曲寿命系数 查课本图 YN12.1YN 尺寸系数 由图 X.5.0YX 许用弯曲应力 Flim1FXS 580.12MPa51.2MpaFliYNSF 90.512a503.42pa 17 验算: 21KTYFaSbdm .5473.261.5908MPa 8.1Mpa 1F2YFS 1.2110 齿轮端面与内机 壁距离 2 210 机盖,机座肋厚 m,1 85.0,.1m8 轴承端盖外径 2D+(55.D2 5) 3d7077 82 八键的设计 1.高速轴键的设计与校核 根据 计手册第四章,选用 圆128,1937.62dmTNm /1096GBT键 845 头普通平 键(A 型),课本第七章表 7.1铸钢的许用挤压应力 2MPap149834.6210.07MPadlh 所以键的强度满足。 所选键为 强度合格;bl 2.中间轴键的设计与校核 根据 查手册第四章,选用 圆275,867.10dmTNm /1096GBT63键 2 头普通平键(A 型),本表 7.1铸钢料的许用挤压应力 ;p 34 48657.106.532pTMPadlh 所选键的度满足。 3.低速轴键的设计与校核 根据 查设手册第四章,选用 键275,483.9dmTNm /1096GBT 圆头普通平90214 键(A 型),查课本表 7.1铸钢料的许用挤压应力 2p53.210.9874MPadlh 所选键的强度满足。 九减速器的各部位附属零件的设计. 1窥视孔盖与窥视孔: 在减速器上部可以看到传动零件啮合处要开窥视孔, 大小只要够手伸进操作可。 以便检查齿面接触斑点和齿侧间隙,了解啮合情况.润滑油也由此注入机体内. 2放油螺塞 放油孔的位置设在油池最低处,并安排在不与其它部件靠近的一侧,以便于放 油,放油孔用螺塞堵住并加封油圈以加强密封。 3油标 油标用来检查油面高度,以保证有正常的油量.因此要安装于便于观察油面及油面稳定之 处即低速级传动件附近;用带有螺纹部分的油尺,油尺上的油面刻度线应按传动件浸入深 度确定。 4通气器 减速器运转时,由于摩擦发热,机体内温度升高,气压增大,导致润滑油从缝隙向外 渗漏,所以在机盖顶部或窥视孔上装通气器,使机体内热空气自由逸处,保证机体内外压 力均衡,提高机体有缝隙处的密封性,通气器用带空螺钉制成. 5启盖螺钉 为了便于启盖,在机盖侧边的边缘上装一至二个启盖螺钉。在启盖时,可先拧动此螺钉顶 起机盖;螺钉上的长度要大于凸缘厚度,钉杆端部要做成圆柱形伙半圆形,以免顶坏螺纹; 螺钉直径与凸缘连接螺栓相同。 在轴承端盖上也可以安装取盖螺钉,便于拆卸端盖.对于需作轴向调整的套环,装上二个螺 钉,便于调整. 6定位销 为了保证剖分式机体的轴承座孔的加工及装配精度,在机体联接凸缘的长度方向两端各安 35 置一个圆锥定位销。两销相距尽量远些,以提高定位精度。如机体是对称的,销孔位置不 应对称布置. 7环首螺钉、吊环和吊钩 为了拆卸及搬运,应在机盖上装有环首螺钉或铸出吊钩、吊环,并在机座上铸出吊钩。 8调整垫片 用于调整轴承间隙,有的起到调整传动零件轴向位置的作用. 9密封装置 在伸出轴与端盖之间有间隙,必须安装密封件,以防止漏油和污物进入机体内. 十防滑方式的确定 1滚动轴承的润滑 滚动轴承的润滑采用脂润滑,它不易流失密封性好加脂周期长。 该滚动轴承的工作温度不太高的可选钙基润滑脂,滚动轴承摩擦力大。可选 1号润滑 脂 GB491-87 2齿轮的润滑 由于展开式齿轮的传动速度比低,载荷大,油脂容易流失,所以采用粘度很高,防锈 性好的开式齿轮油。采用油池润滑,自然冷却,侵入油中的齿轮深度为 1-2个齿高, 采用液压油 GB1118.1-1994. 附注: 参考数据 吴宗泽,罗圣国主编机械设计课程设计手册。 邱宣怀主编机械设计。 编号无锡太湖学院毕业设计(论文)相关资料题目:单级减速机箱体和箱盖工艺工装设计 机电 系 机械工程及自动化专业学 号: 0923199学生姓名: 张亚东 指导教师: 鲍虹苏(职称:高工 ) (职称: )2013年5月25日目 录一、毕业设计(论文)开题报告二、毕业设计(论文)外文资料翻译及原文三、学生“毕业论文(论文)计划、进度、检查及落实表”四、实习鉴定表无锡太湖学院毕业设计(论文)开题报告题目:单级减速机箱体和箱盖工艺工装设计 信机 系 机械工程及自动化专业学 号: 0923199 学生姓名: 张亚东 指导教师: 鲍虹苏 ( 职称:高工) (职称: )2012年11月24日 课题来源机械制造业是一个国家最基础的行业,也决定了一个国家制造业的整体水平现在中国已经是一个制造大国,中国的制造业规模已经达到世界第四位,仅次于美国、日本和德国。研究内容本设计是针对减速机箱体工艺的制作,主要研究的是减速机箱盖的工艺过程、减速机的底座的工艺过程、减速机箱体合装后的工艺过程以及对该技术的测试和其实用性的研究。并由此做出了对现行的减速机的箱体的改造和进一步的完善。在这次的箱体工艺制造中,对一些主要程序比如说结合面联接孔、钻顶面螺纹底孔、攻螺纹、钻侧面测油孔、放油孔、螺纹底孔、沉孔、攻螺纹 等的研究。拟采取的研究方法、技术路线、实验方案及可行性分析设计任务1) 设计一个中等复杂的零件的加工工艺规程;2) 设计一个专用夹具;3) 编写设计说明书。根据设计任务做出减速机箱的基本设计任务1)绘制零件工件图一张;2)绘制毛坯零件合图一张;3)编制机械加工工艺规程卡片一套;4)编写设计说明书一份;5)收集和研究原始资料,为夹具结构设计做好技术准备。6)初步拟定夹具结构方案,绘制夹具结构草图,进行必要的理论计算和分析。选择最佳的夹具结构方案,确定夹具精度和夹具总图尺寸、公差配合与技术要求。7) 绘制夹具总图和主要非标准件零件图,编写设计说明书。8)编制夹具特殊使用维护、操作、制造方面的说明或技术要求。研究计划及预期成果研究计划:2012年11月12日-2012年12月25日:按照任务书要求查阅论文相关参考资料,填写毕业设计开题报告书。2013年1月11日-2013年3月5日:填写毕业实习报告。2013年3月8日-2013年3月14日:按照要求修改毕业设计开题报告。2013年3月15日-2013年3月21日:学习并翻译一篇与毕业设计相关的英文材料。2013年3月22日-2013年4月11日:设计减速机箱体和箱盖的结构并画出相关草图2013年4月12日-2013年4月25日:完善设计所需的各种零件图、夹具图,并对设计的所有数据进行整理,做好撰写毕业论文的准备。2013年4月26日-2013年5月20日:毕业论文撰写和修改工作。预期成果:机械制造技术设计是培养机械工程类专业学生应职应岗能力的重要实践性教学环节,它要求学生能全面综合地运用所学的理论和实践知识,进行零件机械加工工艺规程和工艺装备的设计。其基本目的是:1) 培养工程意识。2) 训练基本技能。3) 培养质量意识。4) 培养规范意识。特色或创新之处1、 设计了一副可以多方面加工的夹具,减少了原材料的应用和所需的工时。2、 设计了多种加工方案,并对其比较,选出最佳方案。已具备的条件和尚需解决的问题1、一是对镗床的不熟悉,二是在公差与配合方面的知识所学较少。2、学院图书馆相关资料有限,并且很多资料不外借处学校,设计此项目任务重工作量大物力条件有限以及经济上的原因造成难以落实原材料加工出成品3、经过努力,设计达到了预想的成功,由于条件的限制没能加工出成品,但对于我自己来说已经学到了不少东西。指导教师意见 指导教师签名:2011年 11 月 20 日教研室(学科组、研究所)意见 教研室主任签名: 年 月 日系意见 主管领导签名: 年 月 日英文原文Mineral product monorail reduction gear synopsisFirst:what is reducerReducer is a dynamic communication agencies, the use of gear speed converters, motor rotational speed reducer to the Rotary to be few, and have greater torque institutions. The reducer role 1) velocity at the same time increase the output torque, torque output ratio by motor output by slowdown, but the attention should be paid to exceed the rated torque reducer. 2) the speed at the same time reduce the inertia load, the inertia of deceleration than reduced to the square. We can look at the General Motors has a value of inertia. The type of reducer General helical gear reducer has reducer (including parallel shaft helical gear reducer, a worm reducer, bevel gear reducer, etc.), planetary gear reducer, Cycloid reducer, a worm reducer, a planetary friction CVT mechanical machines. Common reducer 1) worm reducer is the main characteristics of a reverse self-locking function, can be larger than a slowdown, input shaft and output shaft axis is not the same, nor in the same plane. But generally larger, transmission efficiency is not high, the accuracy is not high. 2) Harmonic Harmonic Drive reducer is controllable using flexible components to transfer elastic deformation and dynamic movement, not volume, high precision, but the disadvantage is that flexible wheel limited life, impatient shocks, rigidity and pieces of metal relatively poor. Not too high speed input. 3) planetary reducer its comparative advantage is compact structure, the return gap small, high precision, and have a long life span rated output torque can be done great. However, a price slightly expensive, the requirements of parts before assembly 1. Rolling cleaning with gasoline, kerosene other parts cleaning. All parts and Xiangbenna not allowed to have any impurities exist. Gear box and the inner wall (Worm), unprocessed surface has not been coated twice erosion-resistant oil paint, box has the outer surface coated primer and paint color (color requested by host). 2. Parts coated with a face wash after lubricants Second, the requirements of installation and adjustment 1. Rolling installation Rolling bearing inner ring should be installed at the shaft shoulder close to gap must not pass 0.05 mm thick Cypriot feet. 2. Bearing axial clearance of the clearance can not be adjusted bearings (such as deep groove ball bearings), axial clearance of 0.25 to 0.4 mm; the clearance adjustable bearing axial clearance numerical table. Click Tapered Roller Bearings axial clearance; angular contact ball bearing axial clearance 3. Gear (Worm) meshing tooth space available Cypriot side foot of lead or pressure. Will be lead wire on the alveolar, and then turning gear and squash lead wire, measuring two teeth side was crushed lead wire thickness and the size of which is adjacent teeth. 4. Tooth contact dot cylinder gear tooth contact Dot 2-10-4; bevel gear tooth contact Dot 2-11-4; Gearing contact Dot 2-12-4 Third, seal requirements 1. Box partition between the surface does not allow any pads filled, but can be coated or water glass sealant to ensure that the seal; 2. Assembly, the bolt tightening box, before using 0.05 mm Cypriot-foot inspection Covers Block with me and between the sealing surface; 3. Shaft seal should stretch to smear grease. The seal should be installed in strict accordance with the requirements Forth, lubrication requirements 1. Rationally determine the types of lubricants and greases and grades 2. Bearing lubrication fat, grease filled in the general Fatliquor space can be 1 / 2 to 2 / 3. 3. Lubricants should be regularly replaced, the new reducer used for the first time, the operation of oil-7 14 days, according to the situation can be after every 3 to 6 months for first oil. Fifth, the test requirements 1. Empty operation: at rated speed is, anti-running 1 to 2 hours; 2. Load test: at rated speed, rated load operation, the oil temperature balance to date. On the gear reducer, requested the pool temperature is not more than 35 oC, bearing temperature rise no more than 40 oC; the worm reducer, requested the pool temperature not more than 60 oC, bearing temperature of not more than 50 oC; 3. Entire testing process for the smooth operation, noise, not loosening the fixed link, sealed, not with the Sixth, packaging and transportation requirements 1. Protruding shaft and its annex should Oiler packaging; 2. Handling, lifting may not use screw rings and lug all of the above technical requirements are not necessarily listed, and sometimes also by other projects, mainly by the specific design requirements. Seventh. Technical requirements 1. Assembly, all parts cleaning with kerosene, gasoline Rolling cleansing, while the existence of any debris. Oil is not painted wall corrosion coatings twice; 2. Backlash with lead wire mesh test of not less than 0.16 mm, lead wire Backlash may not exceed the smallest of the four times; 3. Used Tu-color dot test. Tooth high point of contact by not less than 40% of contact spots on teeth not less than 50 per cent. Can be used when necessary, grinding or scraping after grinding to improve contacts; 4. Bearing axial clearance should be adjusted: 40 0.05 - 0.1 mm, 55 0.08 - 0.15 mm; 5. Test reducer subdivision surface, the contact surface and seal, oil spills are not allowed. Split-Tu allowed to paint or water glass seal and allow the use of any filler; 6. Engine lubricants to the contents N100 provisions height;Below I introduce our country reduction gear the development present situation First, the domestic reduction gear many by the gear drive, the worm drive primarily, but has the power and the load ratio generally is small, or velocity ratio great and mechanical efficiency excessively low question.Moreover, in the material quality and the technological level also has many weakness, the large-scale reduction gear question is specially more prominent, the service life is not long.The domestic use large-scale reduction gear (above 500kw), many from overseas (for example Denmark, Germany and so on) imports The 60s start few tooth reduction gears and so on difference transmission, cycloid pin gear transmission, overtone transmission which produces has the velocity ratio to be big, volume small, mechanical efficiency higher merit? .But its transmission theory limit, cannot transmit the oversized power, the power all must be smaller than generally 40kw. Because in the transmission theoretically, the technological level and the material quality aspect has not broken through, therefore, has not been able fundamentally to solve the transmission power in a big way, the velocity ratio big, the volume small, the weight light, mechanical efficiency higher these requests basically.The 90s initial period, the home appears three links (gear) the reduction gear, is one kind of outside stable motion gear drive reduction gear, it may realize the great velocity ratio, transmission load ability is also big. Its volume and the weight are all lighter than the dead axle speed reducer gear, the structure is simple, the efficiency is also high.Because this reduction gear three axle parallel structure, therefore caused the power/volume (or weight) the ratio is still small.Also its input axis and the output shaft on the identical spool thread, this do not have in the use many inconveniently. Not only Beijing Institute of Technology develops in successful stable motion speed reducer gear to have outside three link reduction gear merit, but also has the big power/weight (or volume) the ratio, as well as the input axis and the output shaft on identical spool thread merit, is at the domestic leading position.The home has the minority college and the factory and mining enterprise does the research work to in stable motion gear drive certain principles, has published some research paper, in has done some work using the cycloidal tooth crop rotation stable motion reduction gear.Second, the stable motion speed reducer gear principle of work synopsis, the stable motion speed reducer gear is refers to in a counter gear transmission, a gear in the stable motion generator actuation mean plane parallel motion, meshing through tooth profile between, actuates another tooth crop rotation dead axle to decelerate the rotation, the realization reduction gear function.The stable motion generator may use the parallelogram organization, either sine organization or cross slide organization.This achievement uses the parallelogram organization to take the stable motion generator. The stable motion generator may be the hypothesized use parallelogram organization, also may be the entity use parallelogram organization.Has the practical value stable motion gear mechanism for in counter gear organization, therefore may divide into the internal tooth crop rotation stable motion movement and the external tooth crop rotation stable motion movement two kind of situations.Outside the stable motion gear reduction organization, its internal tooth crop rotation stable motion movement, actuates the external gear and makes the deceleration rotation output.This organization also calls three links (gear) the reduction gear. As a result of the internal tooth crop rotation stable motion, two crank centers establish outside the annular gear tooth ring, therefore its size is not compact, cannot solve the volume major problem.? In stable motion gear reduction, its external tooth crop rotation stable motion movement, actuation internal tooth crop rotation deceleration rotation output.As a result of the external tooth crop rotation stable motion, two crank centers can establish in the external gear tooth ring, reduced the organization overall size greatly. Because in stable motion gear mechanism transmission efficiency high, volume small, input output coaxial line, therefore by widespread application prospect.Third, this project technical characteristic and key technologies? 1. this project technical characteristics, in this new stable motion speed reducer gear and domestic and foreign had the speed reducer gear compares, has the following characteristic: (1) velocity ratio scope is big, gets up from I=10, may reach most greatly several thousand.If manufactures the great velocity ratio the reduction gear, then demonstrates this reduction gear the merit.(2) transmission power scope is big: And may connect a body manufacture with the electric motor. (3) structure simple, the volume small, the weight is light.Reduces about 1/3 compared to the existing speed reducer gear.(4) mechanical efficiency is high.95 (5) this reduction gear input axis and the output shaft are on the identical spool thread.This reduction gear see Table 1 with other reduction gear performance comparison. Because lacks the data, various reduction gears power/load ratio which in the table arranges in order is most superior.? Table 1? Each kind of reduction gear comparison model power (kw) reduction gear ratio quality (kg) QI-450? 93 31.5 1820 ZSY-250? 95 31.5 540 NGW-92 88.1 31.5 577 SEW (Germany)? 90 28.61 1300 NP-100? 100 30 400 Note: NP-100 is in the stable motion speed reducer gear, the SEW reduction gear quality contains the electrical machinery.2. this project key technologies? May know by Figure 2, in “stable motion speed reducer gear is by annular gear Z2, external gear Z1 and the parallelogram organization combination becomes.Its transmission principle is: The electrical machinery input rotary motion, the external tooth crop rotation parallel migration, its center of circle path is a circle, makes the dead axle rotation with it meshing annular gear. Because external tooth crop rotation parallel migration, therefore name stable motion gear mechanism.The gear parallel migration needs to have the auxiliary body help realization, may use (612) to sell the axis, the roller takes the hypothesized auxiliary stable motion organization, also may use the eccentric shaft to take the entity auxiliary stable motion organization.In the stable motion speed reducer gear key technologies and the essential craft are the composition parallelogram component size computation and the request processing precision, the gear teeth main parameter choice. These factors will all affect the transmission ability and the transmission quality.Overall speaking, the group cost reduction gear various spare parts all request to have the high precision, they will be deciding the reduction gear overall transmis3. this project survey this project has obtained the Chinese practical new patent, the patent number: ZL95227767.0? .? This project trial produced the first prototype from 1995 (power 2.5kW, after velocity ratio I=32), with some factory and mine cooperation, has one after another designed following several kind of different powers, the different velocity ratio reduction gear.(1) electrically operated on rollers gate uses the reduction gear, power 550W, velocity ratio I=26, is united as one body with the electrical machinery.sion quality. (2) mixer uses the reduction gear, power 370W, velocity ratio I=17.(3) some military goods use two kind of reduction gears, one kind of power 370W, velocity ratio I=23.5; Another kind of power 370W, velocity ratio I=103 two level of transmission reduction gear.(4) steel mill large package rotary abutment reduction gear, power 7.5kw, velocity ratio I=64.(5) steel mill table reduction gear, power 7.5kw, transmission I=11. In this patent foundation, has developed one kind of new ultra-large reduction gear, the power may reach 1000kw, at present is developing subminiature (outlook size for a millimeter level) miniature reduction gear. Graduation design task First, a design Monorail Driver Design reducer Second, the design of the original data 1 Monorail drive reducer Power Rating: 7.5 KW; 2 Monorail reducer drive the total transmission ratio: 15 around; 3 Monorail reducer drive car driven by the side of the output shaft from the race distance of not more than 200 mm; 4 Monorail reducer drive the total length of less than 420 mm, the width is not more than 450 mm and the total height of not more than 690 mm; Third, the equipment and the working environment This can be used to mine underground, open-air, dust, humidity, air quality, bad comparison bad work environment, and the operational requirements of a safe space. Fourth, the design requirements To meet the application requirements under the premise that the minimum cost of manufacturing. From the following aspects considered; (L) to streamline the shape of each parts, machinery simple structure; (2) merge the functions of spare parts, reducing the types or quantities of spare parts; (3) Application of the new structure, new technology, new materials, product reliability; (4) decomposition components, its assembly, the assembly of the most simple structure; (5) similar to parts of the division; (6) standards for similar products by product serial number sequence analysis; (7) The realization of the common parts of the product and standardization. (8) assembly equipment design a map (0), the Six Parts (3), the design specification of a (not less than 30,000 words), and the design of technical and economic analysis.中文译文一、 什么是减速器减速器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。1、减速器的作用 1)降速同时提高输出扭矩,扭矩输出比例按电机输出乘减速比,但要注意不能超出减速器额定扭矩。 2) 减速同時降低了负载的惯量,惯量的减少为减速比的平方。大家可以看一下一般电机都有一个惯量数值。2、减速器的种类 一般的减速器有斜齿轮减速器(包括平行轴斜齿轮减速器、蜗轮减速器、锥齿轮减速器等等)、行星齿轮减速器、摆线针轮减速器、蜗轮蜗杆减速器、行星摩擦式机械无级变速机等等。3、常见减速器 1) 蜗轮蜗杆减速器的主要特点是具有反向自锁功能,可以有较大的减速比,输入轴和输出轴不在同一轴线上,也不在同一平面上。但是一般体积较大,传动效率不高,精度不高。 2) 谐波减速器的谐波传动是利用柔性元件可控的弹性变形来传递运动和动力的,体积不大、精度很高,但缺点是柔轮寿命有限、不耐冲击,刚性与金属件相比较差。输入转速不能太高。 3) 行星减速器其优点是结构比较紧凑,回程间隙小、精度较高,使用寿命很长,额定输出扭矩可以做的很大。但价格略贵一、对装配前零件的要求 :1.滚动轴承用汽油清洗,其他零件用煤油清洗。所有零件和箱体内不许有任何杂质存在。箱体内壁和齿轮(蜗轮)等未加工表面先后涂两次不被机油侵蚀的耐油漆,箱体外表面先后涂底漆和颜色油漆(按主机要求配色)。 2.零件配合面洗净后涂以润滑油二、安装和调整的要求 1.滚动轴承的安装滚动轴承安装时轴承内圈应紧贴轴肩,要求缝隙不得通过0.05mm 厚的塞尺。 2.轴承轴向游隙对游隙不可调整的轴承(如深沟球轴承),其轴向游隙为0.250.4mm;对游隙可调整的轴承轴向游隙数值见表。点击查看圆锥滚子轴承轴向游隙;角接触球轴承轴向游隙 3.齿轮(蜗轮)啮合的齿侧间隙可用塞尺或压铅法。即将铅丝放在齿槽上,然后转动齿轮而压扁铅丝,测量两齿侧被压扁铅丝厚度之和即为齿侧的大小。 4.齿面接触斑点圆柱齿轮齿面接触斑点2-10-4;圆锥齿轮齿面接触斑点2-11-4;蜗杆传动接触斑点2-12-4 三、密封要求 1.箱体剖分面之间不允许填任何垫片,但可以涂密封胶或水玻璃以保证密封; 2.装配时,在拧紧箱体螺栓前,应使用0.05mm的塞尺检查箱盖和箱座结合面之间的密封性; 3.轴伸密封处应涂以润滑脂。各密封装置应严格按要求安装四、润滑要求 1.合理确定润滑油和润滑脂类型和牌号 2.轴承脂润滑时,润滑脂的填充量一般为可加脂空间的1/22/3。 3.润滑油应定期更换,新减速器第一次使用时,运转714天后换油,以后可以根据情况每隔36个月换一次油。五、试验要求 1.空载运转:在额定转速下正、反运转12小时; 2.负荷试验:在额定转速、额定负荷下运转,至油温平衡为止。对齿轮减速器,要求油池温升不超过35oC,轴承温升不超过40oC;对蜗杆减速器,要求油池温升不超过60oC,轴承温升不超过50oC; 3.全部试验过程中,要求运转平稳,噪声小,联接固定处不松动,各密封、结合处不 六、包装和运输要求 1.外伸轴及其附件应涂油包装; 2.搬运、起吊时不得使用吊环螺钉及吊耳以上技术要求不一定全部列出,有时还需另增项目,主要由设计的具体要求而定。七、技术要求 1.装配前,所有零件用煤油清洗,滚动轴承用汽油清洗,不许有任何杂物存在。内壁涂上不被机油腐蚀的涂料两次; 2.啮合侧隙用铅丝检验不小于0.16mm,铅丝不得大于最小侧隙的4倍; 3.用涂色法检验斑点。按齿高接触点不小于40%;按齿长接触斑点不小于50%。必要时可用研磨或刮后研磨以便改善接触情况; 4.应调整轴承轴向间隙:40为0.05-0.1mm,55为0.08-0.15mm; 5.检验减速器剖分面、各接触面及密封处,均不许漏油。剖分面允许涂以密封油漆或水玻璃,不允许使用任何填料; 6.机座内装N100润滑油至规定高度。八、下面我介绍我国减速器的发展现状(一)、国内的减速器多以齿轮传动、蜗杆传动为主,但普遍存在着功率与重量比小,或者传动比大而机械效率过低的问题。另外,材料品质和工艺水平上还有许多弱点,特别是大型的减速器问题更突出,使用寿命不长。国内使用的大型减速器(500kw以上),多从国外(如丹麦、德国等)进口。60年代开始生产的少齿差传动、摆线针轮传动、谐波传动等减速器具有传动比大,体积小、机械效率高等优点?。但受其传动的理论的限制,不能传递过大的功率,功率一般都要小于40kw。由于在传动的理论上、工艺水平和材料品质方面没有突破,因此,没能从根本上解决传递功率大、传动比大、体积小、重量轻、机械效率高等这些基本要求
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