普通车床主轴箱设计说明书.doc

【JX17-83】普通车床主轴箱设计(二维+三维+论文)

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【JX17-83】普通车床主轴箱设计二维三维论文.rar
【JX17-83】普通车床主轴箱设计(二维+三维+论文)
普通车床主轴箱设计说明书.doc---(点击预览)
CAD图纸
1轴装配图-a2.dwg
2轴装配图-a2.dwg
3轴装配图a2.dwg
4轴装配图-a2.dwg
5轴装配图-a2.dwg
6轴装配图.dwg
主传动系统结构装配图.dwg
主轴箱箱体零件图.dwg
传动系统图.dwg
双联齿轮 A3.dwg
转速图.dwg
齿轮 A3.dwg
三维图
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主轴箱总装图.SLDASM
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编号:20257603    类型:共享资源    大小:51.45MB    格式:RAR    上传时间:2019-06-25 上传人:caiq****857 IP属地:浙江
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JX17-83 【JX17-83】普通车床主轴箱设计二维+三维+论文
资源描述:
【JX17-83】普通车床主轴箱设计(二维+三维+论文),JX17-83,【JX17-83】普通车床主轴箱设计二维+三维+论文
内容简介:
摘 要车床主传动的设计,包括设计的三个方面,即:在标题之下设计具体使用的机器的规格,主轴转速极限,速度或列数公比范围,其他参数相关的建议确定选定的速度水平值机身;分析和比较,选择传输;配制型或网状结构,高速发展;其次,根据发动机的类型和发动机功率,则确定计算出的轴速度和不同的传输部件中,初始主轴速度米直径模型的皮带和确定摩擦片的数量,大小和数量;经过控制传动部件轴,轴,齿轮,轴承的刚度,强度和使用寿命的完整的装配草图。最后,设计完成和设计的动态运动,尤其是“结构性”节目盘,图中单独设计的组件装配图后。关键词:车床;数控;传动系统;结构网;结构式IVAbstractWith the sophistication of todays industrial equipment have become increasingly demanding, the degree of precision machining processing equipment mechanical processing equipment has become increasingly demanding. Search, Now a lot of research on the basis of the information on the machine automation technology in-depth research and analysis, and describes the design of the machine control system. The whole process is mainly on the lathe main transmission design.Lathe main transmission design, including the three aspects of the design, namely: according to the design of the title given machine use, specifications, spindle speed limit, the speed or the number of columns common ratio series, other relevant motion parameters to determine the selected spindle speed levels value; analysis and comparison, selecting transmission scheme; prepare formula or network structure, develop speed; determining a gear and pulley diameter; transmission drawn map. Secondly, according to the type of machine and motor power, determined that the calculated spindle speed and various transmission parts, an initial shaft diameter modulus gear, belt model and determine the number, size and number of friction plates; after the completion of assembly sketch to checking the transmission member (shaft, spindle, gear, bearing) stiffness, strength or lifetime. Finally, after the completion of design and dynamic design movement, to the main drive program structured designed spindle gearbox assembly drawings and part drawings, conduct focus drive shaft assembly, spindle assembly, transmission mechanism, box, lubrication and sealing, transmission slip gear shaft and parts of the design.Keywords: lathe; transmission, network structure, structure; NC目 录摘 要IAbstractII目 录III第1章 绪 论11.1 数控技术的应用与发展11.1.1数控机床与发展趋势11.1.2数控技术11.1.3数控技术发展趋势21.1.4数控技术在机械工业中的进展21.2数控车床的工艺范围及加工精度31.2.1工艺范围31.2.2加工精度3第2章 传动方案及传动系统图的拟定12.1 电动机的选择12.2 传动路线及转速图的拟定1第3章 主轴箱主要零件的设计及校核43.1 主轴箱箱体尺寸的确定43.2 传动轴各主要零件的设计43.2.1 轴径的估算43.2.2 V带轮的设计43.2.3 多片式摩擦离合器的计算73.2.4 轴I上的一对齿轮的计算83.2.5 齿轮的校核123.2.6 轴的校核133.2.7 轴承的选择143.3 传动轴II各主要零件的设计153.3.1 轴径的估算153.3.2 齿轮的校核163.3.3 传动轴的校核163.3.4 轴承的校核183.4 传动轴III各主要零件的设计183.4.1 轴径的估算183.4.2 齿轮的校核193.4.3 传动轴的校核203.4.4 轴承的校核223.5 传动轴IV各主要零件的设计223.5.1 轴径的估算223.5.2 齿轮的校核233.5.3 传动轴的校核243.5.4 轴承的校核263.6 传动轴V各主要零件的设计273.6.1 轴径的估算273.6.2 齿轮的校核273.6.3 传动轴的校核283.6.4 轴承的校核303.7 传动轴VI各主要零件的设计313.7.1 轴径的估算313.7.2 主轴上一对齿轮的计算313.7.3 齿轮的校核343.7.4 传动轴的校核353.7.5 轴承的校核36第4章 主轴箱结构设计及说明394.1 结构设计的内容、技术要求和方案394.2 展开图及其布置39总结40参考文献41致谢42第1章 绪 论1.1 数控技术的应用与发展1.1.1数控机床与发展趋势1数控机床:出生于1946年,是世界上第一台计算机,这表明人类是为了加强和部分替代工具面试创建。使用这些工具只有提高农业,工业和公民创造人类的体力劳动,从人类社会的基础,有了质的飞跃输入的信息进行比较。数字控制NC阶段1952年至1970年人们需要在一个特定的主机是被称为连接NC材料有线NC数控系统,被称为NCNC采用数字逻辑电路“搭”。随着组件在1952年的发展,历经三代在这个阶段,第一代-管,在1959年的第二代-晶体管,1965年,第三代-集成电路。计算机数控CNC阶段1970年-至今到1970年,通用汽车公司出现了小型机和批量生产。1974年微处理器的数控系统。这是因为一个小的电脑操作也有丰富的控制机器的能力一次来控制多台机器,称为对照组微处理器的经济逻辑,同样采用。然后,介质的可靠性是不理想的。速度和早期的微处理器的功能,尽管它是不够高,然而,可以通过使用多处理器体系结构解决。因为微处理器是通用计算机的一个基本组成部分,称为数字计算机控制。到1990年,PC摄像头PC,用来指你家的电脑,在高性能系统如数控的阶段,以满足基本要素的要求开发的。基于PC的数控系统,现在进入了一个阶段。总之,计算机数控阶段经历了三代。1970年,第四代-介质;1974年,第五代-1990年和第六代微处理器-基于PC国外称为基于PC。1.1.2数控技术随着计算机,微电子,信息,自动控制,精密的检测设备和生产技术的飞速发展,数控机床已取得显著的进展。近年来,一些相关的技术,如新材料和工具,伺服和超高速切削技术的发展主轴伺服电源发展要求和工程质量更高的产品的开发正在增加,加速数控机床的发展。数控机床目前正在朝着高速,高精度和工艺高浓度,高复杂和高可靠性方向发展。技术世界的发展趋势,而数控设备,主要体现在以下几个方面。高速精密有效灵活复杂的过程和多轴实时智能新结构编程自动化整合开环控制模式1.1.3数控技术发展趋势1科技与现代数控技术和装备产业是决定性的整个国民经济的现代化,数字化技术和新的高新技术产业和先进的生产设备发展级别和范围,如信息技术,生物技术和产业,航空,航天和国防工业等,使得技术和最基本的装备。所谓的数字化装备技术范围覆盖几个方面:1工程机械的技术; 2信息处理,加工,传输技术; 3自动控制技术;4伺服驱动技术:5传感器技术6,该技术软件。2数字控制技术趋势根据数控技术与世界装备发展观,研究有以下几个方面的重点目前的趋势:高速,高精加工技术和加工设备是新的发展趋势智能化,打开网络,成为数控系统的现代发展的大趋势设备CNC更加重视安全性,功能数控设备是机电一体化产品,由于自动化程度高,所以他们对安全性和功能性的更高要求。1.1.4数控技术在机械工业中的进展近年来,数控机床业务在中国市场的份额正在逐年增长,在中型和大型企业有更大在中小型企业,甚至开始了一般个人使用。2001年,国内生产数控金属切削机床达到18000辆,比上年增长28.5,17.4,生产数控机床产业在2000年的速度,上升至22.7,2001年,河2001年,机械行业在中国的产值进入世界五机床消费世界他站起身,从第3位,达$ 4.739十亿美国$ 536700万,食物与去年同期相比,营业额增长了25。但是,由于国产数控机床不能满足市场的需求,从而使机床中国正在从逐年增长到一年,2001年的进口,机床进口跃居世界第二位,拥有24.06亿$,27,比去年同期的数值。近年来,数控车床,铣床,数控机床,数控切割,数控折弯,数控机床,在普通机床出口钻探显著上升,锯床,插床,拉床,组合机床,液压冲床,木工工具。数控机床出口主要是中,低三档。1.2数控车床的工艺范围及加工精度1.2.1工艺范围数控车床是一种高精度,自动化工具效率高,而且还使用数控机床数量较多,占数控机床总数的25左右。它主要用于在高精度,良好的表面粗糙度,外形轮廓轴组件,磁盘和身体的其他旋转部件,圆柱形表面的制造,圆锥形表面可自动完成,弧形表面并穿过各种控制切割程序,并且可以使槽,钻孔,扩孔和其他加工。1.2.2加工精度由于高精密数控车床,可以做直线和圆弧插补功能,有的车床还设有自动变速器和其他功能的非圆函数曲线插补和编辑功能,所以它的技术的范围比普通车床非常更广。1.高精密零件从数控车床的刚度,施工,切割精度高,并且可以轻松,准确地补偿手动和自动补偿,我们能够处理高精度零件,甚至在车代磨。2.车削表面的粗糙度数控车床具有恒定线性速度的切割操作可以加工表面粗糙度均匀的部件。恒切削速度模式下,可以选择刀锥和最终的最佳速度,使切割小型和一致后的表面粗糙度。数控车床,也适用于各种表面粗糙度不同的地方治疗。大量食物的粗糙度大的部分被选择,需要的食物少量的位置的一小部分。3.图轮廓是非常复杂和困难,以控制所述主体的旋转部分的尺寸车床具有直线和圆弧插补启闭装置有一些非圆曲线和平面曲线插值函数,从而使形状可以加工特别复杂或难以控制的转子区段的大小。4.关于与特殊螺纹零件螺纹车床类型相当有限,只能导致直卡车,男性锥,螺纹螺杆英寸和螺纹车床加工数量有限。不仅NC车床任何铅直,锥螺纹和面临的问题,也是汽车可变螺距,还车可以非常精确螺纹。44第2章 传动方案及传动系统图的拟定1极限转速数据的设定 已知主轴最低转速mm每秒,最高转速mm每秒,转速调整区间是: 2.12公比数据的设定 选定公比为3算出主轴转速级数Z 2.24结构网或结构式的设定 5画出转速图2.1 电动机的选择普通车床,选Y-132M-4Y型三相异步电动机系列。可选的发动机参数一杯提交设计文档参数:功率:7.5Kw 满载转速:1450 r/min2.2 传动路线及转速图的拟定1减速的速度分布的比率综合索引加速度,低速轴,考虑需要加速或电池标准比例,以增加额外的固定的浮雕延迟和径向和轴向尺寸的数量,和整体指数的比例下降。然后明智递减到每个班次的范围内的最小比率“的原则,第一个紧急救援后”的总体传动比。2固定在驱动轴的车轴数轴数=号+固定比例组号副传动齿轮+ 1 ,统计是6根轴3速度图绘制然后,比变速箱内画在各组的传动比的分配模式更高数量级的类型,以确定各齿轮对的传动比。对于在附近的公比F 为1.25的设计速度,检查机械设计建议手动的速度为:F =1.26,则速度如图2.1所示。4确定系统传动方案图 主轴箱系统传动方案图如图2.2所示。图2.1 转速图5传输线A主传动传输系统经由V型带轴电机带动传播我的头,配备了双向多片式摩擦离合器轴我,主轴线的历史作用,逆转或停止。当按下磁带摩擦片轴我通过M1和相应的一对半轴齿轮的左部通过二,则前进轴上。当M1为在中间位置,主轴将停止。二驱动轴通过轴第三发送。机身结构的动力总成下面的表达式:初设定传动系统图,见图2.3。图2.3 主传动系统图第3章 主轴箱主要零件的设计及校核3.1 主轴箱箱体尺寸的确定材料选择HT20-40。铸造,最低吊柜,根据外形的长宽高,从表3.1选择。表3.1 轮廓尺寸长宽高()壁厚(mm) 500 500 300-800 500 50010-15 800 800 50012-203.2 传动轴各主要零件的设计3.2.1 轴径的估算查阅相关引用书目中表格3.102列出计算式: 3.13,查阅相关引用书目中表格列出计算式:=0.96 ,设 由转速图可列出计算式: 转速:(r/min) 效率: 功率:(kw)(mm) 取mm3.2.2 V带轮的设计1计算V带功率 = 3.14查阅相关引用书目中表格,列出=1.1 =7.5 kw所以 =7.51.1 = 8.25 (kw)2设定V带样式按功率及小带轮转速r每分钟,从相关书目中图,设定A型带型,尺寸区于 112140mm3设定基准直径并且验证带速a初选小带轮的基准直径按V带样式,翻阅相关书目表格86、88定小带轮的的基准直径,应使,设得为132mm, 适当整圆成为130毫米。b验算带速 3.15 设=10m/sc)算出大带轮的基准尺寸从转速图看出,带轮传动比得值为,再根据表88,来整圆,算出 进行适当整圆得=230(mm) 4设出中心距,并且选取V带的基准长度a联合式子820初定中心距 +式子: 设=450(mm)b)算出带长+ 3.16=(mm)带的基准长度根据设得 =1600 (mm)c)计算中心距及其变动范围传动的实际中心距约是 3.17 =(mm)中心距的变化范围:=(mm)(mm)5验算小带轮包角应使: 3.18 (6设出带的根数 3.19翻阅相关表格得=0.99 需要=5根(7设定初拉力从相关引用书目得出每根V带的最小初拉力公式是: 3.20=137.595N(8)算出带传动的压轴力从相关书目,列出式子:N 3.21图3.2 V带轮的结构示意图3.2.3 多片式摩擦离合器的计算磨损板可以从数来计算: 3.22式子里, T-传递的扭矩电动机的额定功率kw(Nmm) 3.23 安装离合器的传动轴的计算转速r/min传动效率K安全系数,一般取1.31.5f摩擦片间的摩擦系数,由摩擦片为淬火钢,设得f设值为0.08摩擦片的平均直径mmmm 3.24b内外摩擦片的接触宽度mmmm 3.25摩擦片的许用压强基本许用压强,找出相关引用书目表格,设得1.1速度修正系数 3.26(m/s) 3.27 根据平均圆周速度设=1.00P1004表3.14-23取1.00P1004表3.14-22取0.76所以3.28设设定轴向压紧力,其式子为: 3.29式子里,每个符号如先前所述。摩擦板的厚度,并且通常1-2 毫米时,最大分隔间隙是0.2-0.4毫米。摩擦片应具有通常为10或钢15的电阻,表面渗碳0.3-0.5毫米,淬火硬度HRC52-62。图3.3 多片式摩擦离合器的示意图3.2.4 轴I上的一对齿轮的计算1齿数值是 ,设a预设载荷b算出扭矩 3.30,算出:r/min,kw (Nmm)c找出相关引用书目表格,设得齿宽系数是d找出相关引用书目表格,设得弹性影响系数是e找出相关引用书目图10-21,设出 , f算出应力循环次数,找出相关书目列出以下式子: 3.31 3.32g找出相关书目图,10-19,设得,h算出接触疲劳许用应力,找出相关书目公式,列得式子如下: MPa 3.33 MPa 3.34(2)算出小齿轮分度圆,找出, 3.35代到中较小的值 (mm) 3.36(a)算出圆周速度:从相关书目,列出式子: 3.37代到已计算的数据得 (m/s)(b算出齿宽b :从相关书目,列出式子:(mm) 3.38(c)算出齿宽与齿高之比: 从相关书目,列出式子:模数 3.39 齿高(mm) (d算出载荷:,是七级别精度,从相关书目 动载系数,又直齿轮 ,又从找到,使用系数,又从找到,非对称的公式是,由,及找出相关书目图,10-13得因而载荷系数式子为:(e分度圆直径:从相关书目式子中找到并列出计算式:3.40,代到已有数据列出计算式: (mm)(f算出模数m : 3.41(3齿根弯曲强度设计算式:从相关书目找出弯曲强度式子是: 3.42a) 从相关书目中图10-20c,找出弯曲强度极限,b)从相关书目中系数是:,c)算出弯曲疲劳许用应力,设它的安全系数是 ,从相关书目式子10-12列出计算式: (MPa) 3.43 (MPa) 3.44d 算出载荷: 3.45e 设齿形系数: 从相关引用书目表格是 ,f设出应力校正系数: 从相关书目表格10-5,设其值为: , g 计算大、小齿轮的 ,并加以比较: 比较得大齿轮的数据大h) 设计计算:从弯曲强度式子 : ,整圆成 ,找出机床书目得到,本文设为齿轮的模数。由于,大、小齿轮的齿数分别为: ,整圆成 (4算以下几何:(a分度圆直径 (mm) 3.47 (mm)(b中心距 (mm) 3.48(c齿轮宽度 (mm) 3.49 (mm)3.2.5 齿轮的校核从相关书目找出验证齿轮需要符合的公式是: , 3.50(1验证齿数为51的齿轮 列出计算式: 比较列出计算式: 故该齿轮符合要求。同理校核其它轴上的齿轮,都验证OK。综上该齿轮副符合要求。图3.4 齿轮副示意图3.2.6 轴的校核传动轴仅需要刚度验算。 花键轴 3.51=式子里,d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=Nmm 3.52式子里,最大功率kw; 该轴的计算最小转速r/min。齿轮的圆周力 3.53式子里, D齿轮节圆直径mm,D=mZ。 齿轮的径向力: 3.52式子里, 为齿轮的啮合角,20;齿面摩擦角,;齿轮的螺旋角;0 (N) 3.53:挤压应力的式子列得如下:(MPa) 3.54式子里,最大转矩; D、d花键轴的大径和小径mm; L花键工作长度; N花键键数; K载荷分布不均匀系数,K=0.70.8;(MPa)花键轴验证合格图3.5 花键轴示意图3.2.7 轴承的选择选轴承所要考虑的因素:(1)轴承所受的载荷 (2)轴承的转速 (3)轴承的调心性能 (4)轴承的安装和拆卸总上所述,本人选择的轴承型号如下:轴I 从左至右分别为深沟球轴承 61808(2对) 618076对3.2.8 轴承的校核滚动轴承的使用时长 从相关书目得出: 3.55把值代到以下式子:轴I上的深沟球轴承的校核:(h) 故该轴承符合要求。图3.6 轴I装配示意图3.3 传动轴II各主要零件的设计3.3.1 轴径的估算查阅相关引用书目中表格3.102列出计算式: ,查阅相关引用书目中表格列出算式:=0.96 , 取 由转速图可列出计算式: 转速:(r/min) (r/min) 效率: 查阅相关引用书目中表格列出计算式: , 功率:kw由轴径确定的公式可知:。(mm) 取mm3.3.2 齿轮的校核从相关书目找出验证齿轮需要符合的公式是: ,验证齿数为43的齿轮 列出计算式: 比较列出计算式: 故该齿轮符合要求。同理,其它齿轮验证OK。3.3.3 传动轴的校核传动轴仅需要刚度验算。花键轴 =式子里, d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=(Nmm)式子里, N最大功率kw; 该轴的最小转速r/min。齿轮的圆周力:式子里, D齿轮节圆直径mm,D=mZ。齿轮的径向力:(N)式子里, 为齿轮的啮合角;齿面摩擦角;齿轮的螺旋角;=20mm,结果符合。挤压应力的式子列得如下:式子里, 最大转矩; D、d花键轴的大径和小径mm; L花键工作长度; N花键键数; K载荷分布不均匀系数,K=0.70.8; (MPa)花键轴验证合格图3.7 轴II装配示意图3.3.4 轴承的校核滚动轴承的使用时长, 从相关书目得出:将代到下列出式:轴II上的圆锥滚子轴承的校核:(h) 所选轴承符合要求。3.4 传动轴III各主要零件的设计3.4.1 轴径的估算查阅相关引用书目中表格3.102列出计算式:,查阅相关引用书目中表格列出计算式:=0.96,取 由转速图可列出计算式: 转速:r/min效率: 查阅相关引用书目中表格列出计算式:圆锥滚子轴承效率=0.98功率:kw mm 取mm3.4.2 齿轮的校核从相关书目找出验证齿轮需要符合的公式是:,验证齿数为63的齿轮 列出计算式: 比较列出计算式: 故该齿轮符合要求。同理,其它齿轮验证OK。图3.8 三联滑移齿轮图3.4.3 传动轴的校核传动轴仅需要刚度验算。花键轴 =式子里, d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=(Nmm)式子里, N最大功率kw; 该轴的最小转速r/min。齿轮的圆周力:式子里, D齿轮节圆直径mm,D=mZ。齿轮的径向力:(N)式子里,为齿轮的啮合角;齿面摩擦角;齿轮的螺旋角;=20mm,结果符合。挤压应力的式子列得如下:式子里,最大转矩; D、d花键轴的大径和小径mm; L花键工作长度; N花键键数; K载荷分布不均匀系数,K=0.70.8; (MPa)花键轴验证合格。图3.9 轴III花轴图3.4.4 轴承的校核滚动轴承的使用时长从相关书目得出:将代到以下式:轴III上深沟球轴承的校核:(h)轴III上圆锥滚子轴承的校核:(h) 轴III上的轴承校核符合要求。图3.10 轴III装配示意图3.5 传动轴IV各主要零件的设计3.5.1 轴径的估算查阅相关引用书目中表格3.102列出计算式: ,查阅相关引用书目中表格列出计算式:=0.96 , 取 由转速图可列出计算式: 转速:(r/min) 效率:功率:(kw)(mm) 取(mm)3.5.2 齿轮的校核从相关书目找出验证齿轮需要符合的公式是:,验证齿数为50的齿轮: 列出计算式: 比较列出计算式: 故该齿轮符合要求。同理,其它齿轮验证OK。图3.11 轴IV双联滑移齿轮1图3.12 轴IV双联滑移齿轮23.5.3 传动轴的校核传动轴仅需要刚度验算。花键轴 =式子里,d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=Nmm式子里, N最大功率kw; 该轴的最小转速r/min。齿轮的圆周力:(N)式子里, D齿轮节圆直径mm,D=mZ。齿轮的径向力:(N)式子里, 为齿轮的啮合角;齿面摩擦角;齿轮的螺旋角;=22.32mm,结果符合。挤压应力的式子列得如下:式子里, 最大转矩Nmm; D、d花键轴的大径和小径mm; L花键工作长度; N花键键数; K载荷分布不均匀系数,K=0.70.8; (MPa)花键轴验证合格。图3.13 轴IV花轴图3.5.4 轴承的校核滚动轴承的使用时长 从相关书目得出:将代到下列式子:验证角接触球轴承:(h)轴IV上的圆锥滚子轴承的校核:(h) 轴IV上的轴承校核符合要求。图3.14 轴IV装配示意图3.6 传动轴V各主要零件的设计3.6.1 轴径的估算查阅相关引用书目中表格3.10-2列出计算式:,查阅相关引用书目中表格列出计算式:=0.96,取 由转速图可列出计算式: 转速:(r/min) 效率:功率:kwmm 取mm3.6.2 齿轮的校核从相关书目找出验证齿轮需要符合的公式是: ,验证齿数为50的齿轮: 列出计算式: 比较列出计算式: 故该齿轮符合要求。同理,其它齿轮验证OK。图3.15 齿数为80的齿轮3.6.3 传动轴的校核传动轴仅需要刚度验算。花键轴 =式子里,d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=(Nmm)式子里,N最大功率kw; 该轴的最小转速r/min。齿轮的圆周力:(N)式子里,D齿轮节圆直径mm,D=mZ。齿轮的径向力:(N)式子里,为齿轮的啮合角;齿面摩擦角;齿轮的螺旋角;=31.43mm,结果符合。挤压应力的式子列得如下:式子里, 最大转矩; D、d花键轴的大径和小径mm:L花键工作长度; N花键键数; K载荷分布不均匀系数,K=0.70.8; (MPa)花键轴验证合格。图3.16 花键轴3.6.4 轴承的校核滚动轴承的使用时长 从相关书目得出:将代到下列式子:轴V上的圆锥滚子轴承的校核:(h) 轴V上的轴承校核符合要求。图3.17 轴V 示意图3.7 传动轴VI各主要零件的设计3.7.1 轴径的估算查阅相关引用书目中表格3.102列出计算式:,查阅相关引用书目中表格列出计算式:=0.96,取 由转速图可列出计算式: 转速:(r/min) 效率:功率:kw(mm) 取(mm)3.7.2 主轴上一对齿轮的计算1齿数值是 取a预设载荷b算出扭矩 从相关引用书目,得出:r/min kw (Nmm)c找出相关引用书目表格,设齿宽系数是d找出相关引用书目表格,设弹性影响系数是e找出相关引用书目图10-21,设出 , f算出应力循环次数,找出相关书目列得以下式子: g找出相关书目图,10-19,设得,h算出接触疲劳许用应力,找出相关书目公式,列得式子如下: (MPa) (MPa)2算出小齿轮分度圆尺寸,从相关书目找出,代到中较小的值 (mm)a算出圆周速度:从相关书目,列出式子:,代到已计算的数据得 (r/min)b算出齿宽b :从相关书目,列出式子:(mm)c算出齿宽与齿高之比: 从相关书目,列出式子:模数 齿高(mm) d算出载荷:由,及找出相关书目图,10-13设得因而载荷系数式子为:e分度圆直径:从相关书目式子中找得列出计算式:,代到已有数据列出计算式: (mm)f算出模数m : 3齿根弯曲强度设计算式:从相关书目找出弯曲强度式子是:a 从相关书目中图10-20c,找出弯曲强度极限,b从相关书目中系数是:,c算出弯曲疲劳许用应力,设它的安全系数是 ,从相关书目式子10-12列出计算式: (MPa) (MPa)d 算出载荷: e 设齿形系数: 从相关引用书目表格是 ,f设出应力校正系数: 从相关书目表格10-5,设其值为:,g 算出大齿轮、小齿轮的 ,再进行比较: 比较得大齿轮的数据大h设计计算:从弯曲强度式子 ,代到数据列出计算式: ,整圆成 ,找出机床书目得到,本文设作为齿轮的模数。由于,大、小齿轮的齿数分别为: ,整圆成 4算以下几何:a分度圆直径式子 (mm) (mm)b中心距式子 (mm)c齿轮宽度式子 (mm) (mm)3.7.3 齿轮的校核从相关书目找出验证齿轮需要符合的公式是: ,验证齿数为50的齿轮: 又从计算齿轮时的数据列出计算式: 比较计算式: 因此这齿轮符合要求。同理,模数为5.75的齿轮也验证OK。图3.18 齿数为50的齿轮示意图3.7.4 传动轴的校核传动轴仅需要刚度验算。花键轴 =式子里, d花键轴的小径mm;D花轴的大径mm;b、N;弯曲载荷摆式子如下:=(Nmm)式子里,N最大功率kw; 该轴的最小转速r/min。齿轮的圆周力:(N)式子里,D齿轮节圆直径mm,D=mZ。齿轮的径向力:(N)式子里,为齿轮的啮合角;齿面摩擦角;齿轮的螺旋角;=35.17(mm),结果符合。挤压应力的式子列得如下:式子里, 最大转矩;D、d花键轴的大径和小径mm;L花键工作长度;N花键键数;K载荷分布不均匀系数,K=0.70.8; (MPa)花键轴验证合格。3.7.5 轴承的校核滚动轴承的使用时长 从相关书目得出:将代到下列式子:轴VI上的圆柱滚子轴承的验证:(h)轴VI上的推力球轴承的验证:(h) 轴VI上的轴承校核验证合格。图3.19 主轴装配示意图第4章 主轴箱结构设计及说明4.1 结构设计的内容、技术要求和方案结构设计包括齿轮箱轴的传动件轴,轴承,滑轮,齿轮,离合器和制动器等,一轴组件,转向,润滑和密封系统耦合构件和设计壳体和设备,以张展开图并示出了一系列张衡的剖面图。课程设计,由于时间的限制,只有10画一般扩展视图。除了检查的相关要求的机械传动的总体设计,可以考虑侧重于以下几个方面。精度,刚性及抗震性要求,传输性能的要求,主轴轴承温度前和过程的控制结构中的温度,操作方便,安全可靠的原则,坚持标准化,通用的原则。工具齿轮轴的设计着重于整体建筑设计,结构复杂,难免设计经过反复思考和许多变化。官方计划必须先草图之前。这样做的目的是:1被布置为选择部分和传输的程序结构。2结果是否存在干扰,碰撞或其他不合理的条件,为及时修正运动规划的考验。3支撑轴的长度,以确定齿轮在轴上的位置和各轴的相对位置,以确定4.2
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