圆柱齿轮减速器的设计

1、郑州轻工业学院轻工职业学院专科毕业设计（论文）题 目 一级圆柱齿轮减速器的设计学生姓名 我专业班级 自动化生产设备及应用081学 号 2 院 （系） 机电系 6指导教师(职称) 6完成时间 2011年01月 04 日6一级圆柱齿轮减速器的设计摘 要齿轮传动是现代机械中应用最广的一种传动形式。它的主要优点是：1、瞬时传动比恒定、工作为平稳、传动准确可靠，可传递空间任意两轴之间运动和动力；2、适用的功率和速度范围广；3、传动效率高，=0.92-0.98；4、工作为可靠、使用寿命长；5、外轮廓尺寸小、结构运送。由齿轮、轴、轴承及箱体组成的齿轮减速器，用于原动机和工作为机或执行机构之间，起匹配转速和传

2、递转矩的作为用，在现代机械中应用极为广泛。6、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代的问题。另外，材料品质和工世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。国外的减速器，以德国、丹麦和日本处于依靠地位，特别在材料和制造工世方面占据优势，减速器工作为可靠性好，使用寿命长。但其传动形式仍以定轴齿轮传动为主，体积和重量问题也未解决好。当今的减速器是向着大功率、大传动比、小体积、高机械效率以及使用寿命长的方向发展。减速器与电动机的连体结构，也是大力开拓的形式，并已生产多种结构形式和多种功率型号的产品。近十几年来，由于近代计算机

3、技术与数控技术的发展，使得机械加工精度，加工效率大大提高，从而失去了机械传动产品的多样化，整机配套的模块化，标准化，以及造型设计艺术化，使产品更加精致，美观化。在21世纪成套机械装备中，齿轮仍然是机械传动的基本部件。CNC机床和工世技术的发展，失去了机械传动结构的飞速发展。在传动系统设计中的电子控制、液压传动、齿轮、带链的混合传动，将成为变速箱设计中优化传动组合的方向。在传动设计中的学科交叉，将成为新型传动产品发展的重要趋势。关键字：减速器/轴承/齿轮/机械传动Level 1 cylindrical gear reducer designAbstractWheel gears spreadin

4、g to move is a the most wide kind of the application spreads to move a form in the modern machine.Its main advantage.BE:1.spreads to move to settle,work than in a moment steady,spread to move accurate credibility ,can deliver space arbitrarily sport and the motive of the of two stalds;Power and spee

5、d scope;2.applies are wide;3.spreads to move an efficiency high, =0.92-0.98; 4.work is dependable,service life long;5.Ortline size outside the is small,structure tightly pacded.The wheel gear constituted to,from wheel gear,stalk,bearings and boxbody decelerates a machine,useding for prime mover and

6、work machine or performance organization of,have already matched to turn soon and deliver a function of turning,the application is extremely extensive in the modern machine;6.local deceleration machine much with the wheel gear spread to move,the pole spread to move for lord ,but widespread exist pow

7、er and weight ratio small,or spread to move ratio big but the machine efficiency lead a low problem.there are also many weadnesses on material quality and craft level moreover,the especially large deceleration machines problem is more outstanding,the service life isnt long.The deceleration machine o

8、f abroad,with Germany,Denmark and Japan be placed in to lead a position,occupying advantage in the material and the manufacturing craft specially,decelerating the machine work credibility like,service life long.But it spreads to move a form to still take settling stalk wheel gear to spread to move a

9、s lord,physical volume and weight problem,dont also resolve like.The direction which decelerates a machine to is the facing big power and spread to move ratio,small physical volume,high machine efficiency and service life to grow greatly nowadays develops.Decelerating the connecting of machine and e

10、lectric motor body structure is also the form which expands strongly,and have already produced various structure forms and various products of power model numbers.Be close to ten several in the last yearses,control a technical development because of the modern calculator technique and the number,mad

11、e the machine process accuracy,process an efficiency to raise consumedly,pushed a machine to spread the diversification of movable property article thus,the mold piece of the whole machine kit turns,standardizing,and shape design the art turn,making product more fine,the beauty turns.Become a set a

12、machine material in 21 centuries medium,the wheel gear is still a machine to spread a dynamic basic parts.CNC tool machine and the craft technical development,pushed a machine to spread to move structure to fly to develop soon.Be spreading to move the electronics control,liquid in the system design

13、to press to spread to move,wheel gear,take the mixture of chain to spread to move,will become become soon a box to design in excellent turn to spread to move a combination of direction.The academics that is in spread move the design crosses,will become new spread a moveable property article the impo

14、rtant trend of the development.Key words: Reduction gear，bearing，gear，mechanical drive目 录摘 要··································

15、3;·················IAbstract·······························&

16、#183;···················II1.前言·····························&

17、#183;························11.1设计目的························

18、;·····················11.2传动方案分析···························&

19、#183;·············12.设计任务···································

20、···············13.传动方案拟定·································

21、83;············14.电动机的选择····································

22、··········24.1电动机类型和结构型式的选择···························24.2确定电动机的功率········&

23、#183;····························24.3确定电动机转速···················&#

24、183;···················34.4确定电动机型号····························

25、83;··········45.计算总传动比及分配各级的传动比····························45.1总传动比·······&

26、#183;·····································45.2分配各级传动比··········&#

27、183;····························46.运动参数及动力参数计算···················

28、·················46.1计算各轴转速（r/min）······························&

29、#183;··46.2计算各轴转矩·········································57.传动零件的设计计算··

30、83;·····································57.1皮带轮传动的设计计算··········&

31、#183;······················57.2齿轮传动的设计计算·························

32、··········78.轴的设计计算······································

33、83;······108.1从动轴设计··········································

34、;108.2主动轴的设计········································158.3主动轴上的轴承:······

35、;·······························189.键联接的选择及校核计算················&#

36、183;··················199.1根据轴径的尺寸，由1中表12-6·······················199.2键的强度校核···

37、·····································1910.减速器箱体、箱盖及附件的设计计算·········

38、83;··············2011.润滑与密封··································

39、;············2111.1齿轮的润滑····································

40、·····2111.2滚动轴承的润滑·····································2111.3润滑油的选择····

41、;···································2111.4密封方法的选取············

42、3;························2112.设计小结························&

43、#183;·······················22致 谢·························&#

44、183;·························23参考资料目录·······················

45、························24附 录·························&

46、#183;···························251.前言1.1设计目的通过本课程设计将学过的基础理论知识进行综合应用，培养结构设计，计算能力，熟悉一般的机械装置过程。1.2传动方案分析 机器一般是由原动机，传动装置和工作装置组成。传动装置是用来传递原动机的运动和动力，变换其运动形式以满足工作装置的需要，是机器

47、的重要主成部分。传动装置是否合理将直接影响机器的工作性能，质量和成本。合理的传动方案除满足工作装置的功能外，还要求结构简单、制造方便、成本低廉、转动效率高和使用维护方便。 本设计中原动机为电动机，工作机为皮带输送机。传动方案采用了两级传动，第一级传动为带传动，第二级传动为单级直齿轮减速器。带传动承载能力较低，在传递相同转矩时，结构尺寸较其他的大，但有过载保护的优点，还可缓和冲击和震动，故布置在传动的高速级，以降低传递的转矩，减小带传动的结构尺寸。 齿轮传动的传动效率高,适用的功率和速度范围广，使用寿命长，是现代机器中应运最为广泛的机构之一。本设计采用的是单级直齿轮传动。2.设计任务具体要求：1

48、、电动机类型确定2、单级减速器的齿轮、轴、轴承、箱体等的设计及强度计算3、编写一份设计说明书4、装配图一张、齿轮及轴的零件图个一张3.传动方案拟定第二组第三个数据：设计带式输送机传动装置中的一级圆柱齿轮减速器。工作条件：使用年限10年，每年按300天计算，两班制工作，载荷平稳。原始数据：滚筒圆周力F=3400N；带速V=1.65m/s；滚筒直径D=345mm。图表 14.电动机的选择4.1电动机类型和结构型式的选择按已知的工作要求和 条件，选用 Y系列三相异步电动机。4.2确定电动机的功率传动装置的总效率由简图知： =1×2×3×4×·

49、3;·×n总=带×2轴承×齿轮×联轴器×滚筒=0.96×0.992×0.97×0.99×0.95=0.86电机所需的工作功率Pd=FV/1000总 =3400×1.65/1000×0.86=3.96KW4.3确定电动机转速滚筒轴的工作转速Nw=60×1000V/D =60×1000×1.65/×220 =143.31r/min根据【2】表2.2中推荐的合理传动比范围，取V带传动比Iv=24，单级圆柱齿轮传动比范围Ic=35，则合理总传动

50、比i的范围为i=620，故电动机转速的可选范围为nd=i×nw=（620）×143.31=8602866r/min符合这一范围的同步转速有960 r/min和1420r/min。由【2】表8.1查出有三种适用的电动机型号、如下表方案电动机型号额定功率电动机转速（r/min）传动装置的传动比KW同转满转总传动比带齿轮1Y132s-6310009607.932.632Y100l2-431500142011.6833.89图表 2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，比较两种方案可知：方案1因电动机转速低，传动装置尺寸较大，价格较高。方案2适中。故选择

51、电动机型号Y100l2-4。4.4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Y100l2-4。其主要性能：额定功率：3KW，满载转速1420r/min，额定转矩2.2。5.计算总传动比及分配各级的传动比5.1总传动比i总=n电动/n筒=1420/143.31=9.95.2分配各级传动比取i带=3i总=i齿×i 带i齿=i总/i带=9.9/3=3.36.运动参数及动力参数计算6.1计算各轴转速（r/min）nI=nm/i带=1420/3=473.33(r/min)nII=nI/i齿=473.33/3.3=143.43(r/min)滚筒nw=nII

52、=473.33/3.3=143.43(r/min)计算各轴的功率（KW）PI=Pd×带=3.96×0.96=3.8KWPII=PI×轴承×齿轮=3.8×0.99×0.97=3.65KW6.2计算各轴转矩Td=9.55Pd/nm=9550×2.76/1420=18.56N·m TI=9.55p2入/n1=9550x3.8/473.33=76.67N·m TII =9.55p2入/n2=9550x3.65/143.43=243.03N·m7.传动零件的设计计算7.1皮带轮传动的设计计算选择普通V带截

53、型由课本1P189表10-8得：kA=1.2 P=2.76KWPC=KAP=1.2×2.76=3.3KW据PC=3.3KW和n1=473.33r/min由课本1P189图10-12得：选用A型V带确定带轮基准直径，并验算带速由1课本P190表10-9，取dd1=95mm>dmin=75dd2=i带dd1(1-)=3×95×(1-0.02)=279.30 mm由课本1P190表10-9，取dd2=280带速V：V=dd1n1/60×1000 =×95×1420/60×1000 =7.06m/s在525m/s范围内，带速合

54、适。确定带长和中心距初定中心距a0=500mmLd=2a0+(dd1+dd2)/2+(dd2-dd1)2/4a0 =2×500+3.14(95+280)+(280-95)2/4×450=1605.8mm根据课本1表（10-6）选取相近的Ld=1600mm确定中心距aa0+(Ld-Ld0)/2=500+(1600-1605.8)/2=497mm验算小带轮包角1=1800-57.30 ×(dd2-dd1)/a =1800-57.30×(280-95)/497=158.670>1200（适用）确定带的根数单根V带传递的额定功率.据dd1和n1，查课本图1

55、0-9得 P1=1.4KWi1时单根V带的额定功率增量.据带型及i查1表10-2得 P1=0.17KW查1表10-3，得K=0.94；查1表10-4得 KL=0.99Z= PC/(P1+P1)KKL =3.3/(1.4+0.17) ×0.94×0.99=2.26 (取3根)计算轴上压力由课本1表10-5查得q=0.1kg/m，由课本式（10-20）单根V带的初拉力：F0=500PC/ZV（2.5/K）-1+qV2 =500x3.3/3x7.06(2.5/0.94-1)+0.10x7.062=134.3kN则作用在轴承的压力FQFQ=2ZF0sin(1/2) =2×

56、3×134.3sin(158.67o/2)=791.9N7.2齿轮传动的设计计算选择齿轮材料与热处理所设计齿轮传动属于闭式传动，通常齿轮采用软齿面。查阅表1 表6-8，选用价格便宜便于制造的材料，小齿轮材料为45钢，调质，齿面硬度260HBS；大齿轮材料也为45钢，正火处理，硬度为215HBS；精度等级：运输机是一般机器，速度不高，故选8级精度。按齿面接触疲劳强度设计由d1 (6712×kT1(u+1)/duH2)1/3确定有关参数如下：传动比i齿=3.89；取小齿轮齿数Z1=20。则大齿轮齿数：Z2=iZ1= ×20=77.8取z2=78。由课本表6-12取d=

57、1.1转矩T1T1=9.55×106×P1/n1=9.55×106×2.61/473.33=52660N·mm载荷系数k 取k=1.2许用接触应力HH= Hlim ZN/SHmin由课本1图6-37查得：Hlim1=610Mpa Hlim2=500Mpa接触疲劳寿命系数Zn：按一年300个工作日，每天16h计算，由公式N=60njtn 计算N1=60×473.33×10×300×18=1.36x109N2=N/i=1.36x109 /3.89=3.4×108查1课本图6-38中曲线1，得 ZN1

58、=1 ZN2=1.05按一般可靠度要求选取安全系数SHmin=1.0H1=Hlim1ZN1/SHmin=610x1/1=610 MpaH2=Hlim2ZN2/SHmin=500x1.05/1=525Mpa故得：d1 (6712×kT1(u+1)/duH2)1/3=49.04mm模数：m=d1/Z1=49.04/20=2.45mm取课本1P79标准模数第一数列上的值，m=2.5校核齿根弯曲疲劳强度 bb=2KT1YFS/bmd1确定有关参数和系数：分度圆直径：d1=mZ1=2.5×20mm=50mmd2=mZ2=2.5×78mm=195mm齿宽：b=dd1=1.1&

59、#215;50mm=55mm取b2=55mm b1=60mm复合齿形因数Yfs 由课本1图6-40得：YFS1=4.35,YFS2=3.95许用弯曲应力bb根据课本1P116：bb= bblim YN/SFmin由课本1图6-41得弯曲疲劳极限bblim应为： bblim1=490Mpa bblim2 =410Mpa由课本1图6-42得弯曲疲劳寿命系数YN：YN1=1 YN2=1弯曲疲劳的最小安全系数SFmin ：按一般可靠性要求，取SFmin =1计算得弯曲疲劳许用应力为bb1=bblim1 YN1/SFmin=490×1/1=490Mpabb2= bblim2 YN2/SFmin

60、 =410×1/1=410Mpa校核计算bb1=2kT1YFS1/ b1md1=71.86pa< bb1bb2=2kT1YFS2/ b2md1=72.61Mpa< bb2故轮齿齿根弯曲疲劳强度足够计算齿轮传动的中心矩aa=(d1+d2)/2= (50+195)/2=122.5mm计算齿轮的圆周速度V计算圆周速度=n1d1/60×1000=3.14×473.33×50/60×1000=1.23m/s因为6m/s，故取8级精度合适图表 38.轴的设计计算8.1从动轴设计选择轴的材料，确定许用应力选轴的材料为45号钢，调质处理。查2表13

61、-1可知：b=650Mpa,s=360Mpa,查2表13-6可知：b+1bb=215Mpa0bb=102Mpa,-1bb=60Mpa按扭转强度估算轴的最小直径单级齿轮减速器的低速轴为转轴，输出端与联轴器相接，从结构要求考虑，输出端轴径应最小，最小直径为：dC查2表13-5可得，45钢取C=118则d118×(2.53/121.67)1/3mm=32.44mm考虑键槽的影响以及联轴器孔径系列标准，取d=35mm齿轮上作用力的计算齿轮所受的转矩：T=9.55×106P/n =9.55×106×3.65/121.67 =286492.15 N齿轮作用力：圆周力

62、：Ft=2T/d=2×286492/195N=2938N径向力：Fr=Fttan200=2938×tan200=841N轴的结构设计轴结构设计时，需要考虑轴系中相配零件的尺寸以及轴上零件的固定方式，按比例绘制轴系结构草图。联轴器的选择 可采用弹性柱销联轴器，查2表9.4可得联轴器的型号为HL3联轴器：35×82 GB5014-85确定轴上零件的位置与固定方式单级减速器中，可以将齿轮安排在箱体中央，轴承对称布置在齿轮两边。轴外伸端安装联轴器，齿轮靠油环和套筒实现轴向定位和固定，靠平键和过盈配合实现周向固定，两端轴承靠套筒实现轴向定位，靠过盈配合实现周向固定 ，轴通过

63、两端轴承盖实现轴向定位，联轴器靠轴肩平键和过盈配合，分别实现轴向定位和周向定位确定各段轴的直径将估算轴d=35mm作为外伸端直径d1与联轴器相配（如图表3），考虑联轴器用轴肩实现轴向定位，取第二段直径为d2=40mm齿轮和右端轴承从左侧装入，考虑装拆方便以及零件固定的要求，装轴处d3应大于d2，取d3=4 5mm，为便于齿轮装拆与齿轮配合处轴径d4应大于d3，取d4=50mm。齿轮左端用用套筒固定,右端用轴环定位,轴环直径d5满足齿轮定位的同时,还应满足右侧轴承的安装要求,根据选定轴承型号确定.右端轴承型号与左端轴承相同,取d6=45mm.选择轴承型号由1P270初选深沟球轴承,代号为6209

64、,查手册可得:轴承宽度B=19,安装尺寸D=52,故轴环直径d5=52mm.确定轴各段直径和长度段：d1=35mm 长度取L1=50mmII段:d2=40mm初选用6209深沟球轴承，其内径为45mm,宽度为19mm.考虑齿轮端面和箱体内壁，轴承端面和箱体内壁应有一定距离。取套筒长为20mm，通过密封盖轴段长应根据密封盖的宽度，并考虑联轴器和箱体外壁应有一定距离而定，为此，取该段长为55mm，安装齿轮段长度应比轮毂宽度小2mm,故II段长：L2=（2+20+19+55）=96mmIII段直径d3=45mmL3=L1-L=50-2=48mm段直径d4=50mm长度与右面的套筒相同，即L4=20m

65、m段直径d5=52mm. 长度L5=19mm由上述轴各段长度可算得轴支承跨距L=96mm按弯矩复合强度计算求分度圆直径：已知d1=195mm求转矩：已知T2=198.58N·m求圆周力：Ft根据课本P127（6-34）式得Ft=2T2/d2=×198.58/195=2.03N求径向力Fr根据课本P127（6-35）式得Fr=Ft·tan=2.03×tan200=0.741N因为该轴两轴承对称，所以：LA=LB=48mm(1)绘制轴受力简图（如图a）(2)绘制垂直面弯矩图（如图b）轴承支反力：FAY=FBY=Fr/2=0.74/2=0.37NFAZ=FBZ

66、=Ft/2=2.03/2=1.01N由两边对称，知截面C的弯矩也对称。截面C在垂直面弯矩为MC1=FAyL/2=0.37×96÷2=17.76N·m截面C在水平面上弯矩为：MC2=FAZL/2=1.01×96÷2=48.48N·m(4)绘制合弯矩图（如图d）MC=(MC12+MC22)1/2=（17.762+48.482)1/2=51.63N·m(5)绘制扭矩图（如图e）转矩：T=9.55×（P2/n2）×106=198.58N·m(6)绘制当量弯矩图（如图f）转矩产生的扭剪文治武功力按脉动循环

67、变化，取=0.2，截面C处的当量弯矩：Mec=MC2+(T)21/2=51.632+(0.2×198.58)21/2=65.13N·m(7)校核危险截面C的强度由式（6-3）表 4e=65.13/0.1d33=65.13x1000/0.1×453=7.14MPa< -1b=60MPa该轴强度足够。图表 58.2主动轴的设计选择轴的材料 确定许用应力选轴的材料为45号钢，调质处理。查2表13-1可知：b=650Mpa,s=360Mpa,查2表13-6可知：b+1bb=215Mpa0bb=102Mpa,-1bb=60Mpa按扭转强度估算轴的最小直径 单级齿轮减速

68、器的低速轴为转轴，输出端与联轴器相接，从结构要求考虑，输出端轴径应最小，最小直径为：dC查2表13-5可得，45钢取C=118，则d118×(2.64/473.33)1/3mm=20.92mm，考虑键槽的影响以系列标准，取d=22mm齿轮上作用力的计算齿轮所受的转矩：T=9.55×106P/n=9.55×106×2.64/473.33=53265 N 齿轮作用力：圆周力：Ft=2T/d=2×53265/50N=2130N径向力：Fr=Fttan200=2130×tan200=775N确定轴上零件的位置与固定方式单级减速器中，可以将齿轮

69、安排在箱体中央，轴承对称布置在齿轮两边。齿轮靠油环和套筒实现轴向定位和固定，靠平键和过盈配合实现周向固定，两端轴承靠套筒实现轴向定位，靠过盈配合实现周向固定 ，轴通过两端轴承盖实现轴向定位。确定轴的各段直径和长度初选用6206深沟球轴承，其内径为30mm,宽度为16mm.考虑齿轮端面和箱体内壁，轴承端面与箱体内壁应有一定矩离，则取套筒长为20mm，则该段长36mm，安装齿轮段长度为轮毂宽度为2mm。按弯扭复合强度计算求分度圆直径：已知d2=50mm求转矩：已知T=53.26N·m求圆周力Ft：根据课本P127（6-34）式得Ft=2T3/d2=2×53.26/50=2.13

70、N求径向力Fr根据课本P127（6-35）式得Fr=Ft·tan=2.13×0.36379=0.76N两轴承对称LA=LB=50mm(1)求支反力FAX、FBY、FAZ、FBZFAX=FBY=Fr/2=0.76/2=0.38NFAZ=FBZ=Ft/2=2.13/2=1.065N(2) 截面C在垂直面弯矩为MC1=FAxL/2=0.38×100/2=19N·m(3)截面C在水平面弯矩为MC2=FAZL/2=1.065×100/2=52.5N·m(4)计算合成弯矩MC=（MC12+MC22）1/2=（192+52.52）1/2=55.83

71、N·m(5)计算当量弯矩：根据课本P235得=0.4Mec=MC2+(T)21/2=55.832+(0.4×53.26)21/2=59.74N·m(6)校核危险截面C的强度由式（10-3）e=Mec/（0.1d3）=59.74x1000/(0.1×303)=22.12Mpa<-1b=60Mpa此轴强度足够滚动轴承的选择及校核计算从动轴上的轴承根据根据条件，轴承预计寿命L'h=10×300×16=48000h(1)由初选的轴承的型号为6209： 查1表14-19可知:d=55mm,外径=85mm,宽度B=19mm,基本额定

72、动载荷C=31.5KN, 基本静载荷CO=20.5KN, 查2表10.1可知极限转速9000r/min (2)已知nII=121.67(r/min)两轴承径向反力：FR1=FR2=1083N根据课本P265（11-12）得轴承内部轴向力FS=0.63FR 则FS1=FS2=0.63FR1=0.63x1083=682N(3) FS1+Fa=FS2 Fa=0故任意取一端为压紧端，现取1端为压紧端FA1=FS1=682N FA2=FS2=682N(4)求系数x、yFA1/FR1=682N/1038N =0.63FA2/FR2=682N/1038N =0.63根据课本P265表（14-14）得e=0.

73、68FA1/FR1<e x1=1 FA2/FR2<e x2=1y1=0 y2=0(5)计算当量载荷P1、P2根据课本P264表（14-12）取f P=1.5根据课本P264（14-7）式得P1=fP(x1FR1+y1FA1)=1.5×(1×1083+0)=1624NP2=fp(x2FR1+y2FA2)= 1.5×(1×1083+0)=1624N(6)轴承寿命计算P1=P2 故取P=1624N深沟球轴承=3根据手册得6209型的Cr=31500N由课本P264（14-5）式得LH=106(ftCr/P)/60n=106(1×31500

74、/1624)3/60X121.67=998953h>48000h 预期寿命足够8.3主动轴上的轴承:(1)由初选的轴承的型号为:6206查1表14-19可知:d=30mm,外径=62mm,宽度B=16mm,基本额定动载荷C=19.5KN,基本静载荷CO=111.5KN,查2表10.1可知极限转速13000r/min根据根据条件，轴承预计寿命L'h=10×300×16=48000h(2)已知nI=473.33(r/min)两轴承径向反力：FR1=FR2=1129N根据课本P265（11-12）得轴承内部轴向力FS=0.63FR 则 FS1=FS2=0.63FR1

75、=0.63x1129=711.8N(2) FS1+Fa=FS2 Fa=0故任意取一端为压紧端，现取1端为压紧端FA1=FS1=711.8N FA2=FS2=711.8N(3)求系数x、yFA1/FR1=711.8N/711.8N =0.63FA2/FR2=711.8N/711.8N =0.63根据课本P265表（14-14）得e=0.68FA1/FR1<e x1=1 FA2/FR2<e x2=1y1=0 y2=0(4)计算当量载荷P1、P2根据课本P264表（14-12）取f P=1.5根据课本P264（14-7）式得P1=fP(x1FR1+y1FA1)=1.5×(1×1129+0)=1693.5NP2=fp(x2FR1+y2FA2)=1.5×(1×1129+0)= 1693.5N(5)轴承寿命计算P1=P2 故取P=1693.5N深沟球轴承=3根据手册得6206型的Cr=19500N由课本P264（14-5）式得LH=106(ftCr/P)/60n=106(1×19500/1693.5)3/60X4