V带-二级展开式圆柱齿轮减速器设计说明书Ⅰ

1、f Hel iWt 008机械设计课程设计原始资料一、设计题目热处理车间零件输送设备的传动装备二、运动简图1 电动机 2 V带3齿轮减速器4联轴器5一滚筒6输送带三、工作条件该装置单向传送，载荷平稳，空载起动，两班制工作，使用期限5年(每年按300 天计算)，输送带的速度容许误差为i5%.四、原始数据滚筒直径D (mm): 320运输带速度 V (m/s): 0.75滚筒轴转矩T (N m): 900五、设计工作量1减速器总装配图一张2齿轮、轴零件图各一张3设计说明书一份六、设计说明书内容1 .运动简图和原始数据2 .电动机选择3 .主要参数计算4 . V带传动的设计计算5 .减速器斜齿圆柱齿

2、轮传动的设计计算6 .机座结构尺寸计算7 .轴的设计计算8 .键、联轴器等的选择和校核9 .滚动轴承及密封的选择和校核10 .润滑材料及齿轮、轴承的润滑方法11 .齿轮、轴承配合的选择12 .参考文献七、设计要求1.各设计阶段完成后，需经指导老师审阅同意后方能进行下阶段的设计；ctiviies, compre hensie adtampig Safey FoundaionTroubleSooIng manageme nt mehaism, give fl pay t roe of echnia spe rvn and r_l at management,bproveprocessmanagem

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10、s'mon' -shoud. dhe e to ecnomicbe.is of im proving ootrac、电动机输入功率Pw60v2 二 Rn60 0.75 22 3.14 0.32=44.785r / minPwTnw9550900 44.7859550= 4.219kw、电动机输出功率Pd其中总效率为3232 =滞 轴承X"齿轮工"联轴 m ” 滚筒=0.96X 0.993 父0.972父 0.99 父 0.96 = 0.833Pw 4.219Pd-5.083kw0.833查表可得Y132S-4符合要求，故选用它。Y132S-4（同步转速144

11、0r/min , 4极）的相关参数额定功率满载转速堵转转矩额定转矩最大转矩额定转矩质量5.5<w1440 r/min2200N mm2300N mm68 kg二.主要参数的计算一、确定总传动比和分配各级传动比传动装置的总传动比i总=nm = 卫上=32.15 nw44.785查表可得V带传动单级传动比常用值24,圆柱齿轮传动单级传动比常用值为35,展开式二级圆柱齿轮减速器i1定(1.31.5)i2。初分传动比为 iV带=2.5, 1=4.243 i2=3.031二、计算传动装置的运动和动力参数c-i - , anda on. TroUl e-ool ng manageme nt m_c.

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16、.a.r s .'-u cmp"of ”nanne . e".y impr o-d 1st. diy c1 e-e mantea nce pr” 3 s 48.7% and- 1speci-yAccm pls - a.d o-eha u of fu " - m-te nace -ms to" exe - e sg a nd cmpl eethe uit enegy cns- pin diagosi ".nt wter b- nce9本装置从电动机到工作机有三轴，依次为I, H,田轴，则1、各轴转速n 1440n -576r.miniv

17、带2.5nz 576nn =135.753 mini1 4.243 nn 135.753rnm = =44.288 mini23.0312、各轴功率R =Pd,i =兄仆带=5.5M0.96=5.28kwPu =R7u =R”轴承式力齿轮=5.28M0.99M0.97 = 5.070kwPm =Rw =Pu 父"轴承父力齿轮=5.070M0.99M0.97 = 4.869kw3、各轴转矩Td = 9550 互=9550-5- = 36.476 N mnd14401=TdiV带n0i =36.476m2.5m0.96=87.542N mTn =Tli/iu =87.542M4.243M

18、0.99M0.97 = 356.695N mTm =Tni2% 皿=356.695父3.031 父0.99父 0.97 = 1038.221N m表2项目电机轴高速轴I中间轴H低速轴m转速(r/min)1440576135.75362.706功率(kw)5.55.285.0704.869test 0 eegyig proje csSecond we shoUd a de e to "tree" ont he ecnomc beeis of mprovi3转矩(NLm)36.47687.542356.6951038.221传动比2.54.2433.031效率0.960.960

19、.922三V带传动的设计计算一、确定计算功率Pca查表可得工作情况系数kA =1.2故 PCa=kA P =1.2 5.5 = 6.6kw二、选择V带的带型根据Pca、n,由图可得选用A型带。三、确定带轮的基准直径dd并验算带速v1、初选小带轮的基准直径ddi。查表8-6和8-8可得选取小带轮的基准直径dd1 = 90mm2、验算带速v按计算式验算带的速度v=4° .6.782m. s60 100060 1000因为5m/s < v <30m/s故此带速合适。3、计算大带轮的基准直径dd2按式(8-15a)计算大带轮的基准直径dd2 =iv带dd1 = 2.5父90 =

20、225mm根据教材表 8-8,圆整得 dd2 = 224mm。4、确定V带的中心距a和基准直径Ld(1)按计算式初定中心距 a。= 500mm( 0.艰 + dd2与a。W2d(1 + Q 2 )(2)按计算式计算所需的基准长度c-i - , anda on. TroUl e-ool ng manageme nt m_c., give ul pay to. of ecnca sue ovedpro maageme”his yea 1owe hea de -kag*”ie r and 3 Genera problem na - Cmp cemisty la cn-r la - “eg- ma a

21、- of 0 - nt*c a. tchnobig -"o|e .casCmpete suect c. 6IMW .nie a.”. on of c cu-I ng water mcc sad”. ，the ta.rm .of 一zton w a-e wate, the ui -r supiy sysem of copehe tr - met a. ,cage- modKaton of c. m 5 key gro.hhs dSence ad teCnolgy innovai on s ur hericese d. Streg he the caa"t - of islu-

22、 grd " iulaiy of -pecii eg ulaiy me cacin tmes sastcs coaa-dme . t sft-e, mpr on1 of lea maag -etlncra- d i - eti n-ene and ecnolgy andtec oects ad 14 ecni ca projec tota cs apr of125%. "LaH.c_cafird po-we pa nt keg- - sului in, - nirlcain cmpete develad apl-n of pro.a w Iciene and tecnolg

23、y proges sc CH -pecica uis optmie d cntrl ID. W d - lpmet ad ap. -.atonfor -pecii-l.ni* sue ctcl M W ui s of ofcm prhe n teamet of lebcts Dta ng tec adthid.an-wie, inbmaion me ntS -s nnm1d "I inbmai .nte cnolgy beCma- ng ete " ".a ir a impr o-d "the. M ion" ndads .d stanadso

24、n arrg u. ba ndadiing Ce-ng ad i eP onre * De "+s , a nd impl -etsmante Re-.n” RB "c nuethe lu-es 0fte RBIno” 0fm.tenace manng-e nt imp - e nttd a pr i. c m.a.r s .'-u cmp" of ”nanne . e".y impr o-d 1st. diy c1 e-e mantea nce pr” 3 s 48.7% and- 1speci-yAccm pls - a .d o-eha u

25、 of fu " - m-te nace -ms to" exe - e sg a nd cmpl eethe uit enegy cns- pin diagosi ".nt wter b- nceest 0 eegys-ing pro. Cs'mon' -shoud. dhe e to ecnomicbe.is of im proving ootrac2, C 一，、 I ' (dd2-ddi)二(224 -90)2Ld0 2a0 (dd1dd2)d"=2 430 (90 224) -24a024 430=1364mm查表可选带

26、的基准长度Ld = 1400mm(3)按计算式计算实际中心距aLd -Ld01400 -1364、a : a0 = (430)mm = 448mm22中心距的变化范围为(427 mm |_ 490 mm 5、验算小带轮上的包角：1n57.3,57.3”.，、1：1801 - dd2 - dd1 =180，- 224 -90 = 163 ” _ 120 -a4486、计算带的根数(1)计算单根V带的额定功率Pr由 dd1 =90mm0 n =1440r/min 查表可得 P0 =1.064kw根据 n =1440r/min, i =2.7和 A 型带，查表可得 AP0 =0.16*w、 = 0.

27、956、 h =0.96。故 Pr NRP0 k.kL F1.064 0.169 0.956 0.96-1.132kw(2)计算V带的根数ZZ=PL = _66_ =5.830 故取V带根数为6根Pr1.1327、计算单根V带的初拉力的最小值(F°Lin查表可得A型带的单位长度质量q=0.10kgm2.5-k- Pca22.5-0.956 6.6F0 min= 500:% qv2 =(5000.1 6.782N=136Jk Zv0.9566 6.782应使带的实际初拉力F0 >( F0 )mintest 0 eegyig proje csSecond we shoUd adee

28、 to "tree" ont he ecnomc beeis of improving o" h58、计算压轴力F压轴力的最小值为_ _： i163Fp min =2Z Fo minSin： = 2 6 136 Sin - = 1614四 减速器斜齿圆柱齿轮传动的设计计算、高速级齿轮1、选定齿轮类型、精度等级、材料及齿数(1)按图所示的传动方案，选用斜齿圆柱齿轮传动。(2)运输装置为一般工作机器，速度不高，故选用7级精度。(3)材料选择：查表可选择小齿轮材料为40Cr (调质)，硬度为280HBS大齿轮材料为45钢(调质)，硬度为240HBs二者材料硬度差为40H

29、BS(4)选小齿轮齿数Z1=20,大齿轮齿数Z2 = 4.243父20 = 85 ,取Z2 = 85(5)选取螺旋角，初选螺旋角P =142、按齿面接触强度设计，按计算式试算即dt3JktT1 u±1ZhZe u I-H 1test 0 eegy-igproje CsSecond we shoUd a dheeto 1r-"on t7(1)确定公式内的各计算数值试选 kt =1.6,由图 10-26 % =0.740 ,之=0.820®有% = %+为2 =1.560小齿轮传递转矩T1 =87.542NLm查图10-30可选取区域系数Zh =2.433 查表10-

30、7可选取齿宽系数 3 =11查表10-6可得材料的弹性影响系数Ze =189.8MP3。查图10-21d得按齿面硬度选取小齿轮的接触疲劳强度极限仃Hlim1 =600MPa，大齿轮的接触疲劳强度极限 仃Hlim2 = 550MPa按计算式计算应力循环次数N1=60njLh=60 576 1 2 8 300 5)=8.294 108N28.294 1084.243= 1.95 108查图可选取接触疲劳寿命系数kHN1 =1.02 , kHN2 =1.12f Hel iWt 008计算接触疲劳许用应力 取失效概率为1%安全系数s = 1,按计算式(10-12)得 = kHN1；一 Hlim1 =1

31、.02 600 =612MPaSkHN2SHHm2二12"化旭l-H 1-H 2612616二614MPatest 0 .egy-ig proje cs' nd we shoUd adee to 1r_on t he ecnomc beets of improving out h9(2)计算相关数值试算小齿轮分度圆直径明，由计算公式得d1t -32 1.6 87.542 1000 5.24 2.433 189.8 21 1.5604.24614=50.07mm计算圆周速度二 dtn1v 二60 1000二 50.07 57660 1000= 1.509 m s计算齿宽b及模数

32、mntb=：，dd1t=1 50.07 = 50.07mmdt cos :50.07 cos14 小“20mnt = = 2.429mm h -2.25m,t -2.25 2.429rnm-5.466rnmb 50.07小=9.16h 5.466 计算总相重合度4-：=0.3181dzitan ： =0.318 1 20 tan14： =1.586计算载荷系数k 查表可得使用系数kA =1 ,根据v=1.509im/s , 7级精度，查表10-8可得动载系数kV =1.07,由表10-4查得K”的值与直齿轮的相同，为1.419 kF p = 1.350, %0f = kp0f =1.4故载荷系

33、数k =kAkVkH.kH二=1 1.07 1.4 1.419 = 2.126按实际的载荷系数校正所算得的分度圆直径，按计算式得di =ditk =45.8142.126kt1.6=55.046mmtest 0 eegyig proje csSecond we shoUd a de e to "tree" ont he ecnomc beeis of mprovi11计算模数0mn 二d1 cos :55.046 cosi4Z120=2.671mm3、按齿根曲强度设计，按计算式（10-17）试算即mn 12k 1TpYc2oPs$ Y3乙2二（1）确定公式内的各计算数值、计

34、算载荷系数k -kAkvkF.kF >.-1 1.07 1.4 1.35 = 2.022根据纵向重合度 邓=1.586,查图10-28可得螺旋角影响系数Yp = 0.88查图可选取区域系数Zh=2.433 ,沁=0.875则有十名1二4= 1.67查表取应力校正系数 YSa1 =1.569, YSa2 =1.783o查表取齿形系数YFa1 =2.724, YFa2 =2.194 （线性插值法）查图10-20C可得小齿轮的弯曲疲劳强度极限FE1= 500MPa ,大齿轮的弯曲疲劳强度极限= 380MR查图可取弯曲疲劳寿命系数kFN1=0.87, kFN2=0.90计算弯曲疲劳许用应力,取弯

35、曲疲劳安全系数S = 1.4,按计算式（10-22）计算得on.Trul esooti ng managme nt mela-, gVe ulp - to roleof ecnca supeicese d. 'teg he Ihe caan_tns of. s. g7. l itid.anw, ifmain tecciveme ay-sng tepari_h of fi.-"I ifmaiegn te cno" becmakkFN1k 二kFN 2 FE2v-n and relztuaiy mame I.p m.ng.tTca .in s*.aai ad mai .

36、ea .|e hhs mpr.ved fiute.his . cmp. I-dme "sf - empr .daisad stands0.87 5001.4310.714MPa0.90 380hebo.r l owe h- de -kge loi e pesuesk m.lg-.l, onl of lea maag -etlncra- d ivesmet ionarrg ula ba sis - ndadzig -1.4of g - r and3 G- -c ng ad i .set .re c.De =244.286 MPanac. Comp chmi sryla cnsr-mal

37、aiI-gd ma saig.ibrain of 0 s-ntic ad tchnolgnd mpl -es manteo- Cs ad 14 ecninane iformat-a projel Iota cs talannu- pr of.*. "a . 'rlanii - R log . nuete -u-es of the ofm_te-Ki. po-ee panI eg- - sului in, de .“caincmpeed-nane ma.ng-e .timp - eadCmp-esu-cInttd a pr >e c maa.rsystm.，- cmp-i

38、napl naton of te.a- >nie smuatin s d lo W .tnom-pro- - a onof ni .uatn.IICno”us ma . tenanne , eiaiiy mpr ovd sta dly "p-meprogtw cco.d-pm二t：l-p.heiansormain of l 5 k" cit-a uis optimise d cnt.isa - esand423% -peci -nd te 631MW d - lpm-l ad ap.onf on ie-u-ion for lupecii-lunissue",

39、cm pls t- . li -la a.d oveha u of fu Ml s m_te na- t_ms to Ht execsecit >>.W ui s of Iuri ne drVe boie fedPromoIe Ihe wrkcal h- sg a ofcm prhe . teameth ."of -acts DtaSiene a. ino3 innovai on s Ur hernd cigcmpl eethe ui enegyng one or Iw adcnsum pti. dagosi s plant wter baance计算大、小齿轮的YFaY

40、Sa并加以计算YFalYSal匕12.724 1.569 , =0.014310.714YFa2Ysa22.194 1.783 (-：-=0.0 16lcF L244.286大齿轮的数值较大。(2)设计计算 3mn -2 2.022 87.542 1000 0.88 cos2 141 202 1.5860.016 = 1.979mm对比计算结果，由齿面接触疲劳强度计算的法面模数大于由齿根弯曲疲劳强度计算的法面模数，故取 mn=2mm,已可满足弯曲强度，但为了同时满足接触疲劳强度，需按接触疲劳强度算得的分度圆直径d1 = 55.046mm来计算应有的齿数，于是有r d1cos ： 55.046

41、cos14 ”Z1 = = = 26.705mn2取Z1=27,贝122=1乙=4.24327之1154、几何尺寸计算(1)计算中心距乙 Z2 mn27 115 22cos :2 cos14=146.347mm将中心距圆整为a=147mm。(2)按圆整后的中心距修正螺旋角乙 Z2 mn27 1152-arccos 二 arccos =14.9862a2 147因P值改变不多，故参数%、kp、ZH等不必修正。(3)计算大、小齿轮的分度圆直径乙mn27 2d1d211= = 55.901 mmcos :cos14.986Z2mn115 2-= =238.099 mmcos :cos14.986(4

42、)计算齿轮宽度b = ：,dd1 =1 55.901 -55.901mm圆整后取 B1 =55mm , B2 =60mm。、低速级齿轮1、选定齿轮类型、精度等级、材料及齿数(1)按图所示的传动方案，选用斜齿圆柱齿轮传动。(2)运输装置为一般工作机器，速度不高，故选用 7级精度。(3)材料选择，在同一减速器各级小齿轮 (或大齿轮)的材料，没有特殊情 况，应选用相同牌号，以减少材料品种和工艺要求，故查表可选择小齿轮材料为40Cr (调质)，硬度为52HRC大齿轮材料为45钢(调质)，硬度为45HRC.(4)选小齿轮齿数Z3=23,大齿轮齿数Z4 = 23 3.031 = 70.924 70(5)选

43、取螺旋角，初选螺旋角P =142、按齿面接触强度设计，按计算式试算即25 u'±1'ZhZe "2 / u工】'/(1)确定公式内的各计算数值试选kt = 1.6小齿轮传递转矩T2=356.695m查表10-7可选取齿宽系数d=1查图10-26可选取区域系数13二4 =1.635Zh =2.433, &03 =0.765,名廓=0.870则有1查表可得材料的弹性影响系数 Ze =189.8MP&。查图得按齿面硬度选取小齿轮的接触疲劳强度极限0Hlim3 =600MPa ,大齿cviescv atigF austggecasgvfi-t

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47、trreont he ecnomic beiis of improving oo-rc轮的接触疲劳强度极限C“m4 =550MPa按计算式计算应力循环次数N3 =60n2jLh =60 135.753 1 2 8 300 5 =1.955 108N41.955 1083.031= 6.450 107查图可选取接触疲劳寿命系数 *3=1.12, *4=1.18计算接触疲劳许用应力取失效概率为1%安全系数S = 1,于是得I-HkHN 3、H lim3= 1.12 600 = 672 MPakH 4 JHN4'” Hlim4 =1.18 550 =649MPa4 S672 649= 660

48、.5 MPa(2)计算相关数值试算小齿轮分度圆直径必，由计算公式得3 52,2M1.6父3.567父105 4.031 i 2.433父 189.8)d3t76.848mm,1 1.673.031660.5计算圆周速度, _ d3tn2v 一60 1000二 76.848 135.75360 1000-0.546m s计算齿宽b'及模数mntb' = 3d3t =1 76.848 = 76.848mmmint '=d3t cos :Z376.848 cos1423=3.240mmh'u2.25mnt'=2.25 3.240 -7.29mmbj = 76.

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