機(jī)械設(shè)計(jì)課程設(shè)計(jì)--設(shè)計(jì)膠帶輸送機(jī)的傳動(dòng)裝置

1、機(jī)械設(shè)計(jì)課程設(shè)計(jì)一設(shè)計(jì)膠帶 輸送機(jī)的傳動(dòng)裝置機(jī)械設(shè)計(jì)課程設(shè)計(jì)機(jī)械設(shè)計(jì)課程設(shè)計(jì)說(shuō)明書(shū)目錄1設(shè)計(jì)任務(wù)書(shū)11題目名稱 設(shè)計(jì)膠帶輸送機(jī)的傳動(dòng)裝置2工作條件13技術(shù)數(shù)據(jù)2電動(dòng)機(jī)的選擇計(jì)算2. 1選擇電動(dòng)機(jī)系列22滾筒轉(zhuǎn)動(dòng)所需要的有效功率2.3確定電動(dòng)機(jī)的轉(zhuǎn)速 3傳動(dòng)裝置的運(yùn)動(dòng)及動(dòng)力參數(shù)計(jì)算3. 1分配傳動(dòng)比31. 1總傳動(dòng)比31.2各級(jí)傳動(dòng)比的分配53. 2各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計(jì)算3.2.1 I軸（高速軸）322 II軸（中間軸）6323 HI軸（低速軸）6324 IV軸（傳動(dòng)軸）6325 V軸（卷筒軸）63. 3開(kāi)式齒輪的設(shè)計(jì)733. 1材料選擇7 3. 3. 2按齒根彎曲疲勞強(qiáng)度確定模數(shù)7333齒

2、輪強(qiáng)度校核83. 3.4齒輪主要幾何參數(shù)4閉式齒輪設(shè)計(jì)104.1減速器髙速級(jí)齒輪的設(shè)計(jì)計(jì)算10機(jī)械設(shè)計(jì)課程設(shè)計(jì)411材料選擇104.1.2按齒面接觸疲勞強(qiáng)度確定中心距10413驗(yàn)算齒面接觸疲勞強(qiáng)度12414驗(yàn)算齒根彎曲疲勞強(qiáng)度-13 -415齒輪主要幾何參數(shù)42減速器低速級(jí)齒輪的設(shè)計(jì)計(jì)算14-14-42材料選擇-14 -4.2.2按齒面接觸疲勞強(qiáng)度確定中心-15-4. 2. 3驗(yàn)算齒面接觸疲勞強(qiáng)度.-16 -4.2.4驗(yàn)算齒根彎曲疲勞強(qiáng)度.-18 -5軸的設(shè)計(jì)計(jì)算5. 1高速軸的設(shè)計(jì)計(jì)算 5.2中間軸的設(shè)計(jì)計(jì)算 5.3低速軸的設(shè)計(jì)計(jì)算4. 25齒輪主要幾何參數(shù)-19 -19-19-20206低

3、速軸的強(qiáng)度校核-21-61繪制低速軸的力學(xué)模型-21-62求支反力-21-6. 3作彎矩、轉(zhuǎn)矩圖-23 -6. 1.4作計(jì)算彎矩Mca圖-24 -6.1.5校核該軸的強(qiáng)度-24 -7低速軸軸承的選擇及其壽命驗(yàn)算-24 - 26機(jī)械設(shè)計(jì)課程設(shè)計(jì)定軸承的承載能力2672計(jì)算軸承的徑向支反力 - 26 -7. 3作彎矩I-28-28-28-29-29-29-297.4計(jì)算派生軸向力S-26 -75求軸承軸向載荷-27 - 76計(jì)算軸承的當(dāng)量動(dòng)載荷P-27 -8鍵聯(lián)接的選擇和驗(yàn)算-28-8. 1低速軸上鍵的選擇與驗(yàn)算28 -811齒輪處-28- & 1. 2聯(lián)軸器處&2中間軸上鍵的選擇與驗(yàn)算&3高速軸

4、上鍵的選擇與驗(yàn)算 9聯(lián)軸器的選擇9. 1低速軸軸端處9. 2高速軸軸端處 10減速器的潤(rùn)滑及密封形式選擇11參考文獻(xiàn)機(jī)械設(shè)計(jì)課程設(shè)計(jì)1設(shè)計(jì)任務(wù)書(shū)XX1.1題目名稱 設(shè)計(jì)膠帶輸送機(jī)的傳動(dòng)裝置XX1. 2工作條件工作年限工作班制工作環(huán)境載荷性質(zhì)生產(chǎn)批量82多灰塵平穩(wěn)小批1. 3技術(shù)數(shù)據(jù)題號(hào)滾簡(jiǎn)圓周力 F(N)帶速 v (m/s)滾簡(jiǎn)直徑D(mm)滾簡(jiǎn)長(zhǎng)度L(mm)ZL-15180000. 2540010002電動(dòng)機(jī)的選擇計(jì)算2.1選擇電動(dòng)機(jī)系列根據(jù)工作要求及工作條件應(yīng)選用三相異步電動(dòng)機(jī)，封閉式結(jié)構(gòu)，電壓380 伏，Y系列。2. 2滾筒轉(zhuǎn)動(dòng)所需要的有效功率Fv1OOO17000x0.241OOO=A

5、r.SkW傳動(dòng)裝置總效率=彈聯(lián)剛聯(lián)兀齒開(kāi)擁懷筒査表17-9得機(jī)械設(shè)計(jì)課程設(shè)計(jì)彈性聯(lián)軸器的效率伽聯(lián)=如5剛性聯(lián)軸器的效率伽聯(lián)=0.99閉式齒輪的嚙合效率皿=0.97(8級(jí)精度)開(kāi)式齒輪的嚙合效率開(kāi)齒=0.95滾動(dòng)軸承的效率軸承=098滾筒的效率7前=0.96傳動(dòng)裝置的總效率“25=彈聯(lián)剛聯(lián)葡齒開(kāi)齒軸吸卷筒=0.995 x 0.99 x 0.972 x 0.95 x 0.985 x 0.96=0.76252.3確定電動(dòng)機(jī)的轉(zhuǎn)速滾筒軸轉(zhuǎn)速 =嚶=11.94/7 min7aJ所需電動(dòng)機(jī)的功率4.5P* 0.7625= 5.9kW7.5kW査表27-1,可選Y系列三相異步電動(dòng)機(jī)電動(dòng)機(jī) 型號(hào)額定功率 /k

6、W同步轉(zhuǎn)速 / (r/min)滿載轉(zhuǎn)速 /(r/min)總傳動(dòng)比Y132M-47.515001440111.87Y132M-67.5100097094.21為使傳動(dòng)裝置結(jié)構(gòu)緊湊，選用Y132M-4型，額定功率7. 5kW,同步轉(zhuǎn)速 1500r/min,滿載轉(zhuǎn)速1440r/min。査表27-2,電動(dòng)機(jī)中心高H=132mm,外伸段D X E=38mm X 80mm3傳動(dòng)裝置的運(yùn)動(dòng)及動(dòng)力參數(shù)計(jì)算3.1分配傳動(dòng)比3.1.1總傳動(dòng)比144011.94= 120.63. 1.2各級(jí)傳動(dòng)比的分配 査表17-9取，開(kāi)=。=6機(jī)械設(shè)計(jì)課程設(shè)計(jì)減速器的傳動(dòng)比& =丄=孚=20.1開(kāi)6高速級(jí)齒輪傳動(dòng)比心=Jl35i

7、減=vl.35x20.1 = 5.21低速級(jí)齒輪傳動(dòng)比 = = = 3.86/125.213.2各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計(jì)算3. 2.0 0 軸 P=5. 9kw, n=1440r/min,T=9. 55*5. 9/1440=40. 246N*m3. 2.1 I軸（高速軸）Px = Pr 彈聯(lián)=5.9 x 0.995 = 5.8705 kWq=4 = 1440 r / niinO1T, = 9.55 -= 9.55 -?，S7（）X1（）- = 38.93/V - m114403. 2.2 II軸（中間軸）P2= Px 冶承閉齒=5.8705 x 0.995 x 0.97 = 5.666RW=

8、= 373.06r/min-in 3.86T、= 9.55-= 9.55 ?，666xl（）- = 145.04/V m 馮373.063. 2.3 m軸（低速軸）Py=P2 、朋閉仏=5.666 x 0.98 x 0.97 = 5386kWn. 373.067 3.86=96.6r/minT O A O 5.386x10、T, =9.55- =9.55 =56.6N m心96.63. 2.4 IV軸（傳動(dòng)軸） =代 供 |訕,=5.386 x 0.98 x 0.99 = 5.225kWn3 96.645 1= 96.6心55牛9.55晉罟沁.75,3.25 V軸（卷筒軸）機(jī)械設(shè)計(jì)課程設(shè)計(jì)匕=

9、 軸肇.q開(kāi)也=5.225 x 0.99 x 0.95 = 4.864kW4 6T、= 9.55 主=9.55 丄川 -=2885.11N - m5n5123. 3開(kāi)式齒輪的設(shè)計(jì)3. 3.1材料選擇小齒輪：45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217255HBS大齒輪：45#鍛鋼，正火處理，齒面硬度162217HBS3. 3.2按齒根彎曲疲勞強(qiáng)度確定模數(shù)按齒面硬度217HBS和162HBS計(jì)算初取小齒輪齒數(shù)Z5 = 20則大齒輪齒數(shù)Z6 =20x6 = 120計(jì)算應(yīng)力循環(huán)次數(shù)N、= 60/1JL；, = 60 x 66.254 x 1.0 x (10 x 300 x 8 x 2) = 1.908 x

10、1081.908x10- =3i8Qx1q74 6査圖 5-19 YN5 = rV6 = 1.0査圖 5-18 (b) o-Flim5 = 270Mpa , crFlim6 = 200Mpa由式 532 YX5 = YX6 = 1.0取 ST =2.0, Spmin =14計(jì)算許用彎曲應(yīng)力由式5-31 *=黑血丫必E 5 =十! xl.0xl.0 = 385.7Mpabj = 2心2.(! % 1.0 x 1.0 = 285.7Mpa查圖 5-14= 2.81,yFfl6 = 2.21査圖 5-15y=1.56,y5n6=1.78機(jī)械設(shè)計(jì)課程設(shè)計(jì)E =285.7初選綜合系數(shù)=11 ,査表5-8

11、如=0.5由式5-262KT,.2x1x508276x0.013769考慮開(kāi)式齒輪工作特點(diǎn)m加大10%-15%,取m=53. 3. 3齒輪強(qiáng)度校核5 = 送5 = 5 x 20 = 100“6 = mZ 6 = 5x 120 = 600da5 =d5+ 2h；m = 100+2x1.0x5 = 110da6 = d6 + 2h；m = 600 +2x1.0x5 = 610/wndf5 =比-2(忙 + c )m = 100 - 2 x (1.0 + 0.25)x 5 = S7.5nundf6 = “6 2(/7 + cx )m = 600-2x(1.0+0.25)x 5 = 587.5mmb6

12、 =札 a = 02 x 350 = lOnvn取 Z?5 = % + 6 = 70 + 6 = 76nun db5 =d5 cos 20 = 93.969db6 = 6 cos20* = 563.816機(jī)械設(shè)計(jì)課程設(shè)計(jì)必 0.3467x20=0.06934100 100査圖 5-4 (d) kv = 1.005 査表 5-3=1.1=0.70 由圖 5-7(a) =118d5 100b査表 5-4=1.2計(jì)算載荷系數(shù) k = kAkvkJska = l.lx 1.005 x 1.18x 1.2 = 1.5654=arccos如1 = arccos93.969110= 31.3215=arcc

13、os563.816arccos610=22.4387 =Z5(mnad5 -Uma) + Z6(tanaa6-tana)271=20x (tan31.321 亍一 tan20) + 120x(加加224387 -tan20) 2兀= 1.715 0.25+空“25+空 “6873a1.715乜=1.5654 x 0.6873 = 1.076與kfYG =1.1相近，無(wú)需修正計(jì)算齒根彎曲應(yīng)力r 2KT。2x1.5654x508276 021 , _= YsZZ =x 2.81x1.56f5 bd5m Fa5 sa5 70x100x5= 199305Mdb/丄安全 rF6 = rF5士理_ = 1

14、99.305M/MX2.21x1.78=222.094Md (M + 1)3由式5-391.0x58705f 2.442x189.8x0.9872x0.4x5.21497.49)= (5.21 + 1)32= 1418”取中心距a = 145/?/?/估算模數(shù) 叫=(0.007 - 002加=0.99 - 2.8/n/n取標(biāo)準(zhǔn)模數(shù)m = 2nun小齒輪齒數(shù)_ _ 2“cos0 _ 2x145xcos13 Zi m (m + 1)2 x(5.21 + 1)大齒輪齒數(shù)Z2 = 5.21 x 20.4 = 106.27取勺=21Z2 = 106實(shí)際傳動(dòng)比=t=1F=5-M傳動(dòng)比誤差A(yù)z =ff|!

15、?xl00%= l5,045,21l xl00% = 3.1%5%/.5.21在允許范圍內(nèi)修正螺旋角0 = arcs如護(hù)2 = arccos2x4) =12.3329。與初選0 = 13。相近，可不修正輪分度圓直徑 =他可 /cos0 = 2x21/cosl23329 =4299?d2 = mnz2 /cos0=2x106/cosl2.3369 = 211.00mm11機(jī)械設(shè)計(jì)課程設(shè)計(jì)圓周速度=324加/s一加屮 JX42.99X144060xl0360x10査表5-6取齒輪精度為8級(jí)4.1. 3驗(yàn)算齒面接觸疲勞強(qiáng)度電機(jī)驅(qū)動(dòng)，稍有波動(dòng)，査表5-3 kA=.100=2366X23 =0.6811

16、00査圖 5-4 (d) kv = 1.007齒寬=物=0.4 x 145 = 58.0/7?/?h=47.0866 =L34査圖 5-7 (a)=1.12査表 5-4=1.4載荷系數(shù) K = KaKv KKa = 1.72齒頂圓直徑 d“=d+2/7：？ = 46.99/w/nda2 = d2 + 2h；m = 221.00mm端面壓力角at = arctan(taikzzi /cos0) = arctan(tan20 /cosl2.8386) = 20.4707齒輪基圓直徑=心 cos% = 42.99xcos20.4707 = 40.275/?/?dbl = d2 costzz = 22

17、1.00 x cos20.4707: =203.30“”端面齒頂壓力角= arccos10,取=1.0Y=123329 =0.897 120 120.c “ v nnc O.75cos2 ph eg 0.75xcos2 11.5759 A由式 5-48 Y, =0.25 + =0.25 +=0.61526L971由式5-44= 11092Mpavcr訃安全_ 2 x 1.971 x 58706 乂 2 ?5 x 】575 x 0.6152x 0.897 58x42.99x2= 110.92x2.25x1.802.75x1.575= 103714MpavbF】2 安全4. 1. 5齒輪主要幾何參

18、數(shù)Z=21 Z2 = 106 u = 5.21 m = 2 p = 12.3329 mt = mn /cos0 = 2.05Ji = 42.99/?vn d2 = 217.00“da = 46.99nun da2 = 221.00”d 八=40.275 mm d fl = 203.30a = ga +2)= 145Z?i = 66m b2 = 5SmmdIA = 44A3mni dh2 = 182.56m/7?4. 2減速器低速級(jí)齒輪的設(shè)計(jì)計(jì)算4. 2.1材料選擇機(jī)械設(shè)計(jì)課程設(shè)計(jì)小齒輪：40Cr ,調(diào)質(zhì)處理，齒面硬度241286HBS 大齒輪:45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217235HBS

19、按齒面硬度241HBS和217HBS計(jì)算N、=60/73./, =60 x 373.06x1x(8 x 300 x 8 x 2) = & 92xl08心= = 2.37 x 108：34査圖 5-17 ZjV3 = 1,Z1V4 =1.05 (允許一定點(diǎn)蝕)由式 5-29 ZX3 = ZX4 = 1.0取仏=1.0,Zw =1.0,Z旳=0.92 (精加工)査圖 5-16 (b)6伽3=650旳卩4, cr/lim4 =650Mpa由式5-28E = i訕bL，0 L = 598 Mpa4. 2.2按齒面接觸疲勞強(qiáng)度確定中心距小輪轉(zhuǎn)矩為=145040 N nun初定螺旋角0 = 13初取 K?

20、 Z： = 1.0,査表 5-5 Z = 189.8jMpa減速傳動(dòng)“ =J =3.86 取0。= 0.4端面壓力角at = arctan(larq /cos/?) = :uctan(tcin20 /cosl3) = 20.4829基圓螺旋角Ph =arctan(tan0cosy ) = arctan(anl3： x cos20.4829) = 12.2035 由式 5-42 Zq = Jcos0 = Jcosl3 = 0.987-15 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)由式5-412cos 仇2 xca 12.2035Z _ cose sine - cos20.4829 sin20.4829 - 244?由

21、式5-39(I KT I ZZeZ Z&e如莎飛廠J“413+護(hù)匹竺嗎 2.442x189.8x0.987、112x0.4x3.86 k627.92=146.67mm取中心距估算模數(shù)a = 150/77/77mn = (0.007 0.02)d = 1.05 3mm取標(biāo)準(zhǔn)模數(shù)m = 2.5mm小齒輪齒數(shù)u二等i大齒輪齒數(shù)Z4 = uz3 = 3.86 x 24.058 = 95.863取 Z3 = 25 =96實(shí)際傳動(dòng)比傳動(dòng)比誤差A(yù)/ =工從 xl00%=卜一斛 xl00% = 0.52% 5% h3.86在允許范圍內(nèi)修正螺旋角 0 = arcco如工上=arccos2-27 t94) = 1

22、2.622x 1552a與初選0 = 13。相近，Z，Z0可不修正輪分度圓直徑 心=Z3 /cos/? = 2.5 x 25 /cos 12.620 = 64.050/?/“4 =叫 j / cos = 2.5 x 96/cosl 2.62 = 244.942a/?/?圓周速度査表5-6取齒輪精度為8級(jí)4. 2. 3驗(yàn)算齒面接觸疲勞強(qiáng)度電機(jī)驅(qū)動(dòng)，稍有波動(dòng)，査表5-3 kA=-16 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)vz3 _ 1.25x25Too 100= 0.313査圖 5-4 (d) kv = 1.03 齒寬 b = a a = 0.4 x 150 = 60.0m”=600 = 0.937d3 64.05

23、0査圖 5-7 (a)= 1.08査表5-4心=1.4載荷系數(shù) K = Ka Kv =1x1.03x1.08x1.4 = 1 .557齒頂圓直徑 % =心 + 2h：m = 64.050+2x1.0x2.5 = 69.050?？da4 =d4 + 2h：m = 245.942 + 2x1.0 x 2.5 = 250.942 nun端面壓力角aj = arctan(tanfzn /cos/7) = arctan(taii20c /cosl2.62) = 20.4546齒輪基圓直徑 db3 = d3 QQsat = 64.050x cos20.4546c =60.012/?/?dh4 = dA c

24、osaz = 245.942 x cos20.4546 = 230.435/wn端 面齒頂 壓力角 aat3 = arccos- = arccos- = 29.645: dai69.050=arcco如=23.324=7-s(tantan) + z4(tanaa(4 -tanat)2兀=y-25x(tan29.645 -tan 20.45468 ) + 96x(tan23.324 -tan 20.45468)= 1.807bsin P % 叫60sin 12.62=-1.7256;rx25由式5一43乙仔馬744-17 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)由式 5-42 Z戸=Jcos0 = Jcosl262。

25、= 0.9878由式5-41Ph =arctan(tan/?cos ) = arctan(tanl 2.62 x cos20.4546) = 11.85c由式5-41Z = ； 2cosA cosa, sin a?2xcosl 1.85cos20.4546 sin 20.4546= 2.444an =z/zzz/J|2AT2 u + *-r=2.444x 189.8 x 0.772x 0.9878x(2x1.807x145040 3.86+160x64.0502 X 3.86=480649Mpa 仏安全4. 2.4驗(yàn)算齒根彎曲疲勞強(qiáng)度査圖 5-18 (b)6向3 = 290M/m , 1.0,

26、取=1.0= l-, = l-lx = 0.898 120 120-18 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)由式5-4陸“25 +冒也= 0.25 +空M竺“5481.8072KT)2xl.807xl45040x262xi 56x0 898x089860x65.040x2.5= 120215MpavsL 安全Y Y=刃.3 嚴(yán)嚴(yán)= 120.215rFa3rSa32.27x1.78x2.62 x 1.6= 1388Mpa 安全4. 2. 5齒輪主要幾何參數(shù)Z3 = 25 Z4 = 96 ii = 3.86m = 2.5p = 12.62 tti =/cosp = 2.563 = 64.050/?/?/ d4 =

27、 245.942 mmda3 = 69.050/?/?/ daA = 250.942 nun3 = 56.887 nun d f4 = 227.3mma = *(心 +4) = 150mmdh3 = 60.012” dh4 = 230.435 nun5軸的設(shè)計(jì)計(jì)算5.1高速軸的設(shè)計(jì)計(jì)算軸的材料為選擇45#,調(diào)質(zhì)處理，傳遞功率P = 5.9kW轉(zhuǎn)速 n = 960/- / min 査表 8-2 Ao =110= 110X514405.9Y1.51mm由于軸上有一個(gè)鍵槽,貝!) J 17.57x(3%-5% + 1) = 18.10-18.45心取%=32訕 估定減速器高速軸外伸段軸徑 査表17-

28、2電機(jī)軸徑電機(jī)=38叫 軸伸長(zhǎng)E = 80mm-19 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)貝！Jd =(0.8 1 0“電也=(0.8 - 1.0)x38 = 30.4 38曲取 d = 32mm根據(jù)傳動(dòng)裝置的工作條件選用HL型彈性柱銷聯(lián)軸p5 OxlO3名義轉(zhuǎn)矩T = 9.55 一 = 9.55 x 一 = 40.246N m n1440査表11-1工作情況系數(shù)K = 1.25 1.5,取K = 1.5計(jì)算轉(zhuǎn)矩7； = AT = 1.5 x 40.246 = 60.369N 加?xùn)吮?2-1選TL6公稱轉(zhuǎn)矩 7； =250N-mT =59.688 TV許用轉(zhuǎn)速 | = 3300 r / niii = 1440

29、min軸孔直徑mm = 30”, max = 38?？取減速器高速軸外伸段軸徑d=32mm,可選聯(lián)軸器軸孔= 電川 =3Sm/n,d2 = 32 min聯(lián)接電機(jī)的軸伸長(zhǎng)E = 80?？聯(lián)接減速器高速軸外伸段的軸伸長(zhǎng)L = 82肋5.2中間軸的設(shè)計(jì)計(jì)算軸的材料為選擇45#,調(diào)質(zhì)處理，傳遞功率P = 5.386RW,轉(zhuǎn)速 =208.696r/min査表8-2 血=118d Anit = 110 x= 28.7”Y nY 373.06由于軸上有一個(gè)鍵槽，則 d 28.7 x (3% 5% +1) = 29.561-30.135min d取 %=40呦5.3低速軸的設(shè)計(jì)計(jì)算軸的材料為選擇40Cr,調(diào)質(zhì)

30、處理，傳遞功率P = 4.69%W,轉(zhuǎn)速=61.147r/min 査表8-2 血=118d n血存=118 x隔尋 = 45.08由于軸上有一個(gè)鍵槽，則 d 45.08x (3% 5% +1) = 46.4324 47.334機(jī)械設(shè)計(jì)課程設(shè)計(jì)nun d 取 Gin =刃加1因?yàn)槭切∨a(chǎn)，故軸外伸段采用圓柱形 根據(jù)傳動(dòng)裝置的工作條件選用HL型彈性柱銷聯(lián)軸名義轉(zhuǎn)矩T = 9.55 - = 9.55 x 小6= 532.033 N mn96.6計(jì)算轉(zhuǎn)矩 T( = KT. = 665 .(MN m查表22-1選TL8査表11-1工作情況系數(shù).T取1. 25公稱直徑 7； =71O2Vm7； =665

31、.O4m許用轉(zhuǎn)速 = 2100r/min n = 96.6/7 nin減速器低速軸外伸段= 50”,厶=112?？從動(dòng)端 d* = 0mm, L = 112 mm6低速軸的強(qiáng)度校核6.1繪制低速軸的力學(xué)模型厶=124.4/72/77厶 2 = 608作用在齒輪的圓周力F, =4330.045 N徑向力 Fr =F, tan a = 4330.045 x tan 20.4546 = 1615 .028 N軸向力 Fa=F, * tan/? = 4330.045 x tan 12.62 =969.4466.2求支反力水平支反力工Mp=0心(厶+厶)一巧厶=0* = 6095.0S60.J 2ooo

32、.955厶 +厶 124.4 + 60.8ZX =0, Rbx =片-RAx = 6095 .014 - 2000.955 = 4094.059N垂直支反力工Mr =0-Ra.(L + L2) + FrL2 -Fa = 0-21 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)FL.-F-心=厶+厶22273.329 x 60.8-1356.570 x 120.409, c “ c=一135.663N工Z = 0124.4 + 60.8/?伏=Fr R ； = 2273 .329 - (-135.663) = 2408.992 N-T妊L_V 機(jī)械設(shè)計(jì)課程設(shè)計(jì)L92777 015NRmmgi27.991NFmT11008S

33、.6S4N*mm192992.995221995.110/,X / / / / / 丿 / / / / / / 丿/ / / / 7 / / / /丿/7 / / / / / / / / / “ 丿/ /丿 / / / / .丿, %/%/%532470 / / / / / /7/ /777/77/7/ar/,/ / /1221995.1106.3作彎矩、轉(zhuǎn)矩圖（上圖）水平彎矩C 點(diǎn) MCx = RAxL = 1386.885 x 139 = 192777 .015 N nun垂直彎矩Al.C 點(diǎn)左 MCz = 一/?血厶=65.669 x 139 = 一9127 991 N nunC 點(diǎn)右

34、MI = R4 = 1680.697 x 65.5 = 110085 .654N mm 合成彎矩MeC 點(diǎn)左 Me = 192992995N mmC 點(diǎn)右 MI = J/W； +M： = 221995.11 ON mm轉(zhuǎn)矩 T = 532470N mm-23 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)6.1.4作計(jì)算彎矩Ms圖(上圖)該軸單向工作，轉(zhuǎn)矩產(chǎn)生的彎曲應(yīng)力按脈動(dòng)循環(huán)應(yīng)力考慮取 a = 0.6C點(diǎn)左McaC = jM：+(a7j = J(192992995)2 +(0.6x532470)2= 373249.3062C點(diǎn)右McaC =叔：+(辺)2 = J(221995.110)2+(0.6x0)2= 2219

35、95.110N77D點(diǎn)Meal) = Jm：+(qC)2 = Jo?+(0.6x532472)2 = 319483 mm6. 1.5校核該軸的強(qiáng)度根據(jù)以上分析，C點(diǎn)彎矩值最大，而D點(diǎn)軸徑最小，所以該 軸危險(xiǎn)斷面是C點(diǎn)和D點(diǎn)所在剖面。軸的材料為40Cr査表 81 bp = 736 Mpa 査表 8-3b“ L = 69/WpaC點(diǎn)軸徑=41.929mmMeaC |508630.646J 一*0.1丄 V 0.1x69因?yàn)橛幸粋€(gè)鍵槽= 41.929 x(l + 0.05) = 42.934mm 62mm安全D點(diǎn)軸徑心| S仏転L1440336.70.1x69=39.962mm因?yàn)橛幸粋€(gè)鍵槽 = 3

36、9.962x(1 + 0.05) = 40.967 ni剖面相比較，只是應(yīng)力集中影響不同?？扇?yīng)力集中系數(shù)值較 大的值進(jìn)行驗(yàn)算即可。同理vn、vid剖面承載情況也接近，可取應(yīng)力集中系數(shù)較 大者進(jìn)行驗(yàn)算。校核I、II剖面的疲勞強(qiáng)度I剖面因鍵槽引起的應(yīng)力集中系數(shù)査附表1-1 (插值)ka = 1.808 9 kT = 1.603II剖面因過(guò)渡圓角引起的應(yīng)力集中系數(shù)查附表1-2= 二化2.5- = = 0.02r 2d 50因I、II剖面主要受轉(zhuǎn)矩作用，&起主要作用，按I鍵槽引起的應(yīng)力集中系數(shù)機(jī)械設(shè)計(jì)課程設(shè)計(jì)計(jì)算T532470Fmax 叫= O.2OX5O=27-299A/Pa蟻= 13.650 M

37、pa査表 8-1 er. = 344 Mpaj = 199 Mpa査附表1-4 鬲=0.73=0.78査附表 1-5 pa = 0.916 pT = 0.916199查表 1-5 (pa = 0.34 ” (p: = 0.21S = Sr = 4.028護(hù)+以” O.9XO.78X2O134 + O-21X20-134取S=l5l& SS枝全校核VL VD的疲勞強(qiáng)度VI剖面因配合(H7/r6)引起的應(yīng)力集中系數(shù)査附表1-1 ka = 2.598 , kT =1.872VI剖面因過(guò)渡圓角引起的應(yīng)力集中系數(shù)査附表1-2D_d 68-60 4r2 八八“=4-=0.033 r2d 60ka =1.8

38、95 , k: =1.60VD剖面因鍵槽引起的應(yīng)力集中系數(shù)査附表1-1心=1.808, kT =1.603按VI配合引起的應(yīng)力集中系數(shù)校核VD剖面VI剖面承受的彎矩和轉(zhuǎn)矩分別為：理(厶一蘭卜 192：.()丸 % (139- 50/2)= 158282.mmL、2 丿 139VD剖面產(chǎn)生正應(yīng)力 crir 1X = - = 12.663Mpa 丄 W； =bEax = 12663Mpa,b加=VD剖面產(chǎn)生的扭剪應(yīng)力及其應(yīng)力幅.平均應(yīng)力為-25 -T532420max =衿:=0.2x50-，2325機(jī)械設(shè)計(jì)課程設(shè)計(jì)G=5=- = 6162Mpa査附表1-4 鬲=0.68片=0.74査附表 1-5

39、0。=0.94, P, =0.92査表 1-5 (pa =0.34,(pT = 0.212.5980.92x0.78sr =34412.325 + 0199= 6.721”=10.188iJ t +(p r x6.162 + 0.21xl2.32506 S 小 0.92x0.74Js； + S；9.262x7.916V9.2622 +7.9162= 10.288取S=l5l& SS枝全其它剖面與上述剖面相比，危險(xiǎn)性小，不予校核7低速軸軸承的選擇及其壽命驗(yàn)算低速軸軸承選擇一對(duì)30211圓錐滾子軸承條件：d=55mm,轉(zhuǎn)速n=61. 147r/min,工作環(huán)境多灰塵，載荷稍有波動(dòng)，工作溫度低于10

40、0 預(yù)計(jì)壽命厶 =2x8x8x300 =38000/?7. 1確定軸承的承載能力査表 21-3 軸承 30212 的 5 二74500N7-2計(jì)算軸承的徑向支反力/?, = J/?二 + Rj = 1388.439NR2=QR；x +尺2 = 3389.2287.3作彎矩圖(如前)7.4計(jì)算派生軸向力S査表 9-8 30212 軸承 Y=l. 5, 0=97800 , e=0. 4S| =&/2Y = 462813N-26 -機(jī)械設(shè)計(jì)課程設(shè)計(jì)S2 =R2/2Y = l29.143Nss?的方向如圖Fa7. 5求軸承軸向載荷F +S = 969.460 + 462.813 = 1432.273 NS, =1129743N故1松2緊A =S =462813N,A2 =S+C = 1432.259 N7.6計(jì)算軸承的當(dāng)量動(dòng)載荷P462.8131388 .439=0.333 , = 0.43389.228査表 9-6 X1 =1, =0査表 9-6 X2 =0.4,K, =1.5査表 9-7 fd=A根據(jù)合成彎矩圖取心=1，僉2=1A = fdfm(X, +)=1.1x1x(1x1388 .439 + 0)= 1527.283NP2 = fd fml(X 2 /?2 + y2 A,) = 1.1X 1 X(0.4 X 4750.217 +1.5 X 2025.