一、設(shè)計(jì)任務(wù)方案號(hào)電機(jī)型號(hào)額定功率同步轉(zhuǎn)速見任務(wù)書原件

滿載轉(zhuǎn)速 總傳動(dòng)比

P=2.015kwW4=0.0816P=r2.469kwP=3kw0n=1420r/min二、電動(dòng)機(jī)的選擇計(jì)算按工作要求條件選用三相異步溝通電動(dòng)機(jī)，封閉式扇冷式構(gòu)造,Y系列。1、選擇電動(dòng)機(jī)功率

°i三=34.3i帶=2.8i減=12.25i=4.06112

PW7

31000.652.015kw

=3.01223

10007] 刀刀

1000

P=2.469 kwon=1420r/min40?”1? 2?17-9確定個(gè)局部效率如下：皮帶傳動(dòng)效率： 400.95

3?44

oT=16.61Nm0P=2.346kwn〔二I507r/min 「二44.18Nm齒輪嚙合效率： 中 為8級(jí)〕

2

8kw滾動(dòng)軸承效率： 刀20.99〔球軸承〕

n=124.6r/min2T=172.66Nm2滾筒效率：

心 0.99. 0.96

P=2.163kw3n=41.4r/min3T=499.1Nm3傳動(dòng)總效率：40.950.9720.9940.990.960.816所需電動(dòng)機(jī)功率：P= =cC“=2.469kwPr]0.816

P=2.12kw4m=41.4r/minT=489.1Nm4P=2.716kwc查設(shè)計(jì)資料表27-1,可選Y系列三相異步電動(dòng)機(jī)Y100L2-4型，dd1=100mmB=3kw;Y系列三相異步電動(dòng)機(jī)Y132S-6型，額定功率V=7.4m/sR=3kw;均?f足B>Pr。2、選取電動(dòng)機(jī)的轉(zhuǎn)速、,小代六由仕、擊懾同岫轉(zhuǎn)速：n

60v600.65/一,.41.4r/min

d=280mmd2i帶=2.8a=493.5mmwTTD3.140.3w

adP=1.24

=1581 01500r/min1000r/min兩種方案進(jìn)展比較，由O表27-1查得電動(dòng)機(jī)數(shù)據(jù)，計(jì)算總傳動(dòng)比列于表 1中。Y100L2-比較兩種方案，方案1的減速器傳動(dòng)比更適合，由表27-2查得表2: 電動(dòng)機(jī)型號(hào)為Y100L2-4,其主要性能如下

△R=0.1913.01500142034.3213.01500142034.324Y132S-63.O100096023.22R/=1.36Z=2F°=155NQ=608.6NP0

/kw

3 電動(dòng)機(jī)軸伸長(zhǎng)度E/mm 60

Ni=1X109n0/(r/min)1420

H/mm

100

8N=3.58X10電動(dòng)機(jī)軸伸直徑D/mm 28 堵轉(zhuǎn)轉(zhuǎn)矩/額定轉(zhuǎn)矩T/N.m2.2三、傳動(dòng)裝置的運(yùn)動(dòng)及動(dòng)力參數(shù)計(jì)算1、安排傳動(dòng)比

[]565.6MPa1H12[]566.7MPa2HZ=2.44總傳動(dòng)比：i如您34.3 H0 41.4w17-9i=2~4i2.8i343則減速器的傳動(dòng)比：i34312.25i帶2.8對(duì)減速器傳動(dòng)比進(jìn)展安排時(shí)，為使兩級(jí)傳動(dòng)浸油深度相近，且避免

K0.3Z189.8JMPaEZ=0.987ZH=2.44a=125mmZ=241中間軸大齒輪齒頂圓與低速軸不想碰，取雙級(jí)齒輪減速器高速級(jí)的傳動(dòng)比：%J.35i減=4.061則低速級(jí)的傳動(dòng)比：

m=2d49.180mm1d=200.81mm2V=1.31m/si25423

3.012

b=40i 4.067122、各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計(jì)算0軸：0軸即電動(dòng)機(jī)軸TF=F=2.469kwT0n=1420r/min0

K=1.25AK=1.024v2=1.06L=1.2K=1.628P 2469103

d=46.156mmb1nT=9.55，n0o

9.5516.61Nm1420

d=188.475mmb2軸:I軸即減速器高速I軸

aat1

=29.782Pi=P0-

401

=P0-40

=2.469義

=23.2640.=2.346kw

aat2n=—1

1420i帶 507r/min2.8

葭=1.349T=9.55 9.5i

2.346103

44.18Nm

=1.38￡35n 50751

Z,=0.86軸: 軸即減速器中間軸II IIP=P2 i? 41?42

=2.3460.97義

ZR0.99n 0.99=2.253kwn=.1

507

124.6r/min

Z=2.452i4.06712

H=537.9Mpa八P八 2.253103 H2 “

9.55 172.66Nm124.6

Z=25.8v1Z=105.4軸:IH

軸即減速器的低速軸=2.253X0.97X0.99=2.163kw41?42

v2Y=2.65Fa1n二124.6“ 3—

41.4r/

YFa2

=2.24i 3.012 min232.163103

Nm

Ysa1

=1.58P3

9.5533 n 41.3

Y=1.814sa sa242軸: 軸即傳動(dòng)滾筒軸IV IV

(T =230MPaFlim1P=P3?

=2.1630.99義

=210MPa4 42Tl3

(TFlim20.99=2.12kwn=n4

[]328.6MPa=41.4r/min F 13 =9.55巳9.552.121034n4 41.4

489.1Nm

[]=300MPaF2將上述計(jì)算結(jié)果匯總?cè)缦?/p>

=108.60MPa(TF1=105.29MPa(TF28Ni=2.24X10N2=7.45X17[6HI1=597.6MPa[6H|2=602.14MPaKtZ2t1.2表三： 各軸運(yùn)動(dòng)及動(dòng)力參數(shù)轉(zhuǎn)速軸序 功率/

T/N? 傳動(dòng)形式

傳動(dòng)比 效率

K0.35Z=0.987號(hào) /KW2.46

(r/minm)

Z=189.8/TMPaE %0 1420 16.61

Z=2.4492.34

2.8 0.95

Ha=155mmm=2.5nI 5076

44.18

齒輪傳動(dòng)

4.067

0.96

Z=301Z=91d二2.25 172.6 2 1R 124.6

76.86mm3 6

3.012

0.96

d=233.14mm22.16m3

41.4

499.1

聯(lián)軸器

v=0.50m/s1.0 0.98 K=1.25AIV2.12 41.4IV

489.1

(=1.025四、傳動(dòng)零件的設(shè)計(jì)計(jì)算1、帶傳動(dòng)的設(shè)計(jì)計(jì)算PC4—4K=1.1

b=54.25mmK=1.03PKa=1.2K=1.6362d=81.86mma1

=KP=1.1X2.469=2.716kw

d=238.14mmC

a=20.46選取V帶型號(hào) 0 td=72.00mmPn4-12P、n工作點(diǎn)處于A型區(qū)，故選C o c oAV帶。d、ddi d2

b1d=218.43mmb2 aat1=28.410=23.48aat2&a=1.69ddi4-54-6確定，由于占用空間限制/ddi

>dmin

&B=1.295乙=0.769ZB=0.988Bb=11.8604-6ddi

=100mm

Z=2.44V

H(T =574.4MPaHV=「…二匚

100_1420=7.4m/s

Z*32.3601000 6010005—25m/s之間，故符合要求。d

Z=97.94v2YB=0.86Ye=0.677d2 [b]F1

=328.6MPad=id=2.8100=280mm查教材表4-6取d=280mmd2 di d2

[(r]=300MPaF2=149MPan和實(shí)際傳動(dòng)比i

(TF12(TF

2=144.402MPa不計(jì)影響，假設(shè)算得n與預(yù)定轉(zhuǎn)速相差5%為允許。e 2

F=1794Ntd 280 0d2=

F=669NrF=400Na2.a8基準(zhǔn)長(zhǎng)度L

R=787N1H1①初定中心a。

dd100d1

=847NRHRS=16.72因沒有給定中心距，故按教材書式4—25確定0.7(d+da2(d+ddi d2 0 di d2

S=68.26S=10.480.7X(100+280)<a0

<2X(100+280)

S=12.14266mm <a<760mm0取a=500mm0L

R=980N1R=1470N按教材式4-26: 2c：/pld2dd1)0L~2a+2(d d )+一4a0c 0 d1 d22802100

A=01A=400N2Ld

_ 冗 =2X500+-(100+280)=1613mm

+----------4500

P=1176N1P=1943.04N2L10h=14.49年4-2Ld

=1600mmo

=87.65MpabPa

T=611.37Nmca=a+—=500+1600_1613=493.5順220aamax

=a+0.03L=493.5+0.03X1600=541.5mmda=a-0.015Ld

=493.5-0.015X1600=469.5mmminai4-28得：a180°-(d1d)X60。=180°(280100)X60。a493.51= d d=158>120符合要求0Z4-29：Z>Pc<ZmaxP04-19,V帶所能傳遞的功率P=K(P+AP+AP)0 a 0 1 24-20得包角系數(shù)K“Ka=1.25(1514-2查得：

)=1.25X(15

C=3.78X104I -

C=9.81X10C=9.6X10-152 -3 3-5C4=4.65X10 L0

=1700mm公山=U20=148rad/s60 604-18、4-21、4-22可知:CP=d0

d131

2d-Cdd1 3

2(d )-Cd131

1g(dd4 1a1)]=100X148X[3.78X104--

9.8110100

3--9.6X10

15(100148)- 2-4.65X10lg(100X148)]-5X=1.24=Cd

21g --------TT----△P1

4d1⑴1

_Co1 1110」一(_1)Cds4 di=4.65X10

-5X

100X1481g-----------23 =0.19..八9.81103

1/1 .、110--------

——(——1)F4.651051002.8可得：

=CdC)1g—LL△p2 4 d1 1 °L=4.65X10100X148X1g-5X

1600=-0.002431700P=K(P+AP1+A )=0.95X(1.24+0.19-0.00243)=1.36c a 0 p2Pc27164-29:V帶的根數(shù)：Z>一=—6=1.99Z=2根PO1.36FO：4-1:q=0.1kg/m.................PC2.5 9按教材書式4-30:FO=500—(——1)+qv vzKaQ

2.716 2.52=500X------(----1)0.17.47.4 20.95 2=155N按教材書式4-31:Q=2FZsina=2X155X2Xsin^^=608.6N°確定帶輪構(gòu)造d(2.5~3)dd s大帶輪承受孔板式構(gòu)造d1=1.8d=1.8x26=46.8mm查設(shè)計(jì)資料表7-8得e=15,f=10,he=12,6=6,小=340,ba=11mmh=2.75amin帶輪的寬度：B=(z-1)e+2f=(2-1)x15+2x10=35mm五、高速級(jí)斜齒圓柱齒輪的設(shè)計(jì)計(jì)算原始數(shù)據(jù)：電動(dòng)機(jī)的輸出功率：2.345kW小齒輪轉(zhuǎn)速傳動(dòng)比

：507r/min：4.067單向傳動(dòng)，工作載荷有稍微沖擊，830010年1、選擇齒輪材料，確定精度等級(jí)及許用應(yīng)力455-1240HB大齒5-1:200HB選齒輪精8級(jí)(GB10095-88)。5-16(b):240HB時(shí)，*皿580MPa200HB時(shí)，*位550MPa計(jì)算應(yīng)力循環(huán)次數(shù)：由教材書式5—33得：__ 8N=60n1 1

jL=60X507X1X(10X8X300)=7.3X10h=1.79X10i4.067N2&31 82查教材書圖5-17得：Zw1.06,Z 1.122N由教材書式5-29得：Z Z 1.0x1 x2取Z=1.0,S=1.0,Z 0.92(精加工齒輪)w Hmin LVR5-28確定疲乏許用應(yīng)力：［用］

可際1

1ZZ=

580

1.061.01.00.92=565.6Mpa［ H SHmin

X WLVR

1.0-ci_|ii9_m

_ _ _

550 _ _ .［］ ZZZb H

Z=一1.121.01.00.92=566.7MPaxH 2II?

N2 x2IN

XLR

」、vv VI 4SHmin

1.0由于［即］1

<［即］,2

所以計(jì)算中?。蹫椋?［即］1

=565.6MPa2、按接觸疲乏強(qiáng)度確定中心距a小齒輪轉(zhuǎn)矩：T=44180Nmm1KZ1.2,B13,M0.3t2t由教材書式5-42得：Z§^coSJJcos135-5得：Z=189.8v”MPaE

0.987估取 =20°an

tana、 /tan20%arctan(

----)axctan( o端面壓力角:

cos0

)20.4829oo基圓螺旋角：瓦arctan(tanpcosat)12.20355-39計(jì)算中心距a：、/KT

ZZZI HE Ba>(u+1)；S------------V2小aU (TH

2.44189.80.987

=121.7mm=4.067

1 1.2441803.20.34.067

2565.6圓整?。篴=125mm估算模數(shù)：m=(0.007 0.02)a=0.875mm-2.5mmn取標(biāo)準(zhǔn)值：m=2mmn,2acos0m(u1)n

2125cos13-==24.032(4.0671)ZuZ1

=4.067X24.03=97.72取ZI24,Z2 98實(shí)際傳動(dòng)比：i實(shí)

4.08乙24傳動(dòng)比誤差：Ai1iI100%i理|

4.08-4.0674.067

100%=0.3%<5%在允許范圍內(nèi)修正螺旋角: =arccos

mZZn I 22a29824 ,=arccos 〃---------=12°34”H與初選B=13接近,Z ZB可不修正。HmZ 2 24 =49.180mm齒輪分度圓直徑：d

n1 cos12.578cos0mZ 298-=200.81mmdn2 cos12.578d2圓周速度: V=

cos0九nd1 l

九49.182507,60103

=1.31m/s33、校核齒面接觸疲乏強(qiáng)度 60105-3,電動(dòng)機(jī)驅(qū)動(dòng)，稍微沖擊，查得K=1.25A按沮1.31240.31,85-4(b)得100100K=1.024v齒寬b=a=0.3X125=37.5mm^a取b=40mm2」0_=0.8,低速軸的剛性較大，二級(jí)傳動(dòng)中齒輪相對(duì)于d149.180軸承為非對(duì)稱布置查教材書圖5-7(a)得：《=1.0685-4得：L=1.25-4計(jì)算載荷系數(shù)：K=KKKB K1.251.0241.061.21.628A V a計(jì)算重合度還，8B齒輪齒頂圓直徑：dd1

+2hmn

=49.180+2X1.0

2=53.462mmXa ad=d+2hm=200.81+21.0X2=204.810mma2 2 an X端面壓力角:aarctan(

tanocn

tan20o0t )arctan( )=20.452n 0cos0 cos12.578

d=dcos =49.180xcos20.452=46.156mmb1 1 at 0d=dcosa=200.18Xcos20.452b2 2 t

0=188.475mm

aat1

=arccos

d 46.156b1Ob1=arccos=29.782d 53.180民at2

=arccos

d 188.475b2 Oa2——=arccos=23.264a2(tan -tan )+Z(tan -tan￡a=27 [Z2 otat1 at 3 aat2 at)]12 tan20.452)+98(tan23.264=1.349

tan20.452)]bsinB40sin12.578 =1.38---由教材書式5-43計(jì)算:

Z=/=

—1—=0.861.349

Z§JcosBJcos12.578=0.99H由教材書式5-41ZH基圓螺旋角: Bb=arctan(tanBcosat)=arctan(tan12.5780xcos20.452°)=11.808°Z=2cosB= 2cos11.808bH--cosatsinOt-，cos20.452sin20.452=2.455-39計(jì)算齒面接觸應(yīng)力叫2KTu1=Z 1Z^H HZ

EZCZB

bdu2=2.45X189.8X0.86X0.992441801.6284.06714049.1802 4.067=537.9MPa<[b]=565.6MPa 安全H4、校核齒根彎曲疲乏強(qiáng)度取ZviY=2.65

=25.8,Z=2.24

=105.4,查教材書圖5-14得：v2FHI ,%a2查教材書圖5-15得：=1.58, =1.81Ka1 %2由教材書式5-47計(jì)算Y,因年=1.38>1.0“=1-

120=1-1.0由教材書式5-48Y2-0.75cosBb

cc0.75cos

11.8082a

b=0.25+ 1.349=0.79查教材書圖5-18bF230MPa 210MPa(TFlim2得:Flim1查教材書圖5-19得:YNIYN21.0YST5-32,由于計(jì)算許用齒根彎曲應(yīng)力

2.0, 1.4SFminm=2<5,所以取

=Y=1.0Y1 2F YFlim1 STv

v_2302.0

1.01.0=328.6MpaSFmin

YN1YX1= 1.4(TFlim2YST、，、， 2102.01.01.0=300MpaSFmin

YYN2

= 1.45-44計(jì)算齒根彎曲應(yīng)力-2KT1

YYY

Y0>1

=1 YFa1

sa1

Ye13bdm1 n21.62844180…c”cc=2.651.580.790.94049.2622=108.6MPa<阡=328.6Mpa安全1(TF2

%%2_==1 Y_=YY

sa12.241.81=108.65、齒輪主要幾何參數(shù)

2.651.58=105.2MPa<

=300MPa安全bF2Z24,Z98,u=4.067,m=2mm0=12°34”41〃d1 2

=49.180mmd=200.81mmda1

=53.180mmda2

=204.81mmdf1

=d「2(hac)mn2=49.180-22X(1.0+0.25)=43.180mmXd=d-2(ha c)m=200.81-2X2X(1.0+0.25)=195.81mmf2 2 na=25mm

齒兒：b1

=45mmb=40mm2六、低速級(jí)斜齒圓柱齒輪的設(shè)計(jì)計(jì)算P=2.252kw,小2n=124.6r/min,傳動(dòng)比i=u=3.0121、選擇齒輪材料，確定精度2455-1齒面硬度為240HB455-1200HB選8級(jí)(GB10095-88)5-16(b):小齒輪齒面240HB寸，/而580MPa200HB時(shí)，叫而550MPa1 2(對(duì)于工業(yè)用齒輪，通常按乂俄取值)5—33得：N8

=60njL=60X124.6X1X(10X8X300)=2.24乂2 hN 2.2410M 1 8 ?N=_ =7.45X102 i 3.0125-17得：Zw5-29得：Zx1

1.12, 1.19ZN2ZZ1.0x2取Z=1.0,S=1.0,Z 0.92(精加工齒輪)w Hmin LVR5-28確定疲乏許用應(yīng)力：r 1[ ]°-H1

7 777Hlim1ZZZZN1x1WLVRSHmin580=——1.121.01.00.92=597.6MPa1.0r i 7777Hlim2[ ] 0^H2SHmin

ZZZZN2x2WLVR550=——1.191.01.00.92=602.14MPa1.0==597.6MPa1 2, bH12、按接觸疲乏強(qiáng)度確定中心距a小齒輪轉(zhuǎn)矩：T=172660NmmIKZ2t1.2,暫取螺旋角13,K0.35t B由教材書式5-42得：ZB 7cosBMcos130.9875-5得：Z=189.8^lMPaE5-41ZH

估取*=20°端面壓力角：0ct基圓螺旋角：

arctan(

cos0

)arctan( )20.4829cos132cos0 _1 _ b

2cos12.2035

=2.44Z= =■HHTcosat

sin0t

tcos20.4829

sin20.48295-39a：1KT1HEa>(u+1)3HE

ZZZZB12=3.0121

U小a (TH小1.0172660\20.353.012

2.44189.80.987597.6=154.38mm圓整?。篴=155mm估算模數(shù)： m=(0.007 0.02)a=1.085mm-3.1mmn取標(biāo)準(zhǔn)值： m=2.5mmn2acos0

2155cos13小齒輪齒數(shù): m(u1)2.5(3.0121)n

==30.1ZuZ1

=30.1X3.012=90.62取乙30,Z 912實(shí)際傳動(dòng)比:傳動(dòng)比誤差:修正螺旋角:

3.012-3.033.012

100%0.7%<5%==arccos

mZZn 1 22a

=arccos2530+91=12。37”44〃2155B=13°接近，ZHZB可不修正mZ1n

2530d

=----= =76.86mm1cosBcos12.628Z,m 2.591=233.14mmZn2 cos12.628 d 2cosB同國(guó)、擊詳 、, 冗冗76.86124.6八“，圓周速度： V=---------3-

=-------

3-------

=0.50m/s3、枚核齒面接觸疲乏強(qiáng)度

60103

601035-3,電動(dòng)機(jī)驅(qū)動(dòng)，稍微沖擊，查得K=1.25A按%0.50300.15100 10085-4(b)K=1.025v齒寬b=Ka=0.35x155=54.25mm取b=55b552^^0.7,低速軸的剛性較大，二級(jí)傳動(dòng)中齒輪相對(duì)于軸d176.86承為非對(duì)稱布置查教材書圖5-7(a)得：。=1.0385-4得：(=1.25-4計(jì)算載荷系數(shù)：K=KKLK=1.251.025X1.03X1.2=1.58A V a計(jì)算重合度篤，齒輪齒頂圓直徑：d=d1

+2hm=76.86+2X1.0X2.5=81.86mma1 a nd=d+2hman

=233.14+2

1.0X2.5=238.14mmX端面壓力角：

a2 2隊(duì)工,arctan(tan、an-----)，,隊(duì)工,arctan(tan、an-----)，,arctan(tan20、八八,八。o}=20.46cos0cos12.628o1 at

0=72.000mmd=dcosa=233.14xcos20.46b2 2 t

=218.43mm0

otat1

=arccos

=arccos =28.41d 81.86a1d 218.43~，c°[Z22兀

(tanat-tana)+Z(tana-at)]=1.69tanat1 t 3 at2tanbsinB54.25sin12.63彳…&B = = =1.295冗111n

2.5冗5-43計(jì)算：Z“fT=J，=0.769;強(qiáng)\1.695-42計(jì)算：乙SJJcos12.628=0.9885-41ZH基圓螺旋角:

B btb=arctan(tan12.628=11.86°

0xcos20.46°)Z=2cosH

瓦=,2cos“86

=2.44\c0soesin0c\cos20.46sin20.46t t5-39計(jì)算齒面接觸應(yīng)力(TH=2.44X189.8X0.769X0.988

21726601.583.01215576.862

3.012=574.4MPa<［叫］=597.6MPa安全4、校核齒根彎曲疲乏強(qiáng)度2取Z=32,Z=98,查教材書圖5-14得：丫尸卻=2.56,Y=2.272VI v2 FH查教材書圖5-15得：％=1.63,Y=1.82sa25-47計(jì)算丫,因電=1.295>1.03=1-e”=1-1.0

12.628

=0.861205-48計(jì)算丫2-—0.75cos

0.75cos

11.862丫=0.25+------

b=0.25+=0.677與高速級(jí)齒輪一樣 昨=328.6MPa,昨=300MPa1 25-44計(jì)算齒根彎曲應(yīng)力=2KT0 1YY0>1

=；~~；-bd〔mn

”Fa1

L1sa1 YB21.58172660?5576.862

2.561.630.6770.86=149MPa<r =328.6Mpa 安全F1=144.402MPa<阡=300MPa 安全25、齒輪主要幾何參數(shù)Z30,Z91,u=3.012,m=2.5mm1 20=12°37”44〃d=76.86mm d=233.14mmd1 2

=81.86mmda2

=238.14mmd=d1

-2(ha

c)mn

=76.86-2X2.5X(1.0+0.25)=70.61mmf1d=d-2(haf2 2

c)mn

=233.14-2X2.5義(1.0+0.25)=226.89mma=155mm

齒寬：b=55mmb=50mm1 2(T=b 2

YFa2

YSa2

2.261.80=147.867 F2 F1

F1YFa1

Ysa1

2.541.64七、軸的設(shè)計(jì)計(jì)算1、減速器軸的設(shè)計(jì)計(jì)算45號(hào)鋼，調(diào)質(zhì)處理按扭矩初步估算軸端直徑初步確定高速軸外伸段直徑，高速軸外伸段上安裝帶輪，其軸徑可按下式求得：P8-2得：dA3I1-8-2得：A=130,0 01n估算高速軸外伸端最小直徑：圓整取：d26mm1該段軸長(zhǎng)：l=(Z-1)e+2f=(2-1)x15+2X10=35mm估算低速軸外伸端最小直徑：圓整?。篸48mm3估算中間軸安軸承處最小直徑：d36mm22、高速軸強(qiáng)度計(jì)算44.18Nm,帶輪上的壓軸力Q=609N齒輪的分度圓直徑d=54.18mmd=49.180mm1 f螺旋角0=12.578°,=20.452°。at設(shè)計(jì)軸的構(gòu)造a1112mm2b、布置軸上零件，設(shè)計(jì)軸的構(gòu)造。依據(jù)安裝和定位的需要，初定各軸段直徑和長(zhǎng)度，各跨度尺寸，作軸的簡(jiǎn)圖如圖1按彎矩合成強(qiáng)度條件校核軸aa所示。bHVb-e所示。計(jì)算齒輪所受的各個(gè)分力，繪制空間受力簡(jiǎn)圖 b圓周力：Ft

2T1=1794Ntd1軸向力：FFtan0400Na徑向力：FrFtan%669NcMf所示。d、畫軸的扭矩圖，T=44180Nmm,g所示。

畫計(jì)算彎矩圖hoa,取依據(jù)：M ‘M (aT) 0.6ca 2 2,aM2HM1Hf、確定危急剖面，校核強(qiáng)度依據(jù)圖中軸的構(gòu)造尺寸，選擇彎矩最大的剖面和彎矩較大,I軸頸較細(xì)的剖面進(jìn)展驗(yàn)算II8-3查得：45號(hào)鋼，[]=55MPa(rb-i剖面的計(jì)算應(yīng)力:I剖面的計(jì)算應(yīng)力：IIMa1

10.44MPa<[(7]=55MPa合格b-i61432°ca

214.3MPa<[

(rb

=55MPa合格-10.1353

按疲乏強(qiáng)度安全系數(shù)校核軸分別選擇田、IV肩圓角處有應(yīng)力集中。IV剖面除受彎矩和扭矩外，四周還有過(guò)盈配合，鍵槽和軸肩圓角三個(gè)應(yīng)力集中源。45鋼調(diào)質(zhì)的機(jī)械性能參數(shù)：丘637MPa,

268MPa,1r 155MPa。1a、III剖面疲乏強(qiáng)度安全系數(shù)校核因軸單向轉(zhuǎn)動(dòng)，彎曲應(yīng)力為對(duì)稱循環(huán)變應(yīng)力。扭剪應(yīng)力按脈動(dòng)循環(huán)處理。依據(jù)教材附表查取應(yīng)力集中系數(shù)，確定尺寸影響系數(shù)和外表質(zhì)量系數(shù)。依據(jù):Dd依據(jù):Dd54.18049.4801.r2.66,d5查得:1.81.5,即0.8487

1.5—049.180

0.03則: S 268 =16.72ff 1.88=S_=—乂K

0.8 4 5

6.801.570.780.95

1550.9750.210.975

=68.2616.7268.26 =16.2316.7268.262 2取 1.8 滿足要求，所以III剖面疲乏強(qiáng)度[S]=1.5才兩足要求。

S>[S],b、IV剖面疲乏強(qiáng)度安全系數(shù)校核因軸單向轉(zhuǎn)動(dòng)，彎曲應(yīng)力為對(duì)稱循環(huán)變應(yīng)力。扭剪應(yīng)力按脈動(dòng)理。

依據(jù)教材附表查取應(yīng)力集中系數(shù)，確定尺寸影響系數(shù)和外表質(zhì)量系數(shù)。查得: 1.76,A1.54, 0.91, 0.89,( ￡ff ￡tT取以0.21268則: =10.481.7612.5600.910.95=1.54

155 =12.140.890.956.280.216.28c S。S 10.4812.14S= =_

=7.98SS22取[S]=1.5 1.8滿足要S>[S],

,10.4812.142 2IV剖面疲乏強(qiáng)度八、滾動(dòng)軸承的選擇和壽命驗(yàn)算I1、滾動(dòng)軸承的選擇減速器中的軸承承受較小的徑向載荷，可承受深溝球軸承。21-135mm選取軸承代6207。40mm6208。55mm6211。2、高速軸滾動(dòng)軸承壽命驗(yàn)算d=35mm該軸承所承受的軸向載荷F=400N,軸轉(zhuǎn)速an=507r/min,工作有輕度沖擊，初選深溝球軸承6207,要求軸承預(yù)期壽24000h。R,RFA由前面計(jì)算得知：R787NIH■,R2合成支反力： R R=：7872■,R2I IH 2V 22 2 R<RR2 2 2 H VF=F=400NA a

1210=1470N2確定軸承的承載力量，查課程設(shè)計(jì)教材表21-1,6207軸承:Cr〔動(dòng)〕=19.8KNCr〔靜〕=13.5KNo計(jì)算當(dāng)量動(dòng)載荷

故：A=F=400N,A=0a I因 黑0.029為:

,確定e=0.22由：L-4000.27>e=0.222 1270所以：X=0.56,Y=1.992 2軸承承受輕度載荷沖擊，按教材書表9-17f=1.2,d9-41=1,由于軸承不承受力矩載荷，故

f=1omPffn(XRYA)1.21(0.562 d 22 22

14701.99400)1943.04N校核軸承壽命P>R,所以按2計(jì)算軸承壽命。,L10h

10fc6 t

106 1

3 ,34784h60nP 605071943.04由于L=34784>24000h,故6207軸承適用。10h九、鍵聯(lián)接的選擇和驗(yàn)算大帶輪裝在高速軸軸端，需用鍵進(jìn)展周向定位和傳遞轉(zhuǎn)矩。由前面設(shè)計(jì)計(jì)算得知：V4545鋼，輪轂長(zhǎng)為33mmT=44180Nmm選擇鍵聯(lián)接的類型和尺寸。選擇最常用的圓頭(A便利等優(yōu)點(diǎn)。鍵的截面尺寸由鍵所在軸段的直徑定，鍵的長(zhǎng)度由輪轂的寬確定，查課程設(shè)計(jì)教材表為：bh=8X7,L=28mm

d由標(biāo)準(zhǔn)中選20-1得兩個(gè)鍵鍵聯(lián)接的強(qiáng)度計(jì)算一般平鍵的主要失效形式是鍵，軸和輪轂三個(gè)零件中較弱零件的壓潰。由于帶輪材料是鋼，許用擠壓應(yīng)力由表鍵的工作長(zhǎng)度：l=L--=28--=24mm22

3-1h=100MPa.,、 ，1 4T444180 、.3-1得：

=-L(rP

= =87.65MPa<bpdhl26728

=100MPa安全p十、聯(lián)軸器的選擇和驗(yàn)算且有稍微沖擊，因此聯(lián)軸器應(yīng)具有緩沖減振力量，應(yīng)選擇彈性柱銷聯(lián)軸器。489.1Nm依據(jù)：d=48mm選擇聯(lián)軸器TL8:48X112(GB/T4323-2002)由課