機械設計程設計計算 說明書 目 二級分流式減速器指導教師 王艾倫院 系 機電工程學班 級 機械0906學 號 0808090717姓 名 陳 良完成時間 2012 年3 月111.·························· 22.························· 23.························· 24.··························· 456172527與29器32箱體附件32潤滑式及密封形式33箱體34課程總結(jié) 35考資料 36說明 果.ηw=0.96；5環(huán)境380V極其生產(chǎn)批量一般機械廠，小批量生產(chǎn)。（1）確定傳動裝置的類型，畫出機械系統(tǒng)傳動方案簡圖；（2）選擇電動機，進行傳動裝置的運動和動力參數(shù)；傳動系統(tǒng)中的傳動零；繪制減器裝配圖圖和裝配圖1（A0）;圖1A1（A2）據(jù)力（N2（D)傳動方案的擬定機電動機動，電動機1器2動力傳減3器4傳機5，動6傳動系統(tǒng)中級流減器，級相對于承位置對稱，沿，高級和低級分別斜圓

L'=14600hhF=2000NV=1.2m/sD=300mm級分流式器PAGEPAGE38說明 果說明 果動機的選擇和計算Y1P：wP×ww轉(zhuǎn)速n

Pwwwn=60×1000V/πD=63.7r/minw2：

n=63.7r/miw2231 2 3 w中 1 2 3 w效 是效98=0.98w =0.96w

1 2

η=0.852231 2 3

92828363Ped輸出PdP=P/η

Pwd w dwP wed

P 4wed轉(zhuǎn)速n=63.7r/miw該傳統(tǒng)為分流式圓柱齒輪傳18-1推薦傳比為ii

=8～601 2則總傳860則轉(zhuǎn)速可范圍為n' =8n=8×63.7=509.6r/mind1 wn' =60n=60×63.7=3822r/mind2 wnnnn說明 果nn[1]16-1方

質(zhì)號率 量案 W比1Y132M1-6410001Y132M1-64100096015.72.2732Y112M-641500144022.52.243

/kg

11ABCDEFGHY132M1-62161788938801033132KABACADHDBBL12280135210315238515傳動比分配傳動比[1]20-2n=r/n；

i=15.07mi=nm/n=960/63.7=15.07分配各級傳動比[1]2—3各級分配各級取高級圓柱齒輪i1.4i則低級圓柱齒輪1 2ii/ii/1.4i

i=4.5912 1 2

i=3.282i1

i=3.282說明 果

nn=nn

=960r/min

I III IIn

960r/minn III

II 960/4.58r/min=209.2i1n

n =209.2r/miIIInn n

209.2/3.28=63.7r/minIV V i

n n=22按額定功率P 入功率ed

Vr/minPwPP

w I

P6wP P =49ww III 1P P

=3.90.98wII

2 3w

P wIIIP P

=3.80.98w

2 3w

P 5wIVP P IV 3

=3.60.99w

P=3.54kwV

T 9550I

PI=9550×4/960NmnI=39.79NmP

T=39.79NmIT =39.39T 9550II

II=9550×3.96/960 NnII=39.39NmP

IINmTIII

9550

n

=9550×3.80/209.2N

T =173.47III說明 果PT 9550 IV nP

=173.47Nm=9550×3.65/63.7N=547.21Nm

NmT NmT 9550 V nVVV

=9550×3.54/63.7 N=530.72 Nm

T 530.72項目表3 軸的運動動力參數(shù)電動機軸 高速級軸 中間軸低速級軸滾筒軸VI IIIV轉(zhuǎn)速960 960 209.263.763.7（r/min）功率4 3.96 3.803.653.54（w）轉(zhuǎn)矩(Nm)39.79 39.39 173.47547.21530.72傳動比 1 4.59 3.28 1效率 0.99 0.96 0..96 0.97六、齒輪傳動設計高速級齒輪傳動設計選擇材料、精度參數(shù)a.按圖1所示傳動方案，選用斜齒圓柱齒輪傳動b.帶式運輸機為一般工作機器，速度不高，故選用7級精度（GB10095-88）c.1表質(zhì)45（調(diào)質(zhì)HBS40HBS。d.Z=28，則大齒輪齒數(shù)1

Nm小齒輪材料為40Cr260HBS大齒輪材料為5，硬度為220HBS，初選小齒輪齒說明 果i=4.592Z=4.59×24z2e.初選螺旋角β=14

Z1Z2β=14f選取齒寬系數(shù)d

=0.8d

=0.8d2）按齒面接觸強度設計按下式試算u2kT uu

1Z Z 2tdt3

1 1 H Ed a 1 H1）確定公式內(nèi)的各數(shù)值a.試選k=1.6t1b.矩T=T /2

k =1.6t11

T=19.70=19.70Nmc.查圖表（P217圖10-30）選取區(qū)域系數(shù)Z =2.433H

1NmZ =2.433HZEd.查圖表（P215圖10-26）得

=189.8

MPa1

Z =189.8E212 =0.77，a2

=0.89

MPa2 =0.77+0.89=1.66a a1 a2

=1.66aL =14600hhL =58hh則應力循環(huán)次數(shù)

N 6.41081N 60jnL1 II

60173014600

6.4108

N 1.6×2N N/i

=6.4×108/4.16=1.6×108

1082 1 1[210-192條線KHN1=0.91，KHN2=0.97。

KHN1=0.91，KHN2=0.97。說明 果S=1[2]10-21dlim1

H1

509.6MPa

K HN1

0.91560MPa

509.6MPaH1 S

504.4MPa

K HN2

0.97520MPa

H2504.4MPa

H2H

S1

2

=507MPH4d1t2

ad =40.48mmd 21.619.71031189.8 mm 3 0.61.66 507 =40.48mmVdn/6010001 14×=2.03m/sb模mnt

V2.03m/1b=d

d =0.8×40.48mm=32.381t

b=32.38mmm =d cosβ/Z=1.64mmnt 1

m =1.64mmh=2.25m =2.25×1.64mm=3.69mm ntntb/h=32.38/3.69=8.77 =0.318 Z d 1

=1.52=0.318×0.8×24×tan14=1.52說明 果KK 37A

K =1.25AP194Kv

94

K9；v

K K H H

K =1.134H3K F

K =1.221FKH

K =1.4F

K K =1H F.4KKKK KA V H H

④

K=2.16K=1.25×1.09×1.4×1.134=2.16 11按實際校正所圓徑KKddKt3t

⑤

d 44.74mm1d 40.481mn1

2.161.6

mm=44.74mm

m =1.81mmn1m =dZ/22mm1 1

=1.81mm按設計2KTY

Y Ym 3 1

n1 Z2 d1 1 F確定說明 果KKKK KA V F F

⑥

K=2.331K=1.25×1.09×1.4×1.221=2.331

Y=0.88根據(jù)縱向重合度

=1.52查圖表（圖10-28）螺旋角影響系數(shù)Y當量齒數(shù)

=0.88

Z =26.3V1Z =120.4Z Z

/

24/14=26.3 V2V1 1Z Z /116/14=120.4V2 2查取齒形系數(shù)查圖表（P20010-5）YF1

=2.588，YF2

=2.178

YF1YF

=2.588，=2.178查取應力校正系數(shù)查圖表（P20010-5）YS1

=1.596，YS2

=1.792

YS1

=1.596，彎曲疲勞許用應力

Y =1.792S2取彎曲疲勞安全系數(shù)S=1.4，彎曲疲勞壽命系數(shù)K =0.85，F(xiàn)N1KFN2

=0.88。查小齒輪彎曲疲勞強度極限

FE1

=500MPa

S=1.4，K大齒輪彎曲疲勞強度極限

FE

=380MPa，

FN1K

=0.85=0.88

KN

⑦

FN2S K

H1 HN1H1

0.85

500/1.4MPa

303.57MPa

303.57MPa

K HN2

0.88

380/1.4MPa

238.86MPa

H2

H2 S

MPaY Y

F

并加以比較說明 果Y Y1F

S11

=2.588×1.596/303.57=0.01372Y Y2F

S2

=2.178×1.792/238.86=0.016342KTY

cos2 Y Ym 3 1 FZ2 d11 F

mm m =1.59mmn1 22.3319.71030.88cos20.016343 0.82421.653=1.59mm由以上，取m =2，按接觸疲勞強度得的分度圓直徑n1d=44.74mm應有的齒數(shù)1

Z=231Z d1 1cos/mn

=44.74×cos/2=23.05

Z Z=231

uZ2 1

2=4.59×23=105.57取106幾何尺寸中心距

a133mmm (ZZ) 2(23106) 1a 1 2 1 2cos

2cos14 mm=132.95mm將中心距圓整為133mm按圓整的中心距修正螺旋角m(ZZ) 2(23106)

45'

5''

1 22a1

2133

14o5'15''因值改變不多，故參數(shù)a

，K ，Z

等不必修正大小齒輪的分度圓直徑d Zm /cos1 1

45'

5''

d 47mm1說明 果=47.4mm47mm

d 219mm2d Zm /2 2 n1

=106×2/cos

4o5'

5''

=218.5.mm219mm

b37.6mm1b1 d

d=0.8×47.4mm=37.6mm1

B=35mm，2圓后B=35mmB=40mm2 1構(gòu)設計由e＜2m，小齒輪做成齒輪軸，t1由d <500mm，大齒輪采用腹板式構(gòu)a2低速級齒輪傳動設計a.按圖1所示方案，選用直齒圓柱齒輪傳動b.選用7級精度（GB10095-85）擇 為5

B=40mm1小齒輪做成齒輪軸，大齒輪采用腹板式結(jié)構(gòu)小齒輪：40Cr（調(diào)質(zhì)度240HBSZ=243選齒寬系數(shù) =1.0d2按下式試算

Zi4 3

=24×3.28=78,7

Z =24 ，3Z=784 =1.0KT u

1 Z 2 d2d 3 t22

E3t u d2 2 H確定公式內(nèi)各數(shù)值試選K =1.3t2

K =1.3t2說明 果TT =173.47Nm

T =173.473 =1.73×105

N1

3NmZ =189.8E查圖表（P表10-6）選取彈性影響系數(shù)Z =189.8MPa2E查圖表（P 圖 10-21d）得接觸疲勞強度極 =670MPa， =610MPaHlim3 Hlim4由式②應力循環(huán)次數(shù)

1MPa2 =670Hlim3MPa，N 60n

=60×175.48×1×14600=1.54×108

Hlim4

=610MPa3 3 h

N 1.54 ×3N N /3.18=6.373×108/3.18=4.84×1074 3查圖表（P10-19）取接觸疲勞壽命系數(shù)K

108N =4.84×107K HN3

HN

=1.06 4g

K

=0.97，得 K =1.06HN4H3

=0.97×670MPa=649.9MPa

H3

=649.9

H4

=1.06×610MPa=646.6MPa

MPaH4

=646.6分度圓直徑

d 3t

中較

MPaH4

=646.6MPa得KT u

1 Z 2d 3t

t22 2u

E

d =68.2mmHd2 2 3tH2.32

1.31.73105

3.281189.82 = 3 1 3.28 646.6 =68.2mm圓周速度V3

V =0.76m/sV d n /601000 33 3t 說明 果4×2s齒寬b3

b=68.2mm3b d

=1×68.2mm=68.2mm3 d2 3t模數(shù)、齒寬高比模數(shù)m =d /Z=68.2/24mm=2.84mm

m =2.84mm22 t 3齒高h=2.25m =2.25×2.84mm=6.39mm3 2則b/h=68.2/6.39=10.73 3載荷系數(shù)數(shù)Ka=1.25 據(jù)V=0.75m/s級精度查圖3

Ka=1.25V=0.75m/s3圖10-8）得動載荷系數(shù)K =1.02，直齒輪V2

H

KF

=1

K =1.02V2 =1和b=68.2mm得

=1.312d2 3

H2

KH2

KF2=1由b/h=10.7和K =1.292查圖表（P圖10-13）得=13 3 H2K =1.312F2

K =1.312H2故根據(jù)式K2

KKK K K=1.59A V H2 H2 2

K =1.352F2K K=1.593K按實際載荷系數(shù)系數(shù)校正所得分度圓直徑。由式dd3KttK

2d=72.9mm2得d d 22 23K2

=72.9mm

m=3.04mm模數(shù)m 22m d /Z=72.9/24mm=3.04mm2 3 3 公式為說明 果2KT

Y Y

=500MPam2 3

22Z2

2

S2

⑨

FE3d2 3 F

=380MPaFE4K =0.892P cN3 =500MPa =380MPaK =0.92FE3 FE4 FN4.PK K FN3 FN4S=1.42

S=1.42

KN mSK

0.892500/1.4MPa

318.57MPa

318.57HN3H3

m3H3

K HN4

m

0.92380/1.4MPa

249.71MPa

MPa

249.71H4 S H4K2

KKK KA V F F

MPaK=1.25×1.02×1×1.352=1.722PYF3

=2.65

YF

=2.22

K=1.722校正P5

Ys3

8YF3

=2.65Ys4

=1.77

YF4

=2.22Y Y

=1.58Y Y

F

并加以比較

Y

=1.773F

S3

=2.65×1.58/318.57=0.013143Y Y4F

S4

=2.22×1.77/249.71=0.015746說明 果m 2

21.72105242

mm=2.45mmmnm=2mnmd1=74.14mm得Z d /m3Z=24，3 3 2 3Z u Z=3.28×24=78.7 4 2 3幾何尺寸中心距

Z=2，34Z=784m(Z Z)a 2 3 42 2

=3×（24+78）/2mm=153mm整后a=1532

a=1532d mZ3 2

3

mm=72mm

d=72mm3d mZ4 2

378mm=234mm

d 4輪寬度b

d=1.0×72mm=72mm

B=75mm，3 d2 3 3BmB03 45）構(gòu)設計e＜2m3做成，t1d <500mm輪4采用腹板式構(gòu)a2

B=70mm43輪軸4板式構(gòu)說明 果徑402234713335106219752472315370782341P6w n nT 9N

TT

/2=19.7II II IINm

1

F 813.0Nt1F t1

cosd1

=××03×s4o5'

5''/47N

F =305.1Nr1=813.0NF

tan

tan200

F =204.2NF r1

n N=305.1N a1cos14o5'15''F Fa1

tan

0tan14o5

5''N=204.2N周F 向F F 方向如圖所示r1 a1說明 果

A 0IIPdA30 n

⑩5d3 A 0 d0II

=18.52mm2d

P3

110

mm=17.64mmII0II nII

960dm5%d2min

d

K =1.5AT KT

）

T =59.69caIIca AP351K =1.5T 59N

NmA caII=59.69 Nm根據(jù)T =213.71NcaII

電動機D=38 mm標

d =32mmIImin14用6彈性套柱銷半孔徑d=32mm半L=82半與配合轂孔長度1L=84mmd =32mm1 IImin構(gòu)設計擬上零件配方案經(jīng)分析比較用如所示配方案說明 果I II III IVV VII VIIIIX X） Imm ）dIIId L

dIII

=32mmd

II

mm mmIII

d =36mm

IIIIId dd

II

=37mmIVVIIIX=43mm400，d×D×B=40mm ×68mm ×15mm

d =42mmVI-dIIIIV

dIX

=40mm dIVV

d

=43mm

dIIIIV

dXL

=6mm

=40mmIVVIIIX）d mmL L

=40mm

VI-VII

VVII

60084指導書表 1 知箱體內(nèi)壁到座孔端面距離L

=58mmLC

(5

mm

=42mm凸緣

III1 1 2 1

L L蓋蓋總寬30mm到距離25mm

VVII則L =55mm

，=6mmIIIII

L L5amm2'13之間距離c=10mm端面距箱體內(nèi)壁S=8mm

VVII=40mmL BSa(L

B)

1 LIIIII

=55mmIIIIV IV1

LIIIIV

=LIXXL LIXX

=15+12+8-2-6=27mmIV =27mm

27mmL =95mmVI-VIILVI

B2c5=95mm3說明 果3C

I

=32

鍵bhl=10mLIII

m6bhl

m×8mm××50mm。滾動承過渡配合來保證直徑尺寸確圓角和倒角尺寸×4I設計

50mm1.5×45圓角R1已知P 0wT 4Nm n III

III

III求作在齒輪力

F =813.0Nt2F Ft2

0NF r2

F F r1 a2

F =204.2a1

F =305.1Nr2F t3 d

III3

=2×173.47/0.072N=4818.6N

F =2.4.2Na2F=4818.6NF Fr3

tan200=1753.8N t35P取A 00III

F =1753.8Nr3說明 果d IIImin

3.80209.2

mm=28.9mm。該軸的最小直徑為安裝軸承

A 0III處的直徑，取為d =30mmIIImin3．軸的構(gòu)設計（1）擬定軸上零件的裝配方案，如圖I II III IV V VII VIII（2）確定軸的各段直徑和長度

d =30mmIIImin1）根據(jù)d =30mm取

=40mm

=40mmIIImin

III

VIIVIII

d =d軸承與齒輪2，2'之間采用套筒定位，取d

d

I

VIIVIIILIIIII

=LVI

=35-2=33mm

IIIII VI

40mmd d23dIIIIV

=d 50mmV-VI

IIIII VI-VII=43mmLIIIIV

=LV

=10m

dIIIIV

=d =V-VI齒輪3采用齒輪軸，LIVV

=B=75mm3

50mm2）初步選擇滾動軸承由于配對的斜齒輪相當于人字齒，軸II相對于機座固定，故初

L L II VII42008d×

L

=LVIVII×90mm×20mm，aS=10mmaS=10mm，則

=33mm1 1 2 2L L 42mm

LIIIIV=10m

=LVVIIII VII

LVIVII

=75mm說明 果3

滾動6208承d dIIIII VI

mB2

承端蓋總寬度L =LIIIII VI

=33mmPIIb××4P×4徑R1

II-III 及b×h×L=14×9×40mm設計已知P w T 1Nm n IV IV IV求作在力F Ft4

=4818.6N

F Fr4 r

=1753.8N初步確最小直徑5PA 0IV

F =10541.8Nt4F =3836.9Nr4d 3IVmin

mm=42.4mm。該最小直徑安裝聯(lián)軸器處直徑選聯(lián)器號。PK =1.5則A

A 0IVT =1.5×547.21Nm=820.8NmcaIV據(jù)T 8Nm準54caIV

K =1.5A說明 果HL6d =45mmIVmin1I II III IV V VII VIII IX2

T =2529.9caIVNm出HL6器d =65mmIVmindVIIIIX

d

=45mmdd

VII

d

=52mmDL

=82mm

VIIVIII

2

LVIIIIX

=82mm00

6211d×D××90mm×

dI

dVIVIIdIII

dVI

=55mm

=55mmd d一套筒一d

dIIIII V

II V，L 28L

=16mm

L =28mmIII VIP處

IIILVI

=16mmdIIIIV

m齒輪=1d取d

=65mmh=7.5mm

IV

=79mm b1.4h=1.4

IIIIVd =79mmLIVV

10mm

IVV說明 果5BmmL mm

10mm4 IIIIV IVISmmL

=68mmL =S+a+B+c+2.5-10

3 IIIL

=58mmIIIII 3 2 2 IIIIImm=58mmL =S+a+B+c+2.5-16-2-10VVI

3 2 2

L =46mm=mmmm6LmmSmm，

VVI1 3B=45mm

30mmS

=25mm

=48mm

30mm3

聯(lián)

VIIVIII

LVII

=48mm據(jù)dIV

mm L'IV

=68mm

IV’-IVCdVIIIIX

mm LVIIIIX

=82mm

b×h×P1VVC×hmm×mm×mmXb×h×mm×mm×mm

L=22×14×100mmXb靠過渡配合來保證直徑尺寸公差為×h×L=20×m612×100mm46×4

倒角尺R R R

mm

R

=1.6mm

寸1.6II VI VII VIII III V八、校核低速軸的校核說明 果上的作用力：F Ft4

=4818.6N

F Fr4 r

=1753.8N再由下圖求出軸承對軸的作用力由機械設15-236211，a=12.5mm，是危險截面，表4危險截面所受彎矩和扭矩載荷 水平面H 垂直面V支反力F

FNH

FNH2

=18962.83

FNV

FNV

=4984.52N

FNH1

F =NH2N 18962.83N矩 M 2NH

M 3NV

FNV1

F =NV2總彎矩M

M8N

4984.52N矩T 3N

M =308245.2HNM =851201.2V3NM =851201.2V3NT=1223504.3N說明 果 =28.16ca=0.

MPa=60MPa1安全 M2)2W

22/=1165529.9/41417.5MPa=28.16MPa前已選定材料45鋼調(diào)質(zhì)處理查圖（P15-1）得 此 ＜ 1 1九、承選擇和說明 果h

=14600h

I

6008C=13200NF

F2F2

NF=0=3

r r1 a

C=9420N08C0PF=00a

P=1042.0NP

f 2p

L =35293hP=f XF+YF2×N hp r a=1042.0N驗106

C

106

132003L 60nP hh =35293h>L'h

=14600hII00

承FF=0=

r aC=22800N82C0PF=00a

C=15800N0P=2470.7N說明 果PP=fXFYF=1.0）p r aN驗軸

=2470.7N

L =62608hh106

C

106

228003

6208軸承安L 60nP hh 全=62608h>L'h

=14600h006210軸承，106

C

106

3L 60nP 87.4hh =73714h>L'h

=72000h故所選用軸承滿足壽命要求。確定使用深溝球軸承6210。3．輸出軸上的軸承選擇與V1

6011的，C=17800N0要一個Fr

F2r4

F2=NF=0=3，t4 a轉(zhuǎn)速n=63.7r/min1額定動額定靜載荷C0P因為F=00a

P=5127.8NP

f 0則pP=f XF+YF=1××Np r a說明 果

=5127.8N

L =24231hh106L

C

106

232003h 60n

P h =24231h>L'h

=14600h。IIcbhl=10mm×8mm×50mm，T =143.9NmII強度和輪轂材料都是鋼，課本（6-2查得許應力pp=100-120MPa，取工作長度ppl=L-b/2=50mm-5mm=45mmk=0.5h=0.5×

上強8mm=4mm式 p

2T103可得kld

度夠，C鍵

103

=2×39.39103/4×45×32MPa

bhl=10×p

p=13.7MPa<p

8×50mm可見強度夠，Cbhl=10mm×8mm×50mm，2（2IIAh×mm×mm×30mm，T=TIII

/2=86.74Nm強度和輪轂材料都是鋼，課本（P表2查得許應力pp=100-120MPa，取工作長度pp說明 果l=L-b=30mm-8mm=22mmk=0.5h=0.5×8mm=4mm。由式 p

2T103可得kld

齒III連接

103

=2×173.47103/4×22×38MPa

強足夠選p

p=76.3MPa<p

用b×h×L=10mm×可見連強足夠選用b×h×L=10mm×8mm×30mm3．齒3III連接

8mm×30mm由軸III設知初步選用b×h×L=14mm×9mm×63mm ，T=T =173.47NmIII校核連強度、軸和材料都是鋼由課本（P6-2）查得許用應力pp=100-120MPa取。工作長度ppl=L-b=63mm-14mm=49mm，k=0.5h=0.5×9mm=4.5mm 103可得p kld

齒3III連強足夠選用b×h×

103

=2×173.47103/4.5×49×42MPa

L=14×9×p

p=37.6MPa<p

63mmb×h×L=14mm×9mm×63mm4．齒4接由軸設知初步選用bhL=18mm11mm63mmT=T =547.21NmIV校核連強度、軸和材料都是鋼由課本（P6-2）查得許用應力

齒4軸說明 果p =100-120MPa連p l=L-b=63mm-18mm