分流式二级圆柱齿轮减速器课程设计剖析

机械设计程设计计算 说明书 目 二级分流式减速器指导教师 王艾伦院 系 机电工程学班 级 机械0906学 号 0808090717姓 名 陈 良完成时间 2012 年3 月111.·························· 22.························· 23.························· 24.··························· 456172527与29器32箱体附件32润滑式及密封形式33箱体34课程总结 35考资料 36说明 果.ηw=0.96；5环境380V极其生产批量一般机械厂，小批量生产。（1）确定传动装置的类型，画出机械系统传动方案简图；（2）选择电动机，进行传动装置的运动和动力参数；传动系统中的传动零；绘制减器装配图图和装配图1（A0）;图1A1（A2）据力（N2（D)传动方案的拟定机电动机动，电动机1器2动力传减3器4传机5，动6传动系统中级流减器，级相对于承位置对称，沿，高级和低级分别斜圆

L'=14600hhF=2000NV=1.2m/sD=300mm级分流式器PAGEPAGE38说明 果说明 果动机的选择和计算Y1P：wP×ww转速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输出PdP=P/η

Pwd w dwP wed

P 4wed转速n=63.7r/miw该传统为分流式圆柱齿轮传18-1推荐传比为ii

=8～601 2则总传860则转速可范围为n' =8n=8×63.7=509.6r/mind1 wn' =60n=60×63.7=3822r/mind2 wnnnn说明 果nn[1]16-1方

质号率 量案 W比1Y132M1-6410001Y132M1-64100096015.72.2732Y112M-641500144022.52.243

/kg

11ABCDEFGHY132M1-62161788938801033132KABACADHDBBL12280135210315238515传动比分配传动比[1]20-2n=r/n；

i=15.07mi=nm/n=960/63.7=15.07分配各级传动比[1]2—3各级分配各级取高级圆柱齿轮i1.4i则低级圆柱齿轮1 2ii/ii/1.4i

i=4.5912 1 2

i=3.282i1

i=3.282说明 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按额定功率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说明 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项目表3 轴的运动动力参数电动机轴 高速级轴 中间轴低速级轴滚筒轴VI IIIV转速960 960 209.263.763.7（r/min）功率4 3.96 3.803.653.54（w）转矩(Nm)39.79 39.39 173.47547.21530.72传动比 1 4.59 3.28 1效率 0.99 0.96 0..96 0.97六、齿轮传动设计高速级齿轮传动设计选择材料、精度参数a.按图1所示传动方案，选用斜齿圆柱齿轮传动b.带式运输机为一般工作机器，速度不高，故选用7级精度（GB10095-88）c.1表质45（调质HBS40HBS。d.Z=28，则大齿轮齿数1

Nm小齿轮材料为40Cr260HBS大齿轮材料为5，硬度为220HBS，初选小齿轮齿说明 果i=4.592Z=4.59×24z2e.初选螺旋角β=14

Z1Z2β=14f选取齿宽系数d

=0.8d

=0.8d2）按齿面接触强度设计按下式试算u2kT uu

1Z Z 2tdt3

1 1 H Ed a 1 H1）确定公式内的各数值a.试选k=1.6t1b.矩T=T /2

k =1.6t11

T=19.70=19.70Nmc.查图表（P217图10-30）选取区域系数Z =2.433H

1NmZ =2.433HZEd.查图表（P215图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则应力循环次数

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条线KHN1=0.91，KHN2=0.97。

KHN1=0.91，KHN2=0.97。说明 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说明 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按实际校正所圆径KKddKt3t

⑤

d 44.74mm1d 40.481mn1

2.161.6

mm=44.74mm

m =1.81mmn1m =dZ/22mm1 1

=1.81mm按设计2KTY

Y Ym 3 1

n1 Z2 d1 1 F确定说明 果KKKK KA V F F

⑥

K=2.331K=1.25×1.09×1.4×1.221=2.331

Y=0.88根据纵向重合度

=1.52查图表（图10-28）螺旋角影响系数Y当量齿数

=0.88

Z =26.3V1Z =120.4Z Z

/

24/14=26.3 V2V1 1Z Z /116/14=120.4V2 2查取齿形系数查图表（P20010-5）YF1

=2.588，YF2

=2.178

YF1YF

=2.588，=2.178查取应力校正系数查图表（P20010-5）YS1

=1.596，YS2

=1.792

YS1

=1.596，弯曲疲劳许用应力

Y =1.792S2取弯曲疲劳安全系数S=1.4，弯曲疲劳寿命系数K =0.85，FN1KFN2

=0.88。查小齿轮弯曲疲劳强度极限

FE1

=500MPa

S=1.4，K大齿轮弯曲疲劳强度极限

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

并加以比较说明 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，按接触疲劳强度得的分度圆直径n1d=44.74mm应有的齿数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几何尺寸中心距

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

2cos14 mm=132.95mm将中心距圆整为133mm按圆整的中心距修正螺旋角m(ZZ) 2(23106)

45'

5''

1 22a1

2133

14o5'15''因值改变不多，故参数a

，K ，Z

等不必修正大小齿轮的分度圆直径d Zm /cos1 1

45'

5''

d 47mm1说明 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圆后B=35mmB=40mm2 1构设计由e＜2m，小齿轮做成齿轮轴，t1由d <500mm，大齿轮采用腹板式构a2低速级齿轮传动设计a.按图1所示方案，选用直齿圆柱齿轮传动b.选用7级精度（GB10095-85）择 为5

B=40mm1小齿轮做成齿轮轴，大齿轮采用腹板式结构小齿轮：40Cr（调质度240HBSZ=243选齿宽系数 =1.0d2按下式试算

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确定公式内各数值试选K =1.3t2

K =1.3t2说明 果TT =173.47Nm

T =173.473 =1.73×105

N1

3NmZ =189.8E查图表（P表10-6）选取弹性影响系数Z =189.8MPa2E查图表（P 图 10-21d）得接触疲劳强度极 =670MPa， =610MPaHlim3 Hlim4由式②应力循环次数

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查图表（P10-19）取接触疲劳寿命系数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分度圆直径

d 3t

中较

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圆周速度V3

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

b=68.2mm3b d

=1×68.2mm=68.2mm3 d2 3t模数、齿宽高比模数m =d /Z=68.2/24mm=2.84mm

m =2.84mm22 t 3齿高h=2.25m =2.25×2.84mm=6.39mm3 2则b/h=68.2/6.39=10.73 3载荷系数数Ka=1.25 据V=0.75m/s级精度查图3

Ka=1.25V=0.75m/s3图10-8）得动载荷系数K =1.02，直齿轮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查图表（P图10-13）得=13 3 H2K =1.312F2

K =1.312H2故根据式K2

KKK K K=1.59A V H2 H2 2

K =1.352F2K K=1.593K按实际载荷系数系数校正所得分度圆直径。由式dd3KttK

2d=72.9mm2得d d 22 23K2

=72.9mm

m=3.04mm模数m 22m d /Z=72.9/24mm=3.04mm2 3 3 公式为说明 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

并加以比较

Y

=1.773F

S3

=2.65×1.58/318.57=0.013143Y Y4F

S4

=2.22×1.77/249.71=0.015746说明 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几何尺寸中心距

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轮宽度b

d=1.0×72mm=72mm

B=75mm，3 d2 3 3BmB03 45）构设计e＜2m3做成，t1d <500mm轮4采用腹板式构a2

B=70mm43轮轴4板式构说明 果径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 方向如图所示r1 a1说明 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根据T =213.71NcaII

电动机D=38 mm标

d =32mmIImin14用6弹性套柱销半孔径d=32mm半L=82半与配合毂孔长度1L=84mmd =32mm1 IImin构设计拟上零件配方案经分析比较用如所示配方案说明 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指导书表 1 知箱体内壁到座孔端面距离L

=58mmLC

(5

mm

=42mm凸缘

III1 1 2 1

L L盖盖总宽30mm到距离25mm

VVII则L =55mm

，=6mmIIIII

L L5amm2'13之间距离c=10mm端面距箱体内壁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说明 果3C

I

=32

键bhl=10mLIII

m6bhl

m×8mm××50mm。滚动承过渡配合来保证直径尺寸确圆角和倒角尺寸×4I设计

50mm1.5×45圆角R1已知P 0wT 4Nm n III

III

III求作在齿轮力

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说明 果d IIImin

3.80209.2

mm=28.9mm。该轴的最小直径为安装轴承

A 0III处的直径，取为d =30mmIIImin3．轴的构设计（1）拟定轴上零件的装配方案，如图I II III IV V VII VIII（2）确定轴的各段直径和长度

d =30mmIIImin1）根据d =30mm取

=40mm

=40mmIIImin

III

VIIVIII

d =d轴承与齿轮2，2'之间采用套筒定位，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齿轮3采用齿轮轴，LIVV

=B=75mm3

50mm2）初步选择滚动轴承由于配对的斜齿轮相当于人字齿，轴II相对于机座固定，故初

L L II VII42008d×

L

=LVIVII×90mm×20mm，aS=10mmaS=10mm，则

=33mm1 1 2 2L L 42mm

LIIIIV=10m

=LVVIIII VII

LVIVII

=75mm说明 果3

滚动6208承d dIIIII VI

mB2

承端盖总宽度L =LIIIII VI

=33mmPIIb××4P×4径R1

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

=4818.6N

F Fr4 r

=1753.8N初步确最小直径5PA 0IV

F =10541.8Nt4F =3836.9Nr4d 3IVmin

mm=42.4mm。该最小直径安装联轴器处直径选联器号。PK =1.5则A

A 0IVT =1.5×547.21Nm=820.8NmcaIV据T 8Nm准54caIV

K =1.5A说明 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处

IIILVI

=16mmdIIIIV

m齿轮=1d取d

=65mmh=7.5mm

IV

=79mm b1.4h=1.4

IIIIVd =79mmLIVV

10mm

IVV说明 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

联

VIIVIII

LVII

=48mm据dIV

mm L'IV

=68mm

IV’-IVCdVIIIIX

mm LVIIIIX

=82mm

b×h×P1VVC×hmm×mm×mmXb×h×mm×mm×mm

L=22×14×100mmXb靠过渡配合来保证直径尺寸公差为×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、校核低速轴的校核说明 果上的作用力：F Ft4

=4818.6N

F Fr4 r

=1753.8N再由下图求出轴承对轴的作用力由机械设15-236211，a=12.5mm，是危险截面，表4危险截面所受弯矩和扭矩载荷 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总弯矩M

M8N

4984.52N矩T 3N

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

MPa=60MPa1安全 M2)2W

22/=1165529.9/41417.5MPa=28.16MPa前已选定材料45钢调质处理查图（P15-1）得 此 ＜ 1 1九、承选择和说明 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验106

C

106

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

=14600hII00

承FF=0=

r aC=22800N82C0PF=00a

C=15800N0P=2470.7N说明 果PP=fXFYF=1.0）p r aN验轴

=2470.7N

L =62608hh106

C

106

228003

6208轴承安L 60nP hh 全=62608h>L'h

=14600h006210轴承，106

C

106

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

=72000h故所选用轴承满足寿命要求。确定使用深沟球轴承6210。3．输出轴上的轴承选择与V1

6011的，C=17800N0要一个Fr

F2r4

F2=NF=0=3，t4 a转速n=63.7r/min1额定动额定静载荷C0P因为F=00a

P=5127.8NP

f 0则pP=f XF+YF=1××Np r a说明 果

=5127.8N

L =24231hh106L

C

106

232003h 60n

P h =24231h>L'h

=14600h。IIcbhl=10mm×8mm×50mm，T =143.9NmII强度和轮毂材料都是钢，课本（6-2查得许应力pp=100-120MPa，取工作长度ppl=L-b/2=50mm-5mm=45mmk=0.5h=0.5×

上强8mm=4mm式 p

2T103可得kld

度够，C键

103

=2×39.39103/4×45×32MPa

bhl=10×p

p=13.7MPa<p

8×50mm可见强度够，Cbhl=10mm×8mm×50mm，2（2IIAh×mm×mm×30mm，T=TIII

/2=86.74Nm强度和轮毂材料都是钢，课本（P表2查得许应力pp=100-120MPa，取工作长度pp说明 果l=L-b=30mm-8mm=22mmk=0.5h=0.5×8mm=4mm。由式 p

2T103可得kld

齿III连接

103

=2×173.47103/4×22×38MPa

强足够选p

p=76.3MPa<p

用b×h×L=10mm×可见连强足够选用b×h×L=10mm×8mm×30mm3．齿3III连接

8mm×30mm由轴III设知初步选用b×h×L=14mm×9mm×63mm ，T=T =173.47NmIII校核连强度、轴和材料都是钢由课本（P6-2）查得许用应力pp=100-120MPa取。工作长度ppl=L-b=63mm-14mm=49mm，k=0.5h=0.5×9mm=4.5mm 103可得p kld

齿3III连强足够选用b×h×

103

=2×173.47103/4.5×49×42MPa

L=14×9×p

p=37.6MPa<p

63mmb×h×L=14mm×9mm×63mm4．齿4接由轴设知初步选用bhL=18mm11mm63mmT=T =547.21NmIV校核连强度、轴和材料都是钢由课本（P6-2）查得许用应力

齿4轴说明 果p =100-120MPa连p l=L-b=63mm-18mm