設(shè)計題目半自動專用機(jī)床

摘 Alongwiththedevelopmentofthemodernmachinery,theintensityoflaborismoreandmorestrong,automaticsemi-automaticmachineryofthedemandishigherandhigher,wedesignthesemi-automaticlatheisadapttothedevelopmentofnow,wedesignamanipulatorinthemachinepartsdidhumannatureandJiNengHua,greatlyimprovingtheworkefficiency,andimprovessecurity,greatlyreducingthelabor,greatlyreducesthelaborintensity,improveproductionefficiency,inthisdesign,weshouldhavetheCAD,ProE,suchasmapsoftware,completedthemachinepartdrawingandassemblydrawing,theworkingprocessofthevirtualdesignofthemachinetool.Semi-automaticlathepartcanrecemanualoperation,canaccordingtotherequirementsofproductionprocessRepeatthesameactiontocompletetheworkpiecemachiningprocess,havethetimeandimprovetheproductionefficiencysignificantlySemi-automaticlatheisthedesignonthebasisofpracticalanditsdrivingmechanismtoagenciesandmanipulatorhascarriedonthedetailedysisanddesign,throughthecalculationandtheactualdatadrawingsconfirmedtheavailabilityofmachinetool.目機(jī)械制造技術(shù)的概念?；Q的齒輪生于1771年，18歲的時候，他是發(fā)明家得的30先以上的請求。。以后，在他自己的車間制造除了一臺更加完善的車床，19世紀(jì)，18世紀(jì)開始的工業(yè)，象征著以工匠主導(dǎo)的農(nóng)業(yè)社會結(jié)束，取而運(yùn)轉(zhuǎn)，20世紀(jì)初擁有了獨(dú)立動力源的動力車床（EngineLathe)終于被開發(fā)，也將車床帶到了新的領(lǐng)域。20世紀(jì)中，計算被發(fā)明，不久計算機(jī)即FCkcap

式中FCkcap-f-

1311.70.65mmc78HBS，查得k750Nmm2cFCkcap

7500.650.3非常小，約占總切削功率的1%~5%，故切削功率PC為：PFv103（1- C根據(jù)工件材料查得vc1.67ms，代入得PC0.90120.90.920.92

P

0.981.3kw由vc1.67m/s，得主軸轉(zhuǎn)速

r帶傳動傳動比i7由此確定電動機(jī)轉(zhuǎn)速范圍nn2454350.57r Y90L-4,P01.5kwn01400r由工況查得工況系數(shù)K 確定傳動比in24541.75，為了方便計算初步選取i

2根據(jù)帶型，查表得小帶輪的基準(zhǔn)直徑dddd)min50mm，初步定為2d d2驗證帶速

dd22

3.148018

滿足5msv25m 計算大帶輪的基準(zhǔn)直徑ddi1dd1.3280 足

dddd）a02(dddd得129.5a0370，選a

2Ld傳動的實際中心距近似為a

LdLd02

a0.03Ld181.252180(dd1dd2查表得P00.44P00.02K0.99KLZ

取Z查表得q0.06，

500(2.5K

500(2.50.99)1.650

K

(FP)min2Z(F0)min

2281.39sin

2

d4d

dd動的規(guī)律性可知凸輪軸轉(zhuǎn)速n'35r/min由變速箱輸入軸到凸輪軸傳動比in21848 取彈簧彈性系數(shù)k10Nmm，刀具行程s平均作用力Fks1070 平均v

24540.30.12m/PFv/1033500.12103GB/T10085-1988HT1003232Z HE0.81848按Z14，估取效率0.81848Pn2n'2T9.55106P2Pn2n'22

9.55106

2067.10N因工作載荷較穩(wěn)定，故取載荷分布不均系數(shù)K

1;KA1.15

KKAKKv1.1511.05確定彈性影響系數(shù)1因選用的是鑄錫磷青銅蝸輪和鋼蝸桿相配，故ZE160MPa確定接觸系數(shù)Zp先假設(shè)蝸桿分度圓直徑

和傳動中心距ad10.35，查得aZpH'H

N60jnL6011848120001.663 88

則 '0.9386268 31.212067.1031.212067.101602.9251.5480mm

84mm

40mmd10.5a查得接觸系數(shù)Z'0.6，因為Z'Z 軸向齒距Pam3.14425.12mm，直徑系數(shù)q齒頂圓直徑da1d12ha14024

f1

2hf

分度圓導(dǎo)蝸桿軸向齒厚s1m13.144 蝸輪齒數(shù)Z231x2驗算傳動比iz2317.757.7583.1% 蝸輪分度圓直徑d2mz2431蝸輪喉圓直徑da2d22ha212424蝸輪齒根圓直徑df2d22hf2124蝸輪咽喉母圓半徑rg

a da2

8012 1.53KT2

Y dd

Fa2 1

根據(jù)x20.5zv232.87，查得齒形系數(shù)YFa2

Y1

F'F99

1.531.212067.103.30.9192 401243.3.2.68fGB/T10089-1988。7選小齒輪齒數(shù)z318z42.524 u1Zd1t

3 E uH選載荷系數(shù)KtT3i蝸輪蝸桿T282607.1020856.8N選取齒寬系數(shù)d1查得材料的彈性影響系數(shù)ZE189.8MPa按齒面硬度查得小齒輪的接觸疲勞強(qiáng)度極限Hlim1600MPa， 輪的接觸疲勞強(qiáng)度極限Hlim2550MPaN60jnL6011848120001.66 3 N2

取接觸疲勞系數(shù)KHN11.35,KHN2

KHN1lim11.35600810MPaKHN2lim21.45550H 1.3 d3t

1

vd3tn229.942310.36m/

模數(shù)

29.941.66mm齒高h(yuǎn)2.25mt2.251.66根據(jù)圓周轉(zhuǎn)速和7級精度，查得動載系數(shù)Kv1.02，直齒輪，KHKF1;查得使用系數(shù)KA1,查得KH1.307,查得KF1.29,故載荷系數(shù)KKAKvKHKH11.0211.3071.33K3d3K3

29.94

計算模數(shù)md332KT32KT3YFaYSad32 Hm查得小齒輪的彎曲疲勞強(qiáng)度極限FE1500MPa；大齒輪的彎曲強(qiáng)度極限FE2380MPa查取彎曲疲勞系數(shù)KFN10.8,KFN2KFN1FE10.8500F

KFN2FE21.18380F

計算載荷系數(shù)KKAKvKFKF11.0211.29查取齒形系數(shù)YFa12.91,YFa2查取應(yīng)力校正系數(shù)YSa11.53,YSa2YFa1YSa12.911.530.01558,YFa2YSa22.351.68

3 21.313 21.31可取由彎曲強(qiáng)度算得的模數(shù)并就近圓整為標(biāo)準(zhǔn)值m1mmz42.530

d330.16 計算分度圓直徑d3mz3301d4mz4751計算中心距ad3d43075 計算齒輪寬度bdd3130取B335mmB4z219z1iz查得工況系數(shù)KA1,查得齒數(shù)系數(shù)KZ0.38PcaKAKzP10.380.04Pca0.0152kwn592.4rp

查圖可選08A-1，查表，鏈條節(jié)距為初選中心距a0(3050p(305012.7381mm6