礦用鏈板輸送機(jī)傳動(dòng)裝置設(shè)計(jì)課程設(shè)計(jì)

機(jī)械設(shè)計(jì)基礎(chǔ)課程設(shè)計(jì)設(shè)計(jì)說明書課題名稱系別專業(yè)班級(jí)姓名學(xué)號(hào)指導(dǎo)老師完成日期1、設(shè)計(jì)條件：（2）工作情況：單向運(yùn)輸，中等沖擊；（3）運(yùn)動(dòng)要求：鏈板輸送機(jī)運(yùn)動(dòng)誤差不超過7%；（4）工作能力：儲(chǔ)備余量15%；（5）使用壽命：10年，每年300天，每天8小時(shí)；（6）檢修周期：半年小修，一年大修；（7）生產(chǎn)批量：小批量生產(chǎn)；1—鏈板運(yùn)輸機(jī)4—運(yùn)輸機(jī)主軸原始數(shù)據(jù)：運(yùn)輸機(jī)鏈條拉力：20KN；主動(dòng)星輪節(jié)距：64mm；【1東南大學(xué)出版社；二、傳動(dòng)方案的確定三、電機(jī)的選擇由參考文獻(xiàn)[1]表9-1查得：12η=0.9713η=0.9624η=0.9635412345η=0.9924Fv100020000×0.6)/1000×0.852)=14.085kw((η=0.852查參考文獻(xiàn)[1]表16-2選擇電動(dòng)機(jī)的型號(hào)為Y180M-4，額定功率18.5kw，滿載轉(zhuǎn)速1470r/min。n'=60×1000v/Zp=60×1000×0.6/11×64=51.14r/minnn'51.14（1）總傳動(dòng)比：i=/=1470/2=14.372則減速器總傳動(dòng)比為i=i/0可得各級(jí)傳動(dòng)比：10212/1470/1=1470r/min1/1470/3.593=409.13r/min/409.13/4=102.28r/minn=1470r/min1n=409.13r/min2n=102.28r/min31×0.99×0.96=15.11kw21233223η123111TPn=9550/×15.11/409.13=352.70N·m2TPn=9550/×14.36/102.28=1340.81N·mT=103.30·m31T=352.70·m2T=1340.81Nm鏈傳動(dòng)的功率P=16.41KW,轉(zhuǎn)速n=102.28r/min,求傳動(dòng)比i=2（1）選擇鏈輪齒數(shù)31122初取a=40p,則鏈節(jié)數(shù)為02p222=109.25pz多排鏈系數(shù)k查表5.6mA鏈長系數(shù)k查圖5-13zL≥0ALmm0k=1.03LP12.62kw0p24A單排鏈由式5-12)()2aLL12122422pPznp/60××102.28×38.1/60×10001（6）計(jì)算壓軸力Q1538.26mmF=1000P/v=100016.41/1.23符合估計(jì)QHSHNHHminN11h92[σ]=5501.04/1FFN=5.91082N[σ]=700N/mm2[σ]=572N/mm2[σ]=572N/mm2H[σ]=42011/1.4Y=Y=1N1N2ZZ22dm1EH1u2dmHY=1XS=1.4Fmin1[σ]=3862大z=iz=25×3.59321[σ]=3002齒數(shù)比uu=z/z=90/25=3.6216611AAψ=0.54dmV1K齒向載荷分布系數(shù)1.0~1.2z=90β2AE1H2d1572212A11Vβ111小輪平均分度圓直徑d)m1112N/mm2Emm11H齒寬bb=ψd=0.54×87.37=47.18圓整dmm112dm1Fu2F111v11uz=zu/cosδ=24.09×3.6221222222222δ=100+240.94231δ=×40.33472a2ZSHNH英里循環(huán)次數(shù)N由式6-711hN=Ni5.89×10/421/接觸強(qiáng)度最小安全系數(shù)SHBS=260HBS1[σ]=550×1.13/1HBS=210HBS2許用彎曲應(yīng)力[σ]由（機(jī)械設(shè)計(jì)課本）式6－12，SFHlim1Hlim1Flim12則[σ]=540×1×1/1.4F1[σ]=420×1×1/1.4F2212KTu1EH31uHd[σ]=621.5N/mm26.9d[σ]=621.5N/mm2H21齒數(shù)比uu=z/z=100/4σFlim1=378N/mm2傳動(dòng)比誤差Δu/uΔu/u=0<0.07T×10P/n=9.55×10×15.11/409.13661載荷系數(shù)KK=KKKKAVK使用系數(shù)查表6.3AαβEHξ1u=41111Ammm11V12d1α大輪齒寬bb=b22β1K=2.178（3）齒根彎曲疲勞強(qiáng)度校核計(jì)算N/2由式6-10公式EFF1HYSa查表6.5ξ1zz(tantan)(tantan)1a12122.1783527002.621.599010041F2m2221f2d=d-2h=400-2×1.25×42f11a1a1齒寬中點(diǎn)直徑d=100mmm圓周力F=2T/d=2×103300/87.37=2364.66Nt11mY=1.59徑向力F=Ftanaδr1t1n=2364.66×0.9635×tan20=829.27Nξa=1.733a1t1n=2364.66×0.2676×tan20=230.35N（）ξδF1=177.78N/mm2δF2=182.78N/mm2由式8-2計(jì)算軸的直徑并加大3%以考慮鍵槽的影響d3查表8.6取A=1152df1f2由參考文獻(xiàn)得a1d30,d40,d45（軸承）,d54,1234d45（軸承）,d40（錐齒）a256l58,l47,l38,l60,lmm12345l71mm62）由軸承、齒輪及鍵的位置可得力L=76.3mmL=135.4mmL=28.77mm123T=103300N·mm1H2水平面F=829.27NR=-98.82NR=2463.48Nv1v22）齒寬中點(diǎn)出的彎矩水平面HvM221HV1軸的材料為45號(hào)鋼調(diào)質(zhì)處理，由表8.2查得640N/mm2B21bM22ca1=16.18N/mm21)計(jì)算軸承支反力合成支反力R2=222R3=FrFt32)計(jì)算軸承派生軸向力由表10.7軸承派生軸向力Sfpf（x2R2+y2A2）=4549.25Np因A3/R3=1.2>e,查表10.5X=0.44,Y=1f（x3R3+y3A3）=3089.07NptfCt(L60nPh2圓周力F=2T/d=2×352700/100=7054Nt222徑向力F=Ftana×tan20=2567.45Nr1t1nnt2圓周力F=-F=-2364.66Nt1t1徑向力F=-F=230.35Nr1a1軸向力F=-F=829.27Na1r1（由式8-2計(jì)算軸的直徑并加大3%以考慮鍵槽的影響d3d由參考文獻(xiàn)得d40（軸承）,d50（圓柱齒）,12d60,d50,d40345l48,l90,l60,21235L=134mmL=93.7mm123求軸承反力水平面H2v1v22）齒寬中點(diǎn)出的彎矩水平面HvM222HV扭矩TT2軸的材料為45號(hào)鋼調(diào)質(zhì)處理，由表8.2查得640N/mm2B21b()取折合系數(shù)α=0.6TM22ca1=40.37N/mm2合成支反力R1=1R4==4281.63N2)計(jì)算軸承派生軸向力由表10.7軸承派生軸向力SS1=R10.5=509.74Nfpf（x1R1+y1A1）=3577.94Np因A3/R3=1.2>e,查表10.5X=0.44,Y=1f（x4R4+y4A4）=2260.70NptfCt)=262400.70H>240000H(L60nPh(1)圓周力F=7054Nt3r3F=7506.71n3(2)由式8-2計(jì)算軸的直徑并加大3%以考慮鍵槽的影響d3d由參考文獻(xiàn)得d65（軸承）,dmm),12d74,d65,d345l,l82,l105,123l,lmm452）由軸承、齒輪及鍵的位置可得力L=125.5mmL=245.5mmL=25.82mm123R=4667.8NR=2386.2NH1H2水平面R=-1698.95NR=868.50Nv1v22）齒寬中點(diǎn)出的彎矩水平面HvM223HV3軸的材料為45號(hào)鋼調(diào)質(zhì)處理，由表8.2查得640N/mm2B21b()取折合系數(shù)α=0.6TM22ca1=32.37N/mm21)計(jì)算軸承支反力合成支反力R1=2211R3=FrFt332)計(jì)算軸承派生軸向力由表10.7軸承派生軸向力Sfpf（x1R1+y1A1）=21371.37Np因A3/R3=1.2>e,查表10.5X=0.44,Y=1f（x3R3+y3A3）=15144.88Npt()=26897.59H>240000HLh十二、聯(lián)軸器的選擇l1從動(dòng)端：Y型軸孔，B型鍵槽d,l1422σ【1】表DZpp002219.5，取[]8MP聯(lián)軸器的標(biāo)準(zhǔn)型號(hào)為：pln28×16GB1096-90即圓頭普通平鍵（A型鍵的參數(shù)為：；則鍵聯(lián)=lb=='接矩14d[σ