畢業(yè)論文設(shè)計：三級圓柱圓錐齒輪減速器設(shè)計

北京化工大學(xué)畢業(yè)設(shè)計PAGE34畢業(yè)論文(設(shè)計)三級圓柱圓錐齒輪減速器設(shè)計1緒論通過查閱一些文獻我們可以了解到帶式傳動裝置的設(shè)計情況，為我所要做的課題確定研究的方向和設(shè)計的內(nèi)容。1.1帶傳動帶傳動是機械設(shè)備中應(yīng)用較多的傳動裝置之一，主要有主動輪、從動輪和傳動帶組成。工作時靠帶與帶輪間的摩擦或嚙合實現(xiàn)主、從動輪間運動和動力的傳遞。帶傳動具有結(jié)構(gòu)簡單、傳動平穩(wěn)、價格低廉、緩沖吸振及過載打滑以保護其他零件的優(yōu)點。1.2圓錐-圓柱齒輪傳動減速器YK系列圓錐-圓柱齒輪傳動減速器適用的工作條件：環(huán)境溫度為-40～40度；輸入軸轉(zhuǎn)速不得大于1500r/min,齒輪嚙合線速度不大于25m/s，電機啟動轉(zhuǎn)矩為減速器額定轉(zhuǎn)矩的兩倍。YK系列的特點：采用一級圓弧錐齒輪和一、二、三級圓柱齒輪組合，把錐齒輪作為高速級（四級減速器時作為第二級），以減小錐齒輪的尺寸；齒輪均采用優(yōu)質(zhì)合金鋼滲碳淬火、精加工而成，圓柱齒輪精度達到GB/T10095中的6級，圓錐齒輪精度達到GB/T11365中的7級；中心距、公稱傳動比等主要參數(shù)均采用R20優(yōu)先數(shù)系；結(jié)構(gòu)上采用模塊式設(shè)計方法，主要零件可以互換；除底座式實心輸出軸的基本型外，還派生出輸出軸為空心軸的有底座懸掛結(jié)構(gòu)；有多中潤滑、冷卻、裝配型式。所以有較大的覆蓋面，可以滿足較多工業(yè)部門的使用要求。減速器的選用原則：（1）按機械強度確定減速器的規(guī)格。減速器的額定功率P1N是按載荷平穩(wěn)、每天工作小于等于10h、每小時啟動5次、允許啟動轉(zhuǎn)矩為工作轉(zhuǎn)矩的兩倍、單向運轉(zhuǎn)、單對齒輪的接觸強度安全系數(shù)為1、失效概率小于等于1%等條件算確定.當載荷性質(zhì)不同，每天工作小時數(shù)不同時，應(yīng)根據(jù)工作機載荷分類按各種系數(shù)進行修正.減速器雙向運轉(zhuǎn)時，需視情況將P1N乘上0.7～1.0的系數(shù)，當反向載荷大、換向頻繁、選用的可靠度KR較低時取小值，反之取大值。功率按下式計算：P2m=P2*KA*KS*KR，其中P2為工作功率；KA為使用系數(shù)；KS為啟動系數(shù)；KR為可靠系數(shù)。（2）熱功率效核.減速器的許用熱功率PG適用于環(huán)境溫度20℃，每小時100%連續(xù)運轉(zhuǎn)和功率利用律（指P2/P1N×100%）為100%的情況，不符合上述情況時，應(yīng)進行修正。（3）校核軸伸部位承受的徑向載荷。2結(jié)構(gòu)設(shè)計2.1V帶傳動帶傳動設(shè)計時，應(yīng)檢查帶輪的尺寸與其相關(guān)零部件尺寸是否協(xié)調(diào)。例如對于安裝在減速器或電動機軸上的帶輪外徑應(yīng)與減速器、電動機中心高相協(xié)調(diào)，避免與機座或其它零、部件發(fā)生碰撞。2.2減速器內(nèi)部的傳動零件減速器外部傳動件設(shè)計完成后，可進行減速器內(nèi)部傳動零件的設(shè)計計算。齒輪材料的選擇應(yīng)與齒坯尺寸及齒坯的制造方法協(xié)調(diào)。如齒坯直徑較大需用鑄造毛坯時，應(yīng)選鑄剛或鑄鐵材料。各級大、小齒輪應(yīng)該可能減少材料品種。蝸輪材料的選者與相對滑動速度有關(guān)。因此，設(shè)計時可按初估的滑速度選擇材料。在傳動尺寸確定后，校核起滑動速度是否在初估值的范圍內(nèi)，檢查所選材料是否合適。傳動件的尺寸和參數(shù)取值要正確、合理。齒輪和蝸輪的模數(shù)必須符合標準。圓柱齒輪和蝸桿傳動的中心距應(yīng)盡量圓整。對斜齒輪圓柱齒輪傳動還可通過改變螺旋角的大小來進行調(diào)整。根據(jù)設(shè)計計算結(jié)果，將傳動零件的有關(guān)數(shù)據(jù)和尺寸整理列表，并畫出其結(jié)構(gòu)簡圖，以備在裝配圖設(shè)計和軸、軸承、鍵聯(lián)結(jié)等校核計算時應(yīng)用。聯(lián)軸器的選擇減速器的類型應(yīng)該根據(jù)工作要求選定。聯(lián)接電動機軸與減速器，由于軸的轉(zhuǎn)速高，一般應(yīng)選用具有緩沖、吸振作用的彈性聯(lián)軸器，例如彈性套柱銷聯(lián)軸器、彈性柱銷聯(lián)軸器。減速器低速軸（輸出軸）與工作機軸聯(lián)接用的連周期，由于軸的轉(zhuǎn)速較低，傳遞的轉(zhuǎn)距較大，又因為減速器軸與工作機軸之間往往有較大的軸線偏移，因此常選用剛性可以移動聯(lián)軸器，例如滾子鏈聯(lián)軸器、齒式聯(lián)軸器。對于中、小型減速器，其輸出與工作機軸的軸線便宜不很大時，也可以選用彈性柱銷聯(lián)軸器這類彈性可移式聯(lián)軸器。聯(lián)軸器型號按計算轉(zhuǎn)距進行選擇。所選定的聯(lián)軸器，起軸孔直徑的范圍應(yīng)與被聯(lián)接兩軸的直徑相適應(yīng)。應(yīng)注意減速器高速軸外伸段軸徑與電動機的軸徑不得相差很大，否則難以選擇合適的聯(lián)軸器。3設(shè)計計算過程及說明3.1選擇電動機3.1.1電動機類型和結(jié)構(gòu)型式選擇Y系列籠型三相異步電動機,臥式閉型電電動機。3.1.2選擇電動機容量工作機所需功率SKIPIF1<0=SKIPIF1<0=7.98kwSKIPIF1<0=80.7r/min電動機的輸出功率SKIPIF1<0=SKIPIF1<0=10.4kwη=SKIPIF1<0*…..*SKIPIF1<0=0.82*0.98*0.95*0.98*0.97*0.98*0.98*0.97*0.98*0.98*0.99*0.96=0.77確定電動機的額定功率Ped>=Pd3.1.3選擇電動機的轉(zhuǎn)速同步轉(zhuǎn)速1500r/min。3.1.4確定電動機型號選擇Y160M-4額定功率11kw轉(zhuǎn)速1460r/min3.2傳動裝置的總傳動比及其分配i=SKIPIF1<0=18.1帶傳動i=2圓錐i=2.5圓柱i=43.3計算傳動裝置的運動和動力裝置參數(shù)各軸轉(zhuǎn)速:電動機軸SKIPIF1<0=1460r/min減速箱輸入軸SKIPIF1<0=SKIPIF1<0=486.7r/min高速軸SKIPIF1<0=SKIPIF1<0=235.1r/min低速軸SKIPIF1<0=SKIPIF1<0=58.8r/min各軸輸入功率:SKIPIF1<0=SKIPIF1<0=11kwSKIPIF1<0=SKIPIF1<0*0.95=10.45kwSKIPIF1<0=SKIPIF1<0*0.98*0.97*0.98=9.73KWSKIPIF1<0=SKIPIF1<0*0.98*0.97*0.98=9.07KW各軸轉(zhuǎn)矩:T0=9550*SKIPIF1<0/SKIPIF1<0=72.0N*mT1=9550*SKIPIF1<0/SKIPIF1<0=205.0N*mT2=9550*SKIPIF1<0/SKIPIF1<0=395.2N*mT3=9550*SKIPIF1<0/SKIPIF1<0=1493.1N*m3.4帶傳動設(shè)計3.4.1定v帶型號和帶輪直徑工作情況系數(shù)SKIPIF1<0=1.1計算功率SKIPIF1<0=SKIPIF1<0SKIPIF1<0=1.1*11=12.1kw選帶型號A型小帶輪直徑SKIPIF1<0=100mm大帶輪直徑SKIPIF1<0=(1-0.01)*100*3=297mm大帶輪轉(zhuǎn)速SKIPIF1<0=SKIPIF1<0=481.8r/min3.4.2計算帶長求SKIPIF1<0SKIPIF1<0=(SKIPIF1<0+SKIPIF1<0)/2=198.5mm求ΔΔ=(SKIPIF1<0-SKIPIF1<0)/2=98.5mm2(SKIPIF1<0+SKIPIF1<0)>=a>=0.7*(SKIPIF1<0+SKIPIF1<0)初取中心距a=600mm帶長L=πDm+2*a+SKIPIF1<0=1839.5基準長度SKIPIF1<0=2000mm求中心距和包角中心距a=SKIPIF1<0+SKIPIF1<0=344.18+337.06=681.24<700mm小輪包角α1=180°-(D2-D1)*60°=180°-(297-100)*60°/681.24=162.6>120°數(shù)求帶根v=3.14*SKIPIF1<0*SKIPIF1<0/(60*1000)=7.64m/s傳動比i=SKIPIF1<0/SKIPIF1<0=2帶根數(shù)SKIPIF1<0=1.32kwSKIPIF1<0=0.95SKIPIF1<0=1.03ΔP=0.17kwz=SKIPIF1<0/((SKIPIF1<0+ΔSKIPIF1<0)*SKIPIF1<0*SKIPIF1<0)=12.1/((1.32+0.17)*0.95*1.03)=8.3取9根求軸上載荷張緊力SKIPIF1<0=500*SKIPIF1<0/v*z(2.5-SKIPIF1<0)/SKIPIF1<0+qv*v=500*12.1/(7.64*9)*(2.5-0.95)/0.95+0.10*SKIPIF1<0=149.3N軸上載荷SKIPIF1<0=2*SKIPIF1<0sin(SKIPIF1<0/2)=2*9*149.3*sin(162.6°/2)=2656.5N

3.5齒輪傳動設(shè)計直齒錐齒:軸交角∑=90°傳遞功率P=10.45kw小齒輪轉(zhuǎn)速SKIPIF1<0=486.7r/m傳動比i=2.07載荷平穩(wěn),直齒為刨齒,小齒輪40Cr,調(diào)質(zhì)處理,241HB~~286HB平均260HB,大齒輪用45號鋼,217HB~~255HB平均230HB齒面接觸疲勞強度計算齒數(shù)和精度等級取SKIPIF1<0=24SKIPIF1<0=i*SKIPIF1<0=48EQSKIPIF1<0SKIPIF1<0SKIPIF1<0選八級精度使用系數(shù)SKIPIF1<0=1.0動載荷系數(shù)SKIPIF1<0=1.15齒間載荷分配系數(shù)SKIPIF1<0估計SKIPIF1<0*Ft/b<100N/mmcosSKIPIF1<0=u/SKIPIF1<0=2/SKIPIF1<0=0.89cosSKIPIF1<0=1/SKIPIF1<0=1/SKIPIF1<0=0.44SKIPIF1<0 =SKIPIF1<0/cosSKIPIF1<0=24/0.89=26.97SKIPIF1<0=SKIPIF1<0/cosSKIPIF1<0=48/0.44=109.1SKIPIF1<0αv=(1.88-3.2(1/(2*SKIPIF1<0)+1/(2*SKIPIF1<0)))cosSKIPIF1<0=1.85SKIPIF1<0=SKIPIF1<0=0.85SKIPIF1<0=SKIPIF1<0=1.4齒向載荷分布函數(shù)SKIPIF1<0=1.9載荷系數(shù)SKIPIF1<0=SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0=1*1.5*1.4*1.9=3.99轉(zhuǎn)矩SKIPIF1<0=9.55*SKIPIF1<0*SKIPIF1<0=9.55*SKIPIF1<0*10.45/486.7=20505N.mm彈性系數(shù)SKIPIF1<0=189.8SKIPIF1<0節(jié)點區(qū)域系數(shù)SKIPIF1<0=2.5接觸疲勞強度SKIPIF1<0=710MpaSKIPIF1<0 =680Mpa接觸最小安全系數(shù)SKIPIF1<0=1.5接觸壽命系數(shù)SKIPIF1<0=SKIPIF1<0=1.0許用接觸應(yīng)力[SKIPIF1<0]=SKIPIF1<0*SKIPIF1<0/SKIPIF1<0=710*/1.05=676Mpa[SKIPIF1<0]=SKIPIF1<0*SKIPIF1<0/SKIPIF1<0=680*/1.05=648Mpa小輪大端分度圓直徑SKIPIF1<0SKIPIF1<0=0.3SKIPIF1<0SKIPIF1<0=70mm驗算圓周速度及Ka*Ft/bSKIPIF1<0=(1-0.5SKIPIF1<0R)SKIPIF1<0=(1-0.5SKIPIF1<0R)70=59.5mmSKIPIF1<0=SKIPIF1<0=3.1459.5*486.7/60000=1.5m/sSKIPIF1<0=SKIPIF1<0

b=SKIPIF1<0*R=SKIPIF1<0*d/(2*sinSKIPIF1<0)=SKIPIF1<0*SKIPIF1<0/(2*SKIPIF1<0=20.4mmSKIPIF1<0*SKIPIF1<0/b=1.0*689.2/20.4=33.8N/mm<100N/mm確定傳動尺寸大端模數(shù)m=SKIPIF1<0/SKIPIF1<0=70/24=2.9mm實際大端分度圓直徑dSKIPIF1<0=mSKIPIF1<0=3*24=84SKIPIF1<0=mSKIPIF1<0=3*48=144b=SKIPIF1<0*R=0.3*80.5=24.15mm齒根彎曲疲勞強度計算齒面系數(shù)SKIPIF1<0=2.72SKIPIF1<0=2.38應(yīng)力修正系數(shù)SKIPIF1<0=1.66SKIPIF1<0=1.78重合度系數(shù)SKIPIF1<0=0.25+0.75/SKIPIF1<0=0.25+0.75/0.85=0.66齒間載荷分配系數(shù)SKIPIF1<0SKIPIF1<0*SKIPIF1<0/b<100N/mmSKIPIF1<0=1/SKIPIF1<0=1/0.66=1.56載荷系數(shù)SKIPIF1<0=SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0=1*1.15*1.56*1.9=3.4彎曲疲勞極限SKIPIF1<0SKIPIF1<0=600MPaSKIPIF1<0 =570MPa彎曲最小安全系數(shù)SKIPIF1<0=1.25彎曲壽命系數(shù)SKIPIF1<0=SKIPIF1<0=1.0尺寸系數(shù)SKIPIF1<0=1.0許用彎曲應(yīng)力[SKIPIF1<0]=SKIPIF1<0limSKIPIF1<0SKIPIF1<0/SKIPIF1<0=600*1.0*1.0/1.25=480MPa[SKIPIF1<0]=570*1.0*1.0/1.25=456MPa驗算SKIPIF1<0=SKIPIF1<0=SKIPIF1<0=152<[SKIPIF1<0]EQEQSKIPIF1<0SKIPIF1<0=SKIPIF1<0=152*2.38*1.78/(2.72*1.66)=142.6MPa標準斜齒圓柱齒輪小齒輪用40Cr調(diào)質(zhì)處理,硬度241HB~~286HB平均260MPa大齒輪用45號鋼,調(diào)質(zhì)處理,硬度229HB~~286HB平均241MPa初步計算轉(zhuǎn)矩SKIPIF1<0=9.55*SKIPIF1<0SKIPIF1<0*9.73/235.1=39524N.mm齒數(shù)系數(shù)SKIPIF1<0=1.0SKIPIF1<0值取SKIPIF1<0=85初步計算的許用接觸應(yīng)力[SKIPIF1<0H1]=0.96SKIPIF1<0Hlim1=0.9*710=619MPa[SKIPIF1<0H2]=0.9SKIPIF1<0Hlim2=1.9*580=522MPa初步計算的小齒輪直徑SKIPIF1<0=AdSKIPIF1<0=85*SKIPIF1<0=48.1mm取d1=50mm初步尺寬b=SKIPIF1<0d*SKIPIF1<0=1*50=50mm校核計算圓周速度v=SKIPIF1<0=0.62m/s精度等級選九級精度齒數(shù)z和模數(shù)m初步齒數(shù)SKIPIF1<0=19;SKIPIF1<0=i*19=4*19=76和螺旋角SKIPIF1<0SKIPIF1<0=SKIPIF1<0/SKIPIF1<0=50/19=2.63158SKIPIF1<0=2.5mmSKIPIF1<0=arcosSKIPIF1<0=arccos2.5/2.63158=18.2°使用系數(shù)SKIPIF1<0=1.10動載系數(shù)SKIPIF1<0=1.5齒間載荷分配系數(shù)SKIPIF1<0SKIPIF1<0=SKIPIF1<0=2*39524/50=1581NSKIPIF1<0=1.1*1.581/50=34N/mm<100N/mmSKIPIF1<0=[1.88-3.2[1/SKIPIF1<0+1/SKIPIF1<0]cosSKIPIF1<0=[1.88-3.25*(1/19+1/76)]cos18.2°=1.59SKIPIF1<0=SKIPIF1<0==2.0SKIPIF1<0=SKIPIF1<0=1.59+2.0=3.59SKIPIF1<0=arctanSKIPIF1<0=arctanSKIPIF1<0=20.9°cosSKIPIF1<0=cos18.2°20cos°/20.9cos°=0.95齒向載荷分布系數(shù)SKIPIF1<0=A+B[1+0.6*SKIPIF1<0]SKIPIF1<0+c*b/1000=1.36SKIPIF1<0=SKIPIF1<0*SKIPIF1<0*SKIPIF1<0*SKIPIF1<0=1.10*1.05*1.76*1.36=2.76彈性系數(shù)SKIPIF1<0=189.8SKIPIF1<0節(jié)點區(qū)域系數(shù)SKIPIF1<0=2.5重合度系數(shù)SKIPIF1<0取SKIPIF1<0螺旋角系數(shù)SKIPIF1<0=SKIPIF1<0許用接觸應(yīng)力SKIPIF1<0驗算SKIPIF1<0=189.8*2.38*0.97SKIPIF1<0=647MPa<690MPa齒根彎曲疲勞強度驗算齒行系數(shù)YFaSKIPIF1<0=SKIPIF1<0SKIPIF1<0YSKIPIF1<0=2.72YSKIPIF1<0=2.2應(yīng)力修正系數(shù)SKIPIF1<0SKIPIF1<0=1.56SKIPIF1<0=1.79重合度系數(shù)SKIPIF1<0SKIPIF1<0=1.61SKIPIF1<0螺旋角系數(shù)SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0齒向載荷分配系數(shù)SKIPIF1<0SKIPIF1<0SKIPIF1<0=1.76<SKIPIF1<0齒向載荷分布系數(shù)SKIPIF1<0b/h=50.(2.25*2.5)=8.9SKIPIF1<0=1.27載荷系數(shù)K=SKIPIF1<0*SKIPIF1<0*SKIPIF1<0許用彎曲應(yīng)力SKIPIF1<0SKIPIF1<0驗算SKIPIF1<0SKIPIF1<03.6軸的設(shè)計輸入軸選用45鋼調(diào)質(zhì)SKIPIF1<0SKIPIF1<0取d=35mm計算齒輪受力SKIPIF1<0=84mmSKIPIF1<0=(1-0.5SKIPIF1<0SKIPIF1<0=689.2NSKIPIF1<0=SKIPIF1<0tanSKIPIF1<0SKIPIF1<0=SKIPIF1<0計算支反力水平面反力SKIPIF1<0=1102.7NSKIPIF1<0=-413.5N垂直面反力SKIPIF1<0=-1235.7NSKIPIF1<0=4115.5N水平面受力圖垂直面受力圖水平面彎矩圖垂直彎矩圖合成彎矩圖轉(zhuǎn)矩圖許用應(yīng)力許用應(yīng)力值SKIPIF1<0應(yīng)力校正系數(shù)SKIPIF1<0當量彎矩圖SKIPIF1<0SKIPIF1<0軸徑SKIPIF1<0SKIPIF1<0高速軸軸材料選用45鋼調(diào)質(zhì),SKIPIF1<0SKIPIF1<0SKIPIF1<0取d=40mm計算螺旋角SKIPIF1<0齒輪直徑小輪SKIPIF1<0=SKIPIF1<0大輪SKIPIF1<0小齒輪受力轉(zhuǎn)矩SKIPIF1<0=9.55*SKIPIF1<0圓周力SKIPIF1<0=2*SKIPIF1<0/SKIPIF1<0=2*39524/50=1581N徑向力SKIPIF1<0畫小齒輪軸受力圖水平反力SKIPIF1<0=1358.1NSKIPIF1<0=912.1N垂直反力SKIPIF1<0=594.7NSKIPIF1<0=103.3N水平受力圖垂直受力圖水平彎矩圖垂直彎矩圖合成彎矩圖畫轉(zhuǎn)矩圖應(yīng)力校正系數(shù)SKIPIF1<0畫當量彎矩圖SKIPIF1<0SKIPIF1<0=50220N.mm校核軸徑SKIPIF1<0=20.3<40mm低速軸材料同前兩軸SKIPIF1<0SKIPIF1<0畫大齒輪受力圖計算支反力水平反力SKIPIF1<0=1185.8SKIPIF1<0=395.2N垂直反力SKIPIF1<0=21.2NSKIPIF1<0=584.6N垂直受力圖水平彎矩圖垂直彎矩圖合成彎矩圖轉(zhuǎn)矩圖當量彎矩SKIPIF1<0SKIPIF1<0校核軸徑SKIPIF1<0=26<60mm3.7軸承的選擇輸入軸軸承選擇:選用圓錐滾子軸承30208e=0.37Y=1.6Cr=63000NSKIPIF1<0 =1177.7NSKIPIF1<0=4297.0NSKIPIF1<0 =SKIPIF1<0/(2*Y)=368NSKIPIF1<0=SKIPIF1<0/(2*Y)=1342.8NSKIPIF1<0=1228.4NSKIPIF1<0=1342.8NSKIPIF1<0/SKIPIF1<0=1.0>eSKIPIF1<0/SKIPIF1<0=0.3<e查表SKIPIF1<0=0.4SKIPIF1<0=1.6SKIPIF1<0=1SKIPIF1<0=0當量動載荷SKIPIF1<0=SKIPIF1<0*(SKIPIF1<0*SKIPIF1<0+SKIPIF1<0*SKIPIF1<0)=1.0*(0.4*1177.7+1.6*1228.4)=2436.5NSKIPIF1<0=SKIPIF1<0*(SKIPIF1<0*SKIPIF1<0+SKIPIF1<0*SKIPIF1<0)=4297.0N軸承壽命SKIPIF1<0=SKIPIF1<0同樣,高速軸承和低速軸承分別用選用圓錐滾子軸承30210和30213。3.8鍵的選擇SKIPIF1<0輸入軸SKIPIF1<0L=20(mm)高速軸SKIPIF1<0L=20低速軸SKIPIF1<0L=30T=SKIPIF1<03.9減速機箱體的設(shè)計名稱符號尺寸關(guān)系結(jié)果箱座壁厚SKIPIF1<0SKIPIF1<0=0.025*a+3SKIPIF1<08箱蓋壁厚SKIPIF1<0SKIPIF1<0=0.02*a+3SKIPIF1<08a=SKIPIF1<0箱體凸緣厚度SKIPIF1<0,SKIPIF1<0,SKIPIF1<0b=1.5=15;SKIPIF1<0=1.5SKIPIF1<0=15;SKIPIF1<0=2.5=25加強肋厚度SKIPIF1<0,SKIPIF1<0m=0.85=8.5;SKIPIF1<0=0.85SKIPIF1<0=8.5地腳螺栓直徑SKIPIF1<0SKIPIF1<014地腳螺栓數(shù)目nSKIPIF1<04軸承旁連接螺栓直徑SKIPIF1<00.75SKIPIF1<0箱蓋,箱座連接螺栓直徑SKIPIF1<0SKIPIF1<0;螺栓間LSKIPIF1<0軸承蓋螺釘直徑數(shù)目SKIPIF1<0,nSKIPIF1<0SKIPIF1<0=8n=4軸承蓋外徑SKIPIF1<0SKIPIF1<0=s(兩連接螺栓間的距離)觀察孔螺釘直徑SKIPIF1<0SKIPIF1<0軸承旁凸臺高度和直徑h,SKIPIF1<0h由結(jié)構(gòu)決定,SKIPIF1<0=SKIPIF1<0箱體外壁至軸承座端面距離SKIPIF1<0SKIPIF1<0+SKIPIF1<0+SKIPIF1<03.10減速器附件設(shè)計3.10.1窺視孔和視孔蓋窺視孔應(yīng)該在箱蓋頂部,以便觀察,應(yīng)在凸臺上以便加工。3.10.2通氣器在箱蓋頂部,要適合環(huán)境,其尺寸要與減速器大小相合適。3.10.3油面指示器應(yīng)該設(shè)在油面比較穩(wěn)定的地方,如低速軸附近。用圓形油標,有標尺的位置不能太高和太低,以免溢出油標尺孔座。3.10.4放油孔和螺塞放在油的最低處,平時用螺塞塞住,放油孔不能低于油池面,以免排油不凈。3.10.5起吊裝置吊環(huán)可按起重重量選擇,箱蓋安裝吊環(huán)螺釘處設(shè)置凸臺,以使吊環(huán)螺釘有足夠的深度。3.10.6定位銷用圓錐銷作定位銷,兩定位銷的距離越遠越可靠,常設(shè)在箱體連接凸緣處的對角處,對稱布置。直徑d=0.8d2。3.10.7起蓋螺釘裝在箱蓋連接凸緣上,其螺紋長度大于箱體凸緣厚度,直徑可與連接螺釘相同。3.11密封與潤滑軸承采用接觸式密封。傳動采用浸油潤滑,盡量使各傳動浸油深度相同。軸承潤滑采用刮油潤滑。4設(shè)計小結(jié)通過這次設(shè)計讓我了解到機械設(shè)計是從使用要求等出發(fā)，對機械的工作原理、結(jié)構(gòu)、運動形式、力和能量的傳遞方式，以及各個零件的材料和形狀尺寸等問題進行構(gòu)思、分析和決策的工作過程，這種過程的結(jié)果要表達成設(shè)計圖紙、說明書及各種技術(shù)文件。通過帶式輸送機傳動裝置的設(shè)計,了解了帶式輸送機傳動裝置的原理以及其結(jié)構(gòu)。從帶式輸送機傳動裝置的設(shè)計，我學(xué)到了機械設(shè)計的思想--以最少的成本達到最好的目的,以最簡單的結(jié)構(gòu)達到所需的功能。設(shè)計思想中最突出得的是—-合理二字。整個設(shè)計過程使我受益非淺。5參考文獻1王昆等主編,機械設(shè)計課程設(shè)計,武漢:高等教育出版社,1995。2邱宣懷主編,機械設(shè)計.第四版,北京:高等教育出版社,1997。3濮良貴主編,機械設(shè)計.第七版,西安:高等教育出版社,2000。4任金泉主編,機械設(shè)計課程設(shè)計,西安:西安交通大學(xué)出版社,2002。5許鎮(zhèn)寧主編,機械零件,北京:人民教育出版社,1959。6TragfahigkeitsberechnungVonStirn-undKegelradern(DIN3990),1970。目錄目錄第一章總論 1一、項目概述 1二、可行性研究報告編制依據(jù)和范圍 2三、項目主要經(jīng)濟技術(shù)指標 3四、******國家森林公園概況 3第二章項目背景及必要性 8一、項目背景 8二、項目建設(shè)的必要性與可行性 10第三章項目選址分析 13一、項目選址 13二、項目城市概況 13三、經(jīng)濟發(fā)展概況 14四、公共設(shè)施依托條件及施工條件 17第四章需求分析與建設(shè)規(guī)模 18一、****國家森