用于帶式運輸機的展開式二級斜齒圓柱齒輪減速器 畢業(yè)論文

目錄1、課程設(shè)計書及設(shè)計要求------------------------------------------12、電動機的選擇及傳動裝置的運動和動力參數(shù)計算---------33、傳動零件的設(shè)計計算（確定齒輪傳動的主要參數(shù)）------64、軸的設(shè)計計算及校核及滾動軸承的選擇和計算------------145、箱體設(shè)計及說明---------------------------------------------------276、鍵聯(lián)接的選擇和計算---------------------------------------------297、聯(lián)軸器的選擇------------------------------------------------------318、潤滑和密封的選擇------------------------------------------------329、減速器附件的選擇及說明---------------------------------------3210、設(shè)計總結(jié)-----------------------------------------------------------33參考資料-----------------------------------------------------------331.《機械設(shè)計》課程設(shè)計任務(wù)書專業(yè)：機械設(shè)計制造及其自動化班級：姓名：學號：一、設(shè)計題目設(shè)計用于帶式運輸機的展開式二級斜齒圓柱齒輪減速器二、原始數(shù)據(jù)(f6)運輸帶工作拉力F=2500Nm運輸帶工作速度v=1.30m/s卷筒直徑D=300mm三、工作條件連續(xù)單向運轉(zhuǎn)，工作時有輕微振動，空載啟動，使用期限為8年，小批量生產(chǎn)，單班制工作，運輸帶速度允許誤差為5%。四、應(yīng)完成的任務(wù)1、減速器裝配圖一張（A0圖或CAD圖）2、零件圖兩張（A2圖或CAD圖）五、設(shè)計時間2009年12月21日至2010年1月8日六、要求1、圖紙圖面清潔，標注準確，符合國家標準；設(shè)計計算說明書字體端正，計算層次分明。七、設(shè)計說明書主要內(nèi)容1、內(nèi)容（1）目錄（標題及頁次）；（2）設(shè)計任務(wù)書；（3）前言（題目分析，傳動方案的擬定等）；（4）電動機的選擇及傳動裝置的運動和動力參數(shù)計算；（5）傳動零件的設(shè)計計算（確定帶傳動及齒輪傳動的主要參數(shù)）；（6）軸的設(shè)計計算及校核；（7）箱體設(shè)計及說明（8）鍵聯(lián)接的選擇和計算；（9）滾動軸承的選擇和計算；（10）聯(lián)軸器的選擇；（11）潤滑和密封的選擇；（12）減速器附件的選擇及說明；（13）設(shè)計小結(jié)；（14）參考資料（資料的編號[]及書名、作者、出版單位、出版年月）；2、要求和注意事項必須用鋼筆工整的書寫在規(guī)定格式的設(shè)計計算說明書上，要求計算正確，論述清楚、文字精煉、插圖簡明、書寫整潔。本次課程設(shè)計說明書要求字數(shù)不少于6-8千字（或30頁），要裝訂成冊。機械制造教研室2、電動機的選擇及傳動裝置的運動和動力參數(shù)計算及傳動裝置的運動和動力參數(shù)計算；（1）選擇電動機的類型按要求選擇Y系列三相異步電動機，電壓380V（2）選擇電動機的容量電動機所需工作功率為：P＝P/η工作機需要的工作功率：SKIPIF1<0=F*V=2500Nm*傳動裝置的總效率為：SKIPIF1<0滾動軸承的傳動效率為SKIPIF1<0閉式齒輪的傳動效率為SKIPIF1<0聯(lián)軸器的效率為SKIPIF1<0傳動滾筒的效率為SKIPIF1<0帶效率SKIPIF1<0動機的效率為SKIPIF1<0因載荷工作時有輕微振動，電動機額定功率SKIPIF1<0略大于P即可。由表16-1，Y系列電動機技術(shù)數(shù)據(jù)，選動機的額定功率SKIPIF1<0為5.5kw。（3）確定電動機的轉(zhuǎn)速綜合考慮電動機和傳動裝置的尺寸、重量、價格減速器的傳動比，選定型號為Y132S-4的三相異步電動機，額定功率為5.5kw，額定電流A，滿載轉(zhuǎn)速SKIPIF1<01440r/min，同步轉(zhuǎn)速1500r/min。SKIPIF1<02.確定傳動裝置的總傳動比和分配傳動比（1）總傳動比由選定的電動機滿載轉(zhuǎn)速n和工作機主動軸轉(zhuǎn)速n，可得傳動裝置總傳動比為SKIPIF1<0＝n/n＝1440/（2）各級傳動裝置傳動比高速級傳動比為SKIPIF1<0＝則低速軸傳動比SKIPIF1<0＝SKIPIF1<03.計算傳動裝置的運動和動力參數(shù)電機軸：P0=Pd=KWn0=1440r/minT0=SKIPIF1<0=NSKIPIF1<0高速軸：

P1=P1*n01=*0.99=KWn1=n0=1440r/minT1=SKIPIF1<0=NSKIPIF1<0中間軸：

P2=P1*n12==KWn2=SKIPIF1<0r/minT2=SKIPIF1<0NSKIPIF1<0低速軸：P3=P2*n23KWn3=SKIPIF1<0r/minT3=SKIPIF1<0NSKIPIF1<0滾筒軸：P4=P3*n3456=3.11KWn4=n3/1=r/minT4=SKIPIF1<0NSKIPIF1<0運動和動力參數(shù)結(jié)果如下表：軸名功率PKW轉(zhuǎn)矩TNm轉(zhuǎn)速r/min輸入輸出輸入輸出電動機軸1440高速軸1440中間軸低速軸393.54滾筒軸軸承傳動效率3、傳動零件的設(shè)計計算（確定齒輪傳動的主要參數(shù)）A高速齒輪的計算1選精度等級、材料及齒數(shù)（1）材料及熱處理；選擇小齒輪材料為40Cr（調(diào)質(zhì)），硬度為280HBS，大齒輪材料為45鋼（調(diào)質(zhì)），硬度為240HBS，二者材料硬度差為40HBS。（2）精度等級選用7級精度；（3）試選小齒輪齒數(shù)z1＝24，大齒輪齒數(shù)z2＝z1*i=24*4.93=118.32；選螺旋角，初選螺旋角SKIPIF1<0=14SKIPIF1<02按齒面接觸強度設(shè)計因為低速級的載荷大于高速級的載荷，所以通過低速級的數(shù)據(jù)進行計算。SKIPIF1<0（1）確定公式內(nèi)的各計算數(shù)值2）選取尺寬系數(shù)φd＝13）材料的區(qū)域系數(shù)ZH＝2.4354）SKIPIF1<0SKIPIF1<0則SKIPIF1<056)材料的彈性影響系數(shù)ZESKIPIF1<07）小齒輪的接觸疲勞強度極限σHlim1＝600MPa大齒輪的解除疲勞強度極限σHlim2＝550MPa8）計算應(yīng)力值環(huán)數(shù)NSKIPIF1<0=60nSKIPIF1<0jSKIPIF1<0=60××1×（1×8×365×8）×10SKIPIF1<0hNSKIPIF1<0×10SKIPIF1<0×10SKIPIF1<0h9）查得：KSKIPIF1<0=1.03KSKIPIF1<010）齒輪的接觸疲勞需用應(yīng)力取失效概率為1%,安全系數(shù)S=1,[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0×600=618SKIPIF1<0[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0×550=594SKIPIF1<0許用接觸應(yīng)力SKIPIF1<0（2）設(shè)計計算①小齒輪的分度圓直徑dSKIPIF1<0SKIPIF1<0=SKIPIF1<0②計算圓周速度SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0③計算齒寬b和模數(shù)SKIPIF1<0計算齒寬bb=SKIPIF1<0=mm計算摸數(shù)mSKIPIF1<0初選螺旋角SKIPIF1<0=14SKIPIF1<0SKIPIF1<0=SKIPIF1<0④計算齒寬與高之比SKIPIF1<0h=mSKIPIF1<0SKIPIF1<0=SKIPIF1<0=⑤計算縱向重合度SKIPIF1<0SKIPIF1<0SKIPIF1<0⑥計算載荷系數(shù)K使用系數(shù)SKIPIF1<0=1.25根據(jù)SKIPIF1<0,7級精度,查課本由SKIPIF1<0表10-8得動載系數(shù)KSKIPIF1<0=查課本由SKIPIF1<0表10-4得KSKIPIF1<046查課本由SKIPIF1<0表10-3得:KSKIPIF1<0=SKIPIF1<0故載荷系數(shù):K＝KKKSKIPIF1<0KSKIPIF1<0=1⑦按實際載荷系數(shù)校正所算得的分度圓直徑:dSKIPIF1<0=dSKIPIF1<0SKIPIF1<0=×SKIPIF1<0=SKIPIF1<0⑧計算模數(shù)SKIPIF1<0:SKIPIF1<0=SKIPIF1<0(3).齒根彎曲疲勞強度設(shè)計由彎曲強度的設(shè)計公式:SKIPIF1<0≥SKIPIF1<01)確定公式內(nèi)各計算數(shù)值①計算載荷系數(shù)KK＝KKKK=②

軸向重合度螺旋角影響系數(shù)③

計算當量齒數(shù)z＝z/cos＝24/cosSKIPIF1<014SKIPIF1<0＝2

z＝z/cos＝119/cosSKIPIF1<014SKIPIF1<0＝④查取齒形系數(shù)Y＝2.592Y＝2.211⑤

應(yīng)力校正系數(shù)YY＝96

Y＝1.775

⑥彎曲疲勞壽命系數(shù):KSKIPIF1<0=0.86KSKIPIF1<0=0.93⑦

彎曲疲勞應(yīng)力[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0⑧

計算大小齒輪的SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0大齒輪的數(shù)值大.選用.2）設(shè)計計算①計算模數(shù)SKIPIF1<0按GB/T1357-1987圓整為標準模數(shù),取mSKIPIF1<0=2mmzSKIPIF1<0=SKIPIF1<0那么zSKIPIF1<0=104

3幾何尺寸計算（1）計算中心距a=SKIPIF1<0=SKIPIF1<0=SKIPIF1<0將中心距圓整為129SKIPIF1<0（2）按圓整后的中心距修正螺旋角SKIPIF1<0=arccosSKIPIF1<0SKIPIF1<0因SKIPIF1<0值改變不多,故參數(shù)SKIPIF1<0,SKIPIF1<0,SKIPIF1<0等不必修正.分度圓直徑dSKIPIF1<0=SKIPIF1<0=SKIPIF1<0dSKIPIF1<0=SKIPIF1<0=SKIPIF1<0（4）計算齒輪寬度B=SKIPIF1<0圓整的SKIPIF1<0 SKIPIF1<0B低速齒輪的計算1選精度等級、材料及齒數(shù)（1）材料及熱處理；選擇小齒輪材料為40Cr（調(diào)質(zhì)），硬度為280HBS，大齒輪材料為45鋼（調(diào)質(zhì)），硬度為240HBS，二者材料硬度差為40HBS。（2）精度等級選用7級精度；（3）試選小齒輪齒數(shù)z1＝24，大齒輪齒數(shù)z2＝85；2按齒面接觸強度設(shè)計SKIPIF1<0（1）確定公式內(nèi)的各計算數(shù)值2）選取尺寬系數(shù)φd＝13）材料的區(qū)域系數(shù)ZH＝4）SKIPIF1<0SKIPIF1<0則SKIPIF1<06)材料的彈性影響系數(shù)ZE7）小齒輪的接觸疲勞強度極限σHlim1＝600MPa大齒輪的解除疲勞強度極限σHlim2＝550MPa8）計算應(yīng)力值環(huán)數(shù)NSKIPIF1<0=60nSKIPIF1<0jSKIPIF1<0=60××1×（1×8×365×8）×10SKIPIF1<0hNSKIPIF1<0×10SKIPIF1<0×10SKIPIF1<0h9）查得：KSKIPIF1<0=1.03KSKIPIF1<010）齒輪的接觸疲勞需用應(yīng)力取失效概率為1%,安全系數(shù)S=1,[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0×600=618SKIPIF1<0[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0×550=594SKIPIF1<0許用接觸應(yīng)力SKIPIF1<0（2）設(shè)計計算①小齒輪的分度圓直徑dSKIPIF1<0SKIPIF1<0=SKIPIF1<0②計算圓周速度SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0③計算齒寬b和模數(shù)SKIPIF1<0計算齒寬bb=SKIPIF1<0=mm計算摸數(shù)mSKIPIF1<0初選螺旋角SKIPIF1<0=14SKIPIF1<0SKIPIF1<0=SKIPIF1<0④計算齒寬與高之比SKIPIF1<0h=mSKIPIF1<0t=2.52*2.45=SKIPIF1<0=SKIPIF1<0⑤計算縱向重合度SKIPIF1<0SKIPIF1<0SKIPIF1<0⑥計算載荷系數(shù)K使用系數(shù)SKIPIF1<0=1.25根據(jù)SKIPIF1<0,7級精度,查課本由SKIPIF1<0表10-8得動載系數(shù)KSKIPIF1<0=1,查課本由SKIPIF1<0表10-4得KSKIPIF1<0查課本由SKIPIF1<0表10-3得:KSKIPIF1<0=SKIPIF1<0故載荷系數(shù):K＝KKKSKIPIF1<0KSKIPIF1<0=⑦按實際載荷系數(shù)校正所算得的分度圓直徑dSKIPIF1<0=dSKIPIF1<0SKIPIF1<0=×SKIPIF1<0=SKIPIF1<0⑧計算模數(shù)SKIPIF1<0SKIPIF1<0=SKIPIF1<0(3).齒根彎曲疲勞強度設(shè)計由彎曲強度的設(shè)計公式SKIPIF1<0≥SKIPIF1<01)確定公式內(nèi)各計算數(shù)值①計算載荷系數(shù)KK＝KKKK=②

軸向重合度螺旋角影響系數(shù)③

計算當量齒數(shù)z＝z/cos＝24/cosSKIPIF1<014SKIPIF1<0＝2

z＝z/cos＝85/cosSKIPIF1<014SKIPIF1<0＝④查取齒形系數(shù)Y＝2.592Y＝2.195⑤

應(yīng)力校正系數(shù)YY＝96

Y＝1.775

⑥彎曲疲勞壽命系數(shù):KSKIPIF1<0KSKIPIF1<0⑦

彎曲疲勞應(yīng)力[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0[SKIPIF1<0]SKIPIF1<0=SKIPIF1<0⑧

計算大小齒輪的SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0大齒輪的數(shù)值大.選用.2）設(shè)計計算①計算模數(shù)SKIPIF1<0按GB/T1357-1987圓整為標準模數(shù),取mSKIPIF1<0=6mmzSKIPIF1<0=SKIPIF1<0那么zSKIPIF1<0=11*3.53=38.33=39zSKIPIF1<0=11zSKIPIF1<0=39

3幾何尺寸計算（1）計算中心距a=SKIPIF1<0=SKIPIF1<0=SKIPIF1<0（2）按圓整后的中心距修正螺旋角SKIPIF1<0=arccosSKIPIF1<0因SKIPIF1<0值改變不多,故參數(shù)SKIPIF1<0,SKIPIF1<0,SKIPIF1<0等不必修正.分度圓直徑dSKIPIF1<0=SKIPIF1<0=SKIPIF1<0dSKIPIF1<0=SKIPIF1<0SKIPIF1<0（4）計算齒輪寬度B=SKIPIF1<0圓整的SKIPIF1<0 SKIPIF1<04、軸的設(shè)計計算及校核及滾動軸承的選擇和計算1、軸1（高速軸）的設(shè)計：初步確定軸的最小直徑選取軸的材料為45鋼，調(diào)制處理。根據(jù)表15-3，取SKIPIF1<0=112，于是得d≥SKIPIF1<0SKIPIF1<0＝SKIPIF1<0mm=mm與聯(lián)軸器采用單鍵連接，則軸允許的最小直徑d=14.38*(1+0.06)=mm角接觸軸承的選型設(shè)計：將角接觸軸承反裝，F(xiàn)=SKIPIF1<03kNSKIPIF1<0=F*SKIPIF1<0=NSKIPIF1<0=SKIPIF1<0’*sinN(壓力角為20)兩軸承徑向分力：SKIPIF1<0=0.5*SKIPIF1<0=N高速級選擇左選，則軸承11被放松，軸承12被壓緊SKIPIF1<0=SKIPIF1<0SKIPIF1<0=NSKIPIF1<0=SKIPIF1<0+SKIPIF1<0=NSKIPIF1<0SKIPIF1<0=SKIPIF1<0SKIPIF1<0=x*SKIPIF1<0+y*SKIPIF1<0=N由c=SKIPIF1<0,SKIPIF1<0=23360h得；C=kN根據(jù)壽命要求選擇7005AC型角接觸軸承；則軸上安裝軸承的軸徑為SKIPIF1<020軸的結(jié)構(gòu)設(shè)計擬定軸上零件的裝配方案假設(shè)軸直徑的最大部分為28mm,其e=34.5-1.6-28-3SKIPIF1<0=2.56即e<2.56所以設(shè)計為齒輪軸輸出軸的最小直徑顯然是安裝聯(lián)軸器處軸的直徑SKIPIF1<0SKIPIF1<0，為了使所選的軸直徑SKIPIF1<0與聯(lián)軸器的孔徑相適應(yīng)，故需同時選取聯(lián)軸器的型號。聯(lián)軸器的計算轉(zhuǎn)矩SKIPIF1<0，查表14-1，考慮到轉(zhuǎn)矩化很小，故取SKIPIF1<01.5，則SKIPIF1<0=SKIPIF1<0*T=1.5*24.4=36.6N*m按照計算轉(zhuǎn)矩應(yīng)小于聯(lián)軸器公稱轉(zhuǎn)矩的條件，查標準GB/T5014-1985或手冊，選用HL4型凸緣聯(lián)軸器，其公稱轉(zhuǎn)矩為40N*m。半聯(lián)軸器的孔徑SKIPIF1<0=18mm，故取YL4半聯(lián)軸器長度L=42mm為了滿足半聯(lián)軸器的軸向定位要求,1軸段右端需制出一軸肩,故取SKIPIF1<0=20mm;半聯(lián)軸器與軸配合的轂孔長度SKIPIF1<0SKIPIF1<0=88mm取齒輪距箱體內(nèi)壁之距離為25mm。半聯(lián)軸器與軸的周向定位均采用平鍵連接。按SKIPIF1<0由手冊查得平鍵截面bSKIPIF1<0h=6SKIPIF1<06，半聯(lián)軸器與軸的配合為H7/k6。2，軸2（中間軸）的設(shè)計：選取軸的材料為45鋼，調(diào)制處理。根據(jù)表15-3，取SKIPIF1<0=112，于是得SKIPIF1<0≥SKIPIF1<0SKIPIF1<0＝SKIPIF1<0mm=25mm角接觸軸承的選型設(shè)計：角接觸軸承的選型設(shè)計：將角接觸軸承反裝，軸承上兩個齒輪受載所以軸承需將兩部分結(jié)合起來分析：對于齒輪2F1=SKIPIF1<0SKIPIF1<0=F*SKIPIF1<0SKIPIF1<0’=F*SKIPIF1<0=1099NSKIPIF1<0=SKIPIF1<0對于齒輪3F2=SKIPIF1<0=2890NSKIPIF1<0=F*SKIPIF1<0SKIPIF1<0’=F*SKIPIF1<0=2805NSKIPIF1<0=SKIPIF1<0’兩齒輪選擇同樣的旋向（右旋）在軸向分力的合力外力：SKIPIF1<0對于徑向的計算按最大徑向力設(shè)計：SKIPIF1<0=0.5*(SKIPIF1<0+SKIPIF1<0派生力：SKIPIF1<0=SKIPIF1<0SKIPIF1<0=453.98NSKIPIF1<0=SKIPIF1<0+SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0=x*SKIPIF1<0+y*SKIPIF1<0由c=SKIPIF1<0,SKIPIF1<0=23360h得；C=7.2kN根據(jù)壽命要求選擇7005AC型角接觸軸承；則軸上安裝軸的直徑徑為SKIPIF1<025；3，軸3（低速軸）的設(shè)計：選取軸的材料為45鋼，調(diào)制處理。根據(jù)表15-3，取SKIPIF1<0=112，于是得d≥SKIPIF1<0SKIPIF1<0＝SKIPIF1<0mm=暫定軸與滾筒的連接采用單鍵，則軸的最小直徑d>1.06*=角接觸軸承的選型設(shè)計：將角接觸軸承反裝，F(xiàn)=SKIPIF1<0SKIPIF1<0=F*SKIPIF1<0=677NSKIPIF1<0’=F*SKIPIF1<0SKIPIF1<0=SKIPIF1<0’兩軸承徑向分力：SKIPIF1<0=0.5*SKIPIF1<0=468N高速級選擇左選，則軸承11被放松，軸承12被壓緊SKIPIF1<0=SKIPIF1<0SKIPIF1<0SKIPIF1<0=SKIPIF1<0+SKIPIF1<0=677+318=995NSKIPIF1<0SKIPIF1<0SKIPIF1<0SKIPIF1<0=x*SKIPIF1<0+y*SKIPIF1<0由c=SKIPIF1<0,SKIPIF1<0=23360h得；C=4.12kN根據(jù)壽命要求選擇角接觸軸承軸承內(nèi)徑為大于SKIPIF1<015，結(jié)合扭轉(zhuǎn)強度的要求，選擇角接觸球軸承7010AC,安裝內(nèi)徑SKIPIF1<050mm;軸的結(jié)構(gòu)設(shè)計擬定軸上零件的裝配方案輸出軸的最小直徑顯然是安裝聯(lián)軸器處軸的直徑SKIPIF1<0SKIPIF1<0（如上圖），為了使所選的軸直徑SKIPIF1<0與聯(lián)軸器的孔徑相適應(yīng)，故需同時選取聯(lián)軸器的型號。聯(lián)軸器的計算轉(zhuǎn)矩SKIPIF1<0，查表14-1，考慮到轉(zhuǎn)矩化很小，故取SKIPIF1<01.3，則SKIPIF1<0=SKIPIF1<0*T=326.7*1.5=490.05N*m按照計算轉(zhuǎn)矩應(yīng)小于聯(lián)軸器公稱轉(zhuǎn)矩的條件，查標準GB/T5014-1985或手冊，選用YL9型凸緣聯(lián)軸器，其公稱轉(zhuǎn)矩為400N*m。半聯(lián)軸器的孔徑SKIPIF1<0=38mm，故取YL4半聯(lián)軸器長度L=82mm，半聯(lián)軸器與軸配合的轂孔長度SKIPIF1<0SKIPIF1<0=164mm取齒輪距箱體內(nèi)壁之距離為25mm。半聯(lián)軸器與軸的周向定位均采用平鍵連接。按SKIPIF1<0由手冊查得平鍵截面bSKIPIF1<0h=10SKIPIF1<08SKIPIF1<082，半聯(lián)軸器與軸的配合為H7/k6軸的校核1，軸3（低速軸）按彎扭組合強度校核：對齒輪的受力分析：總的力F=SKIPIF1<0=2820NSKIPIF1<0=F*sinSKIPIF1<0=686NSKIPIF1<0’=F*SKIPIF1<0=2737NSKIPIF1<0=SKIPIF1<0’*sin20=936NSKIPIF1<0=SKIPIF1<0’*SKIPIF1<020=2572NX平面（水平面）SKIPIF1<0+SKIPIF1<0+SKIPIF1<0=0SKIPIF1<0SKIPIF1<0SKIPIF1<0+SKIPIF1<0SKIPIF1<0122+SKIPIF1<0SKIPIF1<0(122+75)=0解得：SKIPIF1<0SKIPIF1<0=-934NSKIPIF1<0Y平面（垂直平面）SKIPIF1<0+SKIPIF1<0+SKIPIF1<0=0SKIPIF1<0SKIPIF1<0122+SKIPIF1<0SKIPIF1<0(122+75)=0解得：SKIPIF1<0=-979NSKIPIF1<0=-1592NSKIPIF1<0根據(jù)x,y平面彎曲圖形則彎曲的的最大值M:M=SKIPIF1<0其扭矩圖如下：SKIPIF1<0其危險截面為軸3與聯(lián)軸器的結(jié)合面，其抗彎曲截面系數(shù)W為：W=SKIPIF1<0SKIPIF1<0d,為軸的直徑t,為軸上鍵槽的深度b,為鍵的寬度所以按彎扭組合強度校核：SKIPIF1<0SKIPIF1<0SKIPIF1<0,折合系數(shù)SKIPIF1<0SKIPIF1<0，軸所受的扭矩SKIPIF1<0，抗彎截面系數(shù)求得：SKIPIF1<0SKIPIF1<0所以SKIPIF1<0<SKIPIF1<0此軸安全。對于軸向分力對軸的穩(wěn)定性，這里不進行分析校核了（它不屬于細長軸）2，對軸2（中間軸）按彎扭組合強度校核：對齒輪2進行受力分析：對于齒輪2(B)F1=SKIPIF1<0SKIPIF1<0=F*SKIPIF1<0SKIPIF1<0，=F*SKIPIF1<0=1099NSKIPIF1<0=SKIPIF1<0，*sin20=375.88N（x方向)SKIPIF1<0=SKIPIF1<0，SKIPIF1<020=1032.72N(y方向)對于齒輪3(C)F2=SKIPIF1<0=2890SKIPIF1<0=F*SKIPIF1<0SKIPIF1<0’=F*SKIPIF1<0=-2805NSKIPIF1<0=SKIPIF1<0’*sin20=959.37N（x方向）SKIPIF1<0=SKIPIF1<0’*SKIPIF1<020=2635.8N(y方向)X平面（水平面）：SKIPIF1<0+SKIPIF1<0-SKIPIF1<0+SKIPIF1<0=0SKIPIF1<0*81.5+SKIPIF1<0*153/2-SKIPIF1<0*122.5+SKIPIF1<0*30+SKIPIF1<0*197=0解得：SKIPIF1<0SKIPIF1<0SKIPIF1<0Y平面SKIPIF1<0+SKIPIF1<0+SKIPIF1<0+SKIPIF1<0=0SKIPIF1<0*81.5+SKIPIF1<0*122.5+SKIPIF1<0*197=0解得：SKIPIF1<0SKIPIF1<0SKIPIF1<0軸2的扭矩圖：SKIPIF1<0根據(jù)x,y平面彎曲圖形則彎曲的的最大值M:M=SKIPIF1<0其危險截面為軸2（中間軸）與齒輪2的結(jié)合面，其抗彎曲截系數(shù)W為：W=SKIPIF1<0SKIPIF1<0d,為軸的直徑t,為軸上鍵槽的深度b,為鍵的寬度所以按彎扭組合強度校核：SKIPIF1<0SKIPIF1<0SKIPIF1<0,折合系數(shù)SKIPIF1<0SKIPIF1<0，軸所受的扭矩SKIPIF1<0，抗彎截面系數(shù)求得：SKIPIF1<0SKIPIF1<0所以SKIPIF1<0<SKIPIF1<0此軸2(中間軸)安全。3，對軸3（高速軸）按彎扭組合強度校核:對齒輪1的受力分析：F=SKIPIF1<0SKIPIF1<0=F*sinSKIPIF1<0SKIPIF1<0’=F*SKIPIF1<0SKIPIF1<0=SKIPIF1<0’*sin20=-400NSKIPIF1<0=SKIPIF1<0’*SKIPIF1<0X平面（水平面）：SKIPIF1<0-SKIPIF1<0+SKIPIF1<0=0-SKIPIF1<0*35/2-SKIPIF1<0*63.5+SKIPIF1<0*197=0解得：SKIPIF1<0=254NSKIPIF1<0SKIPIF1<0Y平面（垂直平面）：SKIPIF1<0-SKIPIF1<0+SKIPIF1<0=0-SKIPIF1<0*63.5+SKIPIF1<0*197=0解得：SKIPIF1<0=744NSKIPIF1<0=354NSKIPIF1<0軸1（高速軸）的扭矩圖：SKIPIF1<0根據(jù)x,y平面彎曲圖形則彎曲的的最大值M:M=SKIPIF1<0其危險截面為軸2（中間軸）與齒輪2的結(jié)合面，其抗彎曲截面系數(shù)W為：W=SKIPIF1<0SKIPIF1<0d,為軸的直徑t,為軸上鍵槽的深度b,為鍵的寬度所以按彎扭組合強度校核：SKIPIF1<0SKIPIF1<0SKIPIF1<0,折合系數(shù)SKIPIF1<0SKIPIF1<0，軸所受的扭矩SKIPIF1<0，抗彎截面系數(shù)求得：SKIPIF1<0SKIPIF1<0所以SKIPIF1<0<SKIPIF1<0此軸1(高速軸)安全。其強度能滿足要求。軸承的選擇與校核在設(shè)計軸直徑的時候，就是根據(jù)軸承壽命而定的所以此處不必再進行校核。5、箱體設(shè)計及說明減速器機體結(jié)構(gòu)尺寸設(shè)計(低速級中心距a=155mm） 名稱符號計算公式結(jié)果箱座厚度SKIPIF1<08箱蓋厚度SKIPIF1<0SKIPIF1<08箱蓋凸緣厚度SKIPIF1<0SKIPIF1<012箱座凸緣厚度SKIPIF1<012箱座底凸緣厚度SKIPIF1<0SKIPIF1<020地腳螺釘直徑SKIPIF1<0SKIPIF1<0M18地腳螺釘數(shù)目SKIPIF1<0查手冊4軸承旁聯(lián)結(jié)螺栓直徑SKIPIF1<0SKIPIF1<0M14蓋與座聯(lián)結(jié)螺栓直徑SKIPIF1<0SKIPIF1<0=（0.5～0.6）SKIPIF1<0M10視孔蓋螺釘直徑SKIPIF1<0SKIPIF1<0=（0.3～0.4）SKIPIF1<0M6定位銷直徑SKIPIF1<0SKIPIF1<0=（0.7～0.8）SKIPIF1<0M8SKIPIF1<0，SKIPIF1<0，SKIPIF1<0至外箱壁的距離SKIPIF1<0查手冊表11—2221816SKIPIF1<0，SKIPIF1<0,SKIPIF1<0至凸緣邊緣距離SKIPIF1<0查手冊表11—22014外箱壁至軸承端面距離SKIPIF1<0SKIPIF1<0=SKIPIF1<0+SKIPIF1<0+（5～10）47大齒輪頂圓與內(nèi)箱壁距離SKIPIF1<0SKIPIF1<020齒輪端面與內(nèi)箱壁距離SKIPIF1<0SKIPIF1<0>25箱蓋，箱座肋厚SKIPIF1<0SKIPIF1<0軸承端蓋外徑SKIPIF1<0SKIPIF1<0+（5～5.5）SKIPIF1<082（1軸）87（2軸）108（3軸）軸承旁聯(lián)結(jié)螺栓距離SKIPIF1<0SKIPIF1<082（1軸）87（2軸）108（3軸）6、鍵聯(lián)接的選擇和計算（1）a,低速級的校核兩鍵均采用圓頭普通平鍵與齒輪聯(lián)接處的鍵為SKIPIF1<0查表得6-2查得許用應(yīng)力SKIPIF1<0=100～120Mpa，取其中間值SKIPIF1<0=110Mpa，鍵工作長度L’=L-b=50-14=36mm，鍵與輪轂鍵槽的接觸高度k=0.5h=,得SKIPIF1<0(合格)b,低速級與聯(lián)軸器聯(lián)接處鍵為SKIPIF1<0查表得6-2查得許用應(yīng)力SKIPIF1<0=100～120Mpa，鍵工作長度SKIPIF1<0，鍵與輪轂鍵槽的接觸高度SKIPIF1<0=5mm,得SKIPIF1<0（合格）（2）中間軸鍵校核：兩鍵均采用圓頭普通平鍵與寬齒輪聯(lián)接處鍵為:SKIPIF1<0查表得6-2查得許用應(yīng)力SKIPIF1<0=100～120Mpa，取其中間值SKIPIF1<0=110Mpa，鍵工作長度SKIPIF1<0，鍵與輪轂鍵槽的接觸高度SKIP