機(jī)械設(shè)計(jì)課程設(shè)計(jì)卷?yè)P(yáng)機(jī)傳動(dòng)裝置中的二級(jí)圓柱齒輪減速器

1、 機(jī)械設(shè)計(jì)課程設(shè)計(jì)說(shuō)明書(shū) 設(shè)計(jì)題目 卷?yè)P(yáng)機(jī)傳動(dòng)裝置中的二級(jí)圓柱齒輪減速器 廣東石油化工學(xué)院目 錄一、 設(shè)計(jì)任務(wù)·········································

2、;········51、 設(shè)計(jì)任務(wù)········································

3、83;····52、 運(yùn)動(dòng)簡(jiǎn)圖············································&

4、#183;53、 工作條件·············································54、 原始數(shù)據(jù)·

5、83;···········································5二、 擬定傳動(dòng)方案·····

6、;·······································5三、 電動(dòng)機(jī)的選擇·········&

7、#183;··································51、 選擇電動(dòng)機(jī)的類(lèi)型·············&

8、#183;······················52、 選擇電動(dòng)機(jī)功率·························&#

9、183;············63、 選擇電動(dòng)機(jī)轉(zhuǎn)速···································

10、83;··7四、 總傳動(dòng)比及傳動(dòng)比分配····································71、 計(jì)算總傳動(dòng)比·······

11、83;································72、 各級(jí)傳動(dòng)比分配···············

12、3;······················7五、 傳動(dòng)系統(tǒng)的運(yùn)動(dòng)和動(dòng)力參數(shù)計(jì)算························

13、3;··71、 各軸轉(zhuǎn)速············································72、 各軸輸入功率

14、3;·······································83、 各軸轉(zhuǎn)矩·········&#

15、183;··································84、 數(shù)據(jù)總匯··············

16、······························8六、 傳動(dòng)零件的設(shè)計(jì)計(jì)算··················

17、;···················91、 高速級(jí)之露傳動(dòng)設(shè)計(jì)····························

18、3;·····91.1選定齒輪類(lèi)型、精度等級(jí)、材料及齒數(shù)·····················91.2按齒面接觸強(qiáng)度設(shè)計(jì)··················

19、···················91.3按齒根彎曲疲勞強(qiáng)度計(jì)算····························

20、83;···112、 低速級(jí)齒輪傳動(dòng)設(shè)計(jì)·································122.1選定齒輪類(lèi)型、精度等級(jí)、材料及計(jì)算·······

21、83;············122.2按齒面接觸強(qiáng)度設(shè)計(jì)···································&

22、#183;122.3按齒根彎曲疲勞強(qiáng)度計(jì)算································14七、 軸的設(shè)計(jì)計(jì)算············

23、3;······························151、 中間軸結(jié)構(gòu)尺寸設(shè)計(jì)·················&#

24、183;···············151.1選擇軸的材料································

25、83;·········161.2軸的初步估算······································

26、3;···161.3軸的結(jié)構(gòu)設(shè)計(jì)··········································162、 高速（輸入）軸結(jié)構(gòu)尺寸設(shè)

27、計(jì)·························182.1選擇軸的材料·······················

28、···················182.2軸的初步估算·····························&

29、#183;············182.3軸的結(jié)構(gòu)設(shè)計(jì)···································&#

30、183;······183、 低速（輸出）軸結(jié)構(gòu)尺寸設(shè)計(jì)·························203.1選擇軸的材料·············

31、83;····························203.2軸的初步估算···················

32、3;······················203.3軸的結(jié)構(gòu)設(shè)計(jì)··························

33、;················20八、 滾動(dòng)軸承的校核計(jì)算·······························

34、83;····221、 高速軸滾動(dòng)軸承是校核計(jì)算···························222、 中間軸滾動(dòng)軸承的檢核計(jì)算·············

35、;··············233、 低速軸滾動(dòng)軸承的校核計(jì)算···························24九、 平鍵連接是選用與計(jì)算···

36、83;······························241、 高速軸與聯(lián)軸器的鍵連接選用及計(jì)算················

37、··242、 中間軸與齒輪2的鍵連接選用及計(jì)算··················243、 低速軸與齒輪3的鍵連接選用及計(jì)算··················254、 低速軸與聯(lián)軸器的鍵連接選用及計(jì)算·

38、83;················25十、 聯(lián)軸器的選擇計(jì)算·······························&#

39、183;······251、 高速軸輸入端聯(lián)軸器的選擇··························262、 低速軸輸出端聯(lián)軸器的選擇···········

40、3;··············26十一、 減速器箱體及其附件設(shè)計(jì)·······························261、 箱體設(shè)計(jì)&#

41、183;·········································282、 箱體主要附件作用及形式·····

42、3;······················282.1通氣器··························&#

43、183;····················282.2窺視孔和視孔蓋···························&#

44、183;···········282.3油標(biāo)尺油塞····································

45、3;······282.4油塞··········································

46、83;······292.5定位銷(xiāo)··········································&

47、#183;····292.6啟蓋螺釘···········································

48、3;·292.7起吊裝置·············································29十二、 參考文獻(xiàn)

49、83;············································30設(shè)計(jì)內(nèi)容、計(jì)算級(jí)說(shuō)明設(shè)計(jì)結(jié)果一、設(shè)計(jì)任務(wù)1、設(shè)計(jì)題目卷?yè)P(yáng)機(jī)傳動(dòng)

50、裝置中的二級(jí)圓柱齒輪減速器2、運(yùn)動(dòng)簡(jiǎn)圖3、工作條件單向運(yùn)轉(zhuǎn)，輕微振動(dòng)，連續(xù)工作，兩班制，使用期限5年，卷筒轉(zhuǎn)速容許誤差為5%。4、原始數(shù)據(jù)卷筒圓周力F（N）:4000卷筒直徑D（mm）:350卷筒轉(zhuǎn)速 n (r/min) :45二、擬定傳動(dòng)方案 原動(dòng)機(jī)、傳動(dòng)裝置和工作機(jī)是機(jī)器的三個(gè)組成部分。傳動(dòng)裝置將原動(dòng)機(jī)的動(dòng)力和運(yùn)動(dòng)傳遞給工作機(jī)，合理擬定轉(zhuǎn)動(dòng)方案應(yīng)滿足工作機(jī)的性能要求，適應(yīng)工作條件，工作可靠，而且結(jié)構(gòu)簡(jiǎn)單，尺寸緊湊，成本低，轉(zhuǎn)動(dòng)效率高，操作維護(hù)方便。根據(jù)已知條件，該設(shè)計(jì)采用展開(kāi)式二級(jí)圓柱齒輪減速器。三、電動(dòng)機(jī)的選擇1、選擇電動(dòng)機(jī)的類(lèi)型電動(dòng)機(jī)有交流。直流之分，而一般工廠都采用三相交流電，因而選

51、用交流電動(dòng)機(jī)。交流電動(dòng)機(jī)分異步、同步電動(dòng)機(jī)，異步電動(dòng)機(jī)又分為籠型和繞線型兩種，根據(jù)卷?yè)P(yáng)機(jī)要求選擇應(yīng)用較廣的Y系列自冷式籠型三相異步電動(dòng)機(jī)，電壓為380V，其結(jié)構(gòu)簡(jiǎn)單、起動(dòng)性能好，工作可靠、價(jià)格低廉、維護(hù)方便，適用于不易燃、不易爆、無(wú)腐蝕性氣體、無(wú)特殊要求的場(chǎng)合，如：運(yùn)輸機(jī)、機(jī)床、農(nóng)機(jī)、風(fēng)機(jī)、輕功機(jī)械等2、選擇電動(dòng)機(jī)功率D=350mm=0.35mVw=nD/60=45×3.14×0.35/60=0.824m/s已知 Fw=4000N卷筒所需功率Pw=FwVw/1000KW=4000×0.824/1000=3.296KW 電動(dòng)機(jī)至卷筒之間的總效率：其中分別為聯(lián)軸器、齒

52、輪、軸承、卷筒的效率。此設(shè)計(jì)中一共有兩個(gè)聯(lián)軸器，兩對(duì)嚙合齒輪，3.5對(duì)軸承，一個(gè)卷筒。查機(jī)械設(shè)計(jì)計(jì)算手冊(cè)得：彈性聯(lián)軸器=0.990.995, 取0.998級(jí)精度齒輪傳動(dòng)=0.97， 取0.97一對(duì)滾動(dòng)軸承的效率=0.99，取0.99卷筒效率=0.96， 取0.96=0.992×0.972×0.993.5×0.96=0.855實(shí)際需要的電動(dòng)機(jī)輸出功率： Pd= Pw / =3.296÷0.855=3.85 KW查手冊(cè)選電動(dòng)機(jī)額定功率：Pe=4 KW3、選擇電動(dòng)機(jī)轉(zhuǎn)速查表得兩級(jí)減速器機(jī)構(gòu)的推薦傳比：i=840。電動(dòng)機(jī)轉(zhuǎn)速可選范圍： no=i×n=(

53、840)×45=3601880 r/min電動(dòng)機(jī)同步轉(zhuǎn)速符合要求的有：750r/min，100r/min，1500r/min表一：電動(dòng)機(jī) 型號(hào)額定功率同步轉(zhuǎn)速滿載轉(zhuǎn)速最大轉(zhuǎn)速總傳動(dòng)比Y160M1-847507202.020Y132M1-6410009602.226.67Y112M-4410014402.340從電機(jī)價(jià)格和減速器造價(jià)兩個(gè)方面考慮，選同步轉(zhuǎn)速1000r/min的電動(dòng)機(jī)。即： 選用Y132M1-6三相異步電動(dòng)機(jī)四、總傳動(dòng)比及傳動(dòng)比分配1、 計(jì)算總傳動(dòng)比由表一得Y132M1-6型電動(dòng)機(jī)滿載時(shí)轉(zhuǎn)速: no=960r/min總傳動(dòng)比i= no/n=960÷45=21.3

54、32、各級(jí)傳動(dòng)比分配對(duì)于兩級(jí)展開(kāi)式圓柱齒輪減速器，一般按齒輪墩浸油高度要求，即按各級(jí)大齒輪直徑相近的條件分配傳動(dòng)比，常取i1=(1.31.5)i2。（式中i1、i2分別為減速器高速級(jí)和低速級(jí)的傳動(dòng)比）因?yàn)?總傳動(dòng)比 i=21.33所以 i1=5.47 i2=3.90五、傳動(dòng)系統(tǒng)的運(yùn)動(dòng)和動(dòng)力參數(shù)計(jì)算1、各軸轉(zhuǎn)速電機(jī)軸取滿載轉(zhuǎn)速電機(jī)軸0軸：no=960r/min高速軸軸：n= no=960r/min中間軸軸：n= n/ i1=960÷5.47=175.50r/min低速軸軸：n=n/ i2=175.5÷3.9=45r/min 卷筒軸軸：n=n=45r/min2、各軸輸入功率已知

55、： 電機(jī)軸輸入功率取額定功率 Pe=4 KW0軸：PO=3.85 KW軸：P= PO·=3.85×0.99=3.81KW軸: P= P·=3.81×0.97×0.99=3.66KW軸: P=P·=3.66×0.97×0.99=3.51KW軸: P=P·=3.51×0.99=3.47KW3、 各軸轉(zhuǎn)矩0軸：To=9550×PO/ no=9550×3.85/960=38.30N·m軸：T=9550×P/ n=9550×3.81/960=37.90N&

56、#183;m軸: T=9550×P/ n=9550×3.66/175.50 =199.16N·m軸: T=9550×P/ n=9550×3.51/45=744.90N·m軸: T=9550×P/ n=9550×3.47/45=736.41N·m4、數(shù)據(jù)匯總參數(shù)軸號(hào)電動(dòng)機(jī)軸軸軸軸卷筒軸轉(zhuǎn)速r/min9609601764545功率kw3.853.813.663.513.47轉(zhuǎn)矩N·m38.337.9199.16744.9736.41傳動(dòng)比15.253.741效率0.990.960.960.99六、傳

57、動(dòng)零件的設(shè)計(jì)計(jì)算1、高速級(jí)齒輪傳動(dòng)設(shè)計(jì)1.1選定齒輪類(lèi)型、精度等級(jí)、材料及齒數(shù) 根據(jù)已知條件，選擇直齒圓柱齒輪：卷?yè)P(yáng)機(jī)為一般工作機(jī)，轉(zhuǎn)速不高，選用8級(jí)精度查接卸設(shè)計(jì)計(jì)算手冊(cè)，選擇小齒輪材料為40Cr(調(diào)質(zhì))，硬度為280HBS,大齒輪選擇45鋼（調(diào)質(zhì)），硬度為240HBS.兩者硬度差為40HBS為使齒輪磨損均勻，小齒輪選擇齒數(shù)Z1=24則大齒輪齒數(shù)為Z2= Z1×i1=24×5.47=131.28取 Z2=132，查機(jī)械設(shè)計(jì)教材取齒寬系數(shù)，取標(biāo)準(zhǔn)壓力角此為外嚙合閉式軟齒輪傳動(dòng)，以保證齒輪面接觸強(qiáng)度為主1.2按齒面接觸強(qiáng)度設(shè)計(jì)1.2.1查設(shè)計(jì)手冊(cè)確定計(jì)算公式中各個(gè)數(shù)值由公式計(jì)

58、算試選載荷系數(shù)Kt=1.3小齒輪傳遞轉(zhuǎn)矩T1= T=37900N·mm材料的彈性影響系數(shù)ZE=189.8Mpa0.5節(jié)點(diǎn)區(qū)域系數(shù)ZH=2.5由機(jī)械設(shè)計(jì)教材按齒面硬度差得小齒輪的接觸疲勞強(qiáng)度極限=600MPa；大齒輪的接觸疲勞強(qiáng)度極限=550MPa計(jì)算應(yīng)力循環(huán)次數(shù)：N1=60njLh=60×960×1×(2×8×365×5)=1.68×109 N2=1.68×109/5.47=3.07×108從機(jī)械設(shè)計(jì)教材查得接觸疲勞壽命系數(shù)KHN1=0.90; KHN2=0.95計(jì)算接觸疲勞許用應(yīng)力取失效率1%

59、，安全系數(shù)S=1，得/S=0.9×600=540MPa/S=0.95×550=522.5MPa1.2.2試算小齒輪分度圓直徑中取較小值=48.809mm1.2.3計(jì)算圓周速度1.2.4計(jì)算齒寬=1×48.809mm=48.809mm1.2.5計(jì)算齒寬與齒高比模數(shù) mt=d1t/ Z1=48.809/24=2.034mm齒高 h=2.25 mt=2.25×2.034=4.577mm bt/h=48.089/4.577=10.661.2.6計(jì)算載荷系數(shù)根據(jù)V=2.45m/s，8級(jí)精度，查得動(dòng)載系數(shù)Kv=1.15直齒輪，查表得=1取使用系數(shù)KA=1.25用插值

60、法得8級(jí)精度、小齒輪相對(duì)支承非對(duì)稱布置時(shí) =1.452由 bt/h=10.66，=1.452查圖得=1.38故 載荷系數(shù)：K=1.25×1.15×1×1.452=2.0871.2.7按實(shí)際的載荷系數(shù)校正所算的分度圓直徑d1=48.809×=57.151mm1.2.8計(jì)算模數(shù)m m=d1/z1=57.151/24=2.38mm13按齒根彎曲疲勞強(qiáng)度計(jì)算1.3.1確定公式各值m 查得小齒輪的彎曲疲勞強(qiáng)度極限=500MPa大齒輪的彎曲疲勞強(qiáng)度極限=380MPa大齒輪的彎曲疲勞壽命系數(shù)KFN1=0.87 KFN2=0.90計(jì)算彎曲疲勞許用應(yīng)力由S=1.4 得載荷

61、系數(shù)K=KAKVK=1.25×1.15×1×1.40=2.013齒形系數(shù)查表得 YFa1=2.65 YFa2=2.419應(yīng)力校正系數(shù)查表得 YSa1=1.58 YSa2=1.812計(jì)算大小齒輪的,并比較=2.65×1.58/310.71=0.01348=2.419×1.821/244.29=0.01602很明顯大齒輪的數(shù)值大1.2.3設(shè)計(jì)計(jì)算由于齒輪模數(shù)大小主要取決于彎曲強(qiáng)度所決定的承載能力，可取彎曲強(qiáng)度算得模數(shù)1.62就近圓標(biāo)準(zhǔn)值m=2mm。 Z1=d1/m=57.151/2.00=29 Z2=5.47×29=159 這樣設(shè)計(jì)的齒輪

62、傳動(dòng)，既滿足齒面接觸疲勞強(qiáng)度，又滿足齒根彎曲疲勞強(qiáng)度1.3.3幾何尺寸計(jì)算計(jì)算分度圓直徑d1=m×Z1=2×29=58mmd2=m×Z2=2×159=318mm計(jì)算齒頂圓、齒根圓直徑 ha1=1×m=1×2=2mm hf1=(1+0.25)×m=1.25×2=2.5mm da1=d1+2ha1=58+2×2=62mm df1=d1-2hf1=58-2×2.5=53mm計(jì)算中心距 a=(d1+d2)/=(58+318)/2=188mm計(jì)算齒輪寬度 =1×58=58mm 取 =55mm =

63、60mm2、低速級(jí)齒輪傳動(dòng)設(shè)計(jì)2.1選定齒輪類(lèi)型、精度等級(jí)、材料及齒數(shù)根據(jù)已知條件，選定直齒輪圓柱齒輪：卷?yè)P(yáng)機(jī)為一般工作機(jī)，轉(zhuǎn)速不高，選用選用8級(jí)精度；查機(jī)械設(shè)計(jì)計(jì)算手冊(cè)，選擇小齒輪材料為40Cr（調(diào)質(zhì)），硬度為280HBS,大齒輪選擇45鋼（調(diào)質(zhì)），硬度為240HBS。兩者硬度差為40HBS。為使齒輪磨損均勻，小齒輪選擇齒數(shù)Z3=24，則大齒輪齒數(shù)為Z4=Z1×i21=24×3.9=93.6取 Z4=94木質(zhì)傳動(dòng)為軟齒面的閉式齒輪傳動(dòng)，故接觸疲勞強(qiáng)度設(shè)計(jì)2.2按齒面接觸強(qiáng)度設(shè)計(jì)2.2.1查設(shè)計(jì)手冊(cè)確定計(jì)算公式中各個(gè)數(shù)值由公式計(jì)算試選載荷系數(shù)Kt=1.3小齒輪傳遞轉(zhuǎn)矩T2=

64、 T=199.16N·m材料的彈性影響系數(shù)ZE=189.8Mpa0.5查機(jī)械設(shè)計(jì)教材取齒面系數(shù)，取標(biāo)準(zhǔn)壓力角由機(jī)械設(shè)計(jì)教材按齒面硬度差得小齒輪的接觸疲勞強(qiáng)度極限=600MPa；大齒輪的接觸疲勞強(qiáng)度極限=550MPa計(jì)算應(yīng)力循環(huán)次數(shù)：N3=60n1jLh=60×176×1×(2×8×365×5)=3.08×108N4=3.08×108/3.9=0.97×108從機(jī)械設(shè)計(jì)教材查圖取接觸疲勞壽命細(xì)數(shù)KHN3=0.95；KHN4=0.99計(jì)算接觸疲勞許用應(yīng)力去失效率1%，安全系數(shù)S=1，得2.2.2試算

65、小齒輪分度圓直徑=2.32=79.028mm2.2.3計(jì)算圓周速度2.2.4計(jì)算齒寬79.028=79.028mm2.2.5計(jì)算齒寬與齒高比模數(shù) mt=d3t/Z3=79.028/24=3.29mm齒高 h=2.25mt=2.25×3.29=7.403mm齒高比 bt/ h=79.028/7.403=10.682.2.6計(jì)算載荷系數(shù)根據(jù)V=0.730m/s，8級(jí)精度，查得動(dòng)載荷系數(shù)Kv=1.10直齒輪，查表得取使用系數(shù)KA=1.25用插入法得8級(jí)精度、小齒輪相對(duì)支承非對(duì)稱布置時(shí)由bt/ h=10.68，查得故載荷系數(shù)： =1.25×1.10×1×1.46

66、3=2.012.2.7按實(shí)際的載荷系數(shù)校正所算的分度圓直徑 2.2.8計(jì)算模數(shù) m= d3/Z3=91.4/24=3.81mm2.3按齒根彎曲疲勞強(qiáng)度計(jì)算2.3.1確定公式各值查表得寫(xiě)小齒輪的彎曲疲勞強(qiáng)度極限 大齒輪的彎曲疲勞強(qiáng)度極限 取彎曲疲勞壽命系數(shù)計(jì)算彎曲疲勞許用應(yīng)力S=1.4 查得載荷系數(shù)齒形系數(shù) 查表得應(yīng)力校正系數(shù) 查表得計(jì)算大小齒輪的并加以比較 很明顯大齒輪的數(shù)值大2.3.2設(shè)計(jì)計(jì)算 由于齒輪模數(shù)大小主要取決于彎曲強(qiáng)度所決定的承載能力，可取彎曲強(qiáng)度算得模數(shù)3就近圓整為近似值m=2mm。 這樣設(shè)計(jì)的齒輪傳動(dòng)，既滿足齒面接觸疲勞強(qiáng)度，又滿足齒根彎曲疲勞強(qiáng)度。2.3.3幾何尺寸計(jì)算計(jì)算分

67、度直徑d3=m·Z3=3×31=93mmd4=m·Z4=3×121=363mm計(jì)算齒頂圓、齒根圓直徑 ha3=1×m=1×3=3mm hf3=(1+0.25)×m=1.25×3=3.75mm da3=d3+2·ha3=93+2×3=99mm df3=d3-2·hf3=93-2×3.75=85.5mm計(jì)算中心距 計(jì)算齒輪寬度 取 B3=105mm B4=100mm七、軸的設(shè)計(jì)計(jì)算1、中間軸結(jié)構(gòu)尺寸設(shè)計(jì)在兩級(jí)展開(kāi)式減速器中，三根軸跨距相差不宜過(guò)大，故先進(jìn)行中間軸的設(shè)計(jì)，以確定跨距

68、。1.1選擇軸的材料 因?yàn)橹虚g軸為齒輪軸，應(yīng)與齒輪3的材料一致，故材料為40Cr，調(diào)質(zhì)，查表得1.2軸的初步估算考慮該處軸徑尺寸應(yīng)當(dāng)大于高速級(jí)軸頸處直徑取 1.3軸的結(jié)構(gòu)設(shè)計(jì)根據(jù)軸上零件的定位、裝配及軸的工藝性要求，初步確定出中間軸的結(jié)構(gòu)如下：1.3.1各軸段直徑的確定初選滾動(dòng)軸承，代號(hào)為6208，軸頸直徑齒輪2處軸頭直徑d4=45mm齒輪2定位軸肩高度h=(0.070.1)d4=0.1×45=4.5mm該處直徑d4=54mm齒輪3的直徑：d3=93mm; da3=99mm; df3=85.5mm 查表得軸承安裝尺寸 1.3.2各軸段軸向長(zhǎng)度的確定查表得軸承的寬度齒輪3寬度輪轂寬59

69、mm,為定位可靠，應(yīng)小于輪轂寬23mm,取 =57mm取 1.3.3校核軸的強(qiáng)度軸的轉(zhuǎn)矩 齒輪2： 200=456N齒輪3： =4283×tan200=1559NAB軸承垂直支撐反力：AB軸承水平面支撐反力： 垂直面彎矩 水平面彎矩 合成彎矩C截面合成彎矩： D截面合成彎矩：計(jì)算危險(xiǎn)截面是當(dāng)量彎矩 取折合系數(shù)則當(dāng)量彎矩為 危險(xiǎn)截面處的直徑 所以原設(shè)計(jì)強(qiáng)度足夠2.高速(輸出)軸的結(jié)構(gòu)尺寸設(shè)計(jì)2.1選擇軸的材料 因?yàn)檩斎胼S為齒輪軸，應(yīng)與齒輪1 的材料一致，故材料為40Cr，調(diào)質(zhì)，查表得，2.2軸的初步估算2.3軸的結(jié)構(gòu)設(shè)計(jì) 考慮與電動(dòng)機(jī)軸半聯(lián)軸器相匹配的聯(lián)軸器的孔徑標(biāo)準(zhǔn)尺寸的選用，取2.

70、3.1各軸段直徑的確定由于軸身直徑比強(qiáng)度計(jì)算的值要大許多，考慮軸的緊湊性，其他階梯軸段直徑應(yīng)盡可能以較小值增加，因此軸伸段聯(lián)軸器用套筒軸向定位，與套筒配合的軸段直徑2.3.2各軸段軸向長(zhǎng)度的確定初選滾動(dòng)軸承6207，查表得軸頸直徑，齒輪分度圓直徑 半聯(lián)軸器軸向長(zhǎng)為60mm,取l1為60mm其中為壁厚；為軸承旁聯(lián)螺栓扳手位置尺寸，查表得：e為端蓋凸緣厚度，l3=軸承寬度17mml5=齒輪1 寬度60mm有中間軸設(shè)計(jì)知箱體內(nèi)壁間距離A=195mm,兩軸承軸頸間距2.3.3校核軸的強(qiáng)度 軸的轉(zhuǎn)矩齒輪1： AB軸承垂直面支撐反力： AB軸承水平面支反力： 垂直面彎矩 水平彎矩 合成彎矩 計(jì)算危險(xiǎn)截面的

71、當(dāng)量彎矩 取折合系數(shù) 危險(xiǎn)截面處的直徑 所以原設(shè)計(jì)強(qiáng)度足夠3、低速（輸出）軸的設(shè)計(jì)3.1選擇軸的材料材料選用45#鋼，正火處理，查表得3.2軸的初步估算由于安裝聯(lián)軸器處有鍵，故軸需加大4%5%。則故取該軸的基本軸徑3.3軸的結(jié)構(gòu)設(shè)計(jì)根據(jù)軸上零件的定位、裝配及軸的工藝性要求，初步確定出中間軸的結(jié)構(gòu)如下：3.3.1各軸段直徑的確定初選滾動(dòng)軸承6213根據(jù)油封標(biāo)準(zhǔn)，初選滾動(dòng)軸承6213，查表得軸頸直徑由齒輪尺寸，軸肩高查表得軸承安裝尺寸3.3.2各軸段軸向長(zhǎng)度的確定 半聯(lián)軸器軸向長(zhǎng)為84mm,取為82mm 軸承寬度23mm 輪轂寬102mm-2mm=100mm 軸承寬度23mm+外伸2mm=25mm

72、3.3.3校核軸的強(qiáng)度軸的轉(zhuǎn)矩 齒輪4： AB軸承垂直面支撐反力： AB軸承水平面支撐反力： 垂直面彎矩 水平面彎矩合成彎矩計(jì)算危險(xiǎn)截面的當(dāng)量彎矩取折合系數(shù)則當(dāng)量彎矩為：危險(xiǎn)截面處的直徑：所以原設(shè)計(jì)強(qiáng)度足夠八、滾動(dòng)軸承是校核計(jì)算1、高速軸滾動(dòng)軸承的校核計(jì)算選用的軸承型號(hào)為6207，查表得軸承基本額定壽命 查表得 對(duì)球軸承，壽命指數(shù)軸承A的徑向載荷軸承B的徑向載荷,按軸承B的受力大小計(jì)算要求使用壽命故所選軸承合格2、中間軸滾動(dòng)軸承的校核計(jì)算選用的軸承型號(hào)為6208，軸承基本額定壽命 查表得對(duì)球軸承，壽命指數(shù)軸承A的徑向載荷軸承B的徑向載荷,按計(jì)算要求使用壽命故所選軸承合用。3、 低速軸滾動(dòng)軸承的校核計(jì)算選用的軸承型號(hào)為6213，軸承基本額定壽命 查表得 對(duì)球軸承，壽命指數(shù) 軸承A的徑向載荷 軸承B的徑向載荷 ,按計(jì)算 要求使用壽命 故所選軸承合用。九、平鍵連接的選用與計(jì)算1、高速軸與聯(lián)軸器的鍵連接選用及計(jì)算由前面軸的設(shè)計(jì)已知本處軸徑查表選擇：鍵10×8×50GB/T 1096-2003鍵的接觸長(zhǎng)度接觸長(zhǎng)度查表得許用擠壓應(yīng)力鍵連接的強(qiáng)度足夠。2、中間軸與齒輪2的鍵連接選用及計(jì)算由前面軸的設(shè)計(jì)已知本處軸徑查表選擇：鍵14×9×45×GB/T 1096-2003鍵的接觸長(zhǎng)度，接觸長(zhǎng)度查表得許