基于奧拓的汽車轉(zhuǎn)向系統(tǒng)設(shè)計(jì)（含CAD圖紙）

基于奧拓的汽車轉(zhuǎn)向系統(tǒng)設(shè)計(jì)（含CAD圖紙）,基于,汽車,轉(zhuǎn)向,系統(tǒng),設(shè)計(jì),CAD,圖紙 序序號(hào)號(hào)代代號(hào)號(hào)定定義義公公式式/出出處處一一已已知知1前輪距2L汽車軸距3RminRmin最小轉(zhuǎn)彎半徑4輪胎與地面的滑動(dòng)摩擦因素5轉(zhuǎn)向軸負(fù)荷（前輪）6P輪胎氣壓7B主銷中心距8主銷傾角9Dsw轉(zhuǎn)向盤直徑10輪胎規(guī)格10Mh轉(zhuǎn)向盤上的力矩GB7258-2017、Mh=250Dsw二二計(jì)計(jì)算算11rrrr車輪滾動(dòng)半徑11K K主銷延長(zhǎng)線與地面交點(diǎn)的距離12梯形底角13L1L1梯形臂長(zhǎng)度0.11K-0.15K11主銷偏移距12外轉(zhuǎn)角13內(nèi)轉(zhuǎn)角14轉(zhuǎn)向阻力矩13轉(zhuǎn)向力傳動(dòng)比14角傳動(dòng)比2/)(1KB 1Bmin)/arcsin0RL（0)/cot(cot0iLKarcif1G%608.912651G2131)/(*3/PGfMr/*MhDswMrippiDswiipw/200wiMrtan2rrBKKLrc34tana結(jié)結(jié)果果單單位位1405mm2360mm4500mm0.77438.2N210KPa1200mm6度380mm155/65R1495N.m278.55mm1258.55mm72度160mm73.225mm32度32度326639.6603N.mm12.77序序號(hào)號(hào)代代號(hào)號(hào)定定義義公公式式/出出處處一一已已知知1Lz齒條行程2齒輪齒數(shù)3齒輪法向模數(shù)4齒輪螺旋角5齒輪法相壓力角6齒輪齒頂高系數(shù)7齒輪變位系數(shù)8齒輪頂隙系數(shù)9L齒條總長(zhǎng)10螺旋角11齒條直徑12齒條齒數(shù)13齒條法向模數(shù)14齒條法向壓力角15齒條齒頂高系數(shù)16齒條變位系數(shù)17齒條頂隙系數(shù)二二齒齒輪輪計(jì)計(jì)算算18端面模數(shù)19端面分度圓壓力角20端面齒頂高系數(shù)21端面徑向間隙系數(shù)22當(dāng)量齒數(shù)23分度圓直徑24齒頂圓直徑25齒根圓直徑26斷面齒頂圓壓力角27重合度tmcos/ntmm 1d1112aahdd1ad1112ffhdd1fd結(jié)結(jié)果果單單位位189mm10215度20度100.25700mm15度28mm30220度100.252.07mm20.64度0.970.24度1120.7mm24.84mm16.56mm41度0.444序序號(hào)號(hào)代代號(hào)號(hào)定定義義一一已已知知1最小接觸強(qiáng)度應(yīng)力2接觸強(qiáng)度的最小安全系數(shù)3接觸強(qiáng)度計(jì)算的壽命系數(shù)4彈性系數(shù)5區(qū)域系數(shù)6重合度系數(shù)7螺旋角系數(shù)8使用系數(shù)9動(dòng)載荷系數(shù)10齒間載荷分配系數(shù)11試驗(yàn)齒輪的彎曲疲勞極限12彎曲計(jì)算的壽命系數(shù)13試驗(yàn)齒輪的應(yīng)力修正系數(shù)14彎曲強(qiáng)度的最小安全系數(shù)15齒形系數(shù)16應(yīng)力修正系數(shù)17重合度系數(shù)二二計(jì)計(jì)算算18齒輪齒面的接觸許用強(qiáng)度應(yīng)力19實(shí)際接觸強(qiáng)度應(yīng)力20齒向載荷分布系數(shù)21輪齒的彎曲疲勞強(qiáng)度許用應(yīng)力22實(shí)際承受彎曲應(yīng)力三三結(jié)結(jié)論論2324HlimHminHSNZHEZHZZZAKvKaKKHHFlimNYSTYminFSFFFaYSaYYFF公公式式/出出處處結(jié)結(jié)果果單單位位GB/T3480-20081300MPaGB/T3480-20081.1GB/T3480-20081.3GB/T3480-2008189.8GB/T3480-20082.2GB/T3480-20080.77GB/T3480-20080.98GB/T3480-20081.5GB/T3480-20081.1GB/T3480-20081.15GB/T3480-2008620MPaGB/T3480-20081.5GB/T3480-20081GB/T3480-20081.1GB/T3480-20082.1GB/T3480-20081.8GB/T3480-20080.71536.4MPa48.2MPa2.277845.5MPa102.3MPa滿足要求滿足要求minlimH/HNHSZudbuKT*12000Z*Z*Z*Z211HEH）（KKKKKKaVA2.1minlim/FXNFFSYYa21d21Z/cos2000YYYYKTSaFaF序序號(hào)號(hào)代代號(hào)號(hào)定定義義公公式式/出出處處結(jié)結(jié)果果一一已已知知1抗拉強(qiáng)度8002屈服強(qiáng)度4803安全系數(shù)14沖擊載荷1二二計(jì)計(jì)算算5128bsHsS5.1/5.2/HS單單位位MPaMPaMPa序序號(hào)號(hào)代代號(hào)號(hào)定定義義公公式式/出出處處結(jié)結(jié)果果一一已已知知1轉(zhuǎn)向節(jié)臂長(zhǎng)1602彎矩326.63轉(zhuǎn)向力1.6334許用應(yīng)力196二二計(jì)計(jì)算算5轉(zhuǎn)向節(jié)臂最小半徑18三三結(jié)結(jié)論論6轉(zhuǎn)向節(jié)臂最小半徑處應(yīng)大于18mm4L/32/max3MdW4max4/FLMLMFr、FrM4/LMFrd單單位位mmN.mNMPamm序序號(hào)號(hào)代代號(hào)號(hào)定定義義公公式式/出出處處一一已已知知1橫拉桿與轉(zhuǎn)向器連接螺栓中心到轉(zhuǎn)向器殼體軸線與轉(zhuǎn)向節(jié)臂交點(diǎn)處距離2轉(zhuǎn)向器殼體軸線與轉(zhuǎn)向節(jié)臂交點(diǎn)到橫拉桿與轉(zhuǎn)向節(jié)臂連接球頭銷中心距離3轉(zhuǎn)向力4轉(zhuǎn)向阻力矩5許用應(yīng)力6桿的剛度儲(chǔ)備系數(shù)7F桿承受的軸向力8E拉伸時(shí)桿材料的彈性模量二二計(jì)計(jì)算算910慣性矩11三三結(jié)結(jié)論論12斷面直徑取18mm，厚度為4mm時(shí)合適oLaLFrM168)4(h2h2hRRRA hrRRM/)168/(hR64/64/44dDJJ22/aLEJnFn結(jié)結(jié)果果單單位位400mm120mm1.633N326.6N.m196MPa1.5-2.5406.1N200000MPa9mm4659.76N.m(609.151015.25)245.53