搓絲機(jī)傳動(dòng)裝置課程設(shè)計(jì)

1、京航寶就文太孚UNIVERSITY機(jī)械設(shè)計(jì)基礎(chǔ)課程設(shè)計(jì)說(shuō)明書(shū)設(shè)計(jì)題目：搓絲機(jī)傳動(dòng)裝置 四系120417班設(shè)計(jì)者：笑嘻嘻指導(dǎo)老師：土之株日期：2011-6目錄目錄1前言3軸眼搓絲機(jī)傳動(dòng)裝置地設(shè)計(jì)4一課程設(shè)計(jì)題目41搓絲機(jī)傳動(dòng)裝置設(shè)計(jì)42原始技術(shù)數(shù)據(jù)5二擬定傳動(dòng)方案6三傳動(dòng)裝置設(shè)計(jì)71機(jī)構(gòu)初步設(shè)計(jì)72設(shè)計(jì)參數(shù)8四帶傳動(dòng)主要參數(shù)及幾何尺寸計(jì)算10五齒輪傳動(dòng)設(shè)計(jì)計(jì)算121低速級(jí)122高速級(jí)15六軸地設(shè)計(jì)與校核191初估軸徑192軸強(qiáng)度校核191高速軸192中間軸223低速軸24七軸承地選擇與校核261輸入軸承6203262中間軸軸承6209263輸出軸軸承621627八鍵地選擇與校核27九減速器箱體各

2、部分結(jié)構(gòu)尺寸29十潤(rùn)滑及密封形式選擇301二級(jí)減速齒輪地潤(rùn)滑302滾動(dòng)軸承地潤(rùn)滑303密封形式地選擇30十一其他技術(shù)說(shuō)明31十二參考文獻(xiàn)31前言搓絲機(jī)用于加工軸輻螺紋，上搓絲板安裝在機(jī)頭上，下搓絲板安裝在 滑塊上.加工時(shí)，下挫絲板隨著滑塊作往復(fù)運(yùn)動(dòng).在起始（前端）位置時(shí)，送 料裝置將工件送入上、下搓絲板之間，滑塊向后運(yùn)動(dòng)時(shí)，工件在上、下搓 絲板之間滾動(dòng)，搓制出與搓絲板一致地螺紋.搓絲板共兩對(duì)，可同時(shí)搓制出 工件兩端地螺紋.滑塊往復(fù)運(yùn)動(dòng)一次，加工一個(gè)工件.本課程設(shè)計(jì)地要求是設(shè)計(jì)一套搓絲機(jī)傳動(dòng)裝置，配以適當(dāng)?shù)仉妱?dòng)機(jī)等 零部件，實(shí)現(xiàn)自措置螺紋地功能,要求使用期限是雙班制10年大修期為3 年，電機(jī)單向

3、運(yùn)轉(zhuǎn)，載荷比較平穩(wěn).我感覺(jué)自己地收獲還是相當(dāng)大地，從最初地方案簡(jiǎn)圖，到A0地大圖 （我立起來(lái)畫(huà)草圖時(shí)要用1:1就用兩張方格紙拼接了一下），再到最后地 CAD制圖，我花了很大地精力，也力圖使自己所設(shè)計(jì)地圖盡善盡美，同時(shí) 感謝老師地指導(dǎo)，讓我們逐漸學(xué)會(huì)了機(jī)械設(shè)計(jì)地基本方法，從一個(gè)完完全 全地外行人一點(diǎn)點(diǎn)向內(nèi)行邁進(jìn)，為未來(lái)地自主設(shè)計(jì)能力地鍛煉打下了堅(jiān)實(shí) 地基礎(chǔ).軸輻搓絲機(jī)傳動(dòng)裝置地設(shè)計(jì)-課程設(shè)計(jì)題目1搓絲機(jī)傳動(dòng)裝置設(shè)計(jì)QA1電動(dòng)機(jī)2傳動(dòng)裝置3床身4搓絲機(jī)1、設(shè)計(jì)要求（1）搓絲機(jī)用于加工軸輻螺紋，基本結(jié)構(gòu)如上圖所示，上搓絲板安裝在機(jī) 頭4上，下搓絲板安裝在滑塊3上.加工時(shí)，下挫絲板隨著滑塊作往復(fù)運(yùn)動(dòng).

4、 在起始（前端）位置時(shí)，送料裝置將工件送入上、下搓絲板之間，滑塊向 后運(yùn)動(dòng)時(shí)，工件在上、下搓絲板之間滾動(dòng)，搓制出與搓絲板一致地螺紋.搓 絲板共兩對(duì)，可同時(shí)搓制出工件兩端地螺紋.滑塊往復(fù)運(yùn)動(dòng)一次，加工一個(gè) 工件.（2）室內(nèi)工作，動(dòng)力源為三相交流電動(dòng)機(jī)，電動(dòng)機(jī)單向運(yùn)轉(zhuǎn)，載荷較平.（3）動(dòng)力源為三相交流380/220V,電動(dòng)機(jī)單向運(yùn)轉(zhuǎn)，載荷較平穩(wěn),（4）使用 期限為十年，每年工作300天；大修周期為三年.（5）專(zhuān)用機(jī)械廠制造，可加工7、8級(jí)精度地齒輪、蝸輪.2原始技術(shù)數(shù)據(jù)最 大加工 直徑/m m最大加 工長(zhǎng)度 /mm滑塊行 程 /mm搓絲動(dòng) 力 /kN生產(chǎn)率 /（件/min）816030032084

5、03設(shè)計(jì)任務(wù)1）完成搓絲機(jī)傳動(dòng)裝置總體方案地設(shè)計(jì)與論證，繪制總體設(shè)計(jì)原 理方案圖；2）完成主要傳動(dòng)裝置地結(jié)構(gòu)設(shè)計(jì)；3）完成裝配圖一張（A1），零件圖兩張（A3）；4）編寫(xiě)設(shè)計(jì)說(shuō)明書(shū).二擬定傳動(dòng)方案根據(jù)系統(tǒng)要求可知：滑塊每分鐘要往復(fù)運(yùn)動(dòng)40次，所以機(jī)構(gòu)系統(tǒng)地原動(dòng)件地轉(zhuǎn)速應(yīng)為 40r/min,以電動(dòng)機(jī)作為原動(dòng)機(jī)，則需要機(jī)構(gòu)系統(tǒng)有減速功能,運(yùn)動(dòng)形式為連 續(xù)轉(zhuǎn)動(dòng)9往復(fù)直線運(yùn)動(dòng).根據(jù)上述要求，有以下方案，在方案中齒輪1、2可 看作傳動(dòng)部分地最后一級(jí)齒輪.B方案中采用了曲柄滑塊機(jī)構(gòu)，曲柄長(zhǎng)度僅為滑塊行程地一半，故機(jī)構(gòu) 尺寸較小，結(jié)構(gòu)簡(jiǎn)潔,利用曲柄和連桿共線，滑塊處于極限位置時(shí)，可得到 瞬時(shí)停歇地功能.同時(shí)

6、該機(jī)構(gòu)能承受較大地載荷.應(yīng)當(dāng)選擇曲柄滑塊機(jī)構(gòu)實(shí)現(xiàn) 運(yùn)動(dòng)規(guī)律.整個(gè)搓絲機(jī)由電動(dòng)機(jī)、帶傳動(dòng)、二級(jí)減速器、曲柄滑塊機(jī)構(gòu)、最 終執(zhí)行機(jī)構(gòu)組成.三傳動(dòng)裝置設(shè)計(jì)1機(jī)構(gòu)初步設(shè)計(jì)取曲柄長(zhǎng)度為130mm,連桿長(zhǎng)度為400mm,取連桿行程300mm.計(jì)算 如下：最小傳動(dòng)角：rmin = arccos = 43.82° > 40° b急回特性：K = -= 1.221.2,1,5P2滿(mǎn)足要求.2設(shè)計(jì)參數(shù)（1）工作機(jī)輸出功率計(jì)算：已知水平搓絲力大小為8KN,生產(chǎn)率為40件/min,根據(jù)adams仿真知滑塊 最大速度0.7578m/s.則滑塊功率為Ph = & = 8 x 0,7578

7、 kw = 6.06kw系統(tǒng)總效率為n總=0.97 x 0.96 x 0.99 = 0.923電動(dòng)機(jī)所需實(shí)際功率為Pd =P輸出n總6.060.923=6.57KW要求Ped略大于Pd,則選用Y系列電動(dòng)機(jī)，額定功率7.5KW(2 )工作機(jī)轉(zhuǎn)速40r/min傳動(dòng)比范圍：V 型帶：ii=24；減速器：i2=840?？倐鲃?dòng)比 i= ilxi2=16160電動(dòng)機(jī)轉(zhuǎn)速可選范圍為：nd=ixn w=6406400r/min可知電動(dòng)機(jī)應(yīng)選三相異步電動(dòng)機(jī)，380v.查表6-164得：型號(hào)同步轉(zhuǎn)速滿(mǎn)載轉(zhuǎn)速功率Y160M-6lOOOr/min970r/min7.5kw(3)總傳動(dòng)比 i二%n/7%=970ao=2

8、4.25初步取帶輪效率為2,則減速器傳動(dòng)比為12.12Wii = (1.3-1.4) i2取兩級(jí)圓柱齒輪減速器高速級(jí)傳動(dòng)比ii = 4低速級(jí)傳動(dòng)比 i2 = 3.03(4)各軸轉(zhuǎn)速n0 = nm = 970r/minDjl = no/ii = 485r/minn2 = iii/ii = 160 r/minn3 = n2/ i2 40r/min(5)各軸輸入功率Po = Pd = 7.5KWPi = Pd x n 帶=6.2 x 0.96 = 7.2KWB = PX nx = 7.056KWp3 = p2 x q 2 = 6.912KW（6）各軸輸入轉(zhuǎn)矩電動(dòng)機(jī)所需實(shí)際轉(zhuǎn)矩及電動(dòng)機(jī)地輸出轉(zhuǎn)矩為T(mén)i

9、 = 9550Pi/ni = 141.8N - m T2 = 9550 P2 /n2 = 421.155N -mT3 = 9550 B/n? = 1650N , m軸輸入功 率輸出功 率轉(zhuǎn)矩轉(zhuǎn)速傳動(dòng)比效率電機(jī)軸7.5KW970r/min高速軸5.952KW141.8Nm485r/min20.96中間軸5.716KW421.155Nm160r/min40.98低速軸5.489KW1650Nm40r/min3.030.98（7）根據(jù)結(jié)構(gòu)尺寸要求作圖如下帶傳動(dòng)主要參數(shù)及幾何尺寸計(jì)算計(jì)算工程計(jì)算內(nèi)容計(jì)算結(jié)果確定計(jì)算功率由公式旦=膜P = 1.3 x 7.5KwkA = 1.3Pc = 9.75Kw選取

10、帶型查機(jī)械設(shè)計(jì)書(shū)得選用B帶選取小帶輪直徑查表4-15得ddl = 132771771大帶輪直徑= i X ddldd2 = 264mm小帶輪帶速= 7rddii/60 x 1000匕=6.Sm/s初選中心距劭。.55(1 + dd2) <a0< 2® + dd2)0214.5nun < a0 < 786mm初選 a。= 500mm帶初步基準(zhǔn)長(zhǎng)度 Ld，71 r、Ld = 2ao + 彳 Sdi + dd2)(ddl + dd2)24Ld = 1630/71771帶基準(zhǔn)長(zhǎng)度由表31-2Ld = 2000mm實(shí)際中心距山-匕)Q * QO +Jamin = a0

11、0.015Ld = 474mm amax = a0 + 0.03Ld = 548 mm選取 a = 500mm小帶輪包角% = 180° - 20“ 180°- ddl dd2 ax 57.3°% = 165 > 120°適宜查機(jī)械設(shè)計(jì)書(shū)得：?jiǎn)胃鶐Щ绢~定功Po = 2.13KwAPo = 0.13Kw帶地根數(shù)率P0基本額定功率增量分 包角系數(shù)七長(zhǎng)度系數(shù)比z = PC/（PQ + APo）kakLka = 0.98 kL = 1.03z = 4.534取z=5帶地壓軸力查表得：取Pi = 0.10初壓力：瓦=500 (- 1) +。儼UN 八 a/

12、Pq = 2zF()sii 號(hào)Fo = 241.80NFq = 2397N材料選取鑄鐵五齒輪傳動(dòng)設(shè)計(jì)計(jì)算計(jì)算工程計(jì)算內(nèi)容計(jì)算結(jié)果材料選取齒輪都使用45鋼，調(diào)質(zhì)處理，硬度229286HB平均硬度240HB；精度等級(jí)均為8級(jí)，閉式軟齒面.有關(guān)數(shù)據(jù)以及公式 引自機(jī)械設(shè)計(jì)基 礎(chǔ)（下冊(cè)）1低速級(jí)計(jì)算工程|計(jì)算內(nèi)容計(jì)算結(jié)果（1）初步計(jì)算轉(zhuǎn)矩AT1 = 539N -m齒寬系數(shù)上%=。8接觸疲勞極限。HHm查表得0HHm1 = 710MPa 0Hlim2 = 580Mp CL需用接觸應(yīng)力計(jì)算0HpaHPl = °9bHliml 0 Hp2 = °9OHlim2aHP1 = 639MPa 6

13、rHp2 = 522MPaAd由表Bl,估計(jì)夕土11°Ad = 766動(dòng)載荷系數(shù)KK= 1.4初步計(jì)算小 齒輪直徑由3=766 x 3KT】i + 1八=130.847H7H取 di = 1307H7HWdM i11.4 x 539 3.5 + 11.2 x 5222 3.5初步齒寬bb = 3 ddi=104.67mmb = 104/71771（2）校核計(jì)算圓周速度7rdi% v =60 x 1000v = 0.88ni/s精度等級(jí)選取8級(jí)精度8級(jí)精度齒數(shù)z取 Zi = 45z2 iz1 136 + 由于Z1，Z2互質(zhì)取Zi = 44 z2 = 133模數(shù)叫=di/zi 查表取標(biāo)準(zhǔn)

14、值確定齒數(shù)Z1 = d1/mtz2 = izrQm九p = arccos 叫 d2 = mtz2mt = 3.068mm d2 = 408.044mm = 3p= 12.551005°使用系數(shù)必查表2-7得Ka = 1.25動(dòng)載系數(shù)Kp查表2-6得Kv = 1.05齒間載荷分 配系數(shù)首先求解Ft = 2 TJd 年1 117.4 > 100N/mm非硬齒面斜齒輪，8級(jí)精度Ft = 7985/V= 1.0齒向載荷分 配系數(shù)K耶= A + B (o.6) + 1) + C10-3K耶=1.38區(qū)域系數(shù)Z”查表得ZH = 2.5彈性系數(shù)為查表得ZE = 189.8，MPa重合度系數(shù)

15、Ze查表得/tan a 叫牝=tan cos p ) t % atl -COS 1 dal同理at = 22.91°aatl = 22.17°aat2 = 22.091°由于無(wú)變位，端面嚙合角.at = at1% = 2i(tanaatl - tana；) + z2(tanaat2 tan at) b sin 8% 兀g“JIatr = 20.525°ea = 1.73 1.73 > 1 z£ 0.76螺旋角系數(shù) Zb2 = Jcos/?Zp = 0.99許用接觸應(yīng) 力查2-17表取最小安全系數(shù) 總工作時(shí)間打= 3 x 300 x8 盈利

16、循環(huán)次數(shù)NL1 = 60y%單向運(yùn)轉(zhuǎn)丫 = 1M2 = Mi/i表2-27取接觸壽命系數(shù)Znt齒面工作硬化系數(shù)Zw 接觸強(qiáng)度尺寸系數(shù)及 潤(rùn)滑油膜影響系數(shù)取值0 HlimZntZlZpZrZwZx°HPQJHlimS“m = l.05 th 7200/iNL1 = 4.555 x 107NL2 = 1.035 x 107Znti 116 Zn72 = l.20Zwi = Zw2 = 1,14 Zxi = ZX2 = 1.0 ZL1 = ZL2 = l,0 Zri = ZR2 = l.0 Zyi = Zy2 = I。 (7Hpi = 894Mpq0Hp2 = 756MPa驗(yàn)算"

17、h ZhZeZ/b、Ft u + 1 KAKvKHpKHaaH=525.79MPa（3）確定主要傳動(dòng)尺寸中心距a (di + d2)/2 = 271378mm取整 q = 272mm螺旋角c_1血九(Z1 +Z2)p = cos 1Q2aP = 12.551005°端面模數(shù)mt = mn/ cos Pmt = 3.0734分度圓直徑d = mnz/cosP由=135.232mm d2 = 408.768 rnm齒寬b = 98771771（4）齒根彎曲疲勞強(qiáng)度驗(yàn)算齒形系數(shù)匕。由當(dāng)量齒寬查圖取值= 2.2 YFa2 = 2.17應(yīng)力修正系 數(shù)由圖取值Kai = 1.78 匕 a2 =

18、1.82螺旋角系數(shù) 監(jiān)由圖取值修=0.87齒向載荷分 配系數(shù)b/h = 104/(3 x 2,25) = 15.4 由圖2-9取值K“ = 1.28許用彎曲應(yīng) 力由圖2-30取實(shí)驗(yàn)齒輪地齒根彎曲疲 勞極限。Flim由表2-17取最小安全系數(shù)由表233確定尺寸系數(shù)K由圖2-32確定彎曲壽命家數(shù)4r另外取值如右OFlim%TKTrelT 為 re】T為°FP .$JFlbnaFliml = 300N/mm2 Siim2 = 270N/mm2 Fmin = 125 友=匕2 = L0 VTI = 0.93 丫皿=0.99匕 ri =匕 T2 = 2 VrelTl = iVrelT2=1.0

19、RrelTl = RrelT2 =1.0(JFpi = 670MPa (jFP2 = 535MPq驗(yàn)算FtM = KAKvKFaKYFaYSaY£Y- bmnaF1 = 304MPq aF2 = 298MPa（5）齒輪主要傳動(dòng)尺寸列表壓力角a（即）經(jīng)驗(yàn)值20°螺旋角S計(jì)算結(jié)論12,551005°分度圓直徑d計(jì)算結(jié)論dY = 135.2317H7H d2 = 408.7687nm齒頂高七h(yuǎn)a = hamha = 3mm齒根高斗hf = hjmhf = 3.7 5mm齒頂間隙CC = 0.25mC =,075mm中心距Qa =(八 + dz)/2a = 272mm2高

20、速級(jí)計(jì)算工程|計(jì)算內(nèi)容計(jì)算結(jié)果（1）初步計(jì) 算轉(zhuǎn)矩TiTi = 137,52Nm齒寬系數(shù)以查表得Wd = 1.2接觸疲勞極限°Hlim查表得aHliml _ 710MPa 0 Hlim2 = 580MPQ需用接觸應(yīng)力計(jì)算的P0Hpi = 0.9<7Hiiml°HP2 = °90Hlim2cthpi = 639MPa 0 Hp2 = 522MPaAd由表Bl,估計(jì)夕a 11。Ad = 756動(dòng)載荷系數(shù)KK= 1.4初步計(jì)算小齒輪直徑小,31K7 i + 1di > Ad2_3 h4 x 117.12 5.32 + 1756 * J 1.2 x 52225

21、.32.=70.23mm取乙=70/nm初步齒寬bb = Wddib = 84771771（2 ）校核計(jì) 算圓周速度兀di% v =60 x 1000v = 1.84m/s精度等級(jí)選取8級(jí)精度8級(jí)精度齒數(shù)z取 Zi = 23z2 = iz1 = 92由于Z,Z2互質(zhì)取Zi = 23 z2 = 91模數(shù)mt = d1/z1 查表取標(biāo)準(zhǔn)值 確定齒數(shù)Zi = djmtZ2 = izimnB = arccos 恤mt = 3.044mm d2 = 277.004mm取 7nzi = 3p = 10,6549°使用系數(shù)（查表得Ka = 1.25動(dòng)載系數(shù)跖查表得Kv = 1.15齒間載荷分配 系

22、數(shù)首先求解氏=27/KAFt號(hào)=60.88 < 100N/nunFt = 3653非硬齒面斜齒輪，8級(jí)精度KhL 1.35齒向載荷分配 系數(shù)k“b= A + B (:嗚川 IO-3l+CK耶=1.37區(qū)域系數(shù)Z”查表得ZH = 2.5彈性系數(shù)Ze查表得ZE = 189.8 VMP重合度系數(shù)4查表得/tan ar= tan 1-cosp Jatl = COS dal同理由于無(wú)變位，端面嚙合角at = at1“ =-zi(tanaati - tana；)+ z2(tan aat2tan at)b sin B 印Yat = 29.53°aatl = 25.88° aat2

23、= 22.563° atf = 20.211°8a = 1.73Ep = 1.11 > 1 z£ 0.77螺旋角系數(shù)ZeZp = y/COS P= 1許用接觸應(yīng)力查表取最小安全系數(shù)Smim 總工作時(shí)間或= 3 x 300 x8 盈利循環(huán)次數(shù)N1A = 60yn必單向運(yùn)轉(zhuǎn)丫 = 1M2 = %i/i取接觸壽命系數(shù)Znt齒面工作硬化系數(shù)Zw接觸強(qiáng)度尺寸系數(shù)Zx 潤(rùn)滑油膜影響系數(shù)取值0HlimZntZlZi/ZrZwZx°HP HlhnSulim = L05 th = 7200/1NL1 = 4.555 x 107NL2 = 1.139 x 107Z/v

24、ri = l.06 NT2 = 117Zwi = Zw2 = 1.14 Zxi = ZX2 = 1.0 Zli = Zlz = 10 Zri = Zr2 = l.0 ZV1 = ZV2 = 1.0 (Jhpi = 817MPq(Jhp 2 = 736Mpq驗(yàn)算07y = 615Mpa瓦 + 1ZhZnNr KaKyKhrKhci bd （3）確定主 要傳動(dòng)尺寸中心距a =（乙 + d2）/2 = 171.5m?n取整 a = 172mm螺旋角c-17Mn（21 + Z2）p = cosQ2aP = 10,6549°端面模數(shù)mt = mn/ cos/?mt = 3.0526分度圓直徑d

25、 = mnz/cos（idr = 70.210mzn d2 277.790/71771齒寬b = 84mm（4）齒根彎 曲疲勞強(qiáng)度驗(yàn) 算齒形系數(shù)左。由當(dāng)量齒寬查圖取值=2.65YFa2 = 2.38應(yīng)力修正系數(shù)由圖取值Ysai = 1.59Ysa2 = 168螺旋角系數(shù)/由圖取值Yp = 0.87齒向載荷分配 系數(shù)b/h = 84/（3 x 2.25） = 12.44 由圖279取值KFp = 1.38許用彎曲應(yīng)力由圖27-30取實(shí)驗(yàn)齒輪地齒根彎曲疲 勞極限41im由表27-17取最小安全系數(shù)“向九由表2733確定尺寸系數(shù)匕，由圖27-32確定彎曲壽命系數(shù)匕另外取值如右°Flim j

26、 rKTrelT 均 relT&°FP$JFlim°Fiimi = 300/V/mm2 0FHm2 - 270N/iJFmin = 125 %L = Yx2 = I，。Ynti = 0.89Ynt2 = 0.93 STl = ST2 = 2 iVrelTl = iVrelT2 =1.0RrelTl = yRrelT2 =1.0aFP1 = 427MPq aFP2 = 401MPq驗(yàn)算% = KAKvKFaKFYFaYSaY 皋 DlmnaF1 = 130.9MPq ap2 125.9MP。（5 ）齒輪主要傳動(dòng)尺寸列 表壓力角a(a)20°螺旋角?8

27、6;38z分度圓直徑dd = 70.2107HTH d2 = 277.79mm齒頂高h(yuǎn)a = %"mha = 3 mm齒根高為hf = hfmhf = 3.75mm齒頂間隙CC = 0.25mC = 0.75mm中心距Qa = a + 4)/2a = 172mm六軸地設(shè)計(jì)與校核1初估軸徑電機(jī)軸d0 > C/Pq/tiq = 20.092mm取 do。= 24mm高速軸ci】> CJP1/n1 = 27.034mm取 dll = 30/71771中間軸d2 > CjP2/n2 - 42.627mm取 22 = 45nlm低速軸d3 > C/P3/n3 = 61.

28、278TTim取 d? = 65mm2軸強(qiáng)度校核1高速軸齒輪上地作用力轉(zhuǎn)矩Ti = 9550P"%7 = 141.77/V-m圓周力 徑向力 軸向力Ft = 2TJd Fr = Ftx tan an/cos /?Fa = Ft x tan /?Ft = 4051NFr = 1500/VFa = 736/V支反力YZ平面&» + av = FtFbv x 65 = Fy x 171Fav = 903.48/VFbv = 3147.3/V MV1 = 228.157NmXZ平面Fbh + Fah = FrFbh x 65 + 凡 x 35 = Fah x 171Fah

29、= 561/VPbh = "31N MH1 =47.119Nm MH2 =93.504N7幾介成L矩Mc2 = J"/ + MH22MC1 = 228.192/V mMc2 = 359.550Nm轉(zhuǎn)矩7 = 141,77N -m當(dāng)量彎矩a =維=0.579（脈動(dòng)）kobl 95Meci= Jm 窘 + （a7）2Mec2 = JM4 + （叫/a = 0.58Mecl = 252N mMec2 = 374.7/V m校核a,lb = 75MPa _ M82 _ M2 限一 Wc 0,ld3abc = 41MPa<-ib軸初步設(shè)計(jì)圖:垂直面受力圖:彎矩圖:rrTTrnT

30、T I IITTTTtttttt合成彎矩圖:當(dāng)量彎矩圖:2中間軸高速級(jí)大齒輪齒輪上地作用力轉(zhuǎn)矩T2 = 9550P2/ 幾 27； = 555,75Nm圓周力Ft = 2 T2/d2Fn = 4051/V徑向力Fr = Ft x tan an/cos 0Frl = 1500JV軸向力Fa = Ft x tan/?Fai= 762N低速級(jí)小齒輪齒輪上地作用力轉(zhuǎn)矩T2 = 9550P2/©T2 = 555.75Nm圓周力Ft = 2 T2/d2Ft2 = 8007N徑向力Fr = Ft x tan an/cos ?Fr2 = 3982N軸向力Fa = FtX tan ?Fa2 = 178

31、0N支反力YZ平面FbV + PaV = Ptl + Pt2Fav = 4462NFtl x 59 4- Ft2 x 164 = FAV x 200Fbv = 3590NMV1 = 323.49NthMV2 = 376.95N,znXZ平面Fbh + ah =+ Fr2Pah = 628NPbh = 619NFa2 x 59 4- Fah x 200=Fal x 239 + Frl x 132+ 居？ x 102MH1 = 44.877N mMH2 = 65.94/V m合成彎矩Mei = JmY + MH12Me? Jm/ + MH42MC1 = 324.298 mMc2 = 379.62/

32、V - m轉(zhuǎn)矩Ti = 555.75N m當(dāng)量彎矩"靄"579（脈動(dòng)）Meci = Jm急 + （aT】）2 Mg = Jm：2 + （叫/a = 0.58= 553NmMec2 = 568N m校核a.lb = 75MPa _ Mgci Wc Meciabc2 wc（Jbci = 19.4MPa < -ibO“2 = 20.7MPa< 0Tb軸初步設(shè)計(jì)圖:豎直面（YZ平面）支反力及彎矩計(jì)算如下:6784104Fav水平面（XZ平面）支反力及彎矩計(jì)算如下:3低速軸齒輪上地作用力轉(zhuǎn)矩 圓周力 徑向力 釉向力T3 = 9550P2/改Ft = 2 T2/d3Fr =

33、 Ft x tan an/cos p Fa = Ft X tan/?T3 = 1650.26N - mFt = 8074N耳= 3011NFa = 1796N支反力YZ平面Pbv + Pav = F（；FAy x 103 = x 103Fav = 3180NFbv = 4894N MV1 = 636.227V - mXZ平面Fbh + Pah = FrPah = 2297NFbh = 714N MH1 = 40.49/V m MH2 = 509.18/V-m合成彎矩Mc2 = Jm 碧 2 +Mc2 = 310.66/V-m轉(zhuǎn)矩Ti = 2116.598N m當(dāng)量彎矩a =寄= 0.579(脈

34、動(dòng))M82 = Jm% + (%)2a = 0.579Mec2 = 1498/V m校核a.lb = ISM Pa_ M42M WcObc2 = 24.4MPq <軸初步設(shè)計(jì)圖:4數(shù)據(jù)列表高速軸中間軸低速軸當(dāng)量彎矩Mecl = 283.3N 771Mec2 161.6/V mMecl = 627.4/V - mMec2 386.9N mMecl = 1053.6/V - mMec2 646.8/V m危險(xiǎn)截面 校核。兒2 = 41MPq < -ibabc2 = 20.7MPa < -ibabc2 = 24AMPa < 0Tb七軸承地選擇與校核1輸入軸承6203計(jì)算工程計(jì)

35、算內(nèi)容計(jì)算結(jié)果軸承主要 性能參數(shù)6309軸承主要性能參數(shù)如下：d=45mm/D=100mm/B=26mm/ COr = 31800N；COr = 31800N確定AB端X、Y值由表 8.7,乒=0,068,取 e=0.27CorX=l, Y=0X=1Y=0沖擊載荷 系數(shù)由表8.8查得fd = 1.1B端軸承當(dāng) 量載荷P= fd(XFr+Fa)P=5430N軸承壽命L " n3Lioh = 6 年 壽命合格結(jié)論：所選釉承能滿(mǎn)足壽命、靜載荷與許用轉(zhuǎn)速地要求.2中間軸軸承6209計(jì)算工程計(jì)算內(nèi)容計(jì)算結(jié)果軸承主要 性能參數(shù)6209軸承主要性能參數(shù)如下：d=45mm,D=85mm,B=19mm

36、, COr = 20500N；COr = 20500N確定AB端X、Y值由表 18.7,- = 0077,取 e = 0.28X=l, Y=0X= 1Y = 0沖擊載荷 系數(shù)由表18.8查得fd = 11B端軸承當(dāng) 量載荷P= fd（XF,+職）P = 4908N軸承壽命（%31Loh = 7 年 壽命合格結(jié)論：所選軸承能滿(mǎn)足壽命、靜載荷與許用轉(zhuǎn)速地要求.3輸出軸軸承6216計(jì)算工程計(jì)算內(nèi)容計(jì)算結(jié)果軸承主要 性能參數(shù)查手冊(cè)6216軸承主要性能參數(shù)如下：d=70mm/D=125mm/B=24mm/ COr = 45000N；COr = 45000N確定AB端X、Y值由表 8.7,舁=0.033,

37、取e = 0.23 CorX = 0.56, Y = 1.8X = 0.56Y = 1.8沖擊載荷 系數(shù)由表8.8查得fd 1.1B端軸承當(dāng) 量載荷P = W（第+彳）P = 6608N軸承壽命Loh = 10 年 壽命合格結(jié)論：所選軸承能滿(mǎn)足壽命、靜載荷與許用轉(zhuǎn)速地要求.八鍵地選擇與校核高速軸鍵地選擇和參數(shù)選用普通平鍵，圓頭,dl = 30mm，選 用鍵bx/i = 8x7轉(zhuǎn)矩7 = 141.77N- m鍵長(zhǎng)L2 = 90mm接觸長(zhǎng)度1 = 1 b = 82771771l = S2m7n許用擠壓應(yīng)力查表鑄鐵許用擠壓應(yīng)力為oP = 70 80MPQ。=hTdoP = 32.8MPq op &l

38、t; aP 滿(mǎn)足要求，可用中間軸鍵地選擇和參數(shù)選用普通平鍵，圓頭，d1= 55mm , d2 = 55mm，選用鍵 b x h = 16 x 10, b x /i = 16 x 10轉(zhuǎn)矩A = 555.75N - m鍵KLjl = 63mmL2 = 63mm接觸長(zhǎng)度= Lr b = 47mm l2 = L2 b = 47nlm.I = 477n77il2 = 47m7n許用擠壓應(yīng)力查表鑄鐵許用擠壓應(yīng)力為 aP = 70 80MPa 147 api hl'.d,147 ap2 - hl'2d20Pl = 21.5MPq ap 2 = 21.5MPq °pi < a

39、p aP2 < P 滿(mǎn)足要求，可用低速軸鍵地選擇和參數(shù)選用普通平鍵，圓頭，dl = 85mm , d2 = 70mm，選用鍵b x /i = 22 x 14, b x /i = 20 x 12轉(zhuǎn)矩A = 1650.25N-m鍵長(zhǎng)h = 70mmL2 = 7 0 mm接觸長(zhǎng)度= L1 - b = 4Smm l2 = L2 b = SOinmk = 48m7 M l2 = 50mzn許用擠壓應(yīng)力查表鑄鐵許用擠壓應(yīng)力為 aP = 70 80MPqPL"/1147ap21112d2Opi = 44.27MPa oP2 = 62.7 IM PaSi < PaP2 V lap 滿(mǎn)足要求，可用九減速器箱體各部分結(jié)構(gòu)尺寸計(jì)算工程計(jì)算過(guò)程計(jì)算結(jié)果箱蓋壁厚61 = 0.02a + 35 = 9mm箱座壁厚8 = 0,025 x 272 4-3= 10?nm箱蓋凸緣厚度bi = 1.551b = 13.5mm箱座凸緣厚度b = 1.58b = 15mm地腳螺釘直徑df = 0.036a + 12df = 24mm地腳螺釘數(shù)目250 < a < 500n = 6軸承旁連接螺釘 直徑乙=0.75d/di = 16mm箱蓋與箱座連接 螺釘直徑6?2 = 0.5dyd2 = 12mm軸承端蓋螺釘直