帶式輸送機(jī)傳動(dòng)裝置設(shè)計(jì)【圓錐-圓柱齒輪傳動(dòng)減速器】
帶式輸送機(jī)傳動(dòng)裝置設(shè)計(jì)【圓錐-圓柱齒輪傳動(dòng)減速器】,圓錐-圓柱齒輪傳動(dòng)減速器,帶式輸送機(jī)傳動(dòng)裝置設(shè)計(jì)【圓錐-圓柱齒輪傳動(dòng)減速器】,輸送,傳動(dòng),裝置,設(shè)計(jì),圓錐,圓柱齒輪,減速器
帶式輸送機(jī)傳動(dòng)裝置設(shè)計(jì) 28摘 要運(yùn)輸機(jī)械用減速器(JB/T9002-1999)包括:二級(jí)傳動(dòng)硬齒面DBY和中硬齒面DBZ兩個(gè)系列及三級(jí)傳動(dòng)硬齒面DCY和中硬齒面DCZ兩個(gè)系列。第一級(jí)傳動(dòng)為錐齒輪,第二、第三級(jí)傳動(dòng)為漸開線圓柱齒輪。錐齒輪齒形為格里森弧線齒或克林根貝爾格延伸外擺線齒。齒輪及齒輪軸均采用優(yōu)質(zhì)合金鋼鍛件。硬齒面經(jīng)滲碳、淬火磨齒,齒面硬度為:齒輪軸58-62HRC;齒輪54-58HRC。圓柱和圓錐齒輪精度分別不低于GB/T10095和GB/T11365中的6級(jí)。中硬齒面減速器的錐齒輪采用硬齒面,圓柱齒輪采用調(diào)質(zhì)、精滾,齒面硬度為:齒輪軸306-332HB,大齒輪273-314HB,齒輪精度為7級(jí)。這種減速器主要適用于運(yùn)輸機(jī)械,也可用于冶金、礦山、石油、化工等通用機(jī)械.其工作條件為:a. 輸入軸最高轉(zhuǎn)速不大于1500r/min;b. 齒輪圓周速度不大于20m/s;c. 工作環(huán)境溫度為-4045度,當(dāng)環(huán)境溫度低于0度時(shí),啟動(dòng)前潤(rùn)滑油應(yīng)預(yù)熱。從以上資料我們可以看出齒輪減速器結(jié)構(gòu)緊湊、傳動(dòng)效率高、運(yùn)行平穩(wěn)、傳動(dòng)比大、體積小、加工方便、壽命長(zhǎng)等等.因此,隨著我國(guó)社會(huì)主義建設(shè)的飛速發(fā)展,國(guó)內(nèi)已有許多單位自行設(shè)計(jì)和制造了這種減速器,并且已日益廣泛地應(yīng)用在國(guó)防、礦山、冶金、化工、紡織、起重運(yùn)輸、建筑工程、食品工業(yè)和儀表制造等工業(yè)部門的機(jī)械設(shè)備中,今后將會(huì)得到更加廣泛的應(yīng)用。本文首先介紹了帶式輸送機(jī)傳動(dòng)裝置的研究背景,通過(guò)對(duì)參考文獻(xiàn)進(jìn)行詳細(xì)的分析,闡述了齒輪、減速器等的相關(guān)內(nèi)容;在技術(shù)路線中,論述齒輪和軸的選擇及其基本參數(shù)的選擇和幾何尺寸的計(jì)算,兩個(gè)主要強(qiáng)度的驗(yàn)算等在這次設(shè)計(jì)中所需要考慮的一些技術(shù)問題做了介紹;為畢業(yè)設(shè)計(jì)寫作建立了進(jìn)度表,為以后的設(shè)計(jì)工作提供了一個(gè)指導(dǎo)。最后,給出了一些參考文獻(xiàn),可以用來(lái)查閱相關(guān)的資料,給自己的設(shè)計(jì)帶來(lái)方便。關(guān)鍵詞 電動(dòng)機(jī),齒輪,軸,圓錐-圓柱齒輪傳動(dòng)減速器目 錄一 文獻(xiàn)綜述1二 結(jié)構(gòu)設(shè)計(jì)三 設(shè)計(jì)計(jì)算過(guò)程及說(shuō)明.31 選擇電動(dòng)機(jī). .32 傳動(dòng)裝置的總傳動(dòng)比及其分配.33 計(jì)算傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力裝置參數(shù).34 帶傳動(dòng)設(shè)計(jì).45 齒輪傳動(dòng)設(shè)計(jì).56 軸的設(shè)計(jì).117 軸承的選擇 .228 鍵的選擇.229 減速機(jī)箱體的設(shè)計(jì).2310 減速器附件設(shè)計(jì).2311 密封與潤(rùn)滑.24四 設(shè)計(jì)小節(jié).25五 參考文獻(xiàn).261 緒論通過(guò)查閱一些文獻(xiàn)我們可以了解到帶式傳動(dòng)裝置的設(shè)計(jì)情況,為我所要做的課題確定研究的方向和設(shè)計(jì)的內(nèi)容。1.1 帶傳動(dòng)帶傳動(dòng)是機(jī)械設(shè)備中應(yīng)用較多的傳動(dòng)裝置之一,主要有主動(dòng)輪、從動(dòng)輪和傳動(dòng)帶組成。工作時(shí)靠帶與帶輪間的摩擦或嚙合實(shí)現(xiàn)主、從動(dòng)輪間運(yùn)動(dòng)和動(dòng)力的傳遞。帶傳動(dòng)具有結(jié)構(gòu)簡(jiǎn)單、傳動(dòng)平穩(wěn)、價(jià)格低廉、緩沖吸振及過(guò)載打滑以保護(hù)其他零件的優(yōu)點(diǎn)。1.2圓錐-圓柱齒輪傳動(dòng)減速器YK系列圓錐-圓柱齒輪傳動(dòng)減速器適用的工作條件:環(huán)境溫度為-4040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(jī)啟動(dòng)轉(zhuǎn)矩為減速器額定轉(zhuǎn)矩的兩倍。YK系列的特點(diǎn):采用一級(jí)圓弧錐齒輪和一、二、三級(jí)圓柱齒輪組合,把錐齒輪作為高速級(jí)(四級(jí)減速器時(shí)作為第二級(jí)),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(dá)到GB/T10095中的6級(jí),圓錐齒輪精度達(dá)到GB/T11365中的7級(jí);中心距、公稱傳動(dòng)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(jì)方法,主要零件可以互換;除底座式實(shí)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(rùn)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(jī)械強(qiáng)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(shí)啟動(dòng)5次、允許啟動(dòng)轉(zhuǎn)矩為工作轉(zhuǎn)矩的兩倍、單向運(yùn)轉(zhuǎn)、單對(duì)齒輪的接觸強(qiáng)度安全系數(shù)為1、失效概率小于等于1%等條件算確定.當(dāng)載荷性質(zhì)不同,每天工作小時(shí)數(shù)不同時(shí),應(yīng)根據(jù)工作機(jī)載荷分類按各種系數(shù)進(jìn)行修正.減速器雙向運(yùn)轉(zhuǎn)時(shí),需視情況將P1N乘上0.71.0的系數(shù),當(dāng)反向載荷大、換向頻繁、選用的可靠度KR較低時(shí)取小值,反之取大值。功率按下式計(jì)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(dòng)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(shí)100%連續(xù)運(yùn)轉(zhuǎn)和功率利用律(指P2/P1N100%)為100%的情況,不符合上述情況時(shí),應(yīng)進(jìn)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(jì)2.1V帶傳動(dòng)帶傳動(dòng)設(shè)計(jì)時(shí),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(duì)于安裝在減速器或電動(dòng)機(jī)軸上的帶輪外徑應(yīng)與減速器、電動(dòng)機(jī)中心高相協(xié)調(diào),避免與機(jī)座或其它零、部件發(fā)生碰撞。 2.2減速器內(nèi)部的傳動(dòng)零件減速器外部傳動(dòng)件設(shè)計(jì)完成后,可進(jìn)行減速器內(nèi)部傳動(dòng)零件的設(shè)計(jì)計(jì)算。1) 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(shí),應(yīng)選鑄剛或鑄鐵材料。各級(jí)大、小齒輪應(yīng)該可能減少材料品種。2) 蝸輪材料的選者與相對(duì)滑動(dòng)速度有關(guān)。因此,設(shè)計(jì)時(shí)可按初估的滑速度選擇材料。在傳動(dòng)尺寸確定后,校核起滑動(dòng)速度是否在初估值的范圍內(nèi),檢查所選材料是否合適。3) 傳動(dòng)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(biāo)準(zhǔn)。圓柱齒輪和蝸桿傳動(dòng)的中心距應(yīng)盡量圓整。對(duì)斜齒輪圓柱齒輪傳動(dòng)還可通過(guò)改變螺旋角的大小來(lái)進(jìn)行調(diào)整。根據(jù)設(shè)計(jì)計(jì)算結(jié)果,將傳動(dòng)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(jiǎn)圖,以備在裝配圖設(shè)計(jì)和軸、軸承、鍵聯(lián)結(jié)等校核計(jì)算時(shí)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(dòng)機(jī)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(jī)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?yàn)闇p速器軸與工作機(jī)軸之間往往有較大的軸線偏移,因此常選用剛性可以移動(dòng)聯(lián)軸器,例如滾子鏈聯(lián)軸器、齒式聯(lián)軸器。對(duì)于中、小型減速器,其輸出與工作機(jī)軸的軸線便宜不很大時(shí),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(hào)按計(jì)算轉(zhuǎn)距進(jìn)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(dòng)機(jī)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(jì)計(jì)算過(guò)程及說(shuō)明3.1選擇電動(dòng)機(jī)3.1.1電動(dòng)機(jī)類型和結(jié)構(gòu)型式選擇Y系列籠型三相異步電動(dòng)機(jī),臥式閉型電電動(dòng)機(jī)。3.1.2選擇電動(dòng)機(jī)容量工作機(jī)所需功率=7.98kw =80.7r/min電動(dòng)機(jī)的輸出功率=10.4kw=*.* =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(dòng)機(jī)的額定功率Ped=Pd3.1.3選擇電動(dòng)機(jī)的轉(zhuǎn)速同步轉(zhuǎn)速 1500r/min。3.1.4確定電動(dòng)機(jī)型號(hào)選擇 Y160M-4 額定功率 11kw 轉(zhuǎn)速 1460r/min3.2傳動(dòng)裝置的總傳動(dòng)比及其分配i=18.1 帶傳動(dòng) i=2 圓錐 i= 2.5 圓柱 i= 43.3計(jì)算傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力裝置參數(shù)各軸轉(zhuǎn)速: 電動(dòng)機(jī)軸 =1460r/min 減速箱輸入軸 =486.7 r/min 高速軸 =235.1 r/min 低速軸 =58.8 r/min各軸輸入功率: =11kw =*0.95=10.45kw=*0.98*0.97*0.98=9.73KW=*0.98*0.97*0.98=9.07KW各軸轉(zhuǎn)矩:T0=9550*/=72.0N*m T1=9550*/=205.0 N*m T2=9550*/=395.2 N*m T3=9550*/=1493.1 N*m3.4帶傳動(dòng)設(shè)計(jì)3.4.1定v帶型號(hào)和帶輪直徑工作情況系數(shù) =1.1計(jì)算功率 =1.1*11=12.1kw選帶型號(hào) A型小帶輪直徑 =100mm大帶輪直徑 =(1-0.01)*100*3=297mm大帶輪轉(zhuǎn)速 = =481.8r/min3.4.2計(jì)算帶長(zhǎng)求 = (+)/2 =198.5mm求 =(-)/2=98.5mm2(+)=a=0.7*(+)初取中心距 a=600mm帶長(zhǎng) L=Dm+2*a+=1839.5基準(zhǔn)長(zhǎng)度 =2000mm求中心距和包角中心距 a= + =344.18+337.06=681.24120數(shù)求帶根 v=3.14*/(60*1000)=7.64m/s傳動(dòng)比 i=/=2帶根數(shù) =1.32kw =0.95 =1.03 P=0.17kw z=/(+)*)=12.1/(1.32+0.17)*0.95*1.03)=8.3 取9根求軸上載荷張緊力 =500*/v*z(2.5-)/+qv*v=500*12.1/(7.64*9)*(2.5-0.95)/0.95+0.10*=149.3N軸上載荷 =2*sin(/2)=2*9*149.3*sin(162.6/2)=2656.5N3.5齒輪傳動(dòng)設(shè)計(jì)直齒錐齒: 軸交角=90 傳遞功率P=10.45kw 小齒輪轉(zhuǎn)速=486.7r/m 傳動(dòng)比i=2.07載荷平穩(wěn),直齒為刨齒,小齒輪40Cr,調(diào)質(zhì)處理,241HB286HB平均260HB,大齒輪用45號(hào)鋼,217HB255HB 平均230HB齒面接觸疲勞強(qiáng)度計(jì)算齒數(shù)和精度等級(jí) 取=24 =i*=48 選八級(jí)精度使用系數(shù)=1.0 動(dòng)載荷系數(shù)=1.15齒間載荷分配系數(shù) 估計(jì)*Ft/b100N/mm cos=u/=2/=0.89 cos=1/=1/=0.44=/ cos=24/0.89=26.97=/ cos=48/0.44=109.1v=(1.88-3.2(1/(2*)+1/(2*)cos=1.85=0.85=1.4齒向載荷分布函數(shù) =1.9載荷系數(shù) =1*1.5*1.4*1.9=3.99轉(zhuǎn)矩 =9.55*=9.55*10.45/486.7=20505N.mm彈性系數(shù) =189.8節(jié)點(diǎn)區(qū)域系數(shù) =2.5接觸疲勞強(qiáng)度 =710Mpa=680Mpa接觸最小安全系數(shù)=1.5接觸壽命系數(shù) =1.0許用接觸應(yīng)力 = */=710*/1.05=676Mpa = */=680*/1.05=648Mpa小輪大端分度圓直徑 =0.3 =70mm驗(yàn)算圓周速度及Ka*Ft/b =(1-0.5R) =(1-0.5R)70=59.5mm =3.1459.5*486.7/60000=1.5m/s = b=*R=*d/(2*sin)=*/(2*=20.4mm*/b=1.0*689.2/20.4=33.8N/mm100N/mm確定傳動(dòng)尺寸大端模數(shù) m=/=70/24=2.9mm實(shí)際大端分度圓直徑d =m=3*24=84 =m=3*48=144b=*R=0.3*80.5=24.15mm齒根彎曲疲勞強(qiáng)度計(jì)算齒面系數(shù) =2.72 =2.38應(yīng)力修正系數(shù) =1.66 =1.78重合度系數(shù) =0.25+0.75/ =0.25+0.75/0.85=0.66齒間載荷分配系數(shù) */b100N/mm =1/=1/0.66=1.56載荷系數(shù) =1*1.15*1.56*1.9=3.4彎曲疲勞極限 =600MPa=570MPa彎曲最小安全系數(shù) =1.25彎曲壽命系數(shù) =1.0尺寸系數(shù) =1.0許用彎曲應(yīng)力 = lim/=600*1.0*1.0/1.25=480MPa =570*1.0*1.0/1.25=456MPa驗(yàn)算 =152=152*2.38*1.78/(2.72*1.66)=142.6MPa標(biāo)準(zhǔn)斜齒圓柱齒輪 小齒輪用40Cr調(diào)質(zhì)處理,硬度241HB286HB 平均260MPa 大齒輪用45號(hào)鋼,調(diào)質(zhì)處理,硬度229HB286HB 平均241MPa初步計(jì)算轉(zhuǎn)矩=9.55*9.73/235.1=39524N.mm齒數(shù)系數(shù)=1.0值 取=85初步計(jì)算的許用接觸應(yīng)力H1=0.96Hlim1=0.9*710=619MPa H2=0.9Hlim2=1.9*580=522MPa初步計(jì)算的小齒輪直徑 =Ad=85*=48.1mm取 d1=50mm初步尺寬b=d*=1*50=50mm校核計(jì)算圓周速度 v=0.62m/s精度等級(jí) 選九級(jí)精度齒數(shù)z和模數(shù)m 初步齒數(shù)=19; =i*19=4*19=76和螺旋角 =/=50/19=2.63158 =2.5mm =arcos=arccos2.5/2.63158=18.2使用系數(shù) =1.10動(dòng)載系數(shù) =1.5齒間載荷分配系數(shù) =2*39524/50=1581N=1.1*1.581/50=34N/mm100N/mm=1.88-3.21/+1/cos=1.88-3.25*(1/19+1/76)cos18.2 =1.59=2.0=1.59+2.0=3.59= arctan=arctan=20.9cos =cos18.220cos/20.9cos=0.95齒向載荷分布系數(shù) =A+B1+0.6*+c*b/1000=1.36 =* * =1.10*1.05*1.76*1.36=2.76彈性系數(shù) =189.8節(jié)點(diǎn)區(qū)域系數(shù) =2.5重合度系數(shù) 取螺旋角系數(shù) =許用接觸應(yīng)力驗(yàn)算=189.8*2.38*0.97=647MPa690MPa齒根彎曲疲勞強(qiáng)度驗(yàn)算齒行系數(shù)YFa = Y=2.72 Y=2.2應(yīng)力修正系數(shù) =1.56 =1.79重合度系數(shù) =1.61 螺旋角系數(shù) 齒向載荷分配系數(shù) =1.76 齒向載荷分布系數(shù) b/h=50.(2.25*2.5)=8.9 =1.27載荷系數(shù) K=*許用彎曲應(yīng)力 驗(yàn)算 3.6軸的設(shè)計(jì)輸入軸選用45鋼調(diào)質(zhì) 取 d=35mm計(jì)算齒輪受力 =84mm =(1-0.5 =689.2N =tan=計(jì)算支反力水平面反力 =1102.7N =-413.5N垂直面反力 =-1235.7N =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 應(yīng)力校正系數(shù) 當(dāng)量彎矩圖 軸徑 高速軸軸材料選用45鋼調(diào)質(zhì), 取 d=40mm計(jì)算螺旋角 齒輪直徑 小輪 = 大輪小齒輪受力 轉(zhuǎn)矩=9.55*圓周力 =2*/=2*39524/50=1581N 徑向力畫小齒輪軸受力圖水平反力 =1358.1N =912.1N垂直反力 =594.7N =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) 畫當(dāng)量彎矩圖 =50220N.mm校核軸徑 =20.340mm低速軸 材料同前兩軸 畫大齒輪受力圖計(jì)算支反力 水平反力 =1185.8 =395.2N 垂直反力 =21.2N =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(dāng)量彎矩 校核軸徑 =26e /=0.3e查表 =0.4 =1.6 =1 =0當(dāng)量動(dòng)載荷 =*(*+*)=1.0*(0.4*1177.7+1.6*1228.4)=2436.5N=*(*+*)= 4297.0N軸承壽命 =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 輸入軸 L=20 (mm)高速軸 L=20低速軸 L=30T=3.9減速機(jī)箱體的設(shè)計(jì) 名稱 符號(hào) 尺寸關(guān)系 結(jié)果 箱座壁厚 =0.025*a+38 箱蓋壁厚 =0.02*a+38 a=箱體凸緣厚度 , b=1.5=15;=1.5=15;=2.5=25加強(qiáng)肋厚度 , m=0.85=8.5; =0.85=8.5地腳螺栓直徑 14地腳螺栓數(shù)目 n 4軸承旁連接螺栓直徑 0.75箱蓋,箱座連接螺栓直徑 ;螺栓間L軸承蓋螺釘直徑數(shù)目 ,n =8 n=4軸承蓋外徑 =s(兩連接螺栓間的距離)觀察孔螺釘直徑 軸承旁凸臺(tái)高度和直徑 h, h由結(jié)構(gòu)決定, =箱體外壁至軸承座端面距離 +3.10減速器附件設(shè)計(jì)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(tái)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(biāo),有標(biāo)尺的位置不能太高和太低,以免溢出油標(biāo)尺孔座。3.10.4放油孔和螺塞放在油的最低處,平時(shí)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(tái),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(yuǎn)越可靠,常設(shè)在箱體連接凸緣處的對(duì)角處,對(duì)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(zhǎng)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(rùn)滑軸承采用接觸式密封。傳動(dòng)采用浸油潤(rùn)滑,盡量使各傳動(dòng)浸油深度相同。軸承潤(rùn)滑采用刮油潤(rùn)滑。4 設(shè)計(jì)小結(jié)通過(guò)這次設(shè)計(jì)讓我了解到機(jī)械設(shè)計(jì)是從使用要求等出發(fā),對(duì)機(jī)械的工作原理、結(jié)構(gòu)、運(yùn)動(dòng)形式、力和能量的傳遞方式,以及各個(gè)零件的材料和形狀尺寸等問題進(jìn)行構(gòu)思、分析和決策的工作過(guò)程,這種過(guò)程的結(jié)果要表達(dá)成設(shè)計(jì)圖紙、說(shuō)明書及各種技術(shù)文件。通過(guò)帶式輸送機(jī)傳動(dòng)裝置的設(shè)計(jì),了解了帶式輸送機(jī)傳動(dòng)裝置的原理以及其結(jié)構(gòu)。從帶式輸送機(jī)傳動(dòng)裝置的設(shè)計(jì),我學(xué)到了機(jī)械設(shè)計(jì)的思想-以最少的成本達(dá)到最好的目的,以最簡(jiǎn)單的結(jié)構(gòu)達(dá)到所需的功能。設(shè)計(jì)思想中最突出得的是-合理二字。整個(gè)設(shè)計(jì)過(guò)程使我受益非淺。5參考文獻(xiàn)1 王昆等主編,機(jī)械設(shè)計(jì)課程設(shè)計(jì),武漢: 高等教育出版社,1995。2 邱宣懷主編,機(jī)械設(shè)計(jì).第四版,北京:高等教育出版社,1997。3 濮良貴主編,機(jī)械設(shè)計(jì).第七版,西安: 高等教育出版社,2000。4 任金泉主編,機(jī)械設(shè)計(jì)課程設(shè)計(jì),西安:西安交通大學(xué)出版社,2002。5 許鎮(zhèn)寧主編,機(jī)械零件,北京:人民教育出版社,1959。6 Tragfahigkeitsberechnung Von Stirn-und Kegelradern (DIN 3990), 1970。編號(hào)無(wú)錫太湖學(xué)院畢業(yè)設(shè)計(jì)(論文)相關(guān)資料題目: 工業(yè)窯爐的設(shè)計(jì)(輸送裝置) 信機(jī) 系 機(jī)械工程及自動(dòng)化 專業(yè)學(xué) 號(hào): 0923220學(xué)生姓名: 李 歡 指導(dǎo)教師: 徐偉明(職稱: 教 授 ) (職稱: )2013年5月25日目 錄一、畢業(yè)設(shè)計(jì)(論文)開題報(bào)告二、畢業(yè)設(shè)計(jì)(論文)外文資料翻譯及原文三、學(xué)生“畢業(yè)論文(論文)計(jì)劃、進(jìn)度、檢查及落實(shí)表”四、實(shí)習(xí)鑒定表無(wú)錫太湖學(xué)院畢業(yè)設(shè)計(jì)(論文)開題報(bào)告題目: 工業(yè)窯爐的設(shè)計(jì)(輸送裝置) 信機(jī)系 機(jī)械工程及自動(dòng)化 專業(yè)學(xué) 號(hào): 0923220 學(xué)生姓名: 李 歡 指導(dǎo)教師: 徐偉明(職稱: 教 授 ) (職稱: )2012年11月20日課題來(lái)源本課題來(lái)源于導(dǎo)師布置的任務(wù)導(dǎo)老師科學(xué)依據(jù)(包括課題的科學(xué)意義;國(guó)內(nèi)外研究概況、水平和發(fā)展趨勢(shì);應(yīng)用前景等)輸送裝置的設(shè)計(jì)是機(jī)械工程及其自動(dòng)化專業(yè)所包含的一個(gè)較為基礎(chǔ)的內(nèi)容,選擇輸送裝置方向的畢業(yè)設(shè)計(jì)題目完全符合本專業(yè)的要求,從應(yīng)用性方面來(lái)說(shuō),輸送裝置又是很多機(jī)器所必不可少的一個(gè)部分。有效保證輸送裝置的功率及穩(wěn)定性能夠達(dá)到設(shè)計(jì)的要求,具有很好的發(fā)展前途和應(yīng)用前景。研究?jī)?nèi)容 1、 選擇電動(dòng)機(jī),計(jì)算傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力參數(shù); 2、 擬定、分析傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力參數(shù);3、 進(jìn)行傳動(dòng)件的設(shè)計(jì)計(jì)算,校核軸、軸承、聯(lián)軸器、鍵等; 4、 繪制減速器裝配圖及典型零件圖(圖紙數(shù)達(dá)到3張或以上);5、 完成設(shè)計(jì)說(shuō)明一份,分析明晰,計(jì)算正確,闡述清楚。適合的生產(chǎn)加工工 藝擬采取的研究方法、技術(shù)路線、實(shí)驗(yàn)方案及可行性分析首先確定整體設(shè)計(jì)方案,由公式的演算得到電動(dòng)機(jī)的動(dòng)力和運(yùn)動(dòng)分析,在以此推算相配的傳動(dòng)件,軸系零部件的尺寸規(guī)格。綜上計(jì)算可以得到相關(guān)尺寸,再根據(jù)力學(xué)性能對(duì)所得零部件尺寸進(jìn)行校驗(yàn)從而驗(yàn)證整體方案是否可行。研究計(jì)劃及預(yù)期成果研究計(jì)劃:2012年11月 布置任務(wù)。 2013年1月 對(duì)課題研究方向進(jìn)行學(xué)習(xí) 2013年2月3月 擬定方案,提出專機(jī)總體方案,供討論 2013年4月5日10日 確定方案,專機(jī)總體布置 11日20日 整機(jī)設(shè)計(jì)、部件設(shè)計(jì) 21日30日 改進(jìn)并完成設(shè)計(jì) 2013年5月1日10日 撰寫設(shè)計(jì)說(shuō)明書 11日15日 總結(jié)預(yù)期成果:圖紙、設(shè)計(jì)說(shuō)明書特色或創(chuàng)新之處 帶式輸送機(jī)本身便具有價(jià)格便宜,標(biāo)準(zhǔn)化程度高特點(diǎn),使成本大幅降低。高速級(jí)齒輪常布置在遠(yuǎn)離扭矩輸入端的一邊,以減小因彎曲變形所引起的載荷沿齒寬分布不均現(xiàn)象。已具備的條件和尚需解決的問題與指導(dǎo)老師的溝通中,對(duì)自己所做課題有了整體的認(rèn)識(shí),清晰了思路。指導(dǎo)老師提供了論文指導(dǎo),從而使自己明確了每一步的方向。因第一次繪制復(fù)雜的裝配圖,所以在繪圖方面還有待提高。指導(dǎo)教師意見同意作為本專業(yè)學(xué)生畢業(yè)設(shè)計(jì)課題,其難度和工作量均合適。 指導(dǎo)教師簽名: 年 月 日教研室(學(xué)科組、研究所)意見 教研室主任簽名: 年 月 日系意見 主管領(lǐng)導(dǎo)簽名: 年 月 日英文原文Esign of Speed Belt ConveyorsG. Lodewijks, The Netherlands.This paper discusses aspects of high-speed belt conveyor design. The capacity of a belt conveyor is determined by the belt speed given a belt width and troughing angle. Belt speed selection however is limited by practical considerations, which are discussed in this paper. The belt speed also affects the performance of the conveyor belt, as for example its energy consumption and the stability of its running behavior. A method is discussed to evaluate the energy consumption of conveyor belts by using the loss factor of transport. With variation of the belt speed the safety factor requirements vary, which will affect the required belt strength. A new method to account for the effect of the belt speed on the safety factor is presented. Finally, the impact of the belt speed on component selection and on the design of transfer stations is discussed.Belt machine by conveyor belt continuous or intermittent motion to transport all kinds of different things ,Can transport all kinds of bulk materials, but also transport a variety of cardboard boxes, packaging bags, weight of single pieces of small goods, a wide range of uses . Belt conveyor belt material: rubber, silicone, PVC, PU and other materials, in addition to ordinary material conveying, but also to meet the transmission oil resistant, corrosion resistance, antistatic and other special requirements for material. Belt conveyor structure: groove belt machine, flat belt conveyor, climbing belt machine, turning machines and other forms belt, conveyor belt can also be created to enhance the tailgate, skirts and other accessories, can meet a variety of technological requirements.The belt conveyor drive: deceleration motor drive, electric drive roller.Belt conveyor mode: frequency control, stepless transmission.The belt rack material: carbon steel, stainless steel, aluminum profile.Scope of application: light industry, electronics, food, chemical, wood, etc.Belt machine equipment characteristics: belt conveyor is stable, the material and the conveyor belt there is no relative motion, to avoid damage to the carrier material. Low noise, suitable for quiet work environment requirements. Simple structure, easy maintenance. Low energy consumption, low use cost. Conveyor is a common dont have flexible traction component continuous conveying machinery, also called continuous conveyor.It is a material handling equipment, it with handling ability strong, persistent, direction, flexible, and other advantages in industrial production in large being applied. Although many types of belt conveyor, but its working principle is basic similar, most are driving draught device and drive transmission container transport materials. Conveyor can undertake level, the tilt and vertical conveyor, also can make the space transport routes, transmission lines is usually fixed, is a modern production and logistics transport indispensable important mechanical equipment. It has transmission capacity is strong, long distance transportation etc.With the development of industry, conveyor also obtained fast development, conveyor products have been also gradually improved. With the emergence of the power equipment of similar principle is applied, conveyor continuing into the 19th century, britons use basketwork, wire rope for traction belt conveyor. The principle of belt conveyor, when applied in the 17th century also recorded conveyor, in 1880 German company developed driven by steam belt conveyor. Then the British and German and launched inertial conveyor, if the conveyor belt, the application of the principle, creating a tilt of the belt conveyor, belt, traction with chains. All sorts of conveyor during this time arise conveyor, based on human, hydraulic power drive such. All the structures conveyor successively appeared. In 1887 americans produced the screw conveyor, make enterprise internal, between enterprise and inter-city transportation possible. The development history of belt conveyor, they very ancient instead of the original motive for conveyor provide driving force. Ancient people began to use water overturned and high TongChe conveyor, in turn after the water conservancy projects belt conveyor begin in power. Quick-tempered exaltsAccording to the mode of operation conveying machinery can be divided into: 1: belt conveyor 2: screw conveyor 3: dou pattern lift machineThe future of large scale, will toward belt use scope, energy consumption, low pollution less, material automatically grading, etc.Past research has shown the economical feasibility of using narrower, faster running conveyor belts versus wider, slower running belts for long overland belt conveyor systems. See for example I-5. Today, conveyor belts running at speeds around 8 m/s are no exceptions. However, velocities over 10 m/s up to 20 m/s are technically (dynamically) feasible and may also be economically feasible. In this paper belt speeds between the 10 and 20 m/s are classified as high. Belt speeds below the 10 m/s are classified as low.Using high belt speeds should never be a goal in itself. If using high belt speeds is not economically beneficial or if a safe and reliable operation is not ensured at a high belt speed then a lower belt speed should be selected.Selection of the belt speed is part of the total design process. The optimum belt conveyor design is determined by static or steady state design methods. In these methods the belt is assumed to be a rigid, inelastic body. This enables quantification of the steady-state operation of the belt conveyor and determination of the size of conveyor components. The specification of the steady-state operation includes a quantification of the steady-state running belt tensions and power consumption for all material loading and relevant ambient conditions. It should be realized that finding the optimum design is not a one-time effort but an iterative process 6.Design fine-tuning, determination of the optimum starting and stopping procedures, including determination of the required control algorithms, and determination of the settings and sizes of conveyor components such as drives, brakes and flywheels, are determined by dynamic design methods. In these design methods, also referred to as dynamic analyses, the belt is assumed to be a three-dimensional (visco-) elastic body. A three dimensional wave theory should be used to study time dependent transmission of large local force and displacement disturbances along the belt 7. In this theory the belt is divided into a series of finite elements. The finite elements incorporate (visco-) elastic springs and masses. The constitutive characteristics of the finite elements must represent the rheological characteristics of the belt. Dynamic analysis produces the belt tension and power consumption during non-stationary operation, like starting and stopping, of the belt conveyor.This paper discusses the design of high belt-speed conveyors, in particular the impact of using high belt speeds on the performance of the conveyor belt in terms of energy consumption and safety factor requirements. Using high belt speeds also requires high reliability of conveyor components such as idlers to achieve an acceptable component life. Another important aspect of high-speed belt conveyor design is the design of efficient feeding and discharge arrangements. These aspects will be discussed briefly.Many methods of analyzing a belts physical behavior as a rheological spring have been studied and various techniques have been used. An appropriate model needs to address: 1. Elastic modulus of the belt longitudinal tensile member 2. Resistances to motion which are velocity dependent (i.e. idlers) 3. Viscoelastic losses due to rubber-idler indentation 4. Apparent belt modulus changes due to belt sag between idlers Since the mathematics necessary to solve these dynamic problems are very complex, it is not the goal of this presentation to detail the theoretical basis of dynamic analysis. Rather, the purpose is to stress that as belt lengths increase and as horizontal curves and distributed power becomes more common, the importance of dynamic analysis taking belt elasticity into account is vital to properly develop control algorithms during both stopping and starting. Using the 8.5 km conveyor in Figure 23 as an example, two simulations of starting were performed to compare control algorithms. With a 2x1000 kW drive installed at the head end, a 2x1000 kW drive at a midpoint carry side location and a 1x1000kW drive at the tail, extreme care must be taken to insure proper coordination of all drives is maintained. Figure 27 illustrates a 90 second start with very poor coordination and severe oscillations in torque with corresponding oscillations in velocity and belt tensions. The T1/T2 slip ratio indicates drive slip could occur. Figure 28 shows the corresponding charts from a relatively good 180 second start coordinated to safely and smoothly accelerate the conveyor. Figure 27-120 Sec Poor Start BELTSPEED BELT SPEED SELECTIONThe lowest overall belt conveyor cost occur in the range of belt widths of 0.6 to 1.0 m 2. The required conveying capacity can be reached by selection of a belt width in this range and selecting whatever belt speed is required to achieve the required flow rate. Figure 1 shows an example of combinations of belt speed and belt width to achieve Specific conveyor capacities. In this example it is assumed that the bulk density is 850 kg/m3 (coal) and that the trough angle and the surcharge angle are 35 and 20 respectively.Figure 1: Belt width versus belt speed for different capacities.Belt speed selection is however limited by practical considerations. A first aspect is the troughability of the belt. In Figure 1 there is no relation with the required belt strength (rating), which partly depends on the conveyor length and elevation. The combination of belt width and strength must be chosen such that good troughability of the belt is ensured. If the troughability is not sufficient then the belt will not track properly. This will result in unstable running behavior of the belt, in particular at high belt speeds, which is not acceptable. Normally, belt manufacturers expect a sufficiently straight run if approximately 40% of the belt width when running empty, makes contact with the carrying idlers. Approximately 10% should make tangential contact with the center idler roll.A second aspect is the speed of the air relative to the speed of the bulk solid material on the belt (relative airspeed). If the relative airspeed exceeds certain limits then dust will develop. This is in particular a potential problem in mine shafts where a downward airflow is maintained for ventilation purposes. The limit in relative airspeed depends on ambient conditions and bulk material characteristics.A third aspect is the noise generated by the belt conveyor system. Noise levels generally increase with increasing belt speed. In residential areas noise levels are restricted to for example 65 dB. Although noise levels are greatly affected by the design of the conveyor support structure and conveyor covers, this may be a limiting factor in selecting the belt speed.BELT SPEED VARIATIONThe energy consumption of belt conveyor systems varies with variation of the belt speed, as will be shown in Section 3. The belt velocity can be adjusted with bulk material flow supplied at the loading point to save energy. If the belt is operating at full tonnage then it should run at the high (design) belt speed. The belt speed can be adjusted (decreased) to the actual material (volume) flow supplied at the loading point. This will maintain a constant filling of the belt trough and a constant bulk material load on the belt. A constant filling of the belt trough yields an optimum loading-ratio, and lower energy consumption per unit of conveyed material may be expected. The reduction in energy consumption will be at least 10% for systems where the belt speed is varied compared to systems where the belt speed is kept constant 8.Varying the belt speed with supplied bulk material flow has the following advantages:Less belt wear at the loading areasLower noise emissionImproved operating behavior as a result of better belt alignment and the avoidance of belt lifting in concave curve by reducing belt tensionsDrawbacks include: Investment cost for controllability of the drive and brake systemsVariation of discharge parabola with belt speed variationControl system required for controlling individual conveyors in a conveyor systemConstant high belt pre-tensionConstant high bulk material load on the idler rollsAn analysis should be made of the expected energy savings to determine whether it is worth the effort of installing a more expensive, more complex conveyor system.ENERGY CONSUMPTIONClients may request a specification of the energy consumption of a conveyor system, for example quantified in terms of maximum kW-hr/ton/km, to transport the bulk solid material at the design specifications over the projected route. For long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance 9. This is the resistance that the belt experiences due to the visco-elastic (time delayed) response of the rubber belt cover to the indentation of the idler roll. For in-plant belt conveyors, work done to overcome side resistances that occur mainly in the loading area also affects the energy consumption. Side resistances include the resistance due to friction on the side walls of the chute and resistance that occurs due to acceleration of the material at the loading point.The required drive power of a belt conveyor is determined by the sum of the total frictional resistances and the total material lift. The frictional resistances include hysteresis losses, which can be considered as viscous (velocity dependent) friction components. It does not suffice to look just at the maximum required drive power to evaluate whether or not the energy consumption of a conveyor system is reasonable. The best method to compare the energy consumption of different transport systems is to compare their transport efficiencies.TRANSPORT EFFICIENCYThere are a number of methods to compare transport efficiencies. The first and most widely applied method is to compare equivalent friction factors such as the DIN f factor. An advantage of using an equivalent friction factor is that it can also be determined for an empty belt. A drawback of using an equivalent friction factor is that it is not a pure efficiency number. It takes into account the mass of the belt, reduced mass of the rollers and the mass of the transported material. In a pure efficiency number, only the mass of the transported material is taken into account.The second method is to compare transportation cost, either in kW-hr/ton/km or in $/ton/km. The advantage of using the transportation cost is that this number is widely used for management purposes. The disadvantage of using the transportation cost is that it does not directly reflect the efficiency of a system.The third and most pure method is to compare the loss factor of transport 10. The loss factor of transport is the ratio between the drive power required to overcome frictional losses (neglecting drive efficiency and power loss/gain required to raise/lower the bulk material) and the transport work. The transport work is defined as the multiplication of the total transported quantity of bulk material and the average transport velocity. The advantage of using loss factors of transport is that they can be compared to loss factors of transport of other means of transport, like trucks and trains. The disadvantage is that the loss factor of transport depends on the transported quantity of material, which implies that it can not be determined for an empty belt conveyor.The following are loss factors of transport for a number of transport systems to illustrate the concept:Continuous transport: Slurry transport around 0.01 Belt conveyors between 0.01 and 0.1 Vibratory feeders between 0.1 and 1 Pneumatic conveyors around 1 0 Discontinuous transport: Ship between 0.001 and 0.01 Train around 0.01 Truck between 0.05 and 0.1 INDENTATION ROLLING RESISTANCEFor long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance. Idler rolls are made of a relatively hard material like steel or aluminum whereas conveyor belt covers are made of much softer materials like rubber or PVC. The rolls therefore indent the belts bottom-cover when the belt moves over the idler rolls, due to the weight of the belt and bulk material on the belt. The recovery of the compressed parts of the belts bottom cover will take some time due to its visco-elastic (time dependent) properties. The time delay in the recovery of the belts bottom cover results in an asymmetrical stress distribution between the belt and the rolls, see Figure 2. This yields a resultant resistance force called the indentation rolling resistance force. The magnitude of this force depends on the visco-elastic properties of the cover material, the radius of the idler roll, the vertical force due to the weight of the belt and the bulk solid material, and the radius of curvature of the belt in curves in the vertical plane.Figure 2: Asymmetric stress distribution between belt and roll 7.It is important to know how the indentation rolling resistance depends on the belt velocity to enable selection of a proper belt velocity, 11.Figure 3: Loss factor (tanb) of typical cove
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