礦山搖擺式輸送機設(shè)計,礦山搖擺式輸送機設(shè)計,礦山,擺式,輸送,設(shè)計 搖擺式輸送機設(shè)計 緒論 當今社會，隨著科技的發(fā)展，人們對于各種資源的需求和消耗是非常巨大的，因此就會牽涉到資源的開采問題，如何能夠高效率,低風(fēng)險,無污染的開發(fā)礦物資源是當今社會面臨的重大難題。所以針對礦產(chǎn)資源而開發(fā)的礦山搖擺式輸送機的應(yīng)用就越來越廣泛。事實上人們對輸送機的研究從來沒有停止過，為了滿足不同的要求，出現(xiàn)了各式各樣的輸送機，有搖擺式輸送機和帶式輸送機等。 礦山搖擺式運輸機能夠在惡劣的生產(chǎn)條件下進行工作，可以滿足很多種工作條件，適用范圍非常廣泛。初粘性大的物料以外，一般的固體散狀物料和成件物品均可輸送。由于它的牽引構(gòu)件和承載構(gòu)件大多由金屬材料制成，因而與其他輸送機械相比所輸送物料的適應(yīng)性更強。搖擺式運輸機可輸送重的、具有銳利棱邊的、磨損性及腐蝕性強的散狀物料或物品，同時適宜輸送高溫物體。另外在輸送過程中，還可以進行干燥、冷卻、分類、請選等各種工藝作業(yè)。 但是由于其結(jié)構(gòu)原因，自重大，所以消耗也多，空載功率大等原因，嚴重限制了它的推廣和發(fā)展，這些問題都是需要進行設(shè)計和優(yōu)化的。 隨著人類的進步，越來越多并且越來越好的搖擺式輸送機將會被制造出來，來滿足生產(chǎn)發(fā)展的需求，它對提高生產(chǎn)率，降低工人勞動強度具有積極的意義。 搖擺式運輸機在設(shè)計時應(yīng)注意到特殊的工作環(huán)境和工作需求，?轉(zhuǎn)運是礦用運輸機故障較多的一個環(huán)節(jié)，以德國佩雷斯露天煤礦為例,皮帶運輸機每年因轉(zhuǎn)運站故障停車的時間平均達70小時,而由其它環(huán)節(jié)的故障引起的停車時間卻很少.因此,在確定運輸機系統(tǒng)時應(yīng)盡量減少物料的轉(zhuǎn)運次數(shù).而在設(shè)計轉(zhuǎn)運站時,則應(yīng)特別注意此類問題。 我國搖擺式運輸機，自上世紀七十年代中期開發(fā)以來，取得長足進步，但是與國外相比，仍存在較大的差距。首先是整機性能的落后，生產(chǎn)輸送能力相對較低，事故率高；再者使用壽命短，關(guān)鍵零部件使用壽命短，可靠性低；還有生產(chǎn)自動化程度不高，過載保護張力調(diào)節(jié)能力不足。 國外搖擺式運輸機技術(shù)發(fā)展很快，其主要表現(xiàn)在兩個方面；一方面是搖擺式運輸機的功能的多元化，應(yīng)用范圍擴大化，發(fā)展成在各個領(lǐng)域可以使用的運輸機械。另一方面是搖擺式運輸機本身技術(shù)與裝備有了巨大的發(fā)展，尤其是長距離、大運量、高速率運輸機已成為運輸機發(fā)展的主要方向。 搖擺式運輸機是為了適合礦山采礦等目的而設(shè)計的，因此就要解決人力問題，最大限度的解放人力勞動，提高礦產(chǎn)資源的開采效率，增大產(chǎn)量是設(shè)計的主要任務(wù)。 在對搖擺式運輸機的性能和總體結(jié)構(gòu)有了大致了解之后，要對其實際的工作環(huán)境和工作能力進行分析，為了實現(xiàn)預(yù)期目標，我們先要明確作業(yè)的特性和主要任務(wù)，根據(jù)這些特性和所需的任務(wù)來確定方案，試選原動機，傳動裝置，執(zhí)行元件，傳送裝置的選擇等。例如在選擇原動機和傳送帶的時候要考慮載荷、工作環(huán)境、可靠性、費用、安全性及其操作難度等。 本設(shè)計采用電動機，其優(yōu)點是躁聲小，初始成本低，運轉(zhuǎn)費用低，維護要求較少。通過減速箱和傳動裝置連接，傳動系統(tǒng)的基本任務(wù)是將原動機輸出的速度降低或增大，以滿足執(zhí)行機構(gòu)的要求，采用變速傳動來滿足執(zhí)行機構(gòu)經(jīng)常變速的要求，將原動機輸出的轉(zhuǎn)矩變換為執(zhí)行機構(gòu)所需要的轉(zhuǎn)矩和力。在根據(jù)傳動裝置和帶的連接實現(xiàn)帶的運動，通過調(diào)節(jié)減速箱來確定帶的運輸速度，通過以上機構(gòu)可以實現(xiàn)課題的要求。 通過對運輸機進行初步的分析后，發(fā)現(xiàn)其設(shè)計的主要問題和需要重點研究的方向是產(chǎn)品的動力機構(gòu)和傳動機構(gòu)。由于搖擺式運輸機一般是在工作條件較惡劣的環(huán)境下工作，所以它所遇到的突發(fā)故障可能性就大大的提高了，因此這些問題都是要在設(shè)計時進行考慮，這樣就可以降低機器的故障發(fā)生率，使其能夠進行正常的工作生產(chǎn)。在選擇電動機時，應(yīng)該在合適的范圍內(nèi)盡量保持運輸機能有較大的工作負載，這樣就可以防止因為過載而產(chǎn)生故障；其次在對傳動機構(gòu)進行設(shè)計時，要考慮其穩(wěn)定性，保證機器的傳動比。另外，由于搖擺式運輸機一般對質(zhì)量較大的物體進行運輸，所以就要考慮各個傳動部件的磨損問題，以延長運輸機的工作壽命。 在考慮對這些問題進行解決時，我們就要有針對性的進行研究，例如在選擇動力時，首先對運輸機的額定功率進行分析，選擇能夠保證功率的電動機，這樣就可以防止過載而不能正常工作。在對傳動機構(gòu)進行分析時也要對總體的傳動比進行分析，進而設(shè)計每個傳動環(huán)節(jié)的傳動比，這樣就能比較合理的設(shè)計出能夠滿足傳動比的運輸機械。 1.方案設(shè)計 1.1機構(gòu)簡介 搖擺式輸送機是一種傳送材料用的礦山運輸機械，其機構(gòu)運動簡圖如圖。電動機通過二級圓錐圓柱齒輪減速器使曲柄回轉(zhuǎn)，再經(jīng)過六連桿機構(gòu)使輸料車作往復(fù)移動，放置在車上的物料借助摩擦力隨輸料槽一起運動。物料的輸送是利用機構(gòu)在某些位置輸料車8有相當大的加速度，使物料在慣性力的作用下克服摩擦力而發(fā)生滑動，滑動的方向恒自左往右，從而達到輸送物料的目的 1.2 搖擺式輸送機的結(jié)構(gòu)示意圖 圖1-1搖擺式輸送機示意圖 1、電機 2、傳動裝置 3、執(zhí)行機構(gòu) 1.3初步計算和設(shè)計方案的確定 根據(jù)要求礦石重量G（滑塊5的重量都可忽略不計），及其繞重心的轉(zhuǎn)動慣量Jsi與輸?shù)V槽、礦物的重量G6` 、G7；托滾8的半徑及其滾動摩擦系數(shù)f，和每次運送礦石3000N的數(shù)據(jù)經(jīng)初步的計算和分析。確定各運動副中反作用力及曲柄上所需的平衡力矩，和一些桿件的基本參數(shù)。參考《機械原理電算程序設(shè)計》（哈工大出版）第二章有關(guān)內(nèi)容。 初定的一些數(shù)據(jù)為 減速器的輸出轉(zhuǎn)速： 110轉(zhuǎn)/分鐘 桿Lo1A長為：91毫米 桿LAB長為：302毫米 桿Lo2B長為：160毫米 桿Lo2長為: 270毫米 對以下兩種機構(gòu)進行對比分析：圖1-2為六桿機構(gòu)，直接通過電動機帶動曲柄滑塊轉(zhuǎn)動從而是連桿2擺動最終使滑塊左右運動，從而達到輸送貨物的效果。其優(yōu)點是成本比較低，結(jié)構(gòu)簡便，缺點是摩擦大，耗費能量多。圖1-3是通過送料的往復(fù)運動我們用曲柄滑塊機構(gòu)實現(xiàn)，當輸入構(gòu)件等速轉(zhuǎn)動時，輸出構(gòu)件帶動滑塊作往復(fù)移動，機構(gòu)具有急回功能，但該方案不但設(shè)計計算比較復(fù)雜，滑塊5和作平面復(fù)雜運動的連桿2和4的動平衡也比較困難 。 方案一 圖1-2 方案二 圖1-3 2 圖1-4 輸送機結(jié)構(gòu)圖 搖擺式輸送機由電動機，減速器，絞鏈機構(gòu)，和拖扳組成，其中電動機與減速器之間由皮帶輪聯(lián)結(jié)傳動。電動機輸出軸上再加裝飛輪裝置使其工作平穩(wěn)。 2電動機的選擇與計算 2.1電動機類型的選擇 電動機類型根據(jù)動力源和工作條件，選用 Y系列三相異步電動機 2.2電動機功率的選擇 F=38300X0.35=13405N 取拖動板和寬為0.3m，礦石高為0.15m根跟要求每小時540噸計算出礦石的平均速度為0.7m/s 工作機所需要的有效功率： Pw=F·v/1000=3000×0.35×1.7÷1000＝2.35（KW） 傳動裝置總效率（見課程設(shè)計指導(dǎo)書2-5） Pd=Pw/η =1.83/0.76=.35(KW) 根據(jù)JB3074-82 查選電動機。選用Y100L，其額定功率為 3KW，滿載轉(zhuǎn)速nm=2870r/min,同步轉(zhuǎn)速V=3000r/min。再經(jīng)查表得：電動機的中心高H=100mm，外伸軸頸圍 28mm，軸外伸長度為 60mm。 3 傳動裝置的運動及動力參數(shù)的選擇及計算 3.1 傳動比 總傳動比：i總=n/ n12=2870/110=26 各級傳動比分配： 初定 ，， 3.2 各個軸的轉(zhuǎn)速計算 n1=nm/i1=2870 r/min n2=n1/i2=1095 r/min n3=n2/i3=110 r/min 3.3 各軸的輸入功率計算 P1=pdη8η7 =3×0.95×0.99=2.52 P2=p1η6η5=2.52×0.97×0.99=2.42 P3=p2η4η3=2.42×0.97×0.99=2.33 P4=p3η2η1=2.33×0.99×0.99=2.28 4 V 帶的設(shè)計計算 4.1 計算功率P：據(jù)（表 4—10）取工況系數(shù)KA=1.1，則P=KA·P=3.36（KW） 4.2 選取V帶型號：根據(jù)PC=3.36KW和n=2870r/min 查表5-12a(機設(shè))選A型V帶。 確定帶輪直徑 參考表5-12a（機設(shè)）及表5-3（機設(shè)）選取小帶輪直徑 （電機中心高符合要求） 4.3 驗算帶速 由式5-7（機設(shè)） 4.4 從動帶輪直徑 查表5-4（機設(shè)） 取 4.5 傳動比 ; 4.6 從動輪轉(zhuǎn)速 4.7 確定中心距和帶長 （1）、按式（5-23機設(shè)）初選中心距 ; 取 （2）、按式(5-24機設(shè))求帶的計算基礎(chǔ)準長度L0 查圖.5-7(機設(shè))取帶的基準長度Ld=1400mm (3)、按式(5-25機設(shè))計算中心距:a (4)、按式（5-26機設(shè)）確定中心距調(diào)整范圍 4.8 驗算小帶輪包角α1 （由機械設(shè)計公式5-11) 4.9 確定V帶根數(shù)Z (1)、由表（5-7機設(shè)）查得dd1=112， n1=2870r/min時，單根V帶的額定功率為1.6KW，用線性插值法求n1=2870r/min時的額定功率P0值。 (2)、所以要用的皮帶個數(shù)為3/1.6=2根，取Z=2根 4.10 計算單根V帶初拉力F0，由式（5-29）機設(shè)。 4.11 計算對軸的壓力FQ， 由式（5-30機設(shè)）得 4.12 確定帶輪的結(jié)構(gòu)尺寸，給制帶輪工作圖 小帶輪基準直徑d1=90mm采用實心式結(jié)構(gòu)。大帶輪基準直徑d2=224mm，采用腹板式結(jié)構(gòu)，基準圖見工作圖。 5 齒輪的設(shè)計計算 5.1 高速級減速齒輪設(shè)計（直齒圓柱齒輪） 5.1.1齒輪的材料，精度和齒數(shù)選擇 因傳遞功率不大，轉(zhuǎn)速不高，材料按表7-1選取，都采用45號鋼，鍛選項毛坯，大齒輪、正火處理，小齒輪調(diào)質(zhì)，均用軟齒面。齒輪精度用8級，輪齒表面精糙度為Ra3.2，軟齒面閉式傳動，失效形式為占蝕，考慮傳動平穩(wěn)性，齒數(shù)宜取多些，取Z1=34 則Z2=Z1× i=34×2.62=89 5.1.2設(shè)計計算。 （1）設(shè)計準則，按齒面接觸疲勞強度計算，再按齒根彎曲疲勞強度校核。 （2)按齒面接觸疲勞強度設(shè)計，由式（7-9） T1=9.55×106×P/n=9.55×106×3.36/384=10125 N·mm 由機械設(shè)計表（7-1）選取材料的接觸疲勞，極限應(yīng)力為 б1=580 б2=560 由機械設(shè)計表7-3選取材料彎曲疲勞極陰應(yīng)力 бHILim=230 бHILin=210 由機械設(shè)計表3-4查得接觸疲勞壽命系數(shù)；ZN1=1.1 ZN2=1.04 由表7-2查得接觸疲勞安全系數(shù)：SFmin=1.4 又YST=2.0 試選Kt=1.3 由式(7-1)(7-2)求許用接觸應(yīng)力和許用彎曲應(yīng)力 將有關(guān)值代入式得 則V1=(πd1tn1/60×1000)=1.3m/s Z1 V1/100)=1.3×(34/100)m/s=0.44m/s 查表7-10得Kv=1.05 由表7-3查和得K A=1.25.由表7-4查得Kβ=1.08.取Kα=1.05.則KH=KAKVKβKα=1.42 , 修正 M=d1/Z1=1.96mm 由表7-6取標準模數(shù)：m=2mm （3) 計算幾何尺寸 d1=mz1=2×34=68mm 19 d2=mz2=2×89=178mm a=m(z1＋z2)/2=123mm b=φddt=1×68=68mm 取b2=65mm b1=b2+10=75 （4) 校核齒根彎曲疲勞強度 由表7-18查得，YFS1=4.1，YFS2=4.0 取Yε=0.7 由式(7-12)校核大小齒輪的彎曲強度. 5.2 低速級減速齒輪設(shè)計（直齒圓柱齒輪） 5.2.1齒輪的材料，精度和齒數(shù)選擇，因傳遞功率不大，轉(zhuǎn)速不高，材料按表7-1選取，都采用45號鋼，鍛選項毛坯，大齒輪、正火處理，小齒輪調(diào)質(zhì)，均用軟齒面。齒輪精度用8級，輪齒表面精糙度為Ra3.2，軟齒面閉式傳動，失效形式為占蝕，考慮傳動平穩(wěn)性，齒數(shù)宜取多些，取Z1=34 則Z2=Z1×i=34×3.7=104 5.2.2設(shè)計計算。 設(shè)計準則，按齒面接觸疲勞強度計算，再按齒根彎曲疲勞強度校核。 按齒面接觸疲勞強度設(shè)計，由式（7-9） T1=9.55×106×P/n=9.55×106×5.20/148=335540 N·mm 由表7-6選取材料的接觸疲勞，極限應(yīng)力為б1=580 б2=560 由表7-7選取材料彎曲疲勞極陰應(yīng)力б3=230 б4=210 應(yīng)力循環(huán)次數(shù)N由式（7-3）計算 N1=60n at=60×148×(8×360×10)=2.55×109 N2= N1/u=2.55×109/3.07=8.33×108 由表7-8查得接觸疲勞壽命系數(shù)；ZN1=1.1 ZN2=1.04 由表7-2查得接觸疲勞安全系數(shù)：試選Kt=1.3 由式(7-1)(7-2)求許用接觸應(yīng)力和許用彎曲應(yīng)力 將有關(guān)值代入式得 則V1=(πd1tn1/60×1000)=0.55m/s ( Z1 V1/100)=0.55×(34/100)m/s=0.19m/s 查表7-10得Kv=1.05 由表7-3查和得K A=1.25.由表7-4查得Kβ=1.08. 取Kα=1.05.則KH= =1.377 , 修正 M=d1/Z1=2.11mm 由表7-6取標準模數(shù)：m=2.5mm (3) 計算幾何尺寸 d1=mz1=2.5×34=85mm d2=mz2=2.5×104=260mm a=m(z1＋z2)/2=172.5mm b=φdt=1×85=85mm 取b2=85mm b1=b2+10=95 (4).校核齒根彎曲疲勞強度 由表7-18查得，YFS1=4.1，YFS2=4.0 取Yε=0.7 由式(7-12)校核大小齒輪的彎曲強度. 總結(jié)：高速級 z1=34 z2=89 m=2；低速級 z1=34 z2=104 m=2.5 6 軸的直徑計算及校核 6.1高速軸的設(shè)計 6.1.1 選擇軸的材料及熱處理 由于減速器傳遞的功率不大，對其重量和尺寸也無特殊要求故選擇常用材料45鋼,調(diào)質(zhì)處理。 6.1.2初估軸徑 按扭矩初估軸的直徑,查表10-2,得c=106至117,考慮到安裝聯(lián)軸器的軸段僅受扭矩作用。取c=110則: D1min= D2min= D3min= 6.1.3初選軸承 （1)軸選軸承為6208 （2)軸選軸承為6209 （3)軸選軸承為6212 根據(jù)軸承確定各軸安裝軸承的直徑為: D1=40mm D2=45mm D3=60mm 6.1.4結(jié)構(gòu)設(shè)計 為了拆裝方便,減速器殼體用剖分式,軸的結(jié)構(gòu)形狀如圖所示。確定高速軸和各段直徑和長度。 （1)初估軸徑后,句可按軸上零件的安裝順序,從左端開始確定直徑.該軸軸段1安裝軸承6008,故該段直徑為40mm。2段裝齒輪，為了便于安裝，取2段為44mm。齒輪右端用軸肩固定，計算得軸肩的高度為4.5mm，取3段為53mm。5段裝軸承，直徑和1段一樣為40mm。4段不裝任何零件，但考慮到軸承的軸向定位，及軸承的安裝，取4段為42mm。6段應(yīng)與密封毛氈的尺寸同時確定，查機械設(shè)計手冊，選用JB/ZQ4606-1986中d=36mm的毛氈圈，故取6段36mm。7段裝大帶輪，取為32mm>dmin 。 （2）各軸段長度的確定 軸段1的長度為軸承6008的寬度和軸承到箱體內(nèi)壁的距離加上箱體內(nèi)壁到齒輪端面的距離加上2mm，l1=32mm。2段應(yīng)比齒輪寬略小2mm，為l2=73mm。3段的長度按軸肩寬度公式計算l3=1.4h；去l3=6mm，4段：l4=109mm。l5和軸承6008同寬取l5=15mm。l6=55mm，7段同大帶輪 同寬，取l7=90mm。其中l(wèi)4，l6是在確定其它段長度和箱體內(nèi)壁寬后確定的。 于是，可得軸的支點上受力點間的跨距L1=52.5mm，L2=159mm，L3=107.5mm。 （3）軸上零件的周向固定 為了保證良好的對中性，齒輪與軸選用過盈配合H7/r6。與軸承內(nèi)圈配合軸勁選用k6，齒輪與大帶輪均采用A型普通平鍵聯(lián)接，分別為16*63 GB1096-1979 （4）軸上倒角與圓角 為保證6208軸承內(nèi)圈端面緊靠定位軸肩的端面，根據(jù)軸承手冊的推薦，取軸肩圓角半徑為1mm。其他軸肩圓角半徑均為2mm。根據(jù)標準GB6403.4-1986，軸的左右端倒角均為1*45。。 (5) 軸的受力分析 圖6-1軸的受力圖 畫軸的受力簡圖。計算支座反力。 Ft=2T1/d1= Fr=Fttg20。=3784 FQ=1588N 在水平面上 F= FR2H=Fr-FR1H=1377-966=411N 在垂直面上 FR1V= Fr2V=Ft- FR1V=1377-352=1025N 畫彎矩圖 在水平面上，a-a剖面左側(cè) MAh=FR1Hl3=96652.5=50.715N·m a-a剖面右側(cè) M’Ah=FR2Hl2=411153=62.88 N·m 在垂直面上 MAv=M’AV=FR1Vl2=352×153=53.856 N·m 合成彎矩，a-a剖面左側(cè) a-a剖面右側(cè) 畫轉(zhuǎn)矩圖 轉(zhuǎn)矩 3784×（68/2）=128.7N·m (6).判斷危險截面 顯然，如圖所示，a-a剖面左側(cè)合成彎矩最大、扭矩為T，該截面左側(cè)可能是危險截面；b-b截面處合成灣矩雖不是最大，但該截面左側(cè)也可能是危險截面。若從疲勞強度考慮，a-a，b-b截面右側(cè)均有應(yīng)力集中，且b-b截面處應(yīng)力集中更嚴重，故a-a截面左側(cè)和b-b截面左、右側(cè)又均有可能是疲勞破壞危險截面。 (7).軸的彎扭合成強度校核 由表10-1查得 1)a-a剖面左側(cè) 3=0.1×443=8.5184m3 =14.57 2）b-b截面左側(cè) 3=0.1×423=7.41m3 b-b截面處合成彎矩Mb: =174 N·m =27 (8).軸的安全系數(shù)校核在a-a截面左側(cè) WT=0.2d3=0.2×443=17036.8mm3 由附表10-1查得由附表10-4查得絕對尺寸系數(shù);軸經(jīng)磨削加工, 由機械設(shè)計附表10-5查得質(zhì)量系數(shù).則 彎曲應(yīng)力 應(yīng)力幅 平均應(yīng)力 切應(yīng)力 安全系數(shù) 查表10-6得許用安全系數(shù)=1.3～1.5,顯然S>,故a-a剖面安全. 1)b-b截面右側(cè) 抗彎截面系數(shù)3=0.1×533=14.887m3 抗扭截面系數(shù)WT=0.2d3=0.2×533=29.775 m3 又Mb=174 N·m,故彎曲應(yīng)力 切應(yīng)力 由附表10-1查得過盈配合引起的有效應(yīng)力集中系數(shù) 則 顯然S>,故b-b截面右側(cè)安全。 2）b-b截面左側(cè) WT=0.2d3=0.2×423=14.82 m3 b-b截面左右側(cè)的彎矩、扭矩相同。 彎曲應(yīng)力 切應(yīng)力 由附表10-2查得圓角引起的有效應(yīng)力集中系數(shù)。由附表10-4查得絕對尺寸系數(shù)。又。則 顯然S> 6.2中間軸的設(shè)計 6.2.1確定中軸的各軸直徑和長度 初估軸徑后,句可按軸上零件的安裝順序,從左端開始確定直徑.該軸軸段1安裝軸承6209,故該段直徑為45mm。2段裝齒輪，為了便于安裝，取2段為50mm。齒輪右端用軸肩固定，計算得軸肩的高度為5mm，取3段為60mm。4段裝齒輪，為了便于安裝，取段為50mm。5段裝軸承，直徑和1段一樣為45mm。 6.2.2各軸段長度的確定 軸段1的長度為軸承6209的寬度和套筒的距離，取l1=32mm。2段應(yīng)比齒輪寬略小2mm，為l2=63mm。3段的長度按軸肩寬度l3=27mm，4段：l4=93mm。l5和軸承6209同寬取l5=32mm。 6.2.3軸上零件的周向固定 為了保證良好的對中性，齒輪與軸選用過盈配合H7/r6。與軸承內(nèi)圈配合軸勁選用k6，齒輪與大帶輪均采用A型普通平鍵聯(lián)接，分別為16*63 GB1096-1979及鍵10*80 GB1096-1979。 6.2.4軸上倒角與圓角 為保證6209軸承內(nèi)圈端面緊靠定位軸肩的端面，根據(jù)軸承手冊的推薦，取軸肩圓角半徑為1mm。其他軸肩圓角半徑均為2mm。根據(jù)標準GB6403.4-1986，軸的左右端倒角均為1*45 6.3 低速軸的設(shè)計 6.3.1確定低速軸的各軸直徑和長度 初估軸徑后,句可按軸上零件的安裝順序,從左端開始確定直徑.該軸軸段1安裝軸承6212,故該段直徑為60mm。2段裝齒輪，為了便于安裝，取2段為68mm。齒輪右端用軸肩固定，計算得軸肩的高度為4.5mm，取3段為72mm。5段裝軸承，直徑和1段一樣為60mm。4段不裝任何零件，但考慮到軸承的軸向定位，及軸承的安裝，取4段為65mm。6段應(yīng)與密封毛氈的尺寸同時確定，查機械設(shè)計手冊，選用JB/ZQ4606-1986中d=58mm的毛氈圈，故取6段58mm。7段裝大帶輪，取為52mm>dmin 。 6.3.2各軸段長度的確定 軸段1的長度為軸承6212的寬度和套筒的距離l1=37mm。2段應(yīng)比齒輪寬略小2mm，為l2=83mm。3段的長度按軸肩寬度公式計算l3=1.4h；去l3=6mm，4段：l4=94mm。l5和軸承6212同寬和套筒長度取l5=32mm。l6=55mm，7段同大帶輪同寬，取l7=90mm。其中l(wèi)4，l6是在確定其它段長度和箱體內(nèi)壁寬后確定的。 6.3.3軸上零件的周向固定 為了保證良好的對中性，齒輪與軸選用過盈配合H7/r6。與軸承內(nèi)圈配合軸勁選用k6，齒輪與大帶輪均采用A型普通平鍵聯(lián)接，分別為16*63 GB1096-1979 6.3.4軸上倒角與圓角 為保證6212軸承內(nèi)圈端面緊靠定位軸肩的端面，根據(jù)軸承手冊的推薦，取軸肩圓角半徑為1mm。其他軸肩圓角半徑均為2mm。根據(jù)標準GB6403.4-1986，軸的左右端倒角均為1*45。。 7鍵連接的選擇及計算 7.1高速軸 鍵1 10×8 L=80 GB1096-79 則強度條件為 查表許用擠壓應(yīng)力 所以鍵的強度足夠 鍵2 12×8 L=63 GB1096-79 則強度條件為 查表許用擠壓應(yīng)力 所以鍵的強度足夠 7.2中間軸 鍵1 14×9 L=56 GB1096-79 則強度條件為 查表許用擠壓應(yīng)力， 所以鍵的強度足夠 鍵2 14×9 L=80 GB1096-79 則強度條件為 查表許用擠壓應(yīng)力，所以鍵的強度足夠 7.3低速軸 鍵1 18×11 L=70 GB1096-79 鍵2 12×8 L=63 GB1096-79 同上校核所得鍵，所以鍵的強度足夠 8滾動軸承的計算 FR2H=Fr-FR1H=1377-966=411N Fr2V=Ft- FR1V=1377-352=1025N 軸承的型號為6208，Cr=16.2 kN FA/COr=0 計算當量動載荷 查表得fP=1.2徑向載荷系數(shù)X和軸向載荷系數(shù)Y為X=1，Y=0 =1.2×（1×352）=422.4 N 驗算6208的壽命 驗算右邊軸承 9 潤滑和密封方式的選擇 減速器齒輪選擇油潤滑，潤滑油型號為CKC220，采用油池潤滑，浸油深度為H=124mm。由于齒輪圓周速度 V1 =1.659m/s, V2 =0.739m/s,均小于 2m/s，軸承采用脂潤滑。 10 箱體及附件的結(jié)構(gòu)設(shè)計和選擇 10.1箱體的選擇 箱體有鑄造箱體和焊接箱體兩種。鑄造箱體的剛性較好，外形比較美觀，而且易于切削加工，可以吸收振動和消除噪聲，但是鑄造的箱體重量比較大，鑄造還適用于批量生產(chǎn)，生產(chǎn)效率比較高。焊接的箱體針對于單體或小批量生產(chǎn)的箱體，采用鋼板通過焊接而成，箱體壁薄，重量小，可以節(jié)省材料，生產(chǎn)周期也比較短但是要求的技術(shù)含量比較高。本題傳動有輕微振動，考慮到技術(shù)性能而應(yīng)該采用鑄造箱體更適合此設(shè)計。 10.2、箱體的結(jié)構(gòu)尺寸 箱體壁厚 箱蓋壁厚 箱座凸緣厚度b=15mm 箱蓋凸緣厚度b1=15mm 箱座底凸緣厚度b2=25mm 地腳螺栓直徑df=M16 地腳螺栓數(shù)目n=4 軸承旁聯(lián)接螺栓直徑d1=M12 聯(lián)接螺栓d2的間距l(xiāng)=150mm 軸承端蓋螺釘直徑d3=M8 定位銷直徑d=6mm df 、d1 、d2至外箱壁的距離C1=18mm、18 mm、13 mm df、d2至凸緣邊緣的距離C2=16mm、11 mm 軸承旁凸臺半徑R1=11mm 凸臺高度根據(jù)低速軸承座外半徑確定 外箱壁至軸承座端面距離L1=40mm 大齒輪頂圓與內(nèi)箱壁距離△1=10mm 齒輪端面與內(nèi)箱壁距離△2=10mm 箱蓋，箱座肋厚m1=m=7mm 軸承端蓋外徑D2 ：凸緣式端蓋：D+（5～5.5）d3 以上尺寸參考機械設(shè)計課程設(shè)計P17～P21 10.3傳動比 原始分配傳動比為：i1=2.62 i2=3.07 i3=2.5 修正后 ：i1=2.5 i2=2.62 i3=3.07 各軸新的轉(zhuǎn)速為 ：n1=960/2.5=3.84 n2=384/2.61=147 n3=147/3.07=48 10.4各軸的輸入功率 P1=pdη8η7 =3×0.95×0.99=2.52 P2=p1η6η5=2.52×0.97×0.99=2.42 P3=p2η4η3=2.42×0.97×0.99=2.33 P4=p3η2η1=2.33×0.99×0.99=2.28 10.5各軸的輸入轉(zhuǎn)矩 T1=9550Pdi1η8η7/nm=9550×2.52×2.5×0.95×0.99=128.65 T2= T1 i2η6η5=128.65×2.42×0.97×0.99=323.68 T3= T2 i3η4η3=323.68×2.33×0.97×0.99=954.25 T4= T3 η2η1=954.23×0.99×0.99=935.26 齒輪的結(jié)構(gòu)尺寸 兩小齒輪采用實心結(jié)構(gòu) 兩大齒輪采用復(fù)板式結(jié)構(gòu) 齒輪z1尺寸 z=34 d1=68 m=2 d=44 b=75 d1=68 齒輪z2的尺寸d2=178 z2=89 m=2 b=65 d4=49 齒輪3尺寸d=49 d3=85 z3=34 m=2.5 b=95 齒輪4尺寸 d=64 d4=260 z4=104 m=2.5 b=85 11擺桿分析 根據(jù)各軸的輸出轉(zhuǎn)矩的計算結(jié)果得 T3=454.25N.m 既裝有搖桿輸出矩為 T3=454.25N.m 取搖桿在一個較特殊的位置作分析 當搖桿在豎直位置時桿的傳動角近似為90度 即f1*Lab=T3 F1=T3/Lab=454.25/0.09=5047 N 根據(jù)力矩平衡求F2 圖11-1擺桿受力分析 圖11-2搖桿受力分析 即 F1*LO2B=F2*L2OC F2=F1*LO2B/LO2C=5047x0.16/0.27=2990N 即 F0=F1-F2=5047-2990=2057N 可知應(yīng)力集中處為F1受力點 即最大彎矩 M=F0*Lab=4319.62x0.16=691.14 N.m 桿件的形狀為長方形長寬比為2 圖11-3桿件截面尺寸 即 a=2b ， 求 慣性矩為Ix=1/2ba3=1/12x8*b4=2/4b4 最大拉應(yīng)力δ=M*a/2Ix=3M/2b3=1036.71/b3 桿件材料為45鋼正火處理 δmin=300MPa 取安全系數(shù)1.2 即1.2δ<δmin 即 1.2x1036.71/b3 <300x106 b>= b>=0.016m=16mm 取 b 為16mm 既a=2b=32mm 小結(jié) 機械設(shè)畢業(yè)設(shè)計是機械課程當中一個重要環(huán)節(jié)，通過這次畢業(yè)設(shè)計，我從各個方面都受到了機械設(shè)計的訓(xùn)練，對機械的有關(guān)各個零部件有機的結(jié)合在一起得到了深刻的認識。 由于在設(shè)計方面我們沒有經(jīng)驗，理論知識學(xué)的不牢固，在設(shè)計中難免會出現(xiàn)這樣那樣的問題，如：在選擇計算標準件是可能會出現(xiàn)誤差，如果是聯(lián)系緊密或者循序漸進的計算誤差會更大，在查表和計算上精度不夠準 在設(shè)計的過程中，培養(yǎng)了我綜合應(yīng)用機械設(shè)計課程及其他課程的理論知識和應(yīng)用生產(chǎn)實際知識解決工程實際問題的能力，在設(shè)計的過程中還培養(yǎng)出了我們的團隊精神，大家共同解決了許多個人無法解決的問題，在這些過程中我們深刻地認識到了自己在知識的理解和接受應(yīng)用方面的不足，在今后的學(xué)習(xí)過程中我們會更加努力和團結(jié)。 致謝 這次畢業(yè)設(shè)計得到了很多老師和同學(xué)的幫助，其中我的導(dǎo)師劉媛媛老師對我的關(guān)心和支持尤為重要，而劉老師每次不管忙或閑，總會抽空來找我面談，然后一起商量解決的辦法。 另外，感謝校方給予我這樣一次機會，能夠獨立地完成一個課題，并在這個過程當中，能夠更多學(xué)習(xí)一些實踐應(yīng)用知識，增強了我們實踐操作和動手應(yīng)用能力，提高了獨立思考的能力。再一次對我的母校表示感謝。 最后，感謝所有在這次畢業(yè)設(shè)計中給予過我?guī)椭娜恕?對上述同學(xué)老師朋友，再一次真誠地表示感謝 參考文獻 [1] 龔桂義，羅圣國主編.《機械設(shè)計課程設(shè)計指導(dǎo)書》第二版：高等教育出版社，2010. [2] 吳宗澤，羅圣國主編.《機械設(shè)計課程設(shè)計手冊》第三版：高等教育出版社，2006. [3] 大連理工大學(xué)工程圖學(xué)教研室編.《機械制圖》第六版：高等教育出版社，2007. [4] 孫桓，葛文杰主編.《機械原理》第七版：高等教育出版社，2006. [5] 濮良貴，紀名剛主編.《機械設(shè)計》第八版:高等教育出版社，2006. [6] 王忠主編. 《機械工程材料》第一版：清華大學(xué)出版社，2005. [7] 韓進宏主編.《互換性與技術(shù)測量》 第一版：機械工業(yè)出版社，2004. [8] 于俊一，鄒青主編.《機械制造技術(shù)基礎(chǔ)》第二版：機械工業(yè)出版社，2009. [9] 嚴紹華主編.《熱加工工藝基礎(chǔ)》第二版：高等教育出版社，2004. [10] 單祖輝主編.《材料力學(xué)》第二版：高等教育出版社，2004. [11] 楊有道，錢瑞明．I、Ⅱ型曲柄搖桿機構(gòu)的運動性能研究、機械制造與研究，2004. [12] 閔劍青，徐梓斌.鉸鏈六連桿機構(gòu)力學(xué)分析系統(tǒng)，2005 河南理工大學(xué)萬方科技學(xué)院本科畢業(yè)論文 附錄： 外文資料與中文翻譯 外文資料： Common Fault Analysis For Belt Conveyer Ir. G. Lodewijks, Delft University of Technology, The Netherlands Belt conveyers as continuous bulk material conveying machinery have been widely used in the world, electric power plants, metallurgical industry and? foodstuff industry as well as in bulk material conveying machinery such as ship loader and bucket-wheel stacker-reclaimer. In the purchase, design, manufacture, erection and operation of this kind of equipment, some of new users are not familiar with them. Common fault causes and their handling methods of this kind of equipment are analyzed and described herein as a matter of experience in the past years and from the point of view of users. 1. Handling of belt deviation of belt conveyer: The belt deviation of belt conveyer during operation is the most common fault. To handle this type of fault, emphasis should be placed on the dimensional accuracy of erection and the routine maintenance. There are several kinds of causes. The differential treatment should be made according to the different causes. 1.1?? Adjustment of carrying roller set: If the belt of belt conveyer is deviated in the middle of the whole belt conveyer, the position of carrying roller set is adjusted. During the manufacture, the mounting holes on both sides of carrying roller set are machined to slots for the convenience of adjustment. For the specific adjusting methods, see Fig. 1. The specific method is that when the belt is deviated from the side, that side of carrying roller set should be moved forwards the direction of travel, or the other side moved backward the direction of travel. If the belt is deviated from the upper direction as shown in Fig. 1, the bottom position of carrying roller set should be moved to the left side and the upper position of carrying roller set is moved to the right side. ? 1.2 Installation of self-aligning carrying roller set: There are many types of self-aligning carrying roller sets such as intermediate rotating shaft type, four-link type and edging roll type. The principle is that by utilizing blocking or rotating the rollers in the direction of horizontal plane, the rollers are blocked by rotating or the lateral thrust is produce to make the belt be automatically aligned so as to attain the object of adjustment of belt deviation. It is feasible, in general, to use this method when the whole length of belt of belt conveyer is shorter or the belt conveyer is operated in the bidirection. The causes are that the shorter belt conveyer is easier to be deviated and it is not easily adjusted. Therefore, this method is not used for the longer belt conveyers because use of self-aligning carrying roller sets can have certain influence on the service life of belt. 1.3 Adjustment of positions of head roll and bend pulley: Adjustment of head roll and bend pulley is a key link of adjustment of belt deviation. Since there are at least 2 to 5 pulleys in one belt conveyer, the mounting position of all the pulleys must be perpendicular to the central line along the length of belt conveyer. If the deviation is too large, the belt deviation occurs of necessity. The adjusting method is similar to that of carrying roller set. For head pulleys, if the belt is deviated from the right side of pulley, the bearing block at the right side should be moved forward and if the belt is deviated from the left side of pulley, the bearing block at the right side should be moved forward. For corresponding pulleys, the bearing block at the left side can be also moved backward or the bearing block at the right side moved backward. The adjusting method of tail pulleys is just opposite from that of head pulleys. For the adjusting method, see Fig. 2. The pulleys are repeatedly adjusted till the belt is adjusted to the expected position. It is preferable to make the mounting position accurate before adjustment of head rolls or bend pulleys. 1.4 Adjustment of belt tensioning device: Adjustment of belt tensioning device is a very important link of adjustment of belt deviation of belt conveyer. Two bend pulleys on the top of counterweighted tensioning device should be not only perpendicular to the direction of the belt along length but also to the gravity vertical, i.e. it is ensured that the shaft center line is horizontal. When the screw tensioning device or hydraulic tensioning device is used, two bearing blocks of tensioning pulley should be synchronously translated so as to ensure that the axial line of pulley is perpendicular to the longitudinal direction of belt. The specific adjusting method of belt deviation is similar to the adjusting method of pulleys. ?1.5 Influence of material receiving position at the transfer point on the belt deviation: The material receiving position at the transfer point has a great influence on the belt deviation, especially when the projection of two belt conveyers in the horizontal plane. The relative height of the upper belt conveyer and lower belt conveyer at the transfer point should be normally taken into consideration. The lower the relative height the greater the horizontal velocity component of material and also the greater the lateral impact on the lower layer of belt. In addition, the material is difficult to center so as to make the material at the cross section of belt be skew and finally lead to belt deviation. If the material is deviated from the right side, the belt will be deviated from the left side, vice versa. In the course of design, the relative height of two belt conveyers is increased as practically as possible. The form and dimension of the upper hopper and the lower hopper, chute etc. of bulk material mobile conveying machinery which are limited by space should be more carefully taken into consideration. In general, it is applicable for the width of chute being? about 2/3 of that of belt. In order to reduce or avoid the belt from being deviated, the baffles can be increased to block the material and change the falling direction and position of material. For the uncentering of material on the belt, see Fig. 3. ?1.6 Adjustment of belt deviation of bi-directional belt conveyer: Adjustment of belt deviation of bi-directional belt conveyer is relatively more difficult than that of belt deviation of one-way belt conveyer. During the specific adjustment, the adjustment should be done from one direction, and then from the other. During adjusting, it must be carefully observed to the relationship between the travel direction of belt and the tendency of belt deviation. The adjustment should be done one by one. Firstly emphasis should be placed on adjustment of head rolls and bend pulleys. Secondly emphasis is placed on adjustment of the carrying rollers and the material receiving point. In addition, it should be noted that the load is uniformly distributed at the section of the belt along the length when the belt is at the vulcanized joints. When the leading chain is used for traction, the load at both sides should be distributed as equally as possible. 2. Material spillage on belt conveyer: Material spillage on the belt conveyer is a general character. The causes are embodied in several aspects. Therefore, emphasis is placed on strengthening the routine maintenance. 2.1 Material spillage at transfer point: Material spillage occurs mainly at the transfer points such as material receiving hopper and chute. If serious overload occurs on the belt conveyer, the rubber skirt plate of chute of belt conveyer can be damaged. Since the steel plate of chute is far from the rubber skirt plate in the design, the material will be flown out of the chute. The problem can be solved by controlling the conveying capacity and strengthening the routine maintenance. ?2.2 Material spillage at the concave section of belt during hanging: The belt at the concave section is floated when the radius of curvature is smaller. At this tome the belt in the form of trough has been changed because the belt has been deviated from the trough carrying roller set. In that case, the angle of trough becomes small so as to make part of the material be split out. Therefore, the bigger radius of curvature at the concave section is used as practically as possible in the design in order to avoid the material spillage. If the concave section is designed according to the section of transition without arc in the mechanical traveling ship loader or stacker-reclaimer in order to shorten its tail car, the material spillage may easily occur when there is less room for selection of belt width. ?2.3 Material spillage during the belt deviation: The material spillage occurs during the belt deviation because two edges of belt have changed in height during operation, i.e. one edge is higher and the other is lower. The material is split out from the lower edge. The handling method is to adjust the belt deviation. ?3. Abnormal noise: When the belt conveyer is operated, it could sound abnormally from its drive, head roll, bend pulley or carrying roller set. The failure of equipment can be determined according to the abnormal noise. ?3.1 Noise occurs when the carrying roller being seriously deviated: When the belt conveyer is operated, the abnormal noise could be produced and accompanied by periodic vibration, especially in the return rolls. The longer the roll and the heavier the deadweight, the higher the noise. There are mainly two causes for noise: one is that the wall thickness of seamless pipe made of carrying roller is non-uniform so as to produce the greater centrifugal force and the other is that during machining, the center of holes of bearing at both ends is greatly deviated from the center of top circle so as to produce the greater centrifugal force. The rolls can continue to use in case the bearings have not been damaged and the noise is allowed to exist. 3.2 Noise occurs when two shafts of coupling being not coaxial: The abnormal noise is produced from the coupling between the high-speed shaft of motor in the drive and that of reducer or from the coupling with brake wheel, it is also accompanied by the vibration that is identical with the rotational frequency of motor. If the noise is produced, the position of motor or reducer is adjusted in time in order to avoid the rupture of input shaft of reducer. 3.3 Abnormal noise of bend pulley and head roll: When the bend pulleys and head rolls are operated normally, the noise is very low. If the abnormal noise is produced, the bearing, in general, may be damaged. If the cackle is produced from the bearing block, the bearing must be replaced. ?4. Rupture of shaft of reducer: The rupture of shaft of reducer generally occurs at the high-speed shaft of reducer. The usual fault is that the first-stage shaft of reducer is used as the high-speed shaft of vertical bevel gear shaft. There are mainly two causes for shaft rupture as follows. ?4.1 Inadequate design strength of high-speed shaft of reducer: This fault, in general, occurs at the shaft shoulder. Because the transient round angle exists at this place, it is subjected to fatigue damage. If the round angle is too small, the rupture of shaft of reducer can occur in the short time. After shaft rupture, the fracture is generally flush. If this fault is found out, the reducer should be replaced or the design of reducer should be modified. ?4.2 High-speed shaft being non-axial: When the high-speed shaft of motor is non-axial, the radial load will be increased on the input shaft of reducer so as to increase the bending moment on the shaft. If the shafts are operated in such a way for a long time, the shaft rupture could occur. During installation and maintenance, the position of shaft should be carefully adjusted in order to ensure that the two shafts are aligned. In most cases, the rupture of motor shaft can not occur, because the material used for motor shaft is #45 steel, the motor shaft is thicker and has good stress concentration. ?4.3 Rupture of shaft in case two motors are used: The double-motor drive means that two reducers and two motors are installed on one head roll. When there is less room for design or selection of high-speed shaft of reducer, the shaft rupture easily occurs. In the past years the hydraulic coupling was not used in the drive of belt conveyer, so the failure easily occurred. The cause was that it was difficult to ensure that the speeds were synchronous and the loads uniformly distributed. Now the hydraulic couplings have been used in most of the belt conveyers, so the shaft rupture does not frequently occur, but it should be noted that the hydraulic coupling can not be filled with excess quantity of oil during operation so as to make it have an effect on limitation of moment of force and increase the service life of hydraulic coupling. 5. Shorter service life of belt: The service life of belt and the service modes are related to the quality of belt. It should be ensured that the cleaners are operated reliably and in good order when the belt is operated. There is not any material on the return belt. If the above can not be guaranteed, the material on the return belt will enters into the head roll or the bend pulley along with the return belt. The belt will be damaged due to the material on the surface of belt, resulting in damage of the vulcanized rubber layer on the surface of pulley, breach of the belt and decrease of the service life of belt. The manufacturing quality of belt is the problem the users relatively give attention to. After the selection of a model of belt, its manufacturing quality should be also taken into consideration. The belts can be inspected by the national specialized institution of quality determination. The appearance inspection is carried out conventionally to see whether the crazing and aging exist and the resting period is over long after manufacture. One of the above occurs, the belts should not be purchased. The fissured belt to be initially found will be, in general, damaged in a short time. 6. Influence of radius of curvature at the convex-concave section of belt on belt conveyer 6.1 Arch camber at the convex section of belt in the middle of cross section: The arch camber often occurs at the convex section in the middle of cross section and the belt will be pleated, see Fig. 4. After the overlapped? belt enters into the bend pulley or head roll, the extent of damage of belt aggravated. The main causes for arch camber and overlapping are that the difference between the values of tensile force in a unit of length at the cross section of belt in the middle and on the outside is oversized so that the belt is slid into the middle to form the arch camber or overlapping. The magnitude of difference value of tensile force in a unit of length is related to the radius of curvature at the convex section and the trough angle of carrying roller. The bigger the trough angle, the smaller the radius of curvature at the convex section and the severer the arch camber and overlapping. When the trough angle of belt conveyer is equal to and more than 40 degrees, the arch camber and overlapping can occur even at the transition section of trough angle of head or tail roll which is run at the straight section. At this time the trough angle should be reduced or the length of transition section increased so as to make the trough angle of belt be transited. For the belt conveyer at the convex section, the radius of curvature at the convex section should be increased as practically as possible and the trough angle of roll reduced in the condition that the conveying capacity is met.? ?6.2 The belt at the convex section being seized between flat roll and web roll: The belt being seized between the flat roll and the web roll in the carrying roller set may generally occur in the bulk material mobile? conveying machinery such as ship loader and stacker-reclaimer. The belt seizure may easily occur when the cantilever at the root position of cantilever beam of such equipment is pitched downward. At this time it corresponds to the convex section occurring on the belt. The size required for the radius of curvature at the convex transition section can not be easily met because it is limited by the size of geometric position. The belt being seized between the flat roll and the web roll in the carrying roller set can occur only when the belt at the root of cantilever is passed through one or two carrying roller sets to form the convex section. The method of resolution is that the convex section formed by the original one or two carrying roller sets is changed to that formed by four or five carrying roller sets. For example, the belt conveyer is horizontally arrange at its rear, the cantilever is pitched downward at the angle of 12 degrees at its fore and the convex section is changed at the angle of 12 degrees. If five carrying roller sets are used to transit the angle change in this place, the belt is just buckled six times to attain the object of pitching downward at the angle of 12 degrees. The belt is buckled once at the angle of 2 degrees. After modification, the belt being seized between the flat roll and the web roll in the carrying roller set can not occur no longer. The design of four-link lever or follow-up frame can be used for the base of roller carrier in the transition place which position of angle is changed. 6.3 Bouncing and deflection of belt by the wind at the concave section when starting: If there is not any material on the belt when the belt conveyer is started, the belt will be bounced at the concave section and displaced by the wind in windy weather. Therefore, it is preferable that the pressure rollers are provided at the concave section to avoid the belt from being bounced or displaced by the wind. 7. Slipping of belt ?7.1 Slipping of belt of belt conveyer with counterweighed tensioning device: When the belt is slid in the belt conveyer with counterweighted tensioning device, it can be solved by adding the balance weights till the belt can not be slid. However, the balance weights should not be excessive in order to avoid the belt from being subjected to unnecessary oversized tensile force, thus resulting in decrease of the service life of belt. 7.2 Slipping of belt of belt conveyer with screw tensioning device or hydraulic tensioning device: The tensioning travel can be adjusted to increase the tensile force when the belt is slid in the belt conveyer with screw tensioning device or hydraulic tensioning device. At this time, however, a section of the belt can be cut out for re sulfurzation when the tensioning travel is not enough or the belt is permanently deformed. Brief summary: The belt conveyers are general-purpose mechanical equipment. They have been operated by the users for many years. However, the maintenance of belt conveyers must be done at regular intervals. Because of limitation of the length of a piece of writing, it is difficult indeed to include all contents in one article. The experience with operation and maintenance of belt conveyer can be gradually accumulated through routine work. We hope that this text will be helpful for the users of belt conveyer. 中文翻譯： 懸臂皮帶輸送機常見故障分析及處理 伊. 基. 勞德維加克斯，代爾夫特科技大學(xué)，荷蘭 帶式輸送機作為連續(xù)散裝物料的機械已廣泛用于世界，發(fā)電廠，冶金工業(yè)，食品工業(yè)以及散裝物料的輸送，如裝船機斗輪堆料機。在采購，設(shè)計，制造，安裝和運行這種設(shè)備，一些新用戶還不熟悉他們。從過去幾年的經(jīng)驗和用戶的觀點和意見中，對這種設(shè)備常見故障原因和處理方法進行了分析和描述。 1 皮帶輸送機皮帶跑偏處理：在操作中，皮帶輸送機皮帶跑偏是 常見的故障。為了解決這種類型的故障，重點應(yīng)放在安裝尺寸精度和日常維護。有幾種原因，應(yīng)根據(jù)不同原因區(qū)別對待。 1.1 托輥的設(shè)置調(diào)整：如果皮帶輸送機皮帶在輸送機中間跑偏食， 需要對托輥的位置進行調(diào)整。在制造中，托輥上加工的雙面安裝孔是為了方便托輥的調(diào)整。對于具體的調(diào)整方法，見圖1.具體的方法是，當帶是從側(cè)面偏離時，偏離一面的托輥運動方向應(yīng)向前運動，而另一方面向后移動，如圖1所示，如果皮帶是向上跑偏，托輥底部位置設(shè)置應(yīng)移動至左側(cè)并且托輥上不移動至右側(cè)。 1.2 自調(diào)心托輥的安裝設(shè)置：自調(diào)心托輥的種類有許多，如：中間 轉(zhuǎn)軸式，四連桿式和邊輥式。其原理是在水平面內(nèi)利用封鎖或旋轉(zhuǎn)的滾輪。滾輪式有旋轉(zhuǎn)或產(chǎn)生橫向推力使皮帶自動對齊以達到對皮帶跑偏的調(diào)整。這是可行的，在一般情況下，使用這種方法時皮帶輸送機皮帶整體長度較短或皮帶輸送機是雙向操作。其原理是較短的皮帶輸送機易跑偏并且不易調(diào)整。因此這種方法不用于較長的帶式輸送機，因為自調(diào)心托輥的使用對皮帶的使用有一定的影響。 1.3 頭部彎曲輥及滑輪的位置調(diào)整：