家用紙杯成型機(jī)設(shè)計(jì)外文翻譯

杭州電子科技大學(xué)畢業(yè)設(shè)計(jì)（論文）外文文獻(xiàn)翻譯畢設(shè)計(jì)論文）題目家用紙杯成型機(jī)設(shè)計(jì)翻譯題目對(duì)紙杯成型機(jī)桶形凸輪的優(yōu)化研究信息工程學(xué)院機(jī)械設(shè)計(jì)制造機(jī)器自動(dòng)化指導(dǎo)教師巢炎畢設(shè)計(jì)論文）題目家用紙杯成型機(jī)設(shè)計(jì)翻譯題目對(duì)紙杯成型機(jī)桶形凸輪的優(yōu)化研究信息工程學(xué)院機(jī)械設(shè)計(jì)制造機(jī)器自動(dòng)化指導(dǎo)教師巢炎對(duì)紙杯成型機(jī)桶形凸輪的優(yōu)化研究摘要1紙杯成型機(jī)一分鐘最多可以生產(chǎn)140個(gè)紙杯。如果生產(chǎn)率提高，使凸輪的接觸力增加，會(huì)產(chǎn)生更多的振動(dòng)。因此，找一個(gè)減少凸輪振動(dòng)的方法是有必要的。槍管凸輪的輪廓線是通過使用多體動(dòng)力學(xué)模型去優(yōu)化。優(yōu)化的目標(biāo)是使?jié)L子與凸輪之間發(fā)生的接觸力最小。使用優(yōu)化的凸輪進(jìn)行了實(shí)驗(yàn)。對(duì)比目前的利率進(jìn)行優(yōu)化率較高的生產(chǎn)減振。關(guān)鍵字：紙杯；凸輪；多體動(dòng)力學(xué)；優(yōu)化；接觸力1簡(jiǎn)介紙杯的需求迅速增加由于他們?cè)诒Ｗo(hù)環(huán)境方面的便利性和有效性.為了滿足需求，目前的生產(chǎn)力也應(yīng)該要增加。然而，簡(jiǎn)單地增加生產(chǎn)率的結(jié)果在機(jī)器的振動(dòng)床上，當(dāng)機(jī)器受到震動(dòng)床的影響，會(huì)產(chǎn)生有缺陷的紙杯。這是一個(gè)嚴(yán)重的問題。圖1顯示當(dāng)前的紙杯成型機(jī)。目前的機(jī)器每分鐘可生產(chǎn)140個(gè)紙杯。如果生產(chǎn)率增加，回使每個(gè)凸輪磨損得很快，使凸輪不得不更換。紙杯是在紙杯成型機(jī)轉(zhuǎn)塔中形成，七輥指數(shù)是連接到轉(zhuǎn)塔的。該凸輪使?jié)L子凸輪旋轉(zhuǎn)移動(dòng)，所以轉(zhuǎn)塔也是轉(zhuǎn)動(dòng)的。接觸力發(fā)生的凸輪與滾輪之間。紙杯成型機(jī)運(yùn)行一段時(shí)間后，由于有接觸力所以磨損發(fā)生在桶凸輪和滾子的表面。然后，振動(dòng)和噪聲大大增加，需要更換凸輪和滾輪。在這一領(lǐng)域的研究已廣泛。伊佩克調(diào)查磨損機(jī)制的變化與凸輪軸的磨損的表面形貌。該凸輪表面的變化沿接觸表面的磨損機(jī)理H】。提出了一種模擬彭內(nèi)斯特的變速凸輪致動(dòng)器。該致動(dòng)器是一個(gè)凸輪移動(dòng)銷根據(jù)規(guī)定的運(yùn)動(dòng)規(guī)律。在換擋仿真，接觸力和磨損行為進(jìn)行了比較⑵。俊認(rèn)為，凸輪的磨損是由滾子和套筒之間的接觸力引起的。對(duì)圓柱凸輪的磨損點(diǎn)幾乎與多體動(dòng)力學(xué)模型的接觸力大點(diǎn)保持一致.[3].。曉優(yōu)化使用一個(gè)新的多項(xiàng)式樣條曲線和B樣條凸輪驅(qū)動(dòng)發(fā)動(dòng)機(jī)的凸輪輪廓曲線。分析定義的優(yōu)化問題是一種獨(dú)特的凸輪機(jī)構(gòu)⑷。新提出了一種運(yùn)用相對(duì)速度設(shè)計(jì)圓柱凸輪的形狀的方法。局部坐標(biāo)用相對(duì)速度的方法得出，桶凸輪1旭賢基姆韓國水原亞洲大學(xué)的博士生TaeWonpark水原亞洲大學(xué)機(jī)械工程學(xué)院的一名教授。的形狀是由CAD程序創(chuàng)建⑸。基姆開發(fā)了凸輪的形狀設(shè)計(jì)程序。用來參數(shù)輸入程序的凸輪輪廓數(shù)據(jù)點(diǎn)的計(jì)算。然后，數(shù)據(jù)被轉(zhuǎn)換成一個(gè)三維CAD模型⑹。暢作運(yùn)動(dòng)分析的一般框架對(duì)分度凸輪機(jī)構(gòu)的幾何設(shè)計(jì)。螺旋理論是用來描述凸輪結(jié)構(gòu)的機(jī)構(gòu)和運(yùn)動(dòng)方程的推導(dǎo)［7］。圖1紙杯成型機(jī)。然而，不建議用一個(gè)解決方案去減少接觸力。這些研究沒有驗(yàn)證所設(shè)計(jì)的凸輪的性能。對(duì)紙杯成型加工，需要一個(gè)優(yōu)化的筒凸輪輪廓減少接觸力的方法。結(jié)果可用于驗(yàn)證所提出的方法的可靠性。在這項(xiàng)研究中，每個(gè)凸輪型線優(yōu)化減少了滾子與凸輪之間的接觸力［8,9］。一個(gè)多體動(dòng)力學(xué)模型，用亞當(dāng)斯的計(jì)算接觸力來創(chuàng)造。選擇設(shè)計(jì)參數(shù)，顯著影響響應(yīng)變量的靈敏度分析，采用PlackettBurman設(shè)計(jì)表進(jìn)行。然后，根據(jù)中心復(fù)合實(shí)驗(yàn)設(shè)計(jì)表進(jìn)行。其次，利用響應(yīng)面分析，二階遞歸模型的功能，它提供對(duì)設(shè)計(jì)參數(shù)和響應(yīng)變量之間的關(guān)系估計(jì)信息。對(duì)模型的估計(jì)函數(shù)的可靠性進(jìn)行了驗(yàn)證通過方差分析（ANOVA）的方法。最后，序列二次規(guī)劃（SQP）方法被用來找到設(shè)計(jì)變量，使模型的函數(shù)值滿足線性或非線性約束條件［10-13］。為了驗(yàn)證該優(yōu)化方法的可靠性，建立了紙杯成型機(jī)的多體仿真模型。該凸輪和電流和優(yōu)化系統(tǒng)的輥之間的接觸力比較。此外，采用一個(gè)桶形凸輪的CAM原型試驗(yàn)。對(duì)紙杯成型機(jī)電流和優(yōu)化系統(tǒng)在床的振動(dòng)進(jìn)行比較。2.動(dòng)態(tài)分析2.1動(dòng)態(tài)分析模型紙杯成型機(jī)的動(dòng)態(tài)模型的建立分析了圓柱凸輪和采用多體動(dòng)力學(xué)分析軟件亞當(dāng)斯，如圖2所示的輥之間的接觸力。在一個(gè)紙杯成型機(jī)的索引驅(qū)動(dòng)器是一個(gè)旋轉(zhuǎn)或停止連接各生產(chǎn)工藝。該指數(shù)是由凸輪驅(qū)動(dòng)操作。動(dòng)態(tài)模型是由24部分組成的。連接，驅(qū)動(dòng)彈簧和接觸模型中定義的。該模型有一個(gè)總22自由度。表1提供了對(duì)動(dòng)態(tài)模型的信息。對(duì)圓柱凸輪三維模型，利用逆向工程技術(shù)建立.圖3顯示了逆向工程的程序。在這個(gè)過程中，真正的產(chǎn)品是用激光掃描儀，其中，在這項(xiàng)研究中，是一種非接觸式測(cè)量的激光探針。大約1000點(diǎn)，提出由線連接并轉(zhuǎn)化為在3DCAD程序進(jìn)行三維實(shí)體模型的表面2.2接觸力分析俊認(rèn)為凸輪磨損由于凸輪與滾輪之間的接觸力［3。圖5顯示分析結(jié)果的接觸力在滾子與凸輪之間。在三部分，接觸力大大增加。圖6顯示了當(dāng)軋輥孔型的圓柱凸輪導(dǎo)槽。第一點(diǎn)說明進(jìn)入導(dǎo)向槽輥；第二指示輥通過轉(zhuǎn)動(dòng)部分；和最后指示逃生槽輥。三穿點(diǎn)重合的地方，接觸力大大增加。在這三個(gè)部分凸輪磨損非常嚴(yán)重。磨損不僅發(fā)生在槽的整個(gè)表面而且發(fā)生在凹槽的幾點(diǎn)。因此，接觸力可的凸輪磨損的一個(gè)非常重要的因素。部分剛體24共同點(diǎn)外卷16平移7固定的1驅(qū)動(dòng)器1力彈簧14接觸點(diǎn)21自由度22表1.動(dòng)態(tài)模型的信息Etamvl圖2.紙杯成型機(jī)的多體動(dòng)力學(xué)模型5：DnkiHanr^dwl-Fig.3.利用三維激光掃描儀的圓柱凸輪反求工程程序■I3■*凡取由#1由C4TRPH^410五e(cuò)IQfl-Q向距離凸輪滾子幾何形狀變量結(jié)果凸輪曲線無量綱數(shù)X輥和指標(biāo)滾子數(shù)X從從凸輪中心水平向距離X滾子半徑O軋輥凸度的角XContsidFotcm<R：ioll&r0^1>SG-OO-I-S1.-BS向距離凸輪滾子幾何形狀變量結(jié)果凸輪曲線無量綱數(shù)X輥和指標(biāo)滾子數(shù)X從從凸輪中心水平向距離X滾子半徑O軋輥凸度的角XContsidFotcm<R：ioll&r0^1>SG-OO-I-S1.-BSTiirrns-亡"U]-_LA.1一了圖5.分析結(jié)果滾子和凸輪之間的接觸力圖7.參數(shù)從凸輪中心Z向距離半徑指數(shù)'、■圖6.磨損的凸輪..點(diǎn)表2優(yōu)化研究從從凸輪中心ZX滾子高O變量最?。?1）電流（0）最大（+1）滾子半徑12.731.7538.1滾子高度15.87538.144.45半徑指數(shù)180.0203.0206.5表3確定優(yōu)化設(shè)計(jì)的因素3優(yōu)化響應(yīng)面分析法作為優(yōu)化方法。該方法可用于在設(shè)計(jì)時(shí)參數(shù)的連續(xù)值。響應(yīng)函數(shù)是建立在假定的實(shí)驗(yàn)結(jié)果的基礎(chǔ)上，對(duì)設(shè)計(jì)參數(shù)，減少響應(yīng)函數(shù)的值是通過使用一個(gè)最小的算法。3.1設(shè)計(jì)的因素和水平接觸力的磨損的重要因素，并對(duì)凸輪的形狀密切相關(guān)。優(yōu)化的目標(biāo)函數(shù)是確定滾子與凸輪之間的接觸力。接觸力的峰值選擇最小化。表2顯示的凸輪和滾子值幾何位移的設(shè)計(jì)因素。那是可以改變的設(shè)計(jì)選擇的因素考慮到當(dāng)前系統(tǒng)的結(jié)構(gòu)和其他部分的干擾。和改進(jìn)的正弦曲線提供最佳的性能考慮的力傳遞效率仍然使用。如表2所示，滾筒的半徑和高度及半徑變化的指數(shù)。確定設(shè)計(jì)因素通過工程討論了這三個(gè)參數(shù)。表3給出了滾子的高度和半徑及被設(shè)置為設(shè)計(jì)因素指標(biāo)的半徑。圖7顯示了需要確定的圓柱凸輪的最佳形狀參數(shù)。3.2響應(yīng)面分析。設(shè)計(jì)因素的正交數(shù)組創(chuàng)建。十五組實(shí)驗(yàn)，基于正交陣列三個(gè)設(shè)計(jì)因素。表4顯示實(shí)驗(yàn)的響應(yīng)，這是凸輪與滾輪之間的最大接觸力。實(shí)驗(yàn)結(jié)果的基礎(chǔ)上，響應(yīng)面分析法推導(dǎo)出的響應(yīng)函數(shù)，并利用統(tǒng)計(jì)分析的方法和系統(tǒng)性能的設(shè)計(jì)因素之間的數(shù)學(xué)關(guān)系。當(dāng)有許多設(shè)計(jì)因素，二次回歸模型一般是作為響應(yīng)函數(shù)和系統(tǒng)性能的設(shè)計(jì)因素之間的關(guān)系的非線性。在這項(xiàng)研究中，中心復(fù)合設(shè)計(jì)表包括中心點(diǎn)和軸點(diǎn)使用2水平因子實(shí)驗(yàn)來估計(jì)模型的功能。根據(jù)研究結(jié)果，二次回歸模型函數(shù)使用最小二乘法推導(dǎo)。在這項(xiàng)研究中得到的回歸函數(shù)表示為：]-=—了”+網(wǎng)知0艮+63520母—148果-21^600^+514切占「+739202/4-74670耳無+23140^/r-193190^.⑴Y：桶凸輪與滾輪之間的接觸力R：滾子半徑HR：高輥ri：半徑指數(shù)為了驗(yàn)證模型的函數(shù)，方差分析的實(shí)現(xiàn)。表5顯示了方差分析表的大小的變化是，①自由度和V的平均平方，F(xiàn)0值從獲得的實(shí)驗(yàn)結(jié)果和F（0.01）是一個(gè)確定的值在參考根據(jù)水平和設(shè)計(jì)因素的數(shù)量。如表5所示，F(xiàn)0大于F（0.01）。因此，該模型函數(shù)有顯著性水平百分之1的可靠性水平。因此，該模型可用于為目標(biāo)函數(shù)，因?yàn)楣烙?jì)的模型函數(shù)能非常好的表達(dá)設(shè)計(jì)因素和系統(tǒng)性之間的關(guān)系。為了獲得的設(shè)計(jì)因素最小化目標(biāo)函數(shù)值，采用SQP方法。SQP是一種有效的優(yōu)化算法，得到一個(gè)函數(shù)的最低值給定出兩個(gè)以上的設(shè)計(jì)因素和非線性約束條件。表6顯示了設(shè)計(jì)因素最小化目標(biāo)函數(shù)值。次數(shù)滾子半徑滾子高度滾子半徑響應(yīng)1-1-1-1131332-1-11111353-11-112402

4-111974951-1-199300961-11125041711-11197735811151555790002918610-1.2160049652111.21600534829120-1.2160220181301.21601065981400-1.21611287115001.21652623表4.確定優(yōu)化設(shè)計(jì)的因素s4VFOSSR1.92E+12J；51764.43SSE11SST2.ME+12Table5.ANOVAtable.設(shè)計(jì)參數(shù)值（mm）滾子半徑23.8125

滾子高度25.4半徑指數(shù)2047225表6優(yōu)化設(shè)計(jì)變量。電流電流電流滾子半徑（mm）31.7523.8125-26.05滾子高度（mm）38.125.4-33.33半徑指數(shù)（mm203204.7255+0.85凸輪高度（mm）1491490凸輪高度（mm）269222-17.47接觸力的峰值平均（N）29.1865.184-82.24接觸力的均方根值（N）5.5411.309-76.37表7.估計(jì)系統(tǒng)的優(yōu)化結(jié)果…diiTDfltCamAngle(JplimifedCaraAmfHe圖8.優(yōu)化后的凸輪和指數(shù)位移圖

RollerCMRalterOETimeisec'i圖9.當(dāng)前的和優(yōu)化的系統(tǒng)之間的接觸力的比較4.優(yōu)化驗(yàn)證4.1動(dòng)態(tài)模型RollerCMRalterOETimeisec'i驗(yàn)證是否已進(jìn)行了優(yōu)化，利用動(dòng)態(tài)模型優(yōu)化的凸輪模型的建立。以及電流與優(yōu)化模型的接觸力比較。圖8顯示了當(dāng)前的和優(yōu)化的凸輪模型和指數(shù)單元的位移圖。優(yōu)化后的凸輪和分度裝置以及當(dāng)前凸輪的痕跡。七輥接觸力在圖9凸輪與滾輪之間的接觸力峰值相比顯著降低在優(yōu)化后。設(shè)計(jì)值的變化，對(duì)凸輪的大小和接觸力影響如表7所示。該凸輪變得更輕比桶形凸輪體積減小約17.47%。圓柱凸輪和滾子之間接觸壓力的峰值下降約82.24%。此外，接觸力的均方根值降低約76.37%。因此，這次優(yōu)化用動(dòng)態(tài)模型的進(jìn)行了驗(yàn)證。4.2實(shí)驗(yàn)一桶的CAM原型是基于優(yōu)化結(jié)果制作。在紙杯成型機(jī)床的加速度測(cè)量實(shí)驗(yàn)驗(yàn)證了優(yōu)化結(jié)果。圖10顯示了1到6點(diǎn)的加速度的測(cè)量。實(shí)驗(yàn)進(jìn)行了五次是可靠的。獲得的測(cè)量值是平均值。紙杯成型機(jī)的當(dāng)前的和優(yōu)化的凸輪的加速度在圖10進(jìn)行了比較。優(yōu)化后的凸輪平均加速度降低約17%，因此，對(duì)著圓柱凸輪進(jìn)行了好的優(yōu)化。結(jié)論進(jìn)行優(yōu)化以減少凸輪與滾輪之間的接觸力的紙杯成型機(jī)的設(shè)計(jì)。接觸力是通過使用凸輪動(dòng)態(tài)模型和指數(shù)單元分析，這是對(duì)紙杯成型機(jī)操作的一部分。通過工程的探討，為優(yōu)化確定了他們的價(jià)值觀的設(shè)計(jì)因素。滾筒的半徑和高度及半徑進(jìn)行了優(yōu)化指標(biāo)。對(duì)圓柱凸輪的形狀也根據(jù)滾筒的半徑和高度及半徑的優(yōu)化指標(biāo)。為了驗(yàn)證在這項(xiàng)研究中使用優(yōu)化的組件的減振，對(duì)接觸力進(jìn)行了分析。接觸力降低的動(dòng)態(tài)模型與優(yōu)化的組件。此外，通過實(shí)驗(yàn)測(cè)定了紙杯成型機(jī)床的加速度。加速度在優(yōu)化系統(tǒng)中下降?？傊?，通過優(yōu)化輥，指數(shù)和凸輪，讓紙杯成型機(jī)可以在一個(gè)高速，低磨損的環(huán)境中工作。圖11.對(duì)機(jī)械振動(dòng)的比較參考[1]R.IpekandB.Selcuk,，凸輪軸的干磨損形貌，材料研究學(xué)報(bào)，168（2005）373-379.。⑵E.Pennestri,R.Stefanelli,P.P.ValentiniandL.Vita,凸輪曲線的動(dòng)態(tài)仿真驅(qū)動(dòng)變速，DETC'04程序（2004）。[3]K.-J.Jun,T.-W.Park,K.-YCheongandY-G.Kim,，在紙杯中利用多體動(dòng)力學(xué)模型成型機(jī)因素造成的凸輪磨損研究，J.MST，24（3）（2010）361-367。[4]H.XiaoandJ.W.Zu，一種新的凸輪驅(qū)動(dòng)凸輪型線優(yōu)化，機(jī)械科學(xué)與技術(shù)學(xué)報(bào)，23（2009）2592-2602。[5]J.H.Shin,S.W.Kim,D.W.KangandH.E.Yoon對(duì)凸輪的相對(duì)速度的設(shè)計(jì)研究，kspe學(xué)報(bào)，19（8）（2002）47-54。[6]W.H.KimandT.W.Park公園，一個(gè)凸輪設(shè)計(jì)方案一杯成型機(jī)的發(fā)展，ksme學(xué)報(bào)，35（4）（2011）433-438。[7]乙Chang,C.Xu,T.Pan,L.WangandX.Zhang，對(duì)分度凸輪機(jī)構(gòu)一般框架的幾何設(shè)計(jì)，機(jī)械原理，44（2009）2079-2084。[8]R.L.Norton，凸輪的設(shè)計(jì)和制造手冊(cè)，工業(yè)出版社有限公司，紐約。[9]F.YChen，力學(xué)和凸輪機(jī)構(gòu)的設(shè)計(jì)，科學(xué)出版社，紐約。[10]S.-P.Jung,T.-W.Park,K.-J.Jun,J.-W.Yoon,S.-H.LeeandW.-S.Chung一個(gè)優(yōu)化方法研究了響應(yīng)面分析，多體系統(tǒng)jmst，23（2009）950-953。[11]S.-P.Jung,T.-W.Park,K.-J.Jun,J.-W.YoonandW.-S.Chung使用實(shí)驗(yàn)設(shè)計(jì)，彈簧的優(yōu)化設(shè)計(jì)，ijpem，10（4）（2009）77-83.。[12]S.Park,，實(shí)驗(yàn)設(shè)計(jì)的理解，minyoungsa（2005）。【13】G.N.Vanderplaats，應(yīng)用工程設(shè)計(jì)的數(shù)值優(yōu)化技術(shù)，McGraw-Hill（1984）2009年在亞洲大學(xué)旭賢基姆收到他的機(jī)械工程理學(xué)學(xué)士。目前，他是一名韓國水原亞洲大學(xué)的博士生。他的興趣是研究該地區(qū)的多體系統(tǒng)，優(yōu)化和計(jì)算機(jī)輔助工程。TaeWonpark得到來自國立首爾大學(xué)的機(jī)械工程學(xué)士學(xué)位。他接著從愛荷華大學(xué)獲得了碩士和博士學(xué)位。他目前是在韓國。水原亞洲大學(xué)機(jī)械工程學(xué)院的一名教授。Studyofoptimizationofthebarrelcaminapaper-cup-formingmachinefWookHyeonKim1andTaeWonPark2,*AbstractApapercupformingmachinecanproduceamaximumofabout140papercupsaminute.Iftherateofproductionisincreasedtoimproveproductivity,thecontactforceinthebarrelcamincreases,producingmorevibration.Therefore,amethodforreductionofcamvibrationisneeded.Theprofileofthebarrelcamisoptimizedbyusingamultibodydynamicsmodel.Theobjectiveoftheoptimizationistominimizethecontactforcethatoccursbetweentherollersandthebarrelcam.Anexperimentiscarriedoutusingtheoptimizedbarrelcam.Thereductionofvibrationathigherratesofproductionthanthecurrentratesvalidatedtheoptimization.Keywords:Paper-cup;Barrelcam;Multi-bodydynamics;Optimization;ContactforceIntroductionThedemandforpapercupsisincreasingrapidlyduetotheirconvenienceandeffectivenessinprotectingtheenvironment.Tosatisfythedemand,currentproductivityalsoshouldbeincreased.However,simplyincreasingproductivitywouldresultinvibrationatthebedonthemachine,whichisaseriousproblem.Whenthemachineisalsoaffectedbythevibrationonthebed,defectivepapercupsareproduced.Fig.1showsthecurrentpapercupformingmachine.Thecurrentmachinecanproduce140papercupsperminute.Iftheproductivityisincreased,thebarrelcamwillwearoutveryquicklyandthebarrelcamwillhavetobechanged.Thepapercupisformedontheturretinthepapercupformingmachine,andanindexwithsevenrollersisconnectedtotheturret.Thebarrelcammakestherollersmoveasthecamrotates,sotheturretalsorotates.Contactforceoccursbetweenthebarrelcamandtherollers.Afterthepapercupformingmachineoperatesforalongtime,wearoccursonthesurfacesofthebarrelcamandtherollerbecauseofthecontactforce.Thenvibrationandnoiseincreasegreatly,requiringreplacementofthebarrelcamandtherollersshouldbechanged.Researchinthisfieldhasbeenextensive.Ipekinvestigatedthevariationofthewearmechanismandwornsurfaceprofileofthecamshaft.Thewearmechanismofthecamsurfacechangesalongthecontactsurface[1].Pennestripresentedasimulationofthecamactuatorofarobotizedgearbox.Theactuatorisabarrelcamwhichmovesapinaccordingtoaprescribedmotionlaw.Inthegearshiftingsimulation,thecontactforcesandwearactionarecompared[2].Junsuggestedthatbarrelcamweariscausedbythecontactforcebetweenrollerandbarrelcam.Thewearspotofthebarrelcamalmostcoincideswiththepointoflargecontactforceinthemulti-bodydynamicsmodel[3].XiaooptimizedthecamprofileforanewcamdriveengineusingageneralpolynomialsplineandB-spline.Auniquecammechanismisanalyzedtodefinetheoptimizationproblem[4].Shinproposedamethodfordesigningtheshapeofthebarrelcambyusingrelativevelocity.Localcoordinatesarederivedusingtherelativevelocitymethod,andtheshapeofthebarrelcamiscreatedbytheCADprogram[5].Kimdevelopedabarrelcamshapedesignprogram.Parametersareinputtotheprogramandthepointdataofthecamprofilearecalculated.Then,thedataareconvertedtoa3DsolidCADmodel[6].Changpresentedageneralframeworkforkinematicanalysisandgeometrydesignoftheindexingcammechanism.Screwtheoryisappliedtodescribethestructureofthecammechanism,andkinematicequationsarederived[7].Fig.1.Papercupformingmachine.However,asolutiontodecreasethecontactforcehasnotbeensuggested.Andthosestudiesdidnotverifytheperformanceofthedesignedbarrelcam.Forthepapercupformingmachined,amethodtooptimizethebarrelcamprofiletodecreasethecontactforceisneeded.Theresultcanbeusedtoverifyforthereliabilityofthesuggestedmethod.Inthisstudy,thebarrelcamprofileisoptimizedtominimizethecontactforcebetweentherollersandthebarrelcam[8,9].AmultibodydynamicmodeliscreatedusingADAMStocalculatethecontactforce.Tochoosethedesignparameters,whichsignificantlyaffecttheresponsevariables,sensitivityanalysisisperformedbyusingthePlackett-Burmandesigntable.Then,experimentsarecarriedoutaccordingtothecentralcompositedesigntable.Next,usingresponsesurfaceanalysis,thesecondorderrecursivemodelfunction,whichprovidesinformationontherelationshipbetweenthedesignparametersandtheresponsevariables,isestimated.Thereliabilityoftheestimatedmodelfunctionisverifiedaccordingtotheanalysisvariance(ANOVA)method.Finally,thesequentialquadraticprogramming(SQP)methodisusedtofindthevaluesofthedesignvariablesthatminimizethemodelfunctionandsatisfythelinearornonlinearconstraintconditions[10-13].Toverifythereliabilityoftheoptimizationprocedure,amulti-bodysimulationmodelofthepaper-cupformingmachineiscreated.Thecontactforcebetweenthebarrelcamandtherollersofthecurrentandtheoptimizedsystemiscompared.Inaddition,anexperimentusingaprototypeofthebarrelcamisperformed.Thevibrationonthebedofthepaper-cupformingmachinebetweenthecurrentandtheoptimizedsystemiscompared.DynamicanalysisDynamicanalysismodelAdynamicmodelofthepaper-cupformingmachineiscreatedtoanalyzethecontactforcebetweenthebarrelcamandtherollersbyusingamulti-bodydynamicanalysisprogramADAMSasshowninFig.2.Theindexdriveinapapercupformingmachineisacomponentthatrotatesorstopstoconnecteachproductionprocess.Theindexdriveisoperatedbythebarrelcam.Thedynamicmodeliscomposedof24parts.Joint,driverspringandcontactaredefinedinthemodel.ThemodelhasatotalDOFof22.Table1providestheinformationonthedynamicmodel.A3Dmodelofthebarrelcamiscreatedbyusingreverse-engineering.Fig.3showsthereverse-engineeringprocedure.Inthisprocedure,therealproductismeasuredusingalaserscanner,which,inthisstudy,isanon-contactmeasurementlaserprobe.Itmeasuresabout1000points,andpointsareconnectedbyalineandconvertedtoasurfacetomakea3Dsolidmodelinthe3DCADprogram.ContactforceanalysisJunsuggestedthatthecamwearsoutduetothecontactforcebetweenthecamandtherollers[3].Fig.5showstheanalysisresultofthecontactforcebetweenarollerandthebarrelcam.Inthreesections,thecontactforceincreasesgreatly.Fig.6showsthemomentwhenarollerpassesbytheguidegrooveofthebarrelcam.Thefirstspotindicatestherollerenteringtheguidegroove;thesecondindicatestherollerpassingthroughtherotationalsection;andthelastindicatesrollerescapingtheguidegroove.Thethreewearspotscoincidewiththepartswherethecontactforceincreasesgreatly.Thebarrelcamiswornoutverymuchinthesethreeparts.Thewearoftenoccursnotonthewholesurfaceofthegroovebutatsomepointsofthegroove.Therefore,thecontactforcecanbeaveryimportantfactorofthebarrelcamwear.PA1T9J-4KzwhmitsTrnji^-lnticnLn.1711Sprit*142ITable1.Informationofdynamicmodel.HbgETiirlcngniFig.2.Multi-bodydynamicmodelofthepapercupformingmachine.J=l>miLiJ33i*?dvl-Fig.3.Procedureofreverseengineeringofthebarrelcamusing3Dlaserscanner.Fig.4.Comparisonofcamandindexangle.ContsclFarce(RDllerDI)Fig.5.Analysisresultofcontactforcebetweenrollerandbarrelcam.Fig.6.Wearspotsofthebarrelcam.Fig.7.Parameterofrollerandindex.Rj-viilrXczuii&roilerofrollers-XX-clirecnoi]distmicfromctillerXrioijdisraiicec^xliceiiieryJZ-clii-trcti.oiifiroa.licenterXofiaide-TcHfEdrolleroKjid.iu.'sol^i-o-LleroCTcrwuofroJJeiXTable2.Investigationfortheoptimization頓-1)Ciina;r(0iRadiusofrclkr12.7381HeightofrallerIS.87538.144.45RadiusofmcleK180.0203.0灑iTable3.Determineddesignfactorsfortheoptimization.OptimizationTheresponsesurfaceanalysisisusedastheoptimizationmethod.Thismethodcanbeusedwhenthedesignparametershavecontinuousvalues.Theresponsefunctionispresumedbasedontheexperimentalresults,andthevaluesofthedesignparametersthatminimizetheresponsefunctionarefoundbyusingaminimalalgorithm.3.1DesignfactorsandlevelThecontactforceisanimportantfactorofthewear,andiscloselyrelatedtotheshapeofthebarrelcam.Theobjectivefunctionoftheoptimizationistodeterminetheoptimalshapeofthebarrelcamthatminimizesthecontactforcebetweentherollersandthebarrelcam.Thepeakvalueofthecontactforceischosentobeminimized.Table2showsthedesignfactorsofthedisplacementofthecamandgeometricvaluesoftheroller.Thedesignfactorsthatcanbechangedareselectedconsideringthestructureofthecurrentsystemandtheinterferenceofotherparts.Andthemodifiedsinecurvegivingthebestperformanceconsideringtheforcetransferefficiencyisstillused.AsshowninTable2,theradiusandheightoftherollerandtheradiusoftheindexarechanged.Thesethreeparametersaredeterminedasdesignfactorsthroughengineeringdiscussion.Table3presentstheheightandradiusoftherollerandtheradiusoftheindexwhicharesetasdesignfactor.Fig.7showstheparametersrequiredtodeterminetheoptimalshapeofthebarrelcam.ResponsesurfaceanalysisAnorthogonalarrayofthedesignfactorsiscreated.Fifteenexperimentsarecarriedoutbasedontheorthogonalarrayofthreedesignfactors.Table4showstheresponseoftheexperiments,whichisthepeakcontactforcebetweenthebarrelcamandtheroller.Basedontheexperimentalresults,theresponsesurfaceanalysismethoddeducestheresponsefunction,amathematicalcorrelationbetweenthedesignfactorsandsystemperformancesbyusingastatisticalmethod.Whentherearemanydesignfactors,aquadraticregressionmodelis,generallyusedastheresponsefunctionbecauseofthenonlinearityoftherelationbetweenthedesignfactorsandsystemperformances.Inthisstudy,thecentralcompositedesigntableincludingthecentralpointandtheaxialpointisusedin2-levelfactorexperimentstoestimatethemodelfunction.Basedontheresult,aquadraticregressivemodelfunctionisderivedusingthemethodofleastsquares.Theregressivemodelfunctionobtainedinthestudyisexpressedas]-=—79。+犯頒R,+63泗風(fēng)—MS熬°、—215&)叫+74670^+23140^4190.⑴Y:ContactforcebetweenthebarrelcamandtherollersrR:RadiusofrollerhR:HeightofrollerrI:RadiusofindexToverifythemodelfunction,theanalysisofvarianceisimplemented.Table5showstheANOVATable:Sisthesizeofchange,①thgreioffreedom,andVthemeansquare.F0isavalueobtainedfromtheexperimentresultsandF(0.01)isavaluedeterminedinthereferenceaccordingtothelevelandnumberofdesignfactors.AsshowninTable5,F0isgreaterthanF(0.01).Therefore,themodelfunctionhasalevelofreliabilitywithin1percentofthesignificancelevel.Therefore,themodelfunctioncanbeusedasanobjectivefunction,becausetheestimatedmodelfunctioncanexpresstherelationbetweenthedesignfactorsandsystemperformanceverywell.Toobtainthevaluesofthedesignfactorsthatminimizetheobjectivefunction,theSQPmethodisused.TheSQPisanefficientoptimalalgorithmthatobtainsthelowestvaluesofafunctiongivenmorethantwodesignfactorsandnonlinearconstraintconditions.Table6showsthevaluesofthedesignfactorsthatminimizetheobjectivefunction.

No.of玲perimentFtadhisofrollerHeighTofrollerRadiusofrollerR.C51XM15C(N)1-1-1-L131332-1-L]111353-11-L124024-11197495t-1-199300961-11125D41711-11197735S1115155579oQ02912610-1.216O04-9652111.316aQ12o-1.21602201813o1.216010659S14o0-1216112S7115o01.21652623Table4.Determineddesignfactorsfortheoptimization.S中~VFOF(0.01)SSEL1.9ZE-rl23(5.39E+1154.7d443SSE1.2&E+11111.17E-10SST2.C4E-1214Table5.ANOVAtable.DesignPirainererValue(iiiin)R^li痙ofrollff238125Heightofreller'25.4R^dimofindex204.7225Table6.Optimizeddesignvariables.CimctirQprmuzedRjitcofelian^e(na)R^drLE'iofroller(iimih317523.S125?2605HeightofiDllei'(turn)384￥」■Radiusofindex(nimF203204.7225F-85Rjirliu^ofcam(iiini)1491490H^igJiTofcam(null)2692^2-1747A^-erjiffeofpeAk瞬hieofcotiticrfi&rce(IT)29ASG5,184■82.24RAIS睥1gofcoiatactfeace(N-^5,5411^309-7637Table7.Estimatedresultoftheoptimizedsystem.soi-'-QurircntC-^irn朗邵電□pnmizedAngle50tlE;p-」_Fig.8.Displacementdiagramoftheoptimizedbarrelcamandindex.Rc-lterO-1Tie.|vw=}RcmiaiD4Rdiw03IC^'F?r*t卜…“Qpnn—』.11J1...Fegsystem.TimafEwnrvni—■4!^aajQiCurri-nl:E_?Opdrri=3E-dJ一*-J113?3□na.Ll....4.1?-□.isS.-Ol14Tims05C5WWC?rrwl??…Stini—dlTim?Fig.9.ComparisonofcontactforcebetweencurrentandoptimizedOptimizationverificationDynamicmodelToverifywhethertheoptimizationhasbeencarriedoutwell,adynamicmodeliscreatedusingtheoptimizedbarrelcammodel.Andthecontactforceofthecurrentandtheoptimizedmodeliscompared.Fig.8showsthedisplacementdiagramofthecurrentandtheoptimizedbarrelcammodelandindexunit.Theoptimizedbarrelcamandtheindexunitwelltracesofthecurrentcam.ThecontactforcesofsevenrollersarecomparedinFig.9.Thepeakvalueofthecontactforceremarkablydecreasesbetweenthebarrelcamandtherollersafteroptimization.Thechangeofdesignvalue,thesizeofthebarrelcamandthecontactforceareshowninTable7.Thebarrelcambecomeslighterasthevolumeofthebarrelcamdecreasesabout17.47%.Andthepeakvalueofthecontactforcebetweenthebarrelcamandtherollerdecreasesabout82.24%.Also,theRMSvalueofthecontactforcedecreasesabout76.37%.Therefore,theoptimizationusingthedynamicmodelisverified.ExperimentAprototypeofthebarrelcamismanufacturedbasedontheresultoftheoptimization.Theaccelerationatthebedofthepapercupformingmachineismeasuredbyexperimenttoverifytheresultoftheoptimization.Fig.10showsthepoints1to6whereaccelerationismeasured.Theexperimentisdonefivetimesforreliability.Theaverageofthemeasuredvaluesisobtained.TheaccelerationofthepapercupformingmachinewiththecurrentandtheoptimizedbarrelcamiscomparedinFig.10.Theaverageaccelerationdecreasesabout17%afteroptimization.Therefore,thebarrelcamiswelloptimized.Fig.10.Measurepointofthevibration.ITuftIFig.11.ComparisonITuftIFig.11.Comparisonofvibrationonthemachine.ConclusionThedesignofthepaper-cupformingmachinewasoptimizedtodecreasethecontactforcebetweenthebarrelcamandtherollers.Thecontactforcewasanalyzedbyusingadynamicmodelofthebarrelcamandtheindexunit,whichisanoperatingpartofthepapercupformingmachine.Throughengineeringdiscussion,thedesignfactorsandtheirvaluesweredeterminedfortheoptimization.Theradiusandheightoftherollerandtheradiusoftheindexwereoptimized.Andtheshapeofthebarrelcamwasalsooptimizedaccordingtotheradiusandheightoftherollerandtheradiusoftheindex.Toverifythereductionofvibrationusingtheoptimizedcomponentsinthisstudy,thecontactforcewasanalyzed.Thecontactforcesignificantlydecreasedinthedynamicmodelwiththeoptimizedcomponents.Inaddition,theaccelerationofthebedofthepap