機(jī)械設(shè)計(jì)外文翻譯-橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的運(yùn)動(dòng)學(xué)分析及試驗(yàn)研究【中文2867字】【PDF+中文W,中文2867字,機(jī)械設(shè)計(jì),外文,翻譯,橢圓,齒輪,曲柄,搖桿,打緯,機(jī)構(gòu),運(yùn)動(dòng)學(xué),分析,試驗(yàn),研究,中文,2867,PDF 【中文2867字】 橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的運(yùn)動(dòng)學(xué)分析及試驗(yàn)研究 趙雄 任根勇 陳建能 機(jī)械工程及自動(dòng)化學(xué)院，浙江理工大學(xué)，杭州310018，中國(guó) 摘要：為了分析橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的運(yùn)動(dòng)學(xué)性能，建立了一個(gè)運(yùn)動(dòng)學(xué)的數(shù)學(xué)模型，編制了一個(gè)輔助分析與仿真軟件。根據(jù)不同的參數(shù)，這軟件能顯示運(yùn)動(dòng)特性及仿真運(yùn)動(dòng)的機(jī)制。它還為人機(jī)交互提供了一個(gè)平臺(tái)。通過(guò)軟件可以選定一組令人滿(mǎn)意的參數(shù)。通過(guò)這些參數(shù)對(duì)曲柄搖桿打緯機(jī)構(gòu)的測(cè)試床進(jìn)行優(yōu)化。通過(guò)高速視頻磁帶記錄器驗(yàn)證運(yùn)動(dòng)性能的機(jī)理。 關(guān)鍵詞：打緯機(jī)構(gòu) 橢圓齒輪 曲柄搖桿 動(dòng)力學(xué) 引言 打緯機(jī)構(gòu)是紡織機(jī)的一個(gè)重要部位。它是由引緯緯紗插入機(jī)制形成的織物。它的功能是把主軸的恒定速度旋轉(zhuǎn)改變?yōu)轶刈牟缓愣ㄍ鶑?fù)擺動(dòng)。為使引緯機(jī)構(gòu)完成插入緯紗，筘座的打緯機(jī)構(gòu)應(yīng)該有足夠的停留時(shí)間或相對(duì)停留時(shí)間在前方位置。打緯機(jī)構(gòu)的性能測(cè)定織物的質(zhì)量，也決定織機(jī)的質(zhì)量競(jìng)爭(zhēng)力[1]。 現(xiàn)在，有三種普遍的打緯機(jī)構(gòu)：四連桿打緯機(jī)構(gòu)，六連桿打緯機(jī)構(gòu)和共軛凸輪打緯機(jī)構(gòu)[2]。一般來(lái)說(shuō)，四連桿打緯機(jī)構(gòu)是最簡(jiǎn)單的，它有65°-75°的相對(duì)停留時(shí)間。六連桿打緯機(jī)構(gòu)有120°的相對(duì)停留時(shí)間[3]。它更多的取決于它的生產(chǎn)較大累計(jì)誤差。共軛凸輪的停留時(shí)間為220°-240°，但共軛凸輪機(jī)構(gòu)需要很高的加工精度。如果有一些加工誤差會(huì)造成一定的振動(dòng)[4]。 在本文中，一種新型的依據(jù)橢圓齒輪和曲柄搖桿的打緯機(jī)構(gòu)產(chǎn)生了[5]，它的運(yùn)動(dòng)學(xué)數(shù)學(xué)模型也建立了。通過(guò)一個(gè)測(cè)試裝置的開(kāi)發(fā)和對(duì)運(yùn)動(dòng)性能的機(jī)制進(jìn)行了高速視頻磁帶記錄，這表明，這種新的機(jī)制可以滿(mǎn)足打緯要求。 1 橢圓齒輪曲柄搖桿打緯機(jī)構(gòu) 圖1顯示了橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)初始位置。，0為主動(dòng)橢圓齒輪的焦點(diǎn)，也是織機(jī)主軸轉(zhuǎn)動(dòng)中心，a為從動(dòng)橢圓齒輪轉(zhuǎn)動(dòng)中心，為該橢圓齒輪的一個(gè)焦點(diǎn)，曲柄ab(長(zhǎng)度z )與從動(dòng)橢圓齒輪固接，通過(guò)連桿bc(長(zhǎng)度z )帶動(dòng)搖桿cd(長(zhǎng)度z。)作往復(fù)擺動(dòng)。cd與筘座de通過(guò)軸d固連，使筘座de前后往復(fù)擺動(dòng)。通過(guò)優(yōu)化橢圓齒輪的短長(zhǎng)軸之比k(偏心率)、當(dāng)曲柄ab與連桿bc共線時(shí)(即筘座de在前心位置)與支座ad(長(zhǎng)度z )夾角 、初始安裝角 (安裝時(shí)主動(dòng)橢圓齒輪長(zhǎng)軸與ao線的夾角)、四根桿件的長(zhǎng)度和支座ad位置角y，可以獲得類(lèi)似共軛凸輪打緯機(jī)構(gòu)運(yùn)動(dòng)規(guī)律。 1—主動(dòng)橢圓齒輪 2—從動(dòng)橢圓齒輪 DE—筘座 圖1 橢圓齒輪一曲柄搖桿打緯機(jī)構(gòu)示意圖 2 橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的運(yùn)動(dòng)學(xué)數(shù)學(xué)建模 2.1 橢圓齒輪驅(qū)動(dòng)的數(shù)學(xué)模型 當(dāng)主動(dòng)齒輪1一恒定的速度逆時(shí)針旋轉(zhuǎn)時(shí)，齒輪2會(huì)以一個(gè)變速順時(shí)針旋轉(zhuǎn)。設(shè)主動(dòng)輪1轉(zhuǎn)角φ1，，從動(dòng)輪2轉(zhuǎn)過(guò)角φ2，點(diǎn)P到軸O的距離是r1，PA的距離是r2。經(jīng)推導(dǎo)得： r1=b2/(a+c*cosφ1) (1) r2=b2/(a+c*cosφ2) (2) c的范圍是橢圓中心到焦點(diǎn)，φ1，φ2的變化范圍是0到2π[6]。 由橢圓齒輪的傳動(dòng)特性得：r1=2a- r2 （3） 即 （4） 由式（4）可計(jì)算從動(dòng)輪角位移φ2與主動(dòng)輪角位移φ1的關(guān)系。 （5） 對(duì)（5）求導(dǎo)得： （6） 由（1）和（3），根據(jù)求導(dǎo)公式， ，， （7） 2.2 搖桿CD的運(yùn)動(dòng)學(xué)運(yùn)動(dòng)學(xué)模型 由于曲柄固定在從動(dòng)橢圓齒輪，其角速度和角加速度與橢圓齒輪驅(qū)動(dòng)一樣。即：，，根據(jù)圖2，下列方程可以被推導(dǎo)出[7]。 圖2 曲柄搖桿機(jī)構(gòu) （8） (9) （10） （11） （12） （13） （14） 根據(jù)（13）和（14）， （15） （16） 2.3 E在筘座DE的X方向上的運(yùn)動(dòng)學(xué)模型 位移方程： （17） 速度方程： （18） （19） 3 輔助分析與仿真軟件的機(jī)構(gòu)參數(shù)優(yōu)化 3.1 計(jì)算機(jī)輔助分析軟件 可視化的機(jī)制分析優(yōu)化的過(guò)程，可以顯示更多的信息到用戶(hù)的過(guò)程。用戶(hù)可以觀察整個(gè)過(guò)程和發(fā)現(xiàn)的基本參數(shù)的機(jī)制。人機(jī)交互分析和優(yōu)化是人類(lèi)和電腦的優(yōu)點(diǎn)結(jié)合在一起。人類(lèi)擁有的能力，模糊推理，判斷和創(chuàng)新，這可以幫助處理以及隨機(jī)事件。同時(shí)，計(jì)算機(jī)擅長(zhǎng)精確計(jì)算及相關(guān)工作。人類(lèi)和計(jì)算機(jī)能充分發(fā)揮各自的人-計(jì)算機(jī)交互優(yōu)化的優(yōu)勢(shì)。因此，令人滿(mǎn)意的參數(shù)可以很容易的實(shí)現(xiàn)[8-10]。 基于以上橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)，一個(gè)輔助分析與仿真軟件被實(shí)現(xiàn)，在圖3中顯示出來(lái)。它可以用于分析對(duì)不同的機(jī)構(gòu)參數(shù)和驗(yàn)證是否存在干擾在組成部分之間的機(jī)制中。 圖3 分析和仿真機(jī)制的軟件 有了這個(gè)軟件，用戶(hù)可以輸入機(jī)構(gòu)參數(shù)，像a，k，γ，l1，l2，l3，l4和織機(jī)主軸旋轉(zhuǎn)速度。機(jī)構(gòu)運(yùn)動(dòng)仿真將顯示在界面左側(cè)；位移，速度和加速度曲線的點(diǎn)將會(huì)分別顯示在接口的右側(cè)；最優(yōu)值將會(huì)顯示在接口的左下方。位移曲線會(huì)隨著k的增加而減少顯示在后方位置；同時(shí)加速度曲線顯示，最大加速度會(huì)隨k的增加而減少。從運(yùn)動(dòng)學(xué)機(jī)制的性能看，k需要根據(jù)打緯機(jī)構(gòu)的要求進(jìn)行優(yōu)化。l1，l2，l3，l4也需要修改根據(jù)k，從而獲得理想的運(yùn)動(dòng)性能。 3.2 優(yōu)化結(jié)果分析 打緯機(jī)構(gòu)最重要的性能之一是筘座的駐留時(shí)間。增加機(jī)制的參數(shù)可以延長(zhǎng)停留時(shí)間，同時(shí)最大加速度明顯增加，而且特大型加速度波動(dòng)會(huì)降低機(jī)構(gòu)動(dòng)態(tài)特性。設(shè)計(jì)師必須在延長(zhǎng)停留時(shí)間和控制加速度波動(dòng)之間做一個(gè)平衡。 根據(jù)上述輔助分析與仿真軟件，可以獲得一組參數(shù)：δ=4°,k=0.85,γ=135°,a=71.233mm,l1=40mm,l2=100mm,l3=180mm,l4=199mm,lDE=189.5mm。基于這些參數(shù)，當(dāng)織機(jī)速度300轉(zhuǎn)/分鐘，點(diǎn)E運(yùn)動(dòng)曲線顯示在圖4。當(dāng)打緯機(jī)構(gòu)是在后方的位置，位移曲線幾乎是平的。筘座的駐留時(shí)間接近200°（從92°到285°），這就不會(huì)導(dǎo)致打緯機(jī)構(gòu)和打緯插入機(jī)構(gòu)之間的干擾。此外，在這一時(shí)期，筘座曲線的速度和加速度幾乎接近0°因此，他不會(huì)產(chǎn)生振動(dòng)，將有利于緯紗的入境和出境。在打緯結(jié)束時(shí)，最大位移為85mm，最大加速度為615.8434m/s2，滿(mǎn)足了打緯的要求。 圖4 橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的運(yùn)動(dòng)曲線 4 試驗(yàn)研究 根據(jù)上述參數(shù)，橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的測(cè)試床被開(kāi)發(fā)出來(lái)了。（圖5）利用高速視頻磁帶記錄器和視頻分析軟件MAS，得到了當(dāng)織機(jī)的主軸轉(zhuǎn)速在100轉(zhuǎn)/分鐘的時(shí)候的位移和速度。點(diǎn)E的理論和實(shí)驗(yàn)位移顯示在圖6，點(diǎn)E的理論和實(shí)驗(yàn)速度顯示在圖7。實(shí)測(cè)位移曲線是和理論一致，但實(shí)際測(cè)量速度曲線顯示一些波動(dòng)。對(duì)此有2個(gè)原因：該機(jī)制組件之間的差距引起的振動(dòng)；視頻分析包含錯(cuò)誤。 圖5 橢圓齒輪-曲柄搖桿打緯機(jī)構(gòu)測(cè)試床 圖6 打緯機(jī)構(gòu)位移曲線分析圖 圖7 打緯機(jī)構(gòu)速度曲線分析圖 5 總結(jié) （1）在本文中，橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)已經(jīng)生產(chǎn)出來(lái)了。其運(yùn)動(dòng)學(xué)數(shù)學(xué)模型已經(jīng)建立，一個(gè)輔助分析與仿真軟件通過(guò)基本視覺(jué)已經(jīng)完成。通過(guò)這個(gè)軟件一組令人滿(mǎn)意的參數(shù)已經(jīng)得到。 （2）關(guān)于橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的測(cè)試床已經(jīng)比較成熟。通過(guò)視頻磁帶記錄器，運(yùn)動(dòng)學(xué)性能得到了驗(yàn)證。這表明模型的有效性和機(jī)制的可行性。 文獻(xiàn) [1] Zhu S K,Gao W D. 織機(jī)[M]. 第二版.北京：中國(guó)紡織&服裝出版社，2004：267-268. [2] Liang H S，Hu Q E，Wang G C，等等. 四連桿打緯機(jī)構(gòu)模糊優(yōu)化設(shè)計(jì)[J]. 機(jī)械設(shè)計(jì)與研究，2005，21（2）：72-75. [3] Ma S P. 基于matlab的六連桿打緯機(jī)構(gòu)優(yōu)化設(shè)計(jì)和仿真[J]. 紡織研究學(xué)報(bào)，2006，27（3）：40-43. [4] Zheng Z Y. 分析劍桿織機(jī)打緯機(jī)構(gòu)[J]. 紡織研究學(xué)報(bào)，2004，25（4）：73-74. [5] 浙江理工大學(xué) 橢圓齒輪曲柄搖桿打緯機(jī)構(gòu)的引緯打緯：中國(guó)，200810162178.O[P]. 2008-11-18. [6] Chen J N，Zhao X，Xu B，等等。建立關(guān)于橢圓齒輪曲柄搖桿引緯機(jī)構(gòu)的運(yùn)動(dòng)學(xué)模型[J]. 中國(guó)工程機(jī)械，2007，18（19）：2294-2297. [7] Zhao Y. 機(jī)理數(shù)學(xué)分析與合成[M].北京：中國(guó)工業(yè)出版社，2005：177-181. [8] Yang C J，Chen Y，Lu Y X．研究人機(jī)系統(tǒng)及其應(yīng)用[J]. 中國(guó)工程機(jī)械雜志，2000，36（6）：42-47. [9] Teng H F，Wang Y S，Shi Y J．人機(jī)合作的關(guān)鍵技術(shù)研究[J]. 中國(guó)工程機(jī)械雜志，2006，42（11）：1-9. [10] Liu J，Teng H F，Qu F Z．人機(jī)界面交互式基本算法[J].大連大學(xué)技術(shù)學(xué)報(bào)，2005，45（1）：58-63. Received date:2010-01-19Foundation items:National Natural Science Foundation of China(No 50875243);Zhejiang Technique Innovation Group of Modern TextileMachinery，China(No 2009R50018);Foundation of Education Department of Zhejiang Province，China(No Y201019088);Foundation ofNew Textile R D Emphasised Laboratory of Zhejiang Province，China(No 2009FZD004)*Correspondence should be addressed to CHEN Jian-neng，E-mail:jiannengchen zstu edu cnKinematic Analysis and Test Study of Elliptic-Gear and Crank-Rocker Beating-UpMechanismZHAO Xiong(趙雄)，REN Gen-yong(任根勇)，CHEN Jian-neng(陳建能)*College of Mechanical Engineering and Automation，Zhejiang Sci-Tech University，Hangzhou 310018，ChinaAbstract:In order to analyze the kinematic performances ofelliptic-gear and crank-rocker(EGCR)beating-up mechanism，kinematic mathematic models of the mechanism were established，and an aided analysis and simulation software were compiled Thissoftware can display the kinematic characteristics and simulationmotion of the mechanism according to different parameters It alsosupplies a platform for human-computer interaction A group ofsatisfactory parameters were selected by the software A test bed ofEGCR beating-up mechanism was developed according to theseparameters The kinematic performances of the mechanism wereverified by high-speed video tape recorderKeywords:beating-upmechanism;elliptic-gear;crank-rocker;kinematicsCLC number:TS103 135Document code:AArticle ID:1672-5220(2011)02-0222-04IntroductionBeating-up mechanism is one of the key mechanisms of aloom It beats the weft which is inserted by weft-insertionmechanism to form the fabric Its function is to transform theconstant speed rotation of the looms spindle to the non-constant speed reciprocating swing of the sleyIn order toallow the weft-insertion mechanism to finish inserting thewefts，the sley of the beating-up mechanism should haveadequate dwell time or relative dwell time in the front positionThe performances of beating-up mechanism determine thefabricsquality，andalsodecidethequalityandcompetitiveness of a loom1 Nowadays，there are three general kinds of beating-upmechanisms:four-bar linkage beating-up mechanism，six-barlinkage beating-up mechanism，and conjugated cam beating-upmechanismGenerally，four-barlinkagebeating-upmechanism is the simplest mechanism with 65-75 relativedwell time Six-bar linkage beating-up mechanism has about120 relative dwell time It has more hinges which producelarger cumulative errors The dwell time of conjugated cammechanism is 220-240，but the conjugated cam mechanismneeds veryhigh precision machiningIf there are someprocessing errors it will cause certain vibration2-4 In this paper，a new type of beating-up mechanism basedon elliptic-gear and crank-rocker(EGCR)was produced5，and its kinematic mathematic models were established A testbed was developed and the kinematic performances of themechanism were verified by high-speed video tape recorder，which demonstrated that this new mechanism could meet therequirements of weft beating-up1EGCR Beating-Up MechanismFigure 1 shows the EGCR beating-up mechanism in itsinitial position O is one of the focuses of the active elliptic-gear 1 and the rotation centre of the looms spindle A is one ofthe focuses and the rotation centre of the driven elliptic-gear 2Crank AB(l1)is fixed on the driven elliptic-gear Rocker CD(l3)is driven by BC(l2)and swings reciprocally Sley DE(l5)is fixed with CD by axis D and swings reciprocallytogether with CD By optimizing the eccentricity k(the ratioof the elliptic-gears minor radius(b)to major radius(a)，the angle (the included angle between AD(l4)and crank ABwhen crank AB and linkage BC are collinear，that is the sleyDE will be in the front position)，(the included anglebetween the major axis of the active elliptic-gear and AO)，(the included angle between AD and x-axis)，and the lengthsoflinkagesincrank-rockermechanism，thekinematicperformances of this novel beating-up mechanism becomeexcellent，which are similar to those of the conjugated cambeating-up mechanism1 Active elliptic-gear;2 Driven elliptic-gear;DESleyFig 1EGCR beating-up mechanism with its initial position2Kinematic Mathematic Models ofEGCR Beating-Up Mechanism2 1Mathematical models of the driven elliptic-gearIn Fig 1，when the active gear 1 rotates anticlockwise at aconstant speed，gear 2 will rotate clockwise at a non-constantspeed Given the angular displacements of the active gear 1 1and driven gear 2 2，the distance from mesh point P to axis Ois r1and PA is r2 With calculation，thenr1=b2/(a+ccos 1)，(1)r2=b2/(a+ccos 2)，(2)where，c is the distance between the elliptic-gear center and thefocus;1ranges from 0 to 2，and 2from 0 to 26 According to the transmission principles of elliptic-gearsr1=2a r2，(3)222Journal of Donghua University(Eng Ed)Vol 28，No 2(2011)that is，cos 2=(a+ccos 1)b2(2a2+2accos 1 b2)cac(4)From Eq(4)，the relationship between 2and 1can beobtained According to the principles of gear transmission2=1r1r2(5)Given that the velocity of active gear is constant，2=1r1r2 r1r2r22=2a r2r221(6)TakingthederivativeofEqs(1)and(3)，r1=b2csin 1(a+ccos 1)21and r2=r1，so in Eq(6)r2=b2csin 1(a+ccos 1)21(7)2 2Kinematical models of rocker CDSince the crank is fixed on the driven elliptic-gear，itsangular velocity and angular acceleration are the same as thoseof the driven elliptic-gear That is to say，j1=2，j1=2，and j1=+2 From Fig 2，the following equations canbe deduced7 Fig 2Crank-rocker mechanismj2=arctanyC yBxC xB(8)j4=arctan(yB yDxB xD)(9)j3=arccos(l32+(xD xB)2+(yD yB)2 l222l3(xD xB)2+(yD yB)槡2)+j4(10)j2=VxBcos j3+VyBsin j3l2sin(j2 j3)(11)j3=VxBcos j2+VyBsin j2l3sin(j2 j3)(12)j 2=c1cos j3+c2sin j3l2sin(j2 j3)(13)j 3=c1cos j2+c2sin j2l3sin(j2 j3)(14)In Eqs(13)and(14)，c1=axB+l3j23cos j3 l2j22cos j2，(15)c2=ayB+l3j23sin j3 l2j22sin j2(16)2 3Kinematic models of E in x-axis direction onthe sley DEDisplacement equation:sxE=xD+lDEcos(j3)(17)Velocity equation:VxE=lDEj3cos(j3/2)(18)Acceleration equation:axE=lDEj32cos j3+lDEj 3jcos(j3/2)(19)3AidedAnalysisandSimulationSoftwareofMechanismandParameter Optimization3 1Aided analytical softwareThe visualization of the mechanism is analyzing andoptimizing process that can display more information of theprocess to users Users can observe the whole process and findout the essential parameters ofthe mechanismHuman-computer interaction analysis and optimization combine thevirtues of both human and computersHumans possess thecapabilities of illegible illation，judgment and innovation，which can help to dispose random events as well Meanwhile，computers are good at accurate calculation and repeative workHuman andcomputercanfullydisplaytheirrespectiveadvantages in human-computer interaction optimization Thussatisfactory parameters can be easily achieved8-10 Based on the above kinematic models of EGCR beating-upmechanism，an aided analysis and simulation software arecompiled which is shown in Fig 3 It can be used to analyzethe influences of different mechanism parameters and verifywhether there exist interferences among the components of themechanismFig 3Aided analysis and simulation software of mechanismWith this software，users can input mechanism parameterssuch as a，k，l1，l2，l3，l4，and rotary speed of the loomsspindle The mechanism motion simulation will be shown onthe left of the interface;the displacement，velocity，andacceleration curves of point E will be shown respectively on theright of the interface;the optimal value of will be shown onthe left-bottom of the interface The displacement curve showsthat dwell time in the rear position decreases as k increases;322Journal of Donghua University(Eng Ed)Vol 28，No 2(2011)meanwhile the acceleration curve shows that the maximalacceleration also decreases as k increasesFor kinematicperformances of the mechanism，k needs to be optimizedaccording to the requirements of the beating-up weft;l1，l2，l3，and l4also need to be modified by the user in company withk，so as to achieve ideal kinematic performances3 2Optimization results analysisOne of the most important performances of beating-upmechanism is the dwell time of sley Increasing mechanismparameter k can prolong dwell time，meantime the maximalacceleration increases remarkably，and the oversize fluctuationof acceleration will degrade mechanism dynamic performanceDesigner must therefore make a balance between prolongingdwell time and controlling acceleration fluctuationWith the above aided analysis and simulation software，agroup of parameters was obtained:=4，k=0 85，=135，a=71 233 mm，l1=40 mm，l2=100 mm，l3=180mm，l4=199 mm，and lDE=189 5 mm Based on theseparameters，when the loom has a speed of 300 r/min，thekinematical curve of the beating point E is shown in Fig 4When the beating-up mechanism is on the rear position，thedisplacement curve is almost flat The dwell time of sley isclose to 200(ranging from 92 to 285)，which will not leadto interference of the beating-up mechanism and weft-insertionmechanism In addition，during this period，the curves of thevelocity and acceleration of the sley are almost close to 0Therefore it will not cause vibration，which will benefit thewefts entery and exit from shed At the end of the beating-up，the maximaldisplacementis 85mmandthemaximalacceleration is 615 843 4 m/s2，which both can meet therequirements of the beating-up weftFig 4The kinematic curves of EGCR beating-up mechanism4Test StudyBased on the above parameters，a test bed of EGCRbeating-up mechanism is developed(Fig 5)Using the high-speed video tape recorder and video analysis software BlastersMAS，the displacement and velocity are obtained with loomspindlesrotaryspeedat100r/minTheoreticalandexperimental displacements of beating point E are shown inFig 6，and theoretical and experimental velocities of beatingpoint E are shown in Fig 7 The actual measured displacementcurve is consistent with the theoretical one，but the actualmeasured velocity curve shows some fluctuationThere aretwo reasons for this finding:the gap among the components ofthe mechanism causes vibration;the video analysis containserrors422Journal of Donghua University(Eng Ed)Vol 28，No 2(2011)5Conclusions(1)In this paper，the EGCR beating-up mechanism hadbeen producedIts kinematic mathematic models had beenestablished and an aided analysis and simulation software hadbeen compiled byvisual basicAgroup ofsatisfactoryparameters had been got by this software(2)A test bed of the EGCR beating-up mechanism wasdevelopedWiththevideotaperecorder，itskinematicperformances were verified This demonstrated the validity ofthe models and the feasibility of the mechanismReferences1Zhu S K，Gao W D Weaving MachineM 2nd ed Beijing:China Textile Apparel Press，2004:267-268(in Chinese)2Liang H S，Hu Q E，Wang G C，et al The Fuzzy OptimizationDesign ofthe Four-Link Weft Beat-Up Mechanism JMachine Design and Research，2005，21(2):72-75(inChinese)3Ma S POptimal Design and Simulation on 6-Link BeatingConstruction Based on MATLAB JJournal of TextileResearch，2006，27(3):40-43(in Chinese)4Zheng Z Y Analysis of Beating-Up Mechanism of TT96 RapierLoom J Journal of Textile Research，2004，25(4):73-74(in Chinese)5Zhejiang Sci-Tech UniversityWeft Inserting and Beating-UpMechanismwithElliptic-GearCrank-Rocker:CN，200810162178 0P 2008-11-18(in Chinese)6Chen J N，Zhao X，Xu B，et al Establishment of KinematicsModels and Performance Analysis of Elliptic-Gear Crank-Rocker Weft Insertion Mechanism JChina MechanicalEngineering，2007，18(19):2294-2297(in Chinese)7Zhao Y Mechanism Mathematics Analyses and SynthesisMBeijing:China Machine Press，2005:177-181(in Chinese)8Yang C J，Chen Y，Lu Y X Study on the Human-MachineIntelligent System and Its Application J Chinese Journal ofMechanical Engineering，2000，36(6):42-47(in Chinese)9Teng H F，Wang Y S，Shi Y J Key Supporting Techniques ofHuman-ComputerCooperation JChineseJournalofMechanical Engineering，2006，42(11):1-9(in Chinese)10Liu J，Teng H F，Qu F ZInterface of Human-ComputerInteractive Genetic Algorithm J Journal of Dalian Universityof Technology，2005，45(1):58-63(in Chinese)522Journal of Donghua University(Eng Ed)Vol 28，No 2(2011)