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 摘要 全文主要在分析齒凸輪機構，運用在高速軋盒機中，其凸輪運動曲線與間歇運動特性對整個軋盒機系統運動與動態特徵之影響。文中主要是將系統中之馬達驅動組件、傳動齒輪、齒凸輪機構與輸出鍊條組各式同特性之子系統組件結合，經由拉格朗日方程式(Lagrange’s equation)推導整體軋盒機系統之運轉方程式，並在不同運轉條件下針對系統動態影響進行數值模擬分析與探討。 分析方法主要藉由數學分析軟體matlab配合藍日卡達(Runge-Kutta method)，進行非線性系統之時域解析，並分析不同凸輪運動曲線、轉速高低差異、夾紙排數目，對系統動態響應之影響與輸出端殘振峯值之變化。
 AbstractThe gear-cam intermittent mechanism, mainly made up by cam, the sun gear, planet gear and planetary shelf , it has been used in automatically high speed die cutting and creasing machine. The main function of die cutting and creasing machine is cutting and creasing the cardboard, and through compounding the cam motion curves, it will can control the intermittent motion of a gear-cam intermittent mechanism and improve its dynamic characteristic.The effects of gear cam profile and driving speed on the dynamic responses of a box folding and die cutting machine are studied in this work. The input driving motor、gear、gear-cam and output chain mechanics are included in the dynamic system. The equation of motion of the whole system in derived by employing Lagrange’s equation the 4th order Runge-Kutta method is used to simulation the fine domain response of the nonlinear equation of motion. The effect of cam profile, and driving speed on the system dynamic response have been simulated and analysed in the work.
 目錄目錄....................................................................................................... i圖目錄................................................................................................... iii表目錄................................................................................................... vii符號說明............................................................................................... viii摘要....................................................................................................... xiAbstract................................................................................................. xii第ㄧ章 緒論....................................................................................... 1 1-1 前言..................................................................................... 1 1-2 文獻回顧............................................................................. 6 1-3 章節與組織......................................................................... 9第二章 高速印刷機齒凸輪機構係統理論推導............................... 10 2-1 凸輪運動曲線分析............................................................. 10 2-2 高速印刷機運動方程式..................................................... 14 2-2-1 等效振動系與等效飛輪推導模式........................ 14 2-2-2 高速印刷機系統模式............................................ 19 2-3 驅動馬達數學模式.............................................................. 26第三章 數值分析............................................................................... 32 3-1 系統運動方程分析-數值解析........................................... 32 3-2 參數分析............................................................................ 37 3-2-1 馬達轉速效應...................................................... 37 3-2-2 凸輪曲線.............................................................. 38 3-2-3 飛達數之影響...................................................... 39 3-3 數值分析結果..................................................................... 55 3-3-1 轉速響應分析...................................................... 55 3-3-2 運動曲線效應分析.............................................. 62 3-3-3 飛達構件效應分析.............................................. 72第四章 結論....................................................................................... 99附錄A................................................................................................... 101參考文獻............................................................................................... 103
 參考文獻[1] McEvers, D. L. and Strubble, D. P., 1971, “Rotary Die Cutting Machine,” United States Patent 4063493.[2] D’Luhy, E., 1974, ” Rotary Die Cutting,” United States Patent 3965786.[3] Bayer, G., Wegberg, E., and Schwalmtal, Q., 2003, “Sheet Punching and Embossing Machine,” United States Patent US2004/0123748 A1.[4] Hrones, J. A., 1948, “An Analysis of the Dynamic Forces in a Cam-Driven System,” Transactions of the ASME, Vol. 70, 1948.[5] Hundal, M. S., 1963, “Aid of Digital Computer in the Analysis of Rigid, Spring-Loaded Valve Mechanism,” SAE Progress in Technology, Vol. 5[6] Johnson, R. C., 1959, “The Dynamic Analysis and Design of Relatively Flexible Cam Mechanisms Having More than One Degree of Freedom,” Trans. ASME, Journal of Engineering for Industry, Vol. 81B(4), pp.323-331[7] Wang, S. M. and Morse, I. E., 1971, “Torsional Response of a Gear Train System ,”ASME Paper No.71-Vibr-77 , Vibration Conference , Toronto , Sept.8-1[8] Gilbert, A. C. , 1972, “A Note on the Calculation of Trosional Natural Frequencies of Branch System, ”Journal of Engineer for Industry, Feb, pp.279-283.[9] Fukuma, H. ,et al, 1974, “Fundamental Research on Gear Noise Vibration(7th Report,Generation Mechanism of Radical and Axical Vibration of Spur Gear ),” Bull. of JSME, Vol.17,No.113.[10] Chen, F. Y. and Polvanich, N., 1975, Dynamics of High-Speed Cam-Driven Mechanisms:Part 1-Linear System Models, Trans. ASME, Journal of Engineering for Industry, Vol. 97E(3), pp.769-776.[11] Teasar, D. and Matthew, G. K., 1976, “The Dynamics Synthesis, Analysis, and Design of Modeled Cam System,” Lwxington Books.[12] Daw, J. W., 1979, “An Analytical Investigation of Three-Dimensional Vibration in Gear-Coupled Rotor System,”Ph. D. dissertation, Dept. of Mechanical Engineering ,Virginia Polytechnic Institute and State University ,Blacksburg ,Virginia ,May[13] Lee, T. W. and Wang, A. C., 1983, “On The Dynamic of Intermittent-Motion mechanisms Part 1：Geneva Mechanisms, Ratchets, and Escapements,” Trans. ASME, Journal of Mechanisms, Transmissions, and Automation in Design, Vol. 105, pp. 534-540[14] Yan, H. S., Tsai, M. C., and Hsu, M. H., 1996, “A Variable-Speed Method for Improving Motion Characteristics of Cam-Follower Systems,”Journal of Mechamical Dedign, Vol. 118, pp.250-258.[15] Nguyen, Van Khang, 1996, “On the Dynamic Stability and Periodic Vibration of Cam Mechanism with Elastic Drive,” Machine Vibration, Vol. , pp.127-139[16] 黃松炳，1997，“滾子凸輪系統之動態特性分析,”，國立中山大學機械與機電工程學系研究所碩士論文。[17] Rothbart, H. A., 1956, “Cams-Design, Dynamics and Accuracy, ”John Willey &Sons New York.[18] Hsieh, W.H., 1991, “Improving the State of Motion of Followers byControlling Cam Speed,” M.S Thesis , National Cheng Kung University, Tainan.[19] 何宗祐，1999，“具力矩補償機構滾子凸輪系統之動態響應析”，國立中山大學機械與機電工程學系研究所碩士論文。[20] 胡晉哲，2001，“不同力矩補償機構對滾子凸輪系統動態特性影 響之分析”，國立中山大學機械與機電工程學系研究所碩士論文。[21] Lahr, D. F., and Hong, D. W., 2006, “The Operation and Kinematic Analysis of a Novel Cam-Based Infinitely Variable Transmission,”30th ASME Mechanisms and Robotics Conference.[22] Sanchez, M. N. and Jalon, J. G., 1980, “Application of B-Splines Function to the Motion Specification of cam,” ASME pap. 80-DET-28.[23] Tsay, D. M. and Huey, C. O., 1993，”Application of B-Splines to the Synthesis of Cam-follower Motion programs, ”，ASME Journal of Mechanical Design, Vol.115, pp.621-626.[24] Tsay, D. M. and Lin, B. J., 1995, “Geomertric Improvement on Ribbed Globodial Cams for Unsymmetrical Motion Controls,” ASME Proc. The Computers in Engineering Conference and the Engineering Database Symposium, pp.973-978.
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 1 滾子凸輪系統之動態特性分析 2 不同力矩補償機構對滾子凸輪系統動態特性影響之分析 3 具力矩補償機構滾子凸輪系統之動態響應 4 可變慣性矩飛輪對高速間歇機構動態特性之影響 5 轉移矩陣法用於凸輪系統響應之分析

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 1 轉移矩陣法用於凸輪系統響應之分析 2 滾齒凸輪接觸應力之分析 3 滾子凸輪系統之動態特性分析 4 微渦流扇葉片結構強度之研究 5 可變慣性矩飛輪對高速間歇機構動態特性之影響 6 一種齒凸輪間歇機構之設計 7 平移式雙滾子從動件之盤形凸輪機構設計與分析 8 齒凸輪間歇運動機構之分析與運動曲線合成 9 具力矩補償機構滾子凸輪系統之動態響應 10 飛機襟翼齒輪減速機之動態響應 11 滾齒凸輪機構之組裝實驗分析 12 預力與滾子凸輪分割器動態行為之研究 13 滾子輪式凸輪在高速下之定位精度研究 14 不同振動模式用於振模合成法之研究分析 15 以分子動力學探討高分子聚醚醚酮混合不同尺寸二氧化矽奈米粉之機械性質

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