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  1. NTU Theses and Dissertations Repository
  2. 工學院
  3. 機械工程學系
請用此 Handle URI 來引用此文件: http://tdr.lib.ntu.edu.tw/jspui/handle/123456789/29400
完整後設資料紀錄
DC 欄位值語言
dc.contributor.advisor張所鋐(Shuo-Hung Chang)
dc.contributor.authorWei-Lin Hsuen
dc.contributor.author許維麟zh_TW
dc.date.accessioned2021-06-13T01:06:09Z-
dc.date.available2010-07-27
dc.date.copyright2007-07-27
dc.date.issued2007
dc.date.submitted2007-07-24
dc.identifier.citation[1] T.Kobori, M.Takahashi, T.Nasu, N.Niwa, and K.Ogasawara, “Seismic Response Controlled Structure with Active Variable Stiffness System,” Earthquake Engineering and Structural Dynamic, Vol.22, No.11, pp.925-941
[2] M.C.Smith and F.C.Wang. Performance Benefit In Passive Vehicle Suspension Employing Inerters. 42nd IEEE Conference on Decision and Control, Hawaii, USA, December 9-12, 2003.
[3] L.Meirovitch, ‘Dynamics and control of structures,’ John Wiley & Sons, Inc, 1990.
[4] C.R.Fuller, S.J.Elliott and P.A. Nelson, “Active control of vibration, Academic Press,” 1996.
[5] M.A.Barton, N.Kanda, and Kuroda,K.,1996,“Low-Frequency Vibration Isolation Table Using Multiple Crossed-Wire Suspensions,” Review of Scientific Instruments, 67(11), pp.3994.
[6] D.L.Platus, “Negative-Stiffness-Mechanism Vibration Isolation Systems, ”Proceedings of SPIE- The International Society for Optical Engineering and Vibration Control, 3786, pp. 98-105, Jul 20-Jul 23 1999.
[7] D.Trumper and T.Sato, “A vibration isolation platform,” Mechatronics , v 12, n 2, p 281-294, February, 2002.
[8] A.G.Ulsoy, D.Hrovat, and T.Tseng, “Stability robustness of LQ and LQG active suspensions,” Journal of Dynamic Systems, Measurement and Control, Transactions of the ASME, vol.116, pp.123-131, 1994.
[9] L.Zuo and S.Nafeh, “Structured H2 optimization of vehicle suspensions based on multiwheel models,” Vehicle System Dynamics, vol.40, no.5, pp.351-371, 2003.
[10] M.R.Bai and W.Liu, “Control design of active vibration isolation using μ-synthesis,” Journal of Sound and Vibration, vol.257, no.1, pp.157-175, 2002.
[11] J.Yang, Y.Suematsu, and Z.Kang, “Two-degree-of-freedom controller to reduce the vibration of vehicle engine-body system,” IEEE Transactions on Control Systems Technology, vol.9, no.2, pp.295-304, March 2001.
[12] S.Sommerfeldt and J.Tichy, “Adaptive control of a two-stage vibration mount,” J.Acoust. Soc. Amer., vol.88, no.3, pp.938-944, 1990.
[13] Jinsiang Shaw, “Adaptive Vibration Control By Using Magnetostrictive, ”The Fourth International Conference On Motion And Vibration Control.
[14] Y.Sunwoo, K.Ceok, and N.Huang, “Model Reference adaptive control for vehicle suspension systems,” IEEE Transactions on Industrial Electronics, v.38, n.3, pp.217-222, Jun, 1991.
[15] D.Karnopp, M.J.Crosby, and R.A. Harwood, “Vibration control using the semi-active force generators,” Journal of Engineering for Industry, Transactions of the ASME, vol.96, pp.619-626, 1974.
[16] Lei Zuo, Jean-Jacques E. Slotine, Samir A.Nayfeh, “Experimental Study of a Novel Vibration Isolation, ”Proceedings of the American Control Conference, v4, pp.3863-3868, July 2004.
[17] S.S.Parthasarathy, “Design of an active suspension system for a quarter-car road vehicle model using model reference control,” Proceedings of the Institution of Mechanical Engineers. Part I: Journal of Systems and Control Engineering, v 220, n 2, p 91-10, 2006,.
[18] Z.J.Geng and L.S.Haynes, “Six degree of freedom active vibration control using the stewart platform,” IEEE Transactions on Control Systems Technology, v 2, n 1, pp.45-53, March 1994.
[19] Antonio Visioli, “A new design for a PID plus feedforward controller,” Journal of Process Control, v 14, n 4, June, pp. 457-463, 2004.
[20] W.H.Zhu,“On active acceleration control of vibration isolation systems,” Control Engineering Practice, v 14, n 8, p 863-873, August 2006.
[21] Tanakorn Tantanawat, “Application of compliant mechanisms to active vibration isolation systems,” Proceedings of the ASME Design Engineering Technical Conference and Computers and Information in Engineering Conference 2004: Volume 2: 28th Biennial Mechanisms and Robotics Conference, p 1165-1172, 2004.
dc.identifier.urihttp://tdr.lib.ntu.edu.tw/jspui/handle/123456789/29400-
dc.description.abstract隨著科技進入奈米時代,產業進入精密與細微化,振動對於精密機電系統造成很大的影響,各類檢測設備與製程設備對於避振的需求越來越高。為了解決振動問題,避振系統廣泛的被使用。被動式避振系統,具有高穩定性及低成本的優點,目前廣泛的被工業界採用,但避振效果有限;主動式避振系統在近年來已經成為避振系統的趨勢,利用額外的致動器達成抵銷振動的效果,對於被動式避振系統不擅長的低頻段也能有很好的抑振效果,然而其缺點在於避振平台上的負載,可能會使得系統閉回路變為不穩定。
此篇論文旨在研究主動式避振系統之振動抑制,並探討避振平台在變動負載下控制器的定位性能。在文中以雷射干涉儀作為感測器,利用音圈馬達響應速度快、運動行為線性的優點,設計一套主動式避振系統。在建構系統模型方面,推導系統動態方程式並利用系統鑑別找出系統之模型。
本研究採用PID控制器與MRAC控制器補償干擾平台所產生的外界干擾,利用Lyapunov穩定理論驗證避振系統閉迴路之穩定性。藉由電腦模擬與實驗,在抑制固定頻率之振動方面,此兩種控制方法成功的消除35.89dB與24.2dB的振動。此外此篇論文探討PID控制器與MRAC控制器在變動負載下的定位性能,PID的定位性能會受限於平台負載,而MRAC控制器對於平台負載之變化有較佳的定位性能。
zh_TW
dc.description.abstractIn semiconductor industry the feature size in integrated circuit devices shrink continuously and the sizes are going from micrometer to nanometer. Vibration influences the precision in micro-electro-mechanical systems greatly. With the advance of technology, the requirement of vibration isolation in inspection equipment and manufacture process equipment is more and more important.
In order to solve vibration problem, anti-vibration system is widely used in industry. Passive vibration isolation is popular in industry because of its high stability and low cost, but its performance is limited. There is a tendency toward active vibration isolation(AVI) system in recent years. It achieves the result of anti-vibration by using a additional actuator. It also has good performance in low frequency region where passive vibration isolation system is poor at. But the system could be unstable due to the loading of AVI platform.
This research investigates the active vibration isolation issues and the positioning performance under variable loading. In this thesis, we design an AVI system by using laser interferometer as sensor and voice coil motor as actuator having high response velocity and linearity motion. In chapter II, we derive system dynamic equation and identify the system model.
The thesis then compares the vibration isolation performance using a classical proportional-integral-derivative (PID) controller versus using a model reference adaptive controller (MRAC). The thesis also derives adaptive law using Lyapunov stability theory. By computer simulation and experiment, these two controllers achieve the maximum attenuation of 35.89dB and 24.2dB with constant vibration frequency. Finally, we discuss the positioning performance to different platform loading. The PID controller positioning performance is easily affected upon platform loading. MRAC controller has better positioning performance in different platform loading.
en
dc.description.provenanceMade available in DSpace on 2021-06-13T01:06:09Z (GMT). No. of bitstreams: 1
ntu-96-R94522817-1.pdf: 1735798 bytes, checksum: 2c604cc86bfbdda2a1b21eedb77b46cd (MD5)
Previous issue date: 2007
en
dc.description.tableofcontents摘 要 I
Abstract II
目 錄 IV
圖 目 錄 VII
表 目 錄 XI
第一章 序論 1
1.1 前言 1
1.2 文獻回顧 1
1.2.1 避振機構 2
1.2.2 控制器文獻回顧 5
1.3 研究動機與目標 6
1.4 文章架構 7
第二章 系統架構與分析 8
2.1 系統架構 8
2.2 系統各部分介紹 10
2.2.1 音圈馬達原理與作動方式 10
2.2.2 雷射干涉儀 12
2.2.3 電壓放大器 15
2.2.4 頻譜分析儀 16
2.2.5 示波器 18
2.3 系統動態分析 19
2.4 系統鑑別 21
第三章 控制器設計與模擬 24
3.1 PID 控制器 25
3.2 參考模型適應控制器 27
3.2.1 參考模型適應控制器架構 27
3.2.2 Lyapunov穩定理論推導適應律 31
3.3 模擬結果 34
3.3.1 PID控制器模擬 35
3.3.2 參考模型適應控制器模擬 38
第四章 實驗結果及討論 40
4.1 PID控制器實驗結果 41
4.2 參考模型適應控制實驗結果 43
4.3 PID與MRAC針對變動負載之比較 46
4.3.1 PID與MRAC在無固定頻率干擾情況下之比較 46
4.3.2 PID與MRAC在有固定頻率干擾情況下之比較 58
4.3.3 無控制、PID控制、MRAC控制在變動負載下之頻率響應 68
第五章 結論與未來展望 72
5.1 結論 72
5.2 未來展望 73
參考文獻 74
dc.language.isozh-TW
dc.title參考模型適應控制在主動式避振系統之應用zh_TW
dc.titleApplication of Model Reference Adaptive Control In Active Vibration Isolation Systemen
dc.typeThesis
dc.date.schoolyear95-2
dc.description.degree碩士
dc.contributor.oralexamcommittee張家歐(Chia-Ou Chang),施文彬(Wen-Pin Shih)
dc.subject.keyword音圈馬達,主動振動抑制,PID,參考模型適應控制,zh_TW
dc.subject.keywordvoice coil motor,active vibration isolation,PID,MRAC,en
dc.relation.page76
dc.rights.note有償授權
dc.date.accepted2007-07-24
dc.contributor.author-college工學院zh_TW
dc.contributor.author-dept機械工程學研究所zh_TW
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