臺灣博碩士論文加值系統

流體軸承在機械結構中被廣泛的使用，但現今流體軸承皆無法避免流體軸承於運轉時的不穩定狀態（如油漩與油顫）發生，流體軸承於不穩定狀態下運轉可能會造成軸承內部發生碰撞摩擦，使軸承組件損壞。為了改善的軸承不穩定，本研究盡可能列出影響臨界轉速的參數，並從中選出控制因子進行田口法分析。
本研究以磁流體動壓軸承轉子測試平台為實驗系統，透過改變磁流體的體積分率、顆粒大小與磁場強度、配置，配合L8直交表進行實驗。由實驗數據可組成因子反應表進行初步分析，再透過初步數據進行變異分析與F測試，進而獲得更精確的因子貢獻度及實驗配置。
透過數據顯示 為實驗最佳化配置，並利用此配置進行數學預測與確認實驗。數學預測的最佳臨界轉速為2775 rpm，而確認實驗的臨界轉速為2767 rpm，此實驗差為8 rpm。

The fluid bearing has been widely used in the mechanical construction. However, it has been found that fluid bearings may become unstable while in operation (e.g., Whirl and Whip), which may cause damage to bearing assemblies via collision and friction. In order to improve the bearing instability, this study lists the parameters that affect the critical speed as much as possible, and select the control factor from Taguchi analysis.
In this study, use Ferrofluid Hydrodynamic Journal Bearing for the experimental system, by changing the Ferrofluid volume fraction, particle size and magnetic field strength, configuration, with L8 orthogonal array to experiment. Through the experimental data build factor response table to make a preliminary analysis, and then through ANOVA and F-Test analysis the preliminary data, and then obtain the more accurate factor contribution and the experiment configuration.
Through the Taguchi Method experiment data display for the experimental optimization configuration, and use this configuration for mathematical prediction and validation experiments.
The optimal critical speed for mathematical prediction is 2775 rpm, and the critical speed of the experiment is 2767 rpm, and the difference between the both experiments is 8rpm.

摘要 I
Abstract II
致謝 III
目錄 IV
圖目錄 VIII
表目錄 X
符號表 XI
第一章 緒論 1
1.1 研究背景與動機 1
1.2 研究方法與目的 1
1.3 文獻回顧 2
1.4 論文架構 4
第二章 流體動壓軸承系統與磁流體 5
2.1 動壓軸承簡介 5
2.2動壓軸承之基本方程 5
2.3 流體軸承之雷諾方程式 8
2.3-1 流體方程式推導[23] 8
2.3-2 系統平衡 10
2.4 軸承潤滑液之轉子不穩定 13
2.4-1 轉子不穩定介紹 13
2.4-2 油漩和油顫 13
2.4-3 軸承油漩門檻 14
2.5 磁流體簡介 16
2.6 磁流體成品 17
第三章 田口法 18
3.1 田口法簡介 18
3.2 目標設定與因子選擇 18
3.2-1 品質特性 18
3.2-2 理想機能（Ideal Function） 18
3.2-3 控制因子（Control Factors） 19
3.2-4 控制因子的變動水準（Levels of Control Factors） 19
3.3 田口式直交表（TAGUCHI’S ORTHOGONAL ARRAYS）與實驗 20
3.4 因子反應分析 21
3.5 交互作用 22
3.6 變異分析（ANOVA） 23
3.6-1 總變異向量 24
3.6-2 因子效應向量 25
3.6-3 誤差向量 25
3.7 F測試 27
3.8 製程最佳化 28
3.8-1 找出最佳組合 28
3.8-2 確認實驗 28
第四章 實驗平台建立與磁場配置 30
4.1實驗平台架構 30
4.1-1 Bently-Nevada ADRE 108 Data Acquisition Instrument 31
4.1-2 FW-BELL 5180高斯計 31
4.1-3 流體軸承 33
4.2 磁場配置 34
第五章 實驗結果 37
5.1 未外加磁場的實驗數據 37
5.2 磁流體動壓軸承田口法分析 39
5.2-1 控制因子 40
5.2-2 實驗直交表 41
5.2-3 品質特性的反應表及反應圖 42
5.2-4 交互作用 43
5.2-5 變異分析（ANOVA） 44
5.2-6 F測試 45
5.2-7 製程最佳化 45
5.2-8 確認實驗 46
第六章 結論與未來研究方向 50
6.1 結論 50
6.2 未來研究方向 50
參考文獻 52
附錄 54

圖目錄
圖2.1　動壓軸承示意圖（a）靜止狀態（b）運轉狀態 6
圖2.2　頸軸承形態 6
圖2.3　流體連續性系統圖 9
圖2.4　元件的力平衡圖 11
圖2.5　全頻串聯圖 14
圖2.6　流體軸系統承模型 15
圖2.7　 磁流體示意圖 16
圖2.8　 磁流體成品之一 17
圖3.1　因子反應圖 22
圖3.2　交互作用圖（有交互作用） 23
圖4.1　實驗之設計圖 30
圖4.2　ADRE 108 Data Acquisition Instrument 31
圖4.3　FW-BELL 5180高斯計 32
圖4.4　流體軸承之工程圖 33
圖4.5　實驗之磁鐵實體圖 34
圖4.6　磁鐵固定器 34
圖4.7　軸承內磁鐵分佈角度示意圖 35
圖4.8　同向磁場強度圖（0°S朝內） 35
圖4.9　交錯磁場強度圖（0°S朝內） 36
圖5.1　未加入磁場時油軸承之頻譜圖、頻譜分析圖及全頻串聯圖 38
圖5.2　影響因子圖 39
圖5.3　L8點線圖（變形） 41
圖5.4　品質特性因子反應圖 43
圖5.5　流體磁場、磁場與流體交互作用圖 44
圖5.6　加入磁場時油軸承之頻譜圖、頻譜分析圖及全頻串聯圖 （原始實驗） 48
圖5.7　加入磁場時油軸承之頻譜圖、頻譜分析圖及全頻串聯圖 （確認實驗） 49

表目錄
表3-1　本研究控制因子 19
表3-2　控制因子水準表(例) 20
表3-3　L8（ ）田口直交表 20
表3-4　因子反應表 21
表3-5　交互作用表 22
表3-6　ANOVA表 26
表3-7　ANOVA-F測試表 27
表5-1　L8直交表控制因子 40
表5-2　L8田口直交表 41
表5-3　L8各組實驗數據的平均值、標準偏差 42
表5-4　品質特性因子反應表 42
表5-5　流體磁場、磁場與流體交互作用表 43
表5-6　ANOVA表 44
表5-7　ANOVA-F測試表 45
表5-8　預測實驗數據 46
表5-9　確認實驗數據 47
表6-10　因子貢獻度與區域最佳解表 50
表A-1　精密高斯計規格表 54
表A-2　實驗數據表-1 55
表A-3　實驗數據表-2 56

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