為了達成節能減碳的目標，各式熱交換器效率之提升已成為工業界與學術界致力研究發展的重點，其中擾流器為強化管道內熱性能的重要設計之ㄧ，因此本研究根據常見於自然界中對數螺旋結構的概念，提出一款適用於方管中的新型螺旋擾流器，並使用質點影像測速儀和紅外線熱像儀，量測180度銳轉正方形雙通道內全展入口紊流場其結構變化及壁溫分布。正方形管道之水力直徑(DH)為45.5mm，以空氣為工作流體、特徵長度為DH、管道截面平均速度為特徵速度(U b)之雷諾數在紊流場量測中固定為10,000，而在壁溫與壓損量測中由5,000變化至20,000。擾流器之參數變化為截距比(Pi/DH)，其變化範圍為1、2、3及 。研究結果發現流體經螺旋擾流器(Pi/DH=)後會形成四股強度相同的順時針立體螺旋沖壁(Downwash)速度大小為0.24U b，使其後方1DH內平均紐塞數((Nu) ̅)相較於全展紊流平滑圓管紐塞數(〖Nu〗_∞)提升2.5倍。本研究進一步將本文與前人結果之數據于以綜合，並首度同時利用皮爾遜積矩相關係數(Pearson Product-moment Correlation Coefficient)及斯皮爾曼等級相關係數(Spearman Rank Correlation Coefficient)來線性與非線性定量分析軸向流場與熱傳分布之相關性，所探討之相關參數包括無因次化側向對流(((√((〖U_st〗^2+〖U_sp〗^2 ) )⁄U_b ) ) ̅_sp)、縱向(((U_ver⁄U_b ) ) ̅_sp)、絕對縱向(((|U_ver |⁄U_b ) ) ̅_sp)平均速度，主流(((〖u_st)〗_rms/U_b)) ̅_sp)、側向((((〖u_sp)〗_rms/U_b)) ̅_sp)、縱向((((〖u_ver)〗_rms/U_b)) ̅_sp)紊流強度，紊流動能(((k/U_b^2)) ̅_sp)及截面平均渦度(⌈ω ̅ ⌉ D_H/U_b)等八個流力參數與熱傳紐塞數比((Nu) ̅_sp/Nu_∞)，發現最具新穎性之結果為能確認出最具通用性與相關性的流力參數((k/U_b^2)) ̅_sp，其相關係數達到0.89，從而提出一個可同時適用於本研究與前人流道配置的經驗公式((Nu) ̅_sp⁄(Nu_∞=10.76×(((k⁄(U_b^2 )) ) ̅_sp )^0.43 ))，所有數據皆落於±31%之內。本研究亦使用特徵正交分解方法(Proper Orthogonal Decomposition)首度分析180度銳轉雙通道轉彎區流場中高能量比重的相干模態(Coherent Modes)，藉由統計方法可發現定性上於平滑雙通道轉彎區90度截面上存在類似90度圓形彎管流的漩渦交替運動(Swirl Switching)，定量上於上下交替渦旋(模態一、二)的能量比重相近分別為10.1%和7.3%；而加裝螺旋擾流器後會使漩渦交替運動產生改變，其上下交替渦旋(模態一、三)的能量比重分別為8.1%和3%。相較於平滑雙通道兩者渦旋能量間程度上的差異與出現的模態不同是導致交替運動以及平均流場中狄恩渦旋皆呈不對稱之原因。

To save energy and reduce carbon emissions, highly efficient heat exchangers play a pivotal role in industrial applications and academic research. Among all types of heat transfer enhancement techniques, turbulators are most commonly used. In this study, a novel turbulator inspired by logarithmic spiral structure in nature is proposed and its influence on turbulent flow field and temperature distribution in a twin-pass square channel with 180-deg sharp turn is explored by Particle Image Velocimetry (PIV) and Infrared Thermography (IRT). The channel features a fully developed inlet and a hydraulic diameter (DH) of 45.5mm. The Reynolds number (Re) based on working fluid air, bulk mean velocity (Ub), and DH is fixed at 10,000 for PIV and ranges from 5,000 to 20,000 for IRT. For the spiral turbulator, the pitch ratio (Pi/DH) is in the range of 1,2,3, and . The results show that there are four clockwise vortices behind the novel spiral turbulator and their velocity magnitude is around 0.24Ub. The vortex motion results in 2.5 times average Nusselt number ((Nu) ̅) augmentation within 1DH of the turbulator rear compared to that of fully developed pipe flow (〖Nu〗_∞). Furthermore, the linear and nonlinear correlations between fluid flow and heat transfer in present and previous data are firstly analyzed by both Pearson product-moment and Spearman rank correlations. It is newly found that the mean turbulent kinetic energy (((k/U_b^2)) ̅_sp) is the most universal and relevant parameters to the spanwise-averaged Nusselt number ratio ((Nu) ̅_sp/Nu_∞) with a correlation coefficient up to 0.89 among eight parameters examined, including averaged convective velocity (((√((〖U_st〗^2+〖U_sp〗^2 ) )⁄U_b ) ) ̅_sp), vertical velocity (((U_ver⁄U_b ) ) ̅_sp), absolutely vertical velocity (((|U_ver |⁄U_b ) ) ̅_sp), streamwise turbulence intensity (((〖u_st)〗_rms/U_b)) ̅_sp), spanwise turbulence intensity ((((〖u_sp)〗_rms/U_b)) ̅_sp), vertical turbulence intensity ((((〖u_ver)〗_rms/U_b)) ̅_sp), ((k/U_b^2)) ̅_sp, and mean vorticity magnitude ((|ω ̅ | D_H)⁄U_b ). Based on the correlation analysis, an universal empirical correlation ((Nu) ̅_sp⁄(Nu_∞=10.76×(((k⁄(U_b^2 )) ) ̅_sp )^0.43 )) is proposed for the present and previous channels. The maximum absolute difference is less than 31% compared with the experimental data. Finally, the most energetic coherent modes of turbulent flow field in the 180-deg sharp turn are also identified by proper orthogonal decomposition (POD) for the first time. It is observed that there exists swirl switching in the secondary flow at the midturn of smooth channel similar to that of the 90-deg bent pipe flow. The energy proportions of switching vortices in the first and second mode are 10.1% and 7.3%, respectively. As the channel is mounted with spiral turbulators, the swirl switching (Mode 1 and 3) is altered with energy proportions of 8.1% and 3%. Compared to that of the smooth channel, the asymmetry of swirl switching and mean Dean vortex structure is attributed to unequal energy proportions of the switching vortices.

摘要 i
Abstract iii
誌謝 v
圖目錄 ix
表目錄 xiv
符號說明 xv
第1章 緒論 1
1-1 前言 1
1-2 文獻回顧 4
1-2-1 常用於單通道的擾流器 4
1-2-2 常用於雙通道的擾流器 14
1-2-3 常見於自然界的螺旋結構 19
1-2-4 特徵正交分解方法於流場應用 20
1-3 研究目的 21
第2章 實驗系統及方法 41
2-1 實驗管道模型及構造 41
2-1-1 流力實驗模型 41
2-1-2 熱傳及壓力實驗模型 42
2-1-3 新型擾流器幾何結構 42
2-2 實驗系統 43
2-2-1 內流道冷卻系統 43
2-2-2 光學流場量測系統 44
2-2-3 全域熱傳量測系統 47
2-2-4 壓力量測系統 49
2-3 實驗條件 49
第3章 實驗數據處理與誤差分析 65
3-1 實驗數據換算方法 65
3-1-1 流力實驗數據處理 65
3-1-2 熱傳及壓損實驗數據換算 66
3-2 特徵正交分解方法 67
3-3 軸向熱流相關性分析 70
3-4 實驗誤差估算 72
第4章 雙通道內加裝螺旋擾流器之熱傳結果與流場結構 80
4-1 流力與熱傳實驗技術驗證 80
4-2 截距比效應 81
4-2-1 紐塞數比分布 81
4-2-2 整體平均熱傳與壓損表現 84
4-2-3 當前研究數據與先前文獻比較 86
4-3 平均流場結構 86
4-3-1 第一通道流場特性 87
4-3-2 轉彎區流場特性 90
4-3-3 第二通道流場特性 92
4-4 區域熱傳表現與流場之關係 96
第5章 軸向熱流相關性分析 112
5-1 標準實驗組 113
5-2 綜合多組數據分析 117
第6章 POD分析 128
6-1-1 平滑雙通道 128
6-1-2 螺旋擾流器雙通道 130
第7章 結論 138
7-1 結論 138
7-2 未來建議 139
附錄A 於雙通道內設置六組不同螺旋擾流器幾何排列的熱傳表現 140
A-1 三款不同螺旋擾流器幾何結構 140
A-2 擾流器凸出型式及排列方式 140
A-3 結果與討論 141
A-3-1 紐塞數比分布 141
A-3-2 整體平均熱傳與壓損表現 142
A-4 結論 143
附錄B 軸向熱流相關分析於前人平滑雙通道 148
附錄C 論文口試之補充答辯 153
參考文獻 157

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