臺灣博碩士論文加值系統

本研究針對整合噴擊與微流道之混合性散熱機構，散熱器裡設計有數組噴嘴與微流道和微鰭片整合為一體成型之散熱機構。在投影面積為12×12mm2的散熱器，建立流道高0.8mm，寬0.6mm，流道長度為12mm，共計11條微渠道，每條微渠道中設置微鰭片，微鰭片高0.3mm，寬0.2mm長度12mm，微鰭片上方正對著3個噴擊孔，因此微渠道的體積減少約12.5%。本研究實驗工作流體為FC-72，入口飽和溫度為30℃及50℃，並設定噴擊流量為100~710mL/min。結果發現，單相熱傳之熱傳性能皆會隨著噴擊流量增大而呈現線性上升之趨勢，在微渠道中增加微鰭片，有助於熱傳進入兩相沸騰熱傳，而當流量增至一定範圍以上時，因為噴擊到微鰭片壓力過大，使得工作流體在微渠道內部未能有較佳的相變化熱傳，使得熱傳性能下降，本研究在飽和溫度30℃時，中流量450mL/min下，可達最高的熱通量150 W/cm2，並有本實驗中最低的熱阻0.1313K/W。最後，利用迴歸及疊代計算，推導出單相和雙相熱傳的經驗公式，其誤差範圍絕大部分落在±20%和±30%以內。

This study investigate a micro-channel heat sink integrated with micro jets. The cooling fluid was introduced to a 12×12 mm2 heated surface, which had 11 micro-channels, each channel was 0.8 mm high, 0.6 mm wide, and 12 mm in length. Micro-fin of 0.3mm height, 0.2mm width, and 12mm in length is made on the bottom of each channel.The volume of micro-channels reduces approximately 12.5% by the micro-fins.
In the tests, the working fluid is FC-72, the saturation temperature of cooling device system was set at 30 and 50℃, and the volume flow rate varied from 100 to 710 ml/min. The experimental results showed that heat transfer performance increased with increasing flow rate for single phase heat transfer.
The micro fins enhances the heat transfer in two phase boiling heat transfer. However, for the flow rate greater than a certain value, the increase of pressure drop hinders the bubble formation, and results in heat transfer performance degradation. In this study, at the saturation temperature of 30 ℃, and the flow rate of 450mL/min , the heat sink yields the maximum heat flux of 210 W/cm2, and the lowest thermal resistance of 0.1313K / W. Single phase and two phase heat transfer empirical correlations have been developed for the present heat sink, and the prediction error for most data are within ± 20% and± 30%, respectively.

誌謝 iv
表目錄 ix
圖目錄 x
1.1 研究背景 1
1.2 研究目的 4
第二章 文獻回顧 5
2.1噴擊熱傳 5
2.1.1 單相噴擊熱傳 5
2.1.2 雙相噴擊熱傳 8
2.1.3水平直管流譜圖 13
2.1.4 噴淋型式 14
2.1.4 噴淋孔型式之影響 16
2.1.5 噴淋高度對熱傳性能之影響 20
2.2微渠道熱傳 21
2.2.1 微渠道入出口配置之影響 21
2.2.2 堆疊型式微流道熱傳 23
2.3結合噴淋孔與微流道之散熱機制 26
2.4 微渠道底部增強熱傳結構表面之影響 32
2.5過冷度對熱傳性能之影響 37
2.6不凝結氣體之影響分析 38
2.7臨界熱通量分析 39
2.8流道可視化 40
第三章 實驗設備與方法 41
3.1 實驗設備 41
3.2 實驗參數範圍設定 45
3.2.1 工作流體之飽和溫度 45
3.2.2 熱通量參數設定 45
3.2.3 測試機構 47
3.2.4 噴擊孔徑與間距 50
3.2.5微渠道之微鰭片 51
3.2.6 噴擊流量設定 52
3.3 實驗系統 52
3.3.1 工作流體循環系統 53
3.3.2 模擬晶片發熱系統 53
3.3.3 儲液與過濾系統 54
3.3.4 冷凝循環系統 55
3.3.5 充填與除氣系統 55
3.3.6 影像擷取系統 55
3.4 實驗量測儀器 56
3.4.1 壓力轉換計 56
3.4.2 浮球式流量計 56
3.4.3 微齒輪泵 56
3.4.4差壓計 57
3.4.5 熱電偶 57
3.4.6 自偶變壓器 57
3.4.7 資料擷取器 57
3.4.8 真空泵 58
3.4.9 影像擷取設備 58
3.5 實驗步驟 59
3.6 實驗數據與誤差分析 63
3.6.1 實驗數據分析 63
3.7 誤差分析 64
3.7.1 溫度校正 64
3.7.2 流量校正 66
3.7.3 實驗誤差分析 68
第四章 數值模擬方法 72
4.1 基本假設 72
4.2 統禦方程式 73
4.3數值分析模型 74
4.3.1 模擬軟體解析 75
4.4物理模型及邊界條件 76
4.4.1 物理模型建立 76
4.5.2 模型邊界條件設立 76
4.6 數值模擬結果 77
4.6.1微鰭片設計對熱傳性能之影響 77
4.6.2增加微鰭片對流場之影響 81
第五章 結果與討論 86
5.1微渠道內微鰭片對熱傳性能之影響 86
5.2 整合型散熱機制之熱傳 87
5.2.1微鰭片對熱傳性能之影響 87
5.2.2熱阻抗分析 93
5.3 噴擊流量對熱傳性能與壓降之影響 94
5.4與文獻比較討論 97
5.5整合型散熱機制之熱傳經驗式 99
5.5.1 單相熱傳 99
5.5.2 雙相熱傳 103
第六章 結論與未來展望 107
6.1 結論 107
6.2 未來展望 108
參考文獻 109
附錄一 117
A.1本實驗3-0.4-3-f0.3上視圖噴嘴表面 117
附錄二 118
A.2本實驗3-0.4-3-f0.3 側視圖 微渠道與微鰭片 118
符號說明 119

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