臺灣博碩士論文加值系統

粉末冶金軸頸軸承經過粉末冶金燒結而成，擁有表面孔隙的產生，並且可將潤滑油儲存於其中，但也因為表面孔隙的緣故，表面粗糙度起伏變化較大，因此當軸承運轉期間發生摩擦時，可能會對表面產生固體接觸之磨耗而導致金屬顆粒的產生進入潤滑油中，增加運轉的不穩定性，並且產生振動與噪音。在軸套內徑表面加工V字型溝槽可以使軸承運轉期間維持穩定，其原理是透過溝槽紋路峰端所產生的液動壓力將軸承與軸有效隔開，降低軸與軸套摩擦的產生。
本研究利用粉末冶金軸頸軸承，其內徑表面為無花紋表面與V字型花樣表面兩種類型與磨耗，研究兩者傳動性能的差異，軸轉速分為 1000、2000、4000、8000 rpm 四種不同轉速條件，並且使用R32與GF500兩種不同潤滑油品，探討潤滑油黏度對於傳動性能的影響。實驗前先將加速規、應變規、熱電偶、荷重元等設備安裝完畢，便於實驗進行時進行訊號的量測，將量測數據進行整合與分析處理，對於不同條件下所得到的結果進行差異性的比較，探討V字型溝槽對於性能影響之差異。使用白光干涉儀量測軸承表面形貌參數，並代入 COMSOL 液動軸承分析模型，比較四種不同轉速下，油膜所產生變化，並與實驗數據進行相互驗證與探討。
研究結果顯示V字型花樣表面在低轉速運轉下，振動RMS小於無花紋表面，當轉速提升後，空蝕現象造成V字型花樣表面振動RMS上升並大於無花紋表面，但兩者數值差異不大。V型溝槽所產生液動壓力，將軸與軸套隔開，降低摩擦扭矩、表面應變、表面溫昇並低於無花紋表面。使用R32潤滑油高速運轉時，摩擦扭矩與溫昇較低，但容易出現熱膨脹緊迫現象，造成摩擦扭矩出現較大的變化。相比之下，使用GF500潤滑油能夠使振動有效的降低，並且摩擦扭矩在不同轉速下的變化較小，更加穩定，但高黏度將使摩擦扭矩與溫昇較高，則是選用時需要考量之因素。

The powder metallurgy journal bearings are formed through powder metallurgy sintering, resulting in the generation of surface pores that can store lubricating oil. However, due to the surface porosity, the surface roughness fluctuates significantly, which may lead to solid contact wear during bearing operation, causing metal particles to enter the lubricating oil, increasing operational instability, vibration, and noise. Adding V-shaped grooves on the inner diameter surface of the bearing sleeve can help maintain stability during bearing operation. The principle behind this is that the hydrodynamic pressure generated by the groove pattern peaks effectively separates the bearing and shaft, reducing friction between the shaft and bearing sleeve.
This study utilizes two types of powder metallurgy journal bearings, one with a plain surface and the other with a V-shaped pattern surface, to investigate the differences in their transmission performance. The shaft speed is varied at four different conditions: 1000, 2000, 4000, and 8000 rpm, with two different types of lubricating oils, to explore the influence of lubricating oil viscosity on transmission performance. Prior to the experiments, accelerometers, strain gauges, thermocouples, and load cells were installed to facilitate signal measurements during the experiments. The collected data were then integrated and analyzed, comparing the results obtained under different conditions to explore the differences in performance influenced by the V-shaped grooves.Surface morphology parameters of the bearings were measured using a white light interferometer, and they were incorporated into the COMSOL hydrodynamic bearing analysis model to compare the changes in oil film under the four different shaft speeds and verify and discuss the results with the experimental data.
The research findings show that under low-speed operation, the V-shaped groove pattern surface exhibits lower vibration RMS compared to the plain surface. As the rotational speed increases, cavitation results in higher vibration RMS for the V-shaped groove pattern surface, though the numerical difference between the two is not significant. The hydrodynamic pressure generated by the V-shaped grooves separates the shaft and bearing sleeve, leading to lower friction torque, surface strain, and surface temperature rise compared to the plain surface. When using R32 lubricating oil for high-speed operation, friction torque and temperature rise are lower, but thermal expansion tightness may occur, leading to larger variations in friction torque. In contrast, using GF500 lubricating oil effectively reduces vibration, resulting in smaller variations in friction torque at different speeds, making it more stable. However, the higher viscosity of GF500 leads to higher friction torque and temperature rise, factors that need to be considered when choosing lubricants.

摘要......i
Abstract......ii
誌謝......iv
目錄......v
表目錄......viii
圖目錄......ix
第一章 緒論......1
1.1 前言......1
1.2 文獻回顧......2
1.2.1 軸頸軸承液動潤滑與黏溫特性相關研究......2
1.2.2 粉末冶金相關研究......2
1.2.3 軸頸軸承振動與摩擦扭矩相關研究......2
1.2.4 液動潤滑有限元素分析相關研究......3
1.3 研究動機與目的......4
1.4 論文架構......5
第二章 基礎理論......6
2.1 液體動力潤滑理論......6
2.2 訊號處理方法......8
2.2.1 取樣頻率(sampling frequency)......8
2.2.2 取樣定理( Shannon Theorem )......8
2.2.3 混疊(Aliasing)......8
2.2.4 均方根值(RMS)......9
2.2.5 移動平均(MA)......9
2.3 軸承溫昇量測方法......9
2.3.1 熱傳導定律......9
2.4 表面形貌......10
2.4.1 面平均粗糙度(Sa)......10
2.4.2 波峰頂點密度(Spd)......10
2.4.3 平均曲率半徑(Spc)......11
第三章 實驗設備與規劃......12
3.1 實驗流程......12
3.2 實驗設備與儀器介紹......13
3.2.1 軸承試驗機......13
3.2.2 粉末冶金軸頸軸承......14
3.2.3 潤滑油品......15
3.2.4 馬達控制與量測......16
3.2.4.1 直流有刷馬達......16
3.2.4.2 PWM 直流馬達調速器......16
3.2.4.3 光遮斷器......17
3.2.4.4 LCD 顯示屏幕......17
3.2.4.5 非接觸式轉速計......17
3.2.5 摩擦扭矩量測......18
3.2.5.1 荷重元......18
3.2.5.2 放大顯示器......18
3.2.6 加速規......19
3.2.7 應變規......20
3.2.8 熱電偶......20
3.2.9 電流勾表 21
3.2.10 白光干涉儀......21
3.3 實驗步驟......22
3.3.1 實驗前置作業......22
3.3.2 實驗後分析處理......22
3.3.3 有限元素分析模型建立......23
第四章 結果與討論......25
4.1 無花紋表面粉末冶金軸頸軸承傳動性能( R32潤滑油)......25
4.1.1 振動 RMS 分析......25
4.1.2 軸承摩擦扭矩......26
4.1.3 軸承表面應變......27
4.1.4 軸承表面溫昇......28
4.1.5 各數據穩定段綜合討論 29
4.2 V字型花樣表面粉末冶金軸頸軸承傳動性能( R32潤滑油) 32
4.2.1 振動 RMS 分析......32
4.2.2 軸承摩擦扭矩......33
4.2.3 軸承表面應變......34
4.2.4 軸承表面溫昇......35
4.2.5 各數據穩定段綜合討論......36
4.3 表面形貌對軸承傳動性能影響分析( R32潤滑油)......39
4.3.1 振動 RMS 分析......39
4.3.2 軸承摩擦扭矩......40
4.3.3 表面應變與溫昇關係......40
4.4 無花紋表面粉末冶金軸頸軸承傳動性能( GF500潤滑油)......42
4.5 V字型花樣表面粉末冶金軸頸軸承傳動性能(GF500潤滑油)......45
4.6 不同潤滑劑傳動黏溫特性比較......47
4.6.1 振動 RMS 分析......47
4.6.2 摩擦扭矩......48
4.6.3 表面應變與溫昇關係......49
4.7 液體動壓模擬分析......51
4.7.1 液動潤滑油膜壓力......51
4.7.2 液動潤滑油膜厚度......57
第五章 結論......58
第六章 未來展望......59
參考文獻......60
Extended Abstract......63

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