臺灣博碩士論文加值系統

液壓軸承技術發展已有多年歷史。相關文獻指出，採用薄膜節流器設計，其軸承剛性的表現較採用其它種類的節流器好。然而，薄膜節流器的設計也相對複雜許多。於本研究，我們針對薄膜節流器提出兩個無因次的節流器設計參數；無因次薄膜剛性(Dimensionless membrane stiffness, ) 與軸承系統的設計節流比 (Design restriction ratio, λ)。於單向墊軸承，當無因次薄膜剛性 =1.33，設計節流比λ=0.25時，軸承剛性表現最佳(理論上，軸承剛性於某些工作區間趨近無限大)。實際上，該參數組合亦適用於對向墊的軸承配置。當軸承上下墊皆採用相同規格設計時，設計無因次薄膜剛性為1.33，可得到相當高的軸承剛性結果。分析結果顯示，當軸承受一外力，使得上油腔壓力達到73%的供油壓力情況下，其軸承之位移量仍可維持於6%的設計油膜間隙內。

Many studies reported that the membrane restrictor may have excellent performance when it was properly designed. However designs of membrane restrictors are much complicated than other frequently used restrictors i.e. capillary restrictor and orifice restrictor for hydrostatic bearings. General rules of membrane restrictor designs, which can be readily available for use by industry designers and engineers are needed.

In this study, it is examined that a high static stiffness of the bearing is attainable as two design parameters of membrane-type restrictor are properly chosen. The first one is the dimensionless stiffness of the membrane (Kr*) and the other one is the design restriction ratio of the bearing system (λ). When the deformation-load relationship of the restrictor is compliance with the ideal trend, the stiffness of the bearing should theoretically approach infinite in most application range. It was derived that Kr* = 1.33 and λ = 0.25 is the solution for such condition. The film thickness for the bearing will be maintained at designed levels over a loading range.

The optimum result is applicable not only for single-pad bearing but also for opposed-pad case. The recommended value for obtaining the great stiffness of an opposed-pad bearing is Kr* = 1.33 and λ = 0.13~0.24. In the case where the upper pad and lower pad are equally designed, the displacement of the bearing can be maintained less than 6 percent of a non-loading clearance if the recess pressure extending to 73 percent of the supply pressure.

ABSTRACT I
ACKNOWLEDGMENTS II
TABLE OF CONTENTS III
LIST OF FIGURES V
LIST OF TABLES X
NOMENCLATURE XI

1. INTRODUCTION 1
1.1 Ultraprecision Machining 1
1.2 Bearing and Rolling Guidance System 4
1.3 Hydrostatic Bearing 9
1.4 Contents of this Thesis 12

2. LITERATURES REVIEWS 14
2.1 Operation Principle of Hydrostatic Bearing 14
2.2 Compensation Mechanisms for Hydrostatic Bearing 17
2.3 Membrane Restrictor 25
2.4 Design and Operation Parameters 33
2.5 Summary 41

3. MODELING 42
3.1 Navier-Stokes equations 44
3.2 Reynolds Equation 47
3.3 Effective Area of Bearing Pad 50
3.4 Flow Resistance 55
3.5 Analytical Considerations 58
3.6 Design Parameters 65
3.7 Deformation of Membrane 68

4. SINGLE-PAD CONFIGURATION 74
4.1 Bearing Model 74
4.2 Analytical Results 76
4.3 Summary 86

5. OPPOSED-PAD CONFIGURATION 87
5.1 Bearing Model 87
5.2 Analytical Results 91
5.2.1 Cases for α = 1.0 92
5.2.2 Cases for α = 2.0 97
5.2.3 Cases for α = 0.5 100
5.3 Performance Evaluation 104
5.3.1 Cases for α = 1.0 106
5.3.2 Cases for α = 2.0 112
5.3.3 Cases for α = 0.5 117
5.4 Summary 123

6. CONCLUSIONS 125
6.1 Contribution 125
6.2 Recommendation 126

REFERENCE 129

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