西安交通大学能源与动力工程学院,西安,710049
网络首发:2014-01-10,
纸质出版:2014
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马斌 1, 孙皖 1, 赖天伟 1, 等. 波箔箔片动压气体轴承的实验研究[J]. 西安交通大学学报, 2014,48(1):118-122.
Experimental Study on Gas Lubricated Hydrodynamic Bump Type Foil Bearing[J]. 2014, 48(1): 118-122.
马斌 1, 孙皖 1, 赖天伟 1, 等. 波箔箔片动压气体轴承的实验研究[J]. 西安交通大学学报, 2014,48(1):118-122. DOI: 10.7652/xjtuxb201401020.
Experimental Study on Gas Lubricated Hydrodynamic Bump Type Foil Bearing[J]. 2014, 48(1): 118-122. DOI: 10.7652/xjtuxb201401020.
为满足透平机械高速可靠运转的需求
设计了一种波箔型箔片轴承
其基本结构由柔性平箔和支承平箔的弹性波箔组成。在气体轴承-高速低温透平膨胀机实验台上对波箔箔片动压气体轴承进行了实验
实验中采用压缩空气驱动透平转子
以功率75 kW的阿特拉斯螺杆压缩机作为供气源
从而获得了0.1~1.15 MPa、标准工况下最高流量为600 m
3
/h的压缩空气。将波箔厚度为0.05 mm及0.07 mm的2种箔片动压气体径向轴承
应用于主轴Φ25 mm的标准工况下150 m
3
/h制氧机用高速透平膨胀机
研究了箔片支承高速透平转子的振动特性及稳定性。实验结果表明:波箔弹性元件的刚度是轴承性能的重要影响因素之一
0.05 mm波箔刚度小
柔性变形裕度较大
可以抑制转子不稳定涡动
透平膨胀机转子最高转速达93 366 r/min; 0.07 mm波箔刚度较大
柔性变形裕度相对较小
当最高转速达到93 161 r/min时转子出现涡动。2种波箔厚度的轴承最高转速达到9.3万 r/min时转子的最大振幅均小于20 μm
波箔轴承表现出了良好的刚度和阻尼特性
可有效抑制Φ25 mm的高速透平膨胀机转子的涡动。
A bump type gas foil bearing was designed to meet the requirements of reliability and stability of high speed turbomachinery employed in engineering and an experimental investigation into the bump type gas foil bearing was carried out on a gas bearing high speed turbo-expander rotor test rig. The bump type gas foil bearing mainly consists of compliant top plate foil and bottom bump foil layers. In the experiment
the turbo-expander rotor was driven by compressed air with the pressure of 0.1-1.15 MPa and a volume flow rate of up to 600 m
3
/h(under standard conditions)from a 75 kW Atlas scroll compressor
. Two bump type gas foil bearings having the foil 0.05 mm and 0.07 mm in thickness were applied in an industrial 150 m
3
/h(under standard conditions)oxygen high speed turbo-expander in which the diameter of the rotor is 25 mm. The vibration characteristics and the stability were examined. The results show that stiffness was one of the most important factors in bearing performance. The good stiffness characteristic of the 0.05 mm foil promoted effectively the vibration performance of the bearing
and the maximum rotational speed reached 93 366 r/min. In comparison
the larger stiffness of 0.07 mm foil caused the instable rotation of the rotor at 93 161 r/min. When the maximum rotating speed of the turboexpander rotor was 93 000 r/min
the present bump type gas foil bearing had good stiffness and damping performance. In addition
the maximum vibration amplitudes were smaller than 20 μm
thus effectively inhibiting the rotor whir in the high speed turbo-expander.
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RUBIO D, SAN A L. Bump-type foil bearing structural stiffness: experiments and predictions[J]. ASME Journal of Engineering for Gas Turbines and Power, 2006, 128(3): 653-660.
ANDRES L S, RUBIO D, KIM T H. Rotordynamic performance of a rotor supported on bump type foil gas bearings: experiments and predictions[J]. ASME Journal of Engineering for Gas Turbines and Power, 2007, 129(3): 850-857.
ANDRES LS, KIM T H. Forced nonlinear response of gas foil bearing supported rotors[J]. Tribology International, 2008, 41(8): 704-715.
LE L S, ARGHIR M, FRENE J. A new foil bearing dynamic structural model[C]∥Proceedings of the ASME/STLE International Joint Tribology Conference. New York, USA: ASME, 2008: 993-995.
HOWARD S A, ANDRES L S. A new analysis tool assessment for rotor dynamic modeling of gas foil bearings[J]. ASME Journal of Engineering for Gas Turbines and Power, 2011, 133(2): 022505.
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