Abstract：In order to further understand the stiffness characteristics of the aerostatic gas lubricating mechanical seal, an analytical expression of the gas film stiffness was deduced based on analytical method. The calculated results by the analytical expression are very close to the results obtained by differentiating the opening force curve-fitting equation. The gas film stiffness characteristics influenced by the orifice diameter, supplying gas pressure and process gas pressure had been analyzed by the analy-tical expression, and the 3D surface charts of the gas film stiffness influenced by gas film thickness and the supplying gas pressure or the process gas pressure had been obtained. The results show that the effect of orifice diameter on the stiffness is obvious and larger stiffness can be got when the orifice dia-meter is about 0.2 mm as to the seal investigated. The gas film stiffness increases with increasing of supplying gas pressure or boundary pressure ratio of the supplying gas pressure over the process gas pressure. Raising the supplying gas pressure or boundary pressure ratio can obviously increase the gas film stiffness. The gas film stiffness is increasing firstly and then reducing with the increasing of gas film thickness at the specific pressure or pressure ratio. There is maximum gas film stiffness as the gas film thickness reaches a certain value. The gas film stiffness will be larger when the gas film thickness is 3-6 μm as to the dry gas seal investigated.
[1]朱维兵,周圣人,王和顺.静压干气密封端面温度场分析[J].西华大学学报:自然科学版,2010,29(6):1-3. Zhu Weibing,Zhou Shengren,Wang Heshun. Analysis of end surface temperature field for static pressure dry gas seal[J]. Journal of Xihua University:Natural Science Edition,2010,29(6):1-3.(in Chinese)[2]余建平,宋鹏云. 静压气体润滑机械密封技术研究进展[J]. 液压气动与密封, 2007, 27(4): 21-23. Yu Jianping, Song Pengyun. Progress in the study of aerostatic gas lubricating mechanical seal [J]. Hydraulics Pneumatics & Seals, 2007, 27(4): 21-23.(in Chinese)[3]Li Y T, Ding H. A simple calculation method on the performance analysis of aerostatic thrust bearing with multiple pocketed orifice-type restrictors [J]. Tribology International, 2012,56: 66-71.[4]Masaaki M, Shigeka Y. Numerical investigation of static and dynamic characteristics of aerostatic thrust bearings with small feed holes [J]. Tribology International, 2010, 43(8): 1353-1359.[5]Nishio U, Somaya K, Yoshimoto S. Numerical calculation and experimental verification of static and dynamic characteristics of aerostatic thrust bearings with small feedholes [J]. Tribology International, 2011, 44(12): 1790-1795.[6]Chen H S, Chow C Y, Wilcock D F. Behavior of hydrostatic and hydronamic noncontacting face seals [J]. Journal of Lubrication Technology, 1968,90(2):510-519.[7]Yamamoto M, Mori H, Katayama N, et al. Dynamic characteristics of hydrostatic noncontact gas face seals [J]. Journal of Japan Society of Lubrication Engineers, 1984, 29(6): 451-457.[8]Stolarshi T A, Xue Y. Performance study of a back-depression mechanical dry gas seal [J]. Journal of Engineering Tribology, 1998, 212(4): 279-290.[9]余建平. 静压气体润滑机械密封特性研究[D]. 昆明:昆明理工大学化学工程学院, 2008.[10]王和顺,董霖,黄泽沛,等. 静压干气密封端面流场数值模拟[J]. 排灌机械工程学报, 2011, 29(2): 165-169. Wang Heshun, Dong Lin, Huang Zepei, et al. Numerical simulation on flow flied of aerostatic dry gas seal [J]. Journal of Drainage and Irrigation Machinery Engineering, 2011, 29(2): 165-169.(in Chinese)[11]龙威. 平面空气静压轴承承载特性研究[D]. 哈尔滨:哈尔滨工业大学机电工程学院, 2010.[12]刘暾, 刘育华, 陈世杰. 静压气体润滑[M]. 哈尔滨:哈尔滨工业大学出版社, 1990: 85-86.
