Research on the cone angle and clearance of main pump seal

For better film characteristics of the main pump seal (MPS), a theoretical calculation model was proposed based on the Reynolds equation. A case study with defined MPS was carried out, film stiffness was taken as the basic constraint condition, and the cone angle and clearance are two optimization targets. When the film stiffness reaches a maximum, the corresponding cone angle and clearance is the optimal value. The results show that: (1) film stiffness increased and decreased with clearance and cone angle, respectively; (2) the optional clearance was determined to be within a range of 2~8 µm at a cone angle of between 0.1~1.2′; (3) the maximum of film stiffness is inversely proportional to the cone angle (Clearance) approximately under the clearance (Cone angle) is fixed; (4) leakage is directly proportional to the clearance to power three, and the clearance has greater influence on the amount of leakage than the cone angle. These results provide a reliable theoretical justification for MPS-based designs including optimization method. It therefore forms a fundamental base for research and practical application.

[1]  Noël Brunetière,et al.  Modelling of non-laminar phenomena in high reliability hydrostatic seals operating in extreme conditions , 2008 .

[2]  Richard F. Salant,et al.  Unsteady Analysis of a Mechanical Seal Using Duhamel’s Method , 2005 .

[3]  R. P. Gabriel,et al.  Fundamentals of spiral groove noncontacting face seals , 1994 .

[4]  Michael M. Khonsari,et al.  Numerical Simulations of the Flow Field Around the Rings of Mechanical Seals , 2006 .

[5]  Lin Dong,et al.  Design and Performance Analysis of Dual Vibrating Motors Self Synchronous Shaker with Balanced Elliptical Motion , 2013 .

[6]  A. O. Lebeck,et al.  Fluid Temperature and Film Coefficient Prediction and Measurement in Mechanical Face Seals—-Numerical Results , 1998 .

[7]  Noël Brunetière,et al.  A Modified Turbulence Model for Low Reynolds Numbers: Application to Hydrostatic Seals , 2005 .

[8]  E. Galenne,et al.  Thermo-Elasto-Hydro-Dynamic Modeling of Hydrostatic Seals in Reactor Coolant Pumps , 2007 .

[9]  J. D. Summers-Smith Mechanical Seal Practice for Improved Performance , 1988 .

[10]  Noël Brunetière,et al.  Numerical Modeling of Thermohydrodynamic Mechanical Face Seals , 2010 .

[11]  Noël Brunetière,et al.  Influence of Fluid Flow Regime on Performances of Non-Contacting Liquid Face Seals , 2002 .

[12]  W. Ryu,et al.  Corrosion behaviors of sintered and chemically vapor deposited silicon carbide ceramics in water at 360 °C , 2003 .

[13]  The Hydrostatic Noncontact Seal Including Fluid Inertia Effect , 1986 .