ISSN   1004-0595

CN  62-1224/O4

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高压干气密封三体双向流固耦合模型及端面力变形规律研究

Three-Body Two-Way Fluid-Solid Coupling Model and End Face Mechanical Deformation Law of High Pressure Dry Gas Seal

  • 摘要: 本文中综合考虑影响密封环端面力变形的流体膜压力、密封环结构和环座作用力这3个关键要素及其交互影响,提出了干气密封三体双向流固耦合模型,通过求解湍流修正的雷诺方程获得气膜压力场,并应用ANSYS求解密封环端面力变形,研究了不同结构参数和运行工况条件下密封环端面力变形规律,对比分析了3种流固耦合模型以及流态模型、密封环轴向厚度和辅助密封径向位置对密封环端面变形和稳态性能的影响,获得了上述结构参数优选值范围. 结果表明:相较于三体双向模型,忽略流体膜与密封环交互影响的三体单向模型和忽略环座作用力的双体双向模型获得的平均膜厚和泄漏率均显著偏小;流态模型选取对密封间隙形状影响不大,但会使平衡膜厚和泄漏率明显偏低;改变静环轴向厚度和动环辅助密封径向位置均会使对应密封环端面变形方向发生变化,且通过与动环轴向厚度和静环辅助密封圈径向位置取值的合理组合,可实现较低泄漏率和近平行间隙的目标.

     

    Abstract: A three-body two-way fluid-solid coupling model of dry gas seal was proposed by comprehensively considering the three key factors, including fluid film pressure, seal ring structure and seal ring seat force, that affected the mechanical deformation of seal ring end face and their interaction. Taking the classical high-pressure dry gas seal structure as the research object, the film pressure was obtained by solving the Reynolds equation with turbulence, the deformation of seal ring and the stress and strain of the spring energized seal ring was solved by the commercial software ANSYS. The deformation law of seal ring end face under different structural parameters and operating conditions was studied. The effects of three fluid-solid coupling models and flow model, the axial thickness of the sealing ring and the radial position of the auxiliary seal on the deformation of the sealing ring end face and steady-state performance were compared and analyzed, and the optimal value range of the above-mentioned structural parameters was obtained. The results showed that compared with the three-body two-way fluid-solid coupling model of dry gas seal considering the interaction of 'fluid film-sealing ring-ring seat', the three-body one-way model which ignoring the interaction between the fluid film and the sealing ring would make the end face force deformation of the sealing rings larger, while the two-body two-way model which ignoring the ring seat force would make them significantly smaller. The average film thickness and leakage rate obtained by the three-body one-way model and the two-body two-way model were significantly smaller, and the predicted leakage rate was 38.5% and 33.5% smaller, respectively. The selection of turbulent and laminar flow pattern model had little effect on the shape of sealing gap, but the predicted value of laminar flow model for outlet blocking pressure was higher, which would make the average film thickness and leakage rate higher when the pressure was low (8 MPa), and make the average film thickness and leakage rate significantly lower when the pressure was high (16 MPa), and the relative errors reached 38% and 15%, respectively. Increasing the axial thickness of the rotating ring and the radial position of the stationary ring auxiliary seal only changed the deformation of the corresponding seal ring end face without affecting the deformation shape, and made the opening force and leakage rate monotonically decreased. Increasing the axial thickness of the stationary ring and the radial position of the auxiliary seal of the rotating ring would significantly change the deformation direction of the corresponding seal ring, and the opening force and leakage rate would increase monotonously, and by reasonably combining with the axial thickness of the rotating ring and the radial position of the auxiliary seal of the static ring, the goal of lower leakage rate, near parallel gap and suitable operating film thickness could be achieved.

     

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