Dynamic performance analysis of double interlocking padded finger seal based on fluid-structure interaction
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摘要:
提出一种具有双梁、双靴互嵌式非接触指尖密封结构，建立了密封系统动态性能流固耦合数值分析模型，对转子施加正弦激励，分别研究转速、压差以及转子激励幅值对双靴互嵌式指尖密封的动态气膜承载力、密封靴最大变形以及泄漏率的影响，并与典型单靴非接触式指尖密封结构性能进行对比。结果表明：在低速低压工况下，双靴互嵌式指尖密封对不同幅值转子激励的跟随性均良好；高速高压工况时，跟随性有所降低。此外，在高速高压工况时，气膜承载力明显提升，且在转子向上跳动阶段泄漏率随激励幅值增大而明显减小。与典型单靴式流体静动压式指尖密封相比，双靴互嵌式指尖密封泄漏因子平均降低约25%。合理设计初始安装间隙，可避免转子与靴底发生碰撞。该研究结果为设计满足高工况的非接触式指尖密封提供一种思路。
Abstract:A non-contact finger seal structure with double beams and double boots interlocking was proposed. A fluid-structure coupling numerical analysis model of dynamic performance of the sealing system was established. Sinusoidal excitation was applied to the rotor, and the effects of rotor speed, pressure difference and rotor excitation amplitude on dynamic air film bearing capacity, maximum deformation and leakage rate of the double interlocking padded finger seal were studied respectively, and compared with the typical single padded non-contact finger seal structure performance. The results showed that under low speed and low pressure conditions, the double interlocking padded finger seal shoe had good tracking performance against different amplitude rotor excitation; at high speed and high pressure, the following performance was reduced. In addition, under high speed and high pressure conditions, the gas film bearing capacity significantly increased, and the leakage rate significantly decreased with the increase of excitation amplitude during the upward run-out stage of the rotor. Compared with a typical single padded finger seal, the leakage factor of the double interlocking padded finger seal decreased by an average of about 25%. The reasonable design of the initial installation clearance can avoid the collision between the rotor and the sole of the shoe. This work can provide an idea for designing non-contact finger seal meeting high operating conditions.
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图 3 双靴互嵌式指尖密封固场、流场几何模型
Figure 3. Geometric model of solid field and flow field for double interlocking padded finger seal
图 12 靴底变形（压差为0.6 MPa，室温，转速为25 000 r/min）
Figure 12. Shoe sole deformation （pressure difference of 0.6 MPa, room temperature, rotation speed of 25 000 r/min）
图 13 低压差（0.1 MPa）下流体流线图
Figure 13. Fluid streamline diagram under low pressure difference （0.1 MPa）
图 14 低压差（0.1 MPa）下转速对密封动态性能影响
Figure 14. Effect of rotational speed on dynamic performance of seal under low pressure difference （0.1 MPa）
图 15 高压差（0.6 MPa）下转速对密封动态性能影响
Figure 15. Effect of rotational speed on dynamic performance of seal under high pressure difference （0.6 MPa）
图 17 低转速下（12 000 r/min）压差对密封动态性能的影响
Figure 17. Effect of pressure difference on dynamic performance of seals at low speed （
12000 r/min）
图 18 高转速下（
25000 r/min）压差对密封动态性能的影响Figure 18. Effect of pressure difference on dynamic performance of seals at high speed （
25000 r/min）
图 19 低速低压时激励幅值对动态性能的影响
Figure 19. Effect of excitation amplitude on dynamic performance at low speed and low pressure
图 20 高速高压时激励幅值对动态性能的影响
Figure 20. Effect of excitation amplitude on dynamic performance at high speed and high pressure
表 1 密封结构参数
Table 1. Seal structure parameters
参数 数值 D/mm 220 Dr/mm 220.1 Db/mm 240 Do/mm 255 Df/mm 224.1 h/mm 0.05 Bh/mm 4 Bd/mm 5 Bq/mm 3 r/mm 1.5 B/mm 0.4 fm 0.2 fh 0.15 
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表 2 密封材料参数
Table 2. Seal material parameters
材料 GH4169 GH605 $ \rho $/（g/cm3） 8.24 9.13 E/GPa 201 201 μ 0.3 0.286 α/10−6 K−1 13.5 13.5
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表 3 工况参数
Table 3. Working condition parameters
参数 数值及说明 $ {p}_{\mathrm{c}} $/MPa 0.1 $ {p}_{\mathrm{u}} $/MPa 0.2，0.3，0.45，0.6，0.7 $ {n}_{\mathrm{c}} $/（r/min） 12000 ，15000 ，20000 ，25000 $T$/K 298.15 $\Delta r$/mm 0.01，0.02，0.03，0.04 h/mm 0.05 流体介质 理想空气
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表 4 最小安装密封间隙
Table 4. Minimum mounting seal clearance
$\Delta r$/mm ${c_{\min }}$/mm 0.01 0.024 0.02 0.032 0.03 0.056 0.04 0.068
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