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低雷诺数环境下低压涡轮叶栅气动优化设计研究

苏金友 唐智礼 田金虎 李剑白 张维涛

苏金友, 唐智礼, 田金虎, 等. 低雷诺数环境下低压涡轮叶栅气动优化设计研究[J]. 航空动力学报, 2026, 41(X):20250605 doi: 10.13224/j.cnki.jasp.20250605
引用本文: 苏金友, 唐智礼, 田金虎, 等. 低雷诺数环境下低压涡轮叶栅气动优化设计研究[J]. 航空动力学报, 2026, 41(X):20250605 doi: 10.13224/j.cnki.jasp.20250605
SU Yinyou, TANG Zhili, TIAN Jinhu, et al. Research on aerodynamic optimization design of low-pressure turbine cascades at low Reynolds numbers environments[J]. Journal of Aerospace Power, 2026, 41(X):20250605 doi: 10.13224/j.cnki.jasp.20250605
Citation: SU Yinyou, TANG Zhili, TIAN Jinhu, et al. Research on aerodynamic optimization design of low-pressure turbine cascades at low Reynolds numbers environments[J]. Journal of Aerospace Power, 2026, 41(X):20250605 doi: 10.13224/j.cnki.jasp.20250605

低雷诺数环境下低压涡轮叶栅气动优化设计研究

doi: 10.13224/j.cnki.jasp.20250605
基金项目: 某特区支持项目(BK012)
详细信息
    作者简介:

    苏金友(1983-),男,研究员,博士生,主要从事航空发动机设计与试验测试技术研究。E-mail:88929284@qq.com

  • 中图分类号: V231.3

Research on aerodynamic optimization design of low-pressure turbine cascades at low Reynolds numbers environments

  • 摘要:

    为实现低压涡轮在低雷诺数环境下稳定工作,采用数值仿真和试验方法,从雷诺数、载荷系数、来流约化频率和湍流度影响因素方面,分析了低压涡轮叶栅的工作特性,并开展适应低雷诺数工作环境的优化设计。结果表明:随着雷诺数降低,约化频率的影响增加;雷诺数在1.0×104时,约化频率由1.03增加到3.09,效率降低0.9%,损失增加6.0%。优化后的叶栅方案降低了叶片吸力面喉部后逆压梯度,有效抑制了低雷诺数环境下的分离流动,使涡轮叶栅性能大幅提高。低雷诺数环境下,优化后叶栅吸力面无气流分离,压力和能量损失减小30%~40%;高雷诺数环境下无改善;来流攻角在−20°~10°范围内压力和能量损失增加5%~25%,但在−10°~0°时损失相当。

     

  • 图 1  叶栅模型

    Figure 1.  Cascade model

    图 2  仿真计算收敛曲线

    Figure 2.  Convergence curve of simulation calculation

    图 3  叶栅网格划分

    Figure 3.  Cascade grid

    图 4  验证用低压涡轮子午面流道示意图

    Figure 4.  Meridional flow passage for low-pressure turbine verification

    图 5  低压涡轮级交界面静压与试验数据对比

    Figure 5.  Comparison of static pressure at the interface of low-pressure turbine stage with experimental data

    图 6  稳态叶片表面等熵马赫数分布

    Figure 6.  Steady-state isentropic Mach number distribution on the blade surface

    图 7  稳态叶栅槽道马赫数分布

    Figure 7.  Steady-state cascade passage Mach number distribution

    图 8  叶片表面等熵马赫数分布(Zw=1.26, 时均值)

    Figure 8.  Isentropic Mach number distribution on the blade surface (Zw=1.26, time-averaged value)

    图 9  叶片表面切应力(Zw=1.26,时均值)

    Figure 9.  Blade surface shear stress (Zw=1.26, time averaged)

    图 10  一个周期内功率和流量变化(Zw=1.01, fr=2.07, Re=2×105

    Figure 10.  Changes in power and flow rate within one cycle (Zw=1.01, fr =2.07, Re=2×105

    图 11  雷诺数和效率曲线(Zw=1.44)

    Figure 11.  Reynolds number-efficiency curve (Zw=1.44)

    图 12  雷诺数和能量损失曲线(Zw=1.44)

    Figure 12.  Reynolds number-energy loss curve (Zw=1.44)

    图 13  约化频率和效率曲线(Zw=1.44)

    Figure 13.  Reduced frequency-effciency curve (Zw=1.44)

    图 14  约化频率和能量损失曲线(Zw=1.44)

    Figure 14.  Reduced frequency-energy loss curve (Zw=1.44)

    图 15  叶片不同相位

    Figure 15.  Different blade phases

    图 16  不同时刻湍动能

    Figure 16.  Turbulent kinetic energy at different times

    图 17  不同时刻吸力面切应力(Zw=1.44)

    Figure 17.  Isentropic Mach numbers on the suction surface at different times (Zw=1.44)

    图 18  叶型示意图

    Figure 18.  Schematic diagram of blade profile

    图 19  叶栅试验器

    Figure 19.  Cascade tester

    图 20  优化前后叶栅表面等熵马赫数

    Figure 20.  Surface isentropic Mach number of blade cascades before and after optimization

    图 21  不同马赫数下叶片表面等熵马赫数分布

    Figure 21.  Isentropic Mach number distribution on blade surface at different exit Mach numbers

    图 22  总压和能力损失随出口马赫数变化

    Figure 22.  Variation of total pressure and energy loss with outlet Mach number

    图 23  不同雷诺数下叶片表面等熵马赫数分布

    Figure 23.  Isentropic Mach number distribution on blade surface at different Reynolds numbers

    图 24  总压和能量损失随雷诺数变化

    Figure 24.  Variation of total pressure and energy loss with Reynolds number

    图 25  不同攻角时叶片表面等熵马赫数

    Figure 25.  Isentropic Mach number on blade surface at different incidence angles

    图 26  叶片通道马赫数云图(i=10°)

    Figure 26.  Mach Number contours in blade passage (i=10°)

    图 27  总压和能量损失随攻角变化

    Figure 27.  Variation of total pressure and energy loss with incidence degree

    表  1  计算模型

    Table  1.   Computational model

    序号 Zw fr
    1 1.01 0
    2 1.01 1.03
    3 1.01 2.07
    4 1.01 3.09
    5 1.26 0
    6 1.26 1.03
    7 1.26 2.07
    8 1.26 3.09
    9 1.44 0
    10 1.44 1.03
    11 1.44 2.07
    12 1.44 3.09
    下载: 导出CSV

    表  2  仿真动叶叶栅主要参数

    Table  2.   Main parameters of simulated moving blade cascade

    参数叶栅A叶栅B叶栅C
    Zw1.011.261.44
    叶片数占比/%1008070
    安装角/(°)30.535.540.5
    下载: 导出CSV

    表  3  计算时间步

    Table  3.   Computational time step

    参数 叶栅A 叶栅B 叶栅C
    动叶通道时间步 30 35 40
    周期数 18 16 14
    总时间步 540 560 560
    下载: 导出CSV

    表  4  仿真计算与试验数据对比

    Table  4.   Comparison of computational results and test data

    参数 仿真计算 试验数据
    流量/(kg/s) 28.13 28.4
    膨胀比 4.37 4.37
    效率 0.921 0.915
    下载: 导出CSV

    表  5  优化前后叶栅主要参数

    Table  5.   Main parameters of the cascade before and after optimization

    参数 优化前 优化后
    弦长/mm 28 29
    安装角/(°) 62 60
    栅距/mm 21
    进口气流角/(°) 70
    出口气流角/(°) 38.5
    下载: 导出CSV
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  • 收稿日期:  2025-12-29
  • 网络出版日期:  2026-03-24

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