Research on aerodynamic optimization design of low-pressure turbine cascades at low Reynolds numbers environments
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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。
Abstract:To ensure stable operation of the low-pressure turbine under low-Reynolds-number conditions, numerical simulation and experimental methods were adopted to analyze the operating characteristics of the low-pressure turbine cascade with respect to influencing factors including Reynolds number, load coefficient, incoming flow reduced frequency, and turbulence intensity, and further carry out optimal design adapted to the low-Reynolds-number working environment. The results showed that with the decrease in Reynolds number, the influence of reduced frequency increased; when the Reynolds number was 1.0×104, the reduced frequency increased from 1.03 to 3.09, leading to a 0.9% reduction in efficiency and a 6.0% increase in loss. The optimized cascade scheme reduced the adverse pressure gradient downstream of the throat on the blade suction surface, effectively suppressed the separated flow under low-Reynolds-number conditions, and thus significantly improved the performance of the turbine cascade. Under low-Reynolds-number conditions, there was no airflow separation on the suction surface of the optimized cascade, and the pressure and energy losses were reduced by 30%—40%; no improvement was observed under high-Reynolds-number conditions. Within the range of incoming flow angle of attack from −20° to 10°, the pressure and energy losses increased by 5%—25%, while the losses remained nearly the same when the angle of attack was between −10° and 0°.
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Key words:
- low Reynolds number /
- cascade /
- airfoil optimization /
- flow separation /
- low-pressure turbine
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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 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 Zw 1.01 1.26 1.44 叶片数占比/% 100 80 70 安装角/(°) 30.5 35.5 40.5 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 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 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 -
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