c 绝对速度,m/s
g 重力加速度m/s2
H 压头,m
ka、kb等 欧拉线的常数
Q 排量l/s或者 m3/s
u 叶片的切向速度,m/s
w 相对速度,m/s
α 绝对液流角度,度
β 相对液流角度,度
ζ 压力损失系数
* 叶片方向
f.p 前曲泵叶轮
f.t 前曲涡轮机叶轮
p 泵模式
t 涡轮机模式
u 切线方向
x 轴向
参考文献 :
[1] P. Singh and F. Nestmann, ‘Experimental Optimization of a Free Vortex Propeller Runner for Micro Hydro Application’, J. Experimental Thermal & Fluid Science, 33, pp. 991-1002, (2009).
[2] R.R. Mankbadi and S.A. Mikhail, ‘A turbine-pump system for low-head hydropower’, J. Energy Conversion & Management, 25, pp. 339-344, (1985).
[3] A.J. Stepanoff, Centrifugal and Axial Flow Pumps, John Wiley & Sons Inc, Ch. 8 and 16, (1957).
[4] (a) S. Baumgarten, H. Krasmann and J. Rosener, pp. 147-160; (b) U. Stark and H. Siekmann, pp. 87-96; (c) P. Springer, pp. 109-118, Publication 1 of the Pfleiderer Institute of Turbomachines, University of Braunschwig, Verlag und Bildarchiv W. H. Faragallah, Sulzbach, Germany, (1994).
[5] S.L. Dixon, Fluid Mechanics and Thermodynamics of Turbomachinery, Elsevier, Ch. 3, (2005).
[6] P. Singh and F. Nestmann, ‘Exit Blade Geometry and Part-Load Performance of Small Axial Flow Propeller Turbines: An Experimental Investigation’, J. Experimental Thermal & Fluid Science, 34, pp.798-811, (2010).
[7] P. Singh and F. Nestmann, ‘An optimization routine on a prediction and selection model for the turbine operation of centrifugal pumps’, J.Experimental Thermal & Fluid Science, 34, pp. 152-164, (2010).