叶片安放角对轴流泵马鞍区运行特性的影响
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摘要
为分析叶片安放角对轴流泵马鞍区工况运行特性的影响,以比转速822的轴流泵为研究模型,试验测试了不同叶片安放角下的运行特性。研究表明:随着叶片安放角的增大,模型泵最优工况处的扬程、流量和效率均逐渐增大,-4°到+4°的增幅分别为10.4%,26.7%和0.87%;不同安放角下,泵扬程曲线均存在明显的马鞍区;随着叶片安放角的增大,试验泵马鞍区的绝对位置向右上方偏移,但相对位置仍主要位于0.5QBEP~0.6QBEP(QBEP为最高效率点对应的额定流量),且均在0.55QBEP时扬程达到最小值;随着叶片安放角的减小,马鞍区内相对扬程在逐渐增大,马鞍区驼峰特性有所改善;随着叶片安放角的增大,各个安放角下马鞍区范围内的压力脉动较最优工况下更剧烈;叶轮进口压力脉动主频为叶片通过频率,泵出口处压力脉动主要受导叶影响,随流量减小逐渐向高频移动;随着叶片安放角的增大,叶轮进口和泵出口处主频处的压力脉动幅值均逐渐增大,在叶轮进口处,0.6QBEP和0.55QBEP时压力脉动幅值最大增幅分别达1.78和1.65倍,在泵出口处,正安放角下压力脉动幅值相对负角度有所增大;内流分析表明小流量工况下叶轮进口存在回流现象,叶轮出口靠近轮毂处有明显旋涡,导致小流量下压力脉动幅值增大。
In order to analyze the influence of the vane angle on the performance in saddle zone of the axial flow pump, the operation characteristics with different vane angles were tested by the axial flow pump with specific speed of 822 RPM. The research shows that with the increase of vane angle, the head, flow and efficiency of the test pump increase at the optimal working conditions at the same time, and the increase ranges are 10.4%, 26.7% and 0.87% respectively when vane angle changes from-4° to +4°. Under different vane angles, the head curves all present obvious saddle area. With the increase of the vane angle, the coefficient of relative head decreases gradually. It shows that the performance of saddle area is improved with the decrease of the vane angle. The absolute position in the saddle zone of the test pump deviates to the upper right, but the relative position is still mainly located in the range of 0.5 QBEP-0.6 QBEP(QBEP is the flow when efficiency reaches the maximum), and the head reaches a minimum at 0.55 QBEP. The pressure pulsation at monitoring point of impeller inlet under different vane angels is obvious with the feature of 4 peaks and 4 troughs in a single cycle. Under the optimal operating conditions, the pressure fluctuation curve at monitoring point of pump outlet is a regular sine wave, and there are also 4 wave peaks and 4 wave valleys in each cycle, and the peak value of pressure fluctuating peak at monitoring point of pump outlet increase with the decrease of flow rate. With the change of vane angles, the peak value of the pressure fluctuating peak in the saddle area is obviously larger than the optimal operating condition at the monitoring points of impeller inlet and pump outlet. With the increase of the vane angle, the pressure fluctuation in the 0.6 QBEP becomes intense, and the pressure fluctuation in the 0.55 QBEP increases first and then decreases. When the vane angle increases, the flow rate at monitoring point of impeller inlet decreases and when the flow changes from 1.0 QBEP to 0.6 QBEP, the peak value of the pressure fluctuating peak changes gradually, and the pressure fluctuating peak value of each angle changes violently as the flow changes from 0.6 QBEP to 0.55 QBEP. With the decrease of the relative flow, the pressure pulsation under different vane angles increases gradually. When the relative flow reached the range of saddle area, the amplitude of low frequency pulsation increases gradually, and when the flow rate continues to decrease, the broadband frequency distribution moves to the low frequency band, and the amplitude of low frequency increases. The main frequency of pressure pulsation at the pump outlet in the saddle area is basically stable at 6 APF(axial passing frequency) and the secondary frequency is stable at 4 APF. It shows that the pressure pulsation of the pump outlet is mainly influenced by the guide vane, and is also influenced by the blade passing frequency. The main frequency of the pressure pulsation at impeller inlet is the blade passing frequency, as the main frequency at the pump outlet is the guide vane passing frequency, and it moves to high frequency with the decrease of flow gradually. With the increase of the vane angle, the amplitudes of main frequency of pressure fluctuation at the impeller inlet, guide vane and pump outlet all gradually increase. At the impeller inlet, the maximum amplitudes of pressure fluctuation at 0.6 QBEP and 0.55 QBEP were 1.78 and 1.65 times respectively, and at the outlet of the pump, the amplitude of pressure pulsation at the positive angles is increased relative to the negative angles. Finally, the results of numerical simulation show that there is a backflow phenomenon at the impeller inlet under the small flow condition, and the vortex near the hub leads to the increase of the pressure fluctuation amplitude in the small flow condition.
In order to analyze the influence of the vane angle on the performance in saddle zone of the axial flow pump, the operation characteristics with different vane angles were tested by the axial flow pump with specific speed of 822 RPM. The research shows that with the increase of vane angle, the head, flow and efficiency of the test pump increase at the optimal working conditions at the same time, and the increase ranges are 10.4%, 26.7% and 0.87% respectively when vane angle changes from-4° to +4°. Under different vane angles, the head curves all present obvious saddle area. With the increase of the vane angle, the coefficient of relative head decreases gradually. It shows that the performance of saddle area is improved with the decrease of the vane angle. The absolute position in the saddle zone of the test pump deviates to the upper right, but the relative position is still mainly located in the range of 0.5 QBEP-0.6 QBEP(QBEP is the flow when efficiency reaches the maximum), and the head reaches a minimum at 0.55 QBEP. The pressure pulsation at monitoring point of impeller inlet under different vane angels is obvious with the feature of 4 peaks and 4 troughs in a single cycle. Under the optimal operating conditions, the pressure fluctuation curve at monitoring point of pump outlet is a regular sine wave, and there are also 4 wave peaks and 4 wave valleys in each cycle, and the peak value of pressure fluctuating peak at monitoring point of pump outlet increase with the decrease of flow rate. With the change of vane angles, the peak value of the pressure fluctuating peak in the saddle area is obviously larger than the optimal operating condition at the monitoring points of impeller inlet and pump outlet. With the increase of the vane angle, the pressure fluctuation in the 0.6 QBEP becomes intense, and the pressure fluctuation in the 0.55 QBEP increases first and then decreases. When the vane angle increases, the flow rate at monitoring point of impeller inlet decreases and when the flow changes from 1.0 QBEP to 0.6 QBEP, the peak value of the pressure fluctuating peak changes gradually, and the pressure fluctuating peak value of each angle changes violently as the flow changes from 0.6 QBEP to 0.55 QBEP. With the decrease of the relative flow, the pressure pulsation under different vane angles increases gradually. When the relative flow reached the range of saddle area, the amplitude of low frequency pulsation increases gradually, and when the flow rate continues to decrease, the broadband frequency distribution moves to the low frequency band, and the amplitude of low frequency increases. The main frequency of pressure pulsation at the pump outlet in the saddle area is basically stable at 6 APF(axial passing frequency) and the secondary frequency is stable at 4 APF. It shows that the pressure pulsation of the pump outlet is mainly influenced by the guide vane, and is also influenced by the blade passing frequency. The main frequency of the pressure pulsation at impeller inlet is the blade passing frequency, as the main frequency at the pump outlet is the guide vane passing frequency, and it moves to high frequency with the decrease of flow gradually. With the increase of the vane angle, the amplitudes of main frequency of pressure fluctuation at the impeller inlet, guide vane and pump outlet all gradually increase. At the impeller inlet, the maximum amplitudes of pressure fluctuation at 0.6 QBEP and 0.55 QBEP were 1.78 and 1.65 times respectively, and at the outlet of the pump, the amplitude of pressure pulsation at the positive angles is increased relative to the negative angles. Finally, the results of numerical simulation show that there is a backflow phenomenon at the impeller inlet under the small flow condition, and the vortex near the hub leads to the increase of the pressure fluctuation amplitude in the small flow condition.
引文
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[2]张德胜,施卫东,张华,等.轴流泵叶轮端壁区流动特性数值模拟[J].农业机械学报,2012,43(3):73-77.Zhang Desheng,Shi Weidong,Zhang Hua,et al.Nurnerical simulation of flow field characteristics in tip clearance region of axial-flow impeller[J].Transactions of the Chinese Society for Agricultural Machinery,2012,43(3):73-77.(in Chinese with English abstract)
[3]陆林广,伍杰,陈阿萍,等.立式轴流泵装置的三维湍流流动数值模拟[J].排灌机械工程学报,2007,25(1):29-32.Lu Linguang,Wu Jie,Chen Aping,et al.Numerical simulation of 3D turbulent flow in a vertical axial-flow pump system[J].Journal of Drainage&Irrigation Machinery Engineering,2007,25(1):29-32.(in Chinese with English abstract)
[4]关醒凡.轴流泵与斜流泵[M].北京:中国宇航出版社,2009.
[5]Badr H M,Ahmed W H.Axial Flow Pumps[M].United States:John Wiley&Sons Ltd,2014:205-220.
[6]Stepanoff A J.Centrifugal and Axial Flow Pumps[J].Van Chong Book Company,1950,15(11):678-683.
[7]Spencer E A.The performance of an axial-flow pump[J].Proceedings of the Institution of Mechanical Engineers,1956,170(1):874-908.
[8]刘君,华学坤,郑源,等.低扬程立式轴流泵装置模型马鞍形区研究[J].南水北调与水利科技,2011,9(4):34-38.Liu Jun,Hua Xuekun,Zheng Yuan,et al.Study on performance of saddle zone in low lift vertical axial-flow pump system model[J].South-to-North Water Transfer and Water Science&Technology,2011,9(4):34-38.(in Chinese with English abstract)
[9]王福军,张玲,张志民,等.轴流泵不稳定流场的压力脉动特性研究[J].水利学报,2007,38(8):1003-1009.Wang Fujun,Zhang Ling,Zhang Zhimin,et al.Analysis on pressure flucuation of unsteady flow in axial flow pump[J].Journal of Hydraulic Engineering,2007,38(8):1003-1009.(in Chinese with English abstract)
[10]钱忠东,王凡,王志远,等.可调导叶式轴流泵马鞍区水力特性试验研究[J].排灌机械工程学报,2013,31(6):461-465.Qian Zhongdong,Wang Fan,Wang Zhiyuan,et al.Experimental study on hydraulic performance of saddle zone in axial flow pump with adjustable guide vane[J].Journal of Drainage&Irrigation Machinery Engineering,2013,31(6):461-465.(in Chinese with English abstract)
[11]Li S C.Cavitation of Hydraulic Machinery[M].London:Imperial College Press,2000:492.
[12]Pettigrew M J,Taylor C E.Two-phase flow-induced vibration:An overview[J].Transactions-American Society of Mechanical Engineering Journal of Pressure Vessel Technology,1994,116(3):233-253.
[13]Yoshida Y,Murakami Y,Tsurusaki H,et al.Rotating stalls in centrifugal impeller/vaned diffuser system:1st report,experiment[J].Transactions of the Japan Society of Mechanical Engineers Part B,1990,56(530):2991-2998.
[14]耿卫明,刘超,汤方平.轴流泵叶轮出口流场的3D-PIV测量[J].河海大学学报:自然科学版,2010,38(5):516-521.Geng Weiming,Liu Chao,Tang Fangping.3D-PIVmeasurements of flow fields at exit to impeller of an axial flow pump[J].Journal of Hohai University:Natural Sciences,2010,38(5):516-521.(in Chinese with English abstract)
[15]周佩剑,王福军,姚志峰.旋转失速条件下离心泵隔舌区动静干涉效应[J].农业工程学报,2015,31(7):85-90.Zhou Peijian,Wang Fujun,Yao Zhifeng.Impeller-volute interaction around tongue region in centrifugal pump under rotating stall condition[J].Transactions of the Chinese Society of Agricultural Engineering(Transactions of the CASE),2015,31(7):85-90.(in Chinese with English abstract)
[16]Arndt R E A.Cavitation in fluid machinery and hydraulic structures[J].Annual Review of Fluid Mechanics,1981,13(1):273-326.
[17]Laborde R,Chantrel P,Mory M.Tip clearance and tip vortex cavitation in an axial flow pump[J].Journal of Fluids Engineering,1997,119(3):680-685.
[18]Wu C H.A general theory of three-dimensional flow in subsonic and supersonic turbomachines of axial,radial,and mixed-flow types[C].ASME Paper Number 50-A-79,or NACA TN 2604,1952:1-90.
[19]成立,吴璐璐,刘超,等.大型轴流泵水力不稳定区研究[J].灌溉排水学报,2010,29(2):102-104.Cheng Li,Wu Lulu,Liu Chao,et al.Hydraulic unstable operating region of large scale axial flow pump[J].Journal of Irrigation and Drainage,2010,29(2):102-104.(in Chinese with English abstract)
[20]刘竹青,肖若富,吕腾飞,等.弯掠叶片对轴流泵驼峰及空化性能的影响[J].排灌机械工程学报,2012,30(3):270-275.Liu Zhuqing,Xiao Ruofu,LüTengfei,et al.Effect pf swept blade on hump and cavitation characteristics of axial flow pump[J].Journal of Drainage&Irrigation Machinery Engineering,2012,30(3):270-275.(in Chinese with Engish abstract)
[21]刘君,华学坤,郑源,等.低扬程立式轴流泵装置模型马鞍形区研究[J].南水北调与水利科技,2011,9(4):34-38.Liu Jun,Hua Xuekun,Zheng Yuan,et al.Study on performance of saddle zone in low lift vertical axial-flow pump system model[J].South to North Water Transfer and water conservancy technology,2011,9(4):34-38.(in Chinese with English abstract)
[22]茅媛婷,周大庆,郑源,等.轴流泵马鞍区流动特性数值模拟及模型试验[J].工程热物理学报,2010,31(6):25-28.Mao Yuanting,Zhou Daqing,Zheng Yuan,et al.Numerical simulation and model test of flow characteristics in saddle area of axial flow pump[J].Journal of Engineering Thermophysics,2010,31(6):25-28.(in Chinese with English abstract)
[23]程千,冯卫民,周龙才,等.前置导叶对轴流泵马鞍区工况回流涡特性的影响[J].农业机械学报,2016,47(4):8-14.Cheng Qian,Feng Weimin,Zhou Longcai,et al.The influence of the front guide vane on the return vortex characteristics of the axial flow pump saddle area[J].Transactions of the Chinese Society of Agricultural Machinery,2016,47(4):8-14.(in Chinese with English abstract)
[24]郑源,茅媛婷,周大庆,等.低扬程大流量泵装置马鞍区的流动特性[J].排灌机械工程学报,2011,29(5):369-373.Zheng Yuan,Mao Yuanting,Zhou Daqing,et al.Flow characteristics of low lift and large flow pump unit saddle area[J].Journal of Drainage&Irrigation Machinery Engineering,2011,29(5):369-373.(in Chinese with English abstract)
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