高比转速轴流泵水力优化设计
发布时间：2018-12-13 12:38
【摘要】：作为轴流泵装置的核心部件,轴流泵的叶轮和导叶,是整个轴流泵过流装置中重要的组成部分。也是实现能量转换的重要组成,直接关系到水泵的性能。提高整个泵装置的性能,基本都是从叶轮和导叶两个方面入手。因此,研究叶轮的结构参数和导叶体的布置位置对水泵性能的影响具有现实的指导意义。 不同的参数设置方案对轴流泵的性能有着不同的影响。故有必要从轴流泵的内流场和外特性出发来分析和研究不同情况对泵的影响。本文采用了三维湍流数值模拟(CFD)作为研究手段,针对高速轴流泵在三种不同参数下的方案进行了数值模拟和分析,并总结了一些规律。对研究高比转速轴流泵的水力优化设计有一定的参考价值。 本文的主要工作有： 1、结合AutoCAD与Pro/ENGINEER软件对整个泵装置进行三维实体造型,采用ICEM对进水管,出水管,弯管进行网格剖分,对叶轮和导叶体使用Turbo-Grid进行网格剖分； 2、利用CFD软件(ANSYS CFX12.0),基于雷诺时均Navier-Stockes方程和标准κ-ε双方程湍流模型,对三种不同情况下(不同叶片厚度,不同叶片数,不同导叶进口与叶轮出口平行间距)进行全通道数值模拟,捕捉叶轮内速度分布、静压分布等重要流动参数,并进行对比分析； 3、通过CFX-Post后处理得到如下结论： (1)对不同叶片厚度的数值模拟计算分析之后可知,当流量较小时,叶片厚度的变换,不会引起较大的变化,其扬程,功率和效率基本都是重合的；而在设计流量左右,叶片厚度减小,相同流量下扬程趋势会有所改变,其趋势接近于在同一流量下,伴随厚度的增加,其扬程,功率都会下降,在效率方面,可以明显的看出,虽然有类似于上面的趋势,但是某些点还是发生了重叠的现象；大流量时,其扬程,功率和效率基本没有太大变化。 (2)对不同叶片数的数值模拟计算分析后可知,相对于三片叶片而言,四片在小流量情况下扬程和效率都相对较高；而在大流量情况下,两者基本重合。并且在马鞍区右侧部分有上移的现象。 (3)对不同的导叶进口与叶轮出口的平行间距S进行数值模拟分析后可知,当S的数值取值比较小时(在0.05D～0.1D之间),在设计流量下,出口速度环量分布及静压分布相对均匀,对整个泵装置的性能提高有一定的提升。超出0.1D之后,出口速度环量分布及静压分布都不十分理想,S的改变对于整个泵装置性能的改变没有太大的影响。可见S的改变,在一定的范围内对泵装置的性能还是有影响的。单纯的靠改变间距S来提高泵段的整体性能还是有一定局限的,要根据泵的实际工况水平,来选择相对应的距离S。
[Abstract]:As the core component of axial flow pump, the impeller and guide vane of axial flow pump is an important part in the whole axial flow pump overflowing device. Is also an important component of energy conversion, directly related to the performance of the pump. Improve the performance of the whole pump device, basically from the impeller and guide vane two aspects. Therefore, it is of practical significance to study the influence of impeller structure parameters and impeller position on pump performance. Different parameter setting schemes have different influence on the performance of axial flow pump. Therefore, it is necessary to analyze and study the influence of different conditions on the pump from the internal flow field and external characteristics of the axial flow pump. In this paper, three-dimensional turbulent numerical simulation (CFD) is used to simulate and analyze the scheme of high-speed axial flow pump under three different parameters, and some rules are summarized. It has certain reference value for studying the hydraulic optimization design of high specific speed axial flow pump. The main work of this paper is as follows: 1. Using AutoCAD and Pro/ENGINEER software to model the whole pump device, using ICEM to mesh the intake pipe, outlet pipe and elbow pipe, and using Turbo-Grid to mesh the impeller and guide blade body; 2. Using CFD software (ANSYS CFX12.0), based on Reynolds time average Navier-Stockes equation and standard 魏-蔚 two-equation turbulence model, three different conditions (different blade thickness, different blade number), The flow parameters such as velocity distribution and static pressure distribution in the impeller are captured and analyzed by numerical simulation of the parallel distance between the inlet of the guide vane and the outlet of the impeller. 3, through CFX-Post post-processing, the following conclusions are obtained: (1) after the numerical simulation and analysis of different blade thickness, it is known that when the flow rate is small, the change of blade thickness will not cause great change, and its head will not change. Power and efficiency are basically the same; But at the design flow rate, the blade thickness decreases, and the lift trend will change at the same flow rate. The trend is close to that under the same flow rate, and with the increase of the thickness, the head and power will decrease. In terms of efficiency, it can be seen clearly. Although there is a trend similar to the above, some points still overlap; When large flow rate, its lift, power and efficiency basically have not changed too much. (2) after numerical simulation and analysis of different blade numbers, it can be seen that compared with three blades, the lift and efficiency of the four blades are relatively high in the case of small flow rate, while in the case of large flow rate, the two basically coincide. And there is an upward movement in the right part of the saddle area. (3) the numerical simulation of the parallel distance S between the inlet of the guide vane and the outlet of the impeller shows that when the numerical value of S is small (between 0.05D~0.1D), under the design flow rate, The volume distribution and static pressure distribution of the outlet velocity ring are relatively uniform, which can improve the performance of the whole pump device to a certain extent. After 0.1 D, the distribution of the outlet velocity loop and the static pressure are not very ideal, and the change of S has no great effect on the performance of the whole pump device. Visible changes in S, in a certain range of pump device performance is still affected. Simply by changing the distance S to improve the overall performance of the pump is still limited, according to the actual operating level of the pump, to select the corresponding distance S.
【学位授予单位】：扬州大学
【学位级别】：硕士
【学位授予年份】：2012
【分类号】：TH312
本文编号：2376538
[Abstract]:As the core component of axial flow pump, the impeller and guide vane of axial flow pump is an important part in the whole axial flow pump overflowing device. Is also an important component of energy conversion, directly related to the performance of the pump. Improve the performance of the whole pump device, basically from the impeller and guide vane two aspects. Therefore, it is of practical significance to study the influence of impeller structure parameters and impeller position on pump performance. Different parameter setting schemes have different influence on the performance of axial flow pump. Therefore, it is necessary to analyze and study the influence of different conditions on the pump from the internal flow field and external characteristics of the axial flow pump. In this paper, three-dimensional turbulent numerical simulation (CFD) is used to simulate and analyze the scheme of high-speed axial flow pump under three different parameters, and some rules are summarized. It has certain reference value for studying the hydraulic optimization design of high specific speed axial flow pump. The main work of this paper is as follows: 1. Using AutoCAD and Pro/ENGINEER software to model the whole pump device, using ICEM to mesh the intake pipe, outlet pipe and elbow pipe, and using Turbo-Grid to mesh the impeller and guide blade body; 2. Using CFD software (ANSYS CFX12.0), based on Reynolds time average Navier-Stockes equation and standard 魏-蔚 two-equation turbulence model, three different conditions (different blade thickness, different blade number), The flow parameters such as velocity distribution and static pressure distribution in the impeller are captured and analyzed by numerical simulation of the parallel distance between the inlet of the guide vane and the outlet of the impeller. 3, through CFX-Post post-processing, the following conclusions are obtained: (1) after the numerical simulation and analysis of different blade thickness, it is known that when the flow rate is small, the change of blade thickness will not cause great change, and its head will not change. Power and efficiency are basically the same; But at the design flow rate, the blade thickness decreases, and the lift trend will change at the same flow rate. The trend is close to that under the same flow rate, and with the increase of the thickness, the head and power will decrease. In terms of efficiency, it can be seen clearly. Although there is a trend similar to the above, some points still overlap; When large flow rate, its lift, power and efficiency basically have not changed too much. (2) after numerical simulation and analysis of different blade numbers, it can be seen that compared with three blades, the lift and efficiency of the four blades are relatively high in the case of small flow rate, while in the case of large flow rate, the two basically coincide. And there is an upward movement in the right part of the saddle area. (3) the numerical simulation of the parallel distance S between the inlet of the guide vane and the outlet of the impeller shows that when the numerical value of S is small (between 0.05D~0.1D), under the design flow rate, The volume distribution and static pressure distribution of the outlet velocity ring are relatively uniform, which can improve the performance of the whole pump device to a certain extent. After 0.1 D, the distribution of the outlet velocity loop and the static pressure are not very ideal, and the change of S has no great effect on the performance of the whole pump device. Visible changes in S, in a certain range of pump device performance is still affected. Simply by changing the distance S to improve the overall performance of the pump is still limited, according to the actual operating level of the pump, to select the corresponding distance S.
【学位授予单位】：扬州大学
【学位级别】：硕士
【学位授予年份】：2012
【分类号】：TH312
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