高速水下航行器低比转速轴流推进泵设计方法

张子若; 罗凯; 秦侃

doi:10.11993/j.issn.2096-3920.2023-0036

高速水下航行器低比转速轴流推进泵设计方法

doi: 10.11993/j.issn.2096-3920.2023-0036

西北工业大学航海学院, 陕西西安, 710072

详细信息

作者简介:
张子若(1999-), 女, 在读硕士, 主要研究方向为流体机械

中图分类号: TJ630.33; U664.34
计量
- 文章访问数: 40
- HTML全文浏览量: 13
- PDF下载量: 13
- 被引次数: 0
出版历程
- 收稿日期: 2023-04-11
- 修回日期: 2023-05-22
- 录用日期: 2023-05-30
- 网络出版日期: 2024-01-29

Design Method for Low Specific Speed Axial Flow Pump for High-Speed Undersea Vehicles

Marine Science and Technology, Northwestern Polytechnical University, Xi’an 710072, China

摘要

摘要: 对于水下航行器轴流泵喷水推进系统, 现有升力法设计的高比转速轴流泵无法满足在浅水高速工况下正常工作的需求, 为解决这一问题, 提出一种针对低比转速轴流泵的设计方法。考虑所选NACA66_a_=0.8翼型的叶栅特性, 通过改变攻角和升力系数等参数的设计关系，建立适用于高航速工况的轴流泵模型, 并运用SST k-ω 湍流模型和多重参考系模型对设计泵的流场运动情况进行仿真。结果表明: 设计工况下, 设计泵的扬程和水力效率与设计值误差均控制在8%以内, 同时测试了设计泵在不同水深下的抗空化性能, 进一步探索设计泵工作的最小航深。
- 高速水下航行器 /
- 轴流泵 /
- 浅水 /
- 喷水推进
Abstract: For the axial flow pumps water-jet propulsion system of undersea vehicles, the high specific speed axial flow pump designed by the lift method fails to work under shallow water and high-speed conditions at present. Therefore, this study put forward a method to design a low specific speed axial flow pump. By considering the blade grid characteristics of the NACA66_a=0.8 airfoil, the design relationship among the angle of attack, lift coefficient, and other parameters was changed to establish an axial flow pump model suitable for high-speed conditions, and SST k-ω turbulence model and multi-reference frame model were used to simulate the flow field motion of the designed pump. The results show that under the design conditions, for the head and hydraulic efficiency of the designed pump, the error between the design value and the emulation value is controlled within 8%. At the same time, the cavitation resistance of the designed pump at different depths is tested to explore the minimum depth where the designed pump can work.
- highspeed undersea vehicle /
- axial flow pump /
- shallow water /
- water-jet propulsion

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图 1 实验泵模型

Figure 1. Model of experimental pump

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图 2 实验泵网格划分

Figure 2. Mesh of experimental pump

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图 3 实验泵数值仿真计算域边界条件设置

Figure 3. Simulation of experimental pump calculation of domain boundary condition settings

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图 4 验证泵实验数据与仿真数据对比

Figure 4. Comparison of experimental data and simulation data of the verification pump

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图 5 内流道结构示意图

Figure 5. Schematic diagram of internal flow channel structure

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图 6 设计泵进出口速度三角形

Figure 6. Design pump inlet and outlet velocity triangle

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图 7 泵叶轮设计流程图

Figure 7. Flow chart of pump impeller design

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图 8 泵叶轮叶片表面空化面积图

Figure 8. Diagram of pump impeller blade surface cavitation area

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图 9 泵导叶设计流程

Figure 9. Flow chart of pump guide vane design

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图 10 设计泵模型及网格划分示意图

Figure 10. Model and mesh of designed pump

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图 11 叶轮在30 m、40 m、50 m水深下汽相体积分数及静压分布图

Figure 11. Vapor phase volume fraction and static pressure distribution of impeller at water depths of 30 m, 40 m, 50 m

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表 1 实验泵在标况下的网格无关性验证

Table 1. Verification of grid independence of experimental pumps under standard conditions

工况类型	网格数目	仿真扬程/m
Q/Q_d=1	$1.0\times {10}^{6}$	2.96
	$ 2.7\times {10}^{6} $	2.91
	$ 4.5\times {10}^{6} $	3.06

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表 2 常规升力法叶轮各截面部分设计参数

Table 2. Design parameters of each section of impeller by the conventional lift method

参数	r₁	r₂	r₃	r₄	r₅	r₆	r₇	r₈	r₉	r₁₀
截面半径/m	0.04	0.04	0.05	0.05	0.06	0.06	0.06	0.07	0.07	0.08
几何平均速度/(m/s)	37.50	42.70	47.90	53.00	58.00	63.00	68.00	72.90	77.80	82.60
翼型安放角/(°)	0.61	0.53	0.47	0.42	0.38	0.34	0.31	0.29	0.27	0.25
叶栅稠密度	1.22	1.16	1.12	1.09	1.08	1.06	1.05	1.04	1.04	1.03
升阻比	0.00	0.00	0.00	0.00	0.00	0.00	0.00	0.00	0.00	0.00
升力系数	1.17	0.99	0.84	0.72	0.62	0.54	0.47	0.42	0.37	0.33
攻角/(°)	15.90	13.50	11.50	10.00	8.70	7.60	6.80	6.00	5.40	4.90
翼型相对拱度	0.03	0.03	0.02	0.02	0.02	0.01	0.01	0.01	0.01	0.01
水力效率	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00

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表 3 改进升力法叶轮各截面部分设计参数

Table 3. Design parameters of each section of impeller by the improved conventional lift method

参数	r₁	r₂	r₃	r₄	r₅	r₆	r₇	r₈	r₉	r₁₀
截面半径/m	0.04	0.04	0.05	0.05	0.06	0.06	0.06	0.07	0.07	0.08
几何平均速度/(m/s)	37.50	42.70	47.90	53.00	58.00	63.00	68.00	72.90	77.80	82.60
翼型安放角/(°)	27.10	23.60	20.90	18.80	17.10	15.80	14.60	13.60	12.70	12.00
叶栅稠密度	1.24	1.17	1.13	1.10	1.08	1.06	1.05	1.05	1.04	1.03
升阻比	0.04	0.04	0.04	0.04	0.04	0.04	0.04	0.04	0.04	0.04
升力系数	1.15	0.98	0.83	0.71	0.62	0.54	0.47	0.42	0.37	0.33
攻角/(°)	9.32	7.79	6.55	5.56	4.78	4.16	3.67	3.28	2.96	2.71
翼型相对拱度	0.02	0.02	0.02	0.01	0.01	0.01	0.01	0.01	0.01	0.01
水力效率	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00	1.00

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表 4 导叶各截面部分设计参数

Table 4. Design parameters of each section of the guide vane

参数	r₁	r₂	r₃	r₄	r₅	r₆	r₇	r₈	r₉	r₁₀
截面半径/m	0.04	0.04	0.05	0.05	0.06	0.06	0.06	0.07	0.07	0.08
导叶弦长/m	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02
进口液流角/(°)	32.8	35.20	37.50	39.70	41.70	43.60	45.40	47.10	48.70	50.20
骨线圆弧半径/m	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02	0.02
流道扩散角/(°)	29.00	29.40	29.60	29.50	29.30	29.00	28.60	28.10	27.50	26.90

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表 5 低比转速设计泵设计值和仿真值对比表

Table 5. Comparison of low specific speed designed pump design value and simulation value

	设计值	仿真值	相对误差
扬程	128 m	125 m	2.34%
效率	88.3%	81.53%	7.66%

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表 6 轴流泵空化面积量化表

Table 6. Cavitation area quantification table of axial flow pump

水深/m	叶轮面积/m²	叶轮空化面积/m²	面积占比
30	0.028	0.005	0.193
40	0.028	0.005	0.183
50	0.028	0.004	0.148

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