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浙江大学学报(工学版)
Journal of ZheJiang University (Engineering Science)  2024, Vol. 58 Issue (8): 1577-1584    DOI: 10.3785/j.issn.1008-973X.2024.08.005
    
Axial force balance method for floating impeller of shielded centrifugal pump
Xin WANG1(),Yifan WU2,Chengshuo WU1,Peng WU1,*(),Shuai YANG1,Dazhuan WU1
1. College of Energy Engineering, Zhejiang University, Hangzhou 310027, China
2. Kunming Branch of the 705th Research Institute of China State Shipbuilding Corporation Limited Company, Kunming 650118, China
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Abstract  

A floating impeller design with axial force self-balancing capability was proposed to balance the axial force of the centrifugal impeller of the shielded pump. The mechanism and influencing factors of the axial force balance were analyzed through three-dimensional numerical simulation of the full flow path. Numerical calculations were conducted under various operating conditions and impeller positions after validating the simulation method. Results show that leakage decreases, head and efficiency increase when moving towards the inlet within the impeller’s floating range. The closer towards the inlet, the more significant impact on the pump performance is. The axial force initially decreases but then increases. The direction points to the pump inlet when it is far from the inlet. The impeller axial force increases rapidly to realize the reverse when it is close to the pump inlet, pointing to the pump outlet and helping the impeller stop moving to the inlet. This trend of axial force change can make the impeller always be in a floating state when working and realize the axial force self-balancing.

Key words： centrifugal pump      floating impeller      axial position      axial force     
Received: 07 July 2023      Published: 23 July 2024
CLC:  TH 311  
Fund:  国家自然科学基金资助项目（51839010）.
Corresponding Authors: Peng WU     E-mail: 22127040@zju.edu.cn;roc@zju.edu.cn
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Xin WANG
Yifan WU
Chengshuo WU
Peng WU
Shuai YANG
Dazhuan WU
Cite this article:

Xin WANG,Yifan WU,Chengshuo WU,Peng WU,Shuai YANG,Dazhuan WU. Axial force balance method for floating impeller of shielded centrifugal pump. Journal of ZheJiang University (Engineering Science), 2024, 58(8): 1577-1584.

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https://www.zjujournals.com/eng/10.3785/j.issn.1008-973X.2024.08.005     OR     https://www.zjujournals.com/eng/Y2024/V58/I8/1577


屏蔽式离心泵浮动叶轮轴向力平衡方法

为了实现屏蔽泵离心叶轮轴向力平衡，设计浮动叶轮轴向力自平衡结构，借助全流道三维数值模拟手段，研究浮动叶轮的轴向力平衡作用机理和影响因素. 在对数值模拟方法进行试验验证的基础上，开展针对不同工况下叶轮不同轴向位置轴向力的数值计算. 数值模拟结果表明，在同一流量工况下，在叶轮浮动范围内，当叶轮向泵入口方向移动时，泵前腔泄漏量减小，扬程和效率增大，且越靠近入口，对泵的性能影响越显著. 轴向力呈现先减后增的趋势，在远离入口时方向指向泵入口，在靠近入口时，叶轮轴向力迅速增大，实现反向，指向泵出口，帮助叶轮停止向入口移动，这种轴向力变化趋势可以使叶轮在工作时始终处于浮动状态，实现轴向力自平衡.


关键词： 离心泵,  浮动叶轮,  轴向位置,  轴向力 
Fig.1 Schematic diagram of floating impeller structure
Fig.2 Schematic diagram of circulating circuit
Fig.3 Three-dimensional model of main structure of pump
参数数值
比转速${n_{\mathrm{s}}}$61
叶轮入口直径${D_1}/{{\mathrm{mm}}} $22
叶轮出口直径${D_2}/{{\mathrm{mm}}} $60
叶轮出口宽度${b_2}/{{\mathrm{mm}}} $2
叶片数${Z_1}$ (长+短)
叶片包角$\varphi /(^\circ) $
叶片厚度$t/{{\mathrm{mm}}} $		5+5
120
1
导叶数${Z_{\mathrm{g}}}$13
背叶片数${Z_2}$4
背叶片高度$H/{{\mathrm{mm}}} $13
背叶片宽度$W/{{\mathrm{mm}}} $3
背叶片厚度$T/{{\mathrm{mm}}} $1.65
叶轮轴向浮动范围$d/{{\mathrm{mm}}} $0.8
Tab.1 Main parameter of pump
Fig.4 Pump computational domain model
计算域N/${10^6}$网格类型
进口段0.33非结构化
前盖板间隙1.40结构化
叶轮1.10结构化
背叶片
导叶		1.74
1.91		非结构化
结构化
后盖板间隙1.37结构化
出口段0.96非结构化
Tab.2 Grid division situation
Fig.5 Main component grid of pump
Fig.6 Verification of grid independence
Fig.7 Model pump testing platform
项目精度量程
进口压力表$ \pm 0.01{\text{%}} $$ - 0.1 \sim 0{\text{ }}{{\mathrm{MPa}}} $
出口压力表$ \pm 0.01{\text{%}} $$0 \sim 0.25{\text{ }}{{\mathrm{MPa}}} $
流量计$ \pm 0.3{\text{%}} $$0 \sim 5{\text{ }}{{{\mathrm{m}}} ^3}/{\mathrm{h}}$
转速$ \pm 0.5{\text{%}} $$500 \sim 40{\text{ }}000{\text{ }}{{\mathrm{r}}} /{\mathrm{min}}$
电压$ \pm 1.5{\text{%}} $$10 \sim 300{\text{ }}{{\mathrm{V}}} $
电流$ \pm 1.5{\text{%}} $$0 \sim 5{\text{ }}{{\mathrm{A}}} $
Tab.3 Range and accuracy of measuring instrument
Fig.8 Hydraulic performance simulation and test comparison curve
Fig.9 Schematic diagram of axial relative position of impeller
Fig.10 Curve of relationship between leakage of front ring and axial position of impeller
Fig.11 Relationship curve of pump hydraulic performance parameter and impeller axial position
Fig.12 Curve of relationship between axial force and axial position of impeller
Fig.13 Axial force distribution surface of each part of impeller
Fig.14 Axial force component of impeller under different working condition
Fig.15 Position of monitoring line within gap
Fig.16 Static pressure distribution of gap between front and rear cover plate under different working condition
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