Research Papers: Multiphase Flows

Influence of Guide Ring on Energy Loss in a Multistage Centrifugal Pump

[+] Author and Article Information
Ren Yun

Zhijiang College,
Zhejiang University of Technology,
Shaoxing 312030, China;
Faculty of Mechanical Engineering and
Zhejiang Sci-Tech University,
Hangzhou 310018, China
e-mail: renyun_ry@hotmail.com

Zhu Zuchao

Faculty of Mechanical Engineering
and Automation,
Zhejiang Sci-Tech University,
Hangzhou 310018, China
e-mail: zhuzuchao@zstu.edu.cn

Wu Denghao

College of Mechanical Engineering,
Zhejiang University of Technology,
Hangzhou 310014, China
e-mail: wudenghao@aliyun.com

Li Xiaojun

Faculty of Mechanical Engineering
and Automation,
Zhejiang Sci-Tech University,
Hangzhou 310018, China
e-mail: lixj@zstu.edu.cn

Contributed by the Fluids Engineering Division of ASME for publication in the JOURNAL OF FLUIDS ENGINEERING. Manuscript received May 12, 2018; final manuscript received October 10, 2018; published online December 24, 2018. Assoc. Editor: Philipp Epple.

J. Fluids Eng 141(6), 061302 (Dec 24, 2018) (13 pages) Paper No: FE-18-1336; doi: 10.1115/1.4041876 History: Received May 12, 2018; Revised October 10, 2018

Multistage centrifugal pumps are highly efficient and compact in structure. Pump efficiency can be improved by an effective understanding of hydraulic behavior and energy loss, however, the traditional hydraulic loss evaluation method does not readily reveal the specific locations of energy loss in the pump. In this study, a guide ring was imposed in multistage pumps, and an entropy production theory was applied to investigate irreversible energy loss of a multistage pump with and without guide ring. Detailed distributions of energy losses in the pumps were calculated to determine the respective entropy production rates (EPRs). The EPR values as calculated are in close accordance with actual hydraulic loss values in the pumps. EPR values were higher in the multistage pump with the guide ring than the pump without a guide ring under part-load flow conditions (0.2Qd). However, the vortex flow in the pump was weakened (or eliminated) by the guide ring as flow rate increased; this reduced energy loss in the chambers. Flow passing the chamber was stabilized by the guide ring, which decreased shock and vortex loss in the chamber and guide vane. Under both designed flow condition and overload conditions, the EPR values of the guide ring-equipped multistage pump were lower than those without the guide ring. Furthermore, minimum efficiency index (MEI) values were also calculated for the two chamber structures; it was found that overall efficiency of pump with guide ring is better than that without.

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Fig. 1

Cross section of the investigated pump

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Fig. 2

Geometric model of the impeller and guide vane: (a) geometric model of the impeller blade and (b) geometric model of the guide vane

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Fig. 3

Schematic of different chambers: (a) chamber without guide ring and (b) chamber with guide ring

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Fig. 4

Geometric model of the guide ring

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Fig. 5

Calculation domains and boundary conditions

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Fig. 6

Computational grids used for the guide vane and impeller

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Fig. 7

Comparisons of hydraulic performance under different chamber schemes: (a) ψ–Φ curve and (b) η–Φ curve

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Fig. 8

Comparisons of individual hydraulic loss and total hydraulic loss under different chamber schemes

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Fig. 9

Total entropy production value of hydraulic components under different chamber schemes

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Fig. 10

Entropy production value of individual hydraulic components under different chamber schemes

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Fig. 11

Proportion for EPR of each component under different chamber schemes: (a) chamber without guide ring and (b) chamber with guide ring

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Fig. 12

EPR distribution in the whole stages of different chamber schemes under different flow conditions: (a) 0.2Qd, (b) 0.6Qd, (c) 1.0Qd, and (d) 1.4Qd

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Fig. 13

EPR distribution and sectional streamlines in different spans of impeller at 0.2Qd (3 m3/h)

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Fig. 14

EPR distribution and sectional streamlines in different spans of impeller at 0.6Qd (9 m3/h)

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Fig. 15

EPR distribution and sectional streamlines in different spans of impeller at 1.0Qd (15 m3/h)

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Fig. 16

EPR distribution and sectional streamlines in different spans of impeller at 1.4Qd (21 m3/h)



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