Effect of the blade loading distribution on hydrodynamic performance of a centrifugal pump with cylindrical blades

Li, Xiaojun; Gao, Panlong; Zhu, Zuchao; Li, Yi

doi:10.1007/s12206-018-0219-4

Cited by 59 publications

(22 citation statements)

References 15 publications

Supporting

Mentioning

Contrasting

Order By: Relevance

“…Pumps are a type of general machine with many varieties and extensive applications, and they are used in all places with liquid flow in all national economic sectors. [1][2][3][4][5] Statistics indicate that pumps' power consumption accounts for nearly 22% of the world's energy used by electric motors. [6][7][8][9][10] Self-priming centrifugal pumps, or self-priming pumps, have no bottom valve in the inlet pipe.…”

Section: Introductionmentioning

confidence: 99%

Numerical and experimental study of the self‐priming process of a multistage self‐priming centrifugal pump

Wang

Zhang

et al. 2019

Int J Energy Res

View full text Add to dashboard Cite

Summary Pumps are a type of general machine with many varieties and extensive application. To simulate really the self‐priming process of multistage self‐priming centrifugal pump, the numerical calculation of gas‐water two‐phase flow on a four‐stage self‐priming pump was performed based on ANSYS CFX software. Moreover, a transparent plastic tube was installed at the pump outlet, and the photographic technology was used to observe the appearance of gas‐water escape during the self‐priming process of multistage self‐priming centrifugal pump. The experimental results were compared with the numerical results. It is found that the whole self‐priming process of self‐priming pump can be divided into three stages: the initial self‐priming stage, the middle self‐priming stage, and the final self‐priming stage. Moreover, the self‐priming time of the initial and final self‐priming stages accounts for a small percentage of the whole self‐priming process, while the middle self‐priming stage is the main stage in the self‐priming process, which determines the length of self‐priming time. The experimental results are very close to the numerical results in the initial and middle self‐priming stages.

show abstract

Section: Introductionmentioning

confidence: 99%

Numerical and experimental study of the self‐priming process of a multistage self‐priming centrifugal pump

Wang

Zhang

et al. 2019

Int J Energy Res

View full text Add to dashboard Cite

show abstract

“…Complicated flow instabilities can be easy to discover through visualization experiments and numerical simulations under part load conditions in pumps, which include the rotating stall, the backflow, and the viscous wake [10,11]. The unsteady flow in the pump not only results in the unsteady dynamic characteristics, which include the pressure pulsations and the hydraulic excitation force [12], but also causes the vibration of the structures and the noise [13]. It is presented that the rotating stall in the pump turbines can be detected by the nonintrusive method in Botero's research [14].…”

Section: Introductionmentioning

confidence: 99%

Detection of the Flow State for a Centrifugal Pump Based on Vibration

Liu

Zeng

et al. 2019

Energies

View full text Add to dashboard Cite

A combined numerical and experimental method study was performed to detect the inner flow state for a type of centrifugal pump. It was found that the inlet attack angles of blades in an impeller have a great influence on the flow instabilities in a centrifugal pump. The mechanism of the rotating stall in the impeller channel was explained. Meanwhile, flow state identification with vibration (FSIV) was proposed to detect the flow instabilities in a centrifugal pump. The relationship between the external vibration and the inner flow state has been established by FSIV. The characteristics and mechanism of the vibration produced by the flow instabilities in a centrifugal pump were investigated. It was found that the hump, the rotating stall, the backflow, the occurrence of unstable flow, and the cavitation in the centrifugal pump can be effectively detected by applying the vibration signals, which helps to obtain safe and steady operating conditions for the system.

show abstract

“…The Curle noise source model is adopted to compute the dipole noise of the turbulent boundary layer flow on the solid surface. The surface acoustic power (SAP) can be written as: (2) where c0 is the sound speed in the far field, and Ac(y) denotes the correlation area. The steady-state RANS turbulence models can be employed to obtain the turbulence length scale, turbulence time scale and wall shear stress, and further calculate Figure 10 shows the vorticity and pressure curve along the PTLV trajectory.…”

Section: Curle Surface Acoustic Power Characteristicmentioning

confidence: 99%

“…Hydraulic machineries are widely used in modern submarines and warships, such as pumps, duct propulsors and waterjet propulsors, which have attracted the attention of researchers on a worldwide scale [1][2][3][4][5]. However, due to the limitation of the impeller structure, there is inevitably a gap between the rotating blades and the fixed impeller chamber [6,7].…”

Section: Introductionmentioning

confidence: 99%

Influence of T-Shape Tip Clearance on Energy Performance and Broadband Noise for a NACA0009 Hydrofoil

et al. 2019

View full text Add to dashboard Cite

In the present paper, the effect of the proposed T-shape tip on the energy performance, flow patterns and broadband noise sources of a NACA0009 hydrofoil with tip clearance is investigated. The vortex induced by the gap is simulated by means of the SST k-ω turbulence model, and then, the noise generated by dipoles and quadrupoles are analyzed by using the Curle acoustic analogy and Proudman acoustic analogy, respectively. The numerical simulation results agree well with the experimental measurements. Results indicate that three tip shapes, including the half pressure side T-shape model (MPT), the half suction side T-shape model (MST) and the T-shape model (MT), have complex influence on energy performance of the foil. Only the MST model can promote the energy performance of the hydrofoil at all inlet velocities, with the maximum ratio of lift coefficient to drag coefficient increasing by 4.26%. In addition, the ratio of lift coefficient to drag coefficient for MT obviously increases when the inlet velocity is 7.5 m/s, 10 m/s, 12.5 m/s and 15 m/s, and the maximum promotion is 15.21% at 7.5 m/s. The T-shape tip can effectively suppress the tip clearance leakage vortex, which makes the vortex area decrease with a maximum drop of 5.02%. Furthermore, the MPT and MT have good suppression effect on the hydrofoil dipole noise, and reduce the maximum Curle Acoustic Power (AP) of the foil with 2.64% and 3.03%, respectively. The MST model obviously reduces the isosurface area of the Proudman AP by 6.55% for 55 dB.

show abstract

Effect of the blade loading distribution on hydrodynamic performance of a centrifugal pump with cylindrical blades

Cited by 59 publications

References 15 publications

Numerical and experimental study of the self‐priming process of a multistage self‐priming centrifugal pump

Numerical and experimental study of the self‐priming process of a multistage self‐priming centrifugal pump

Detection of the Flow State for a Centrifugal Pump Based on Vibration

Influence of T-Shape Tip Clearance on Energy Performance and Broadband Noise for a NACA0009 Hydrofoil

Contact Info

Product

Resources

About