Dynamic Instability Analysis of a Double-Blade Centrifugal Pump
Abstract
:1. Introduction
2. Computational Modeling and Experimental Test
2.1. Pump Model
2.2. Simulation Setup
2.3. Experimental Setup
2.4. Layout of Monitoring Points
2.5. Simulation Validation
3. Results and Discussion
3.1. Pressure Pulsations of Volute at Different Flow Rates
3.2. Pressure Pulsations of Impeller at Different Flow Rates
3.3. Loads of Blade under Different Flow Rates
3.4. Vibration Characteristics of Pump
3.5. Relationship between the Unsteady Flow and the Structural Vibration
4. Conclusions
- (1)
- The region in the pump experiencing the largest pressure pulsation is located at the vicinity of tongue of volute. The amplitude of pressure pulsation decreases as the relative gap between the impeller outlet and the volute wall surface increases. The rotor-stator interference between the impeller and volute is the main source of pressure pulsation. Highly intensive pressure pulsation is found at part-load conditions due to serious flow instability.
- (2)
- A strong vorticity fields in the vicinities of volute tongue and suction side of impeller blade were observed. These vortices are unstable, and they influence the normal flow streamlines, and destabilize the radial forces on each blade. Additionally, the interaction between blade and tongue causes the dynamic fluctuation of blade loads.
- (3)
- The main excitation frequencies were identified by measuring the vibration data of the double-blade centrifugal pump. In general, vibration amplitude at blade passing frequency (St = 1) is higher than others. There is a direct link between pressure pulsation and pump vibration, and pressure pulsation is a major source of fluid-induced vibration.
- (4)
- Considering the difficulties in performing the dynamic pressure measurement on pump volute, due to the pump volute being located inside the chamber, CFD was used as a main tool to analyze the dynamic instability of pump model. In future, it will be more comprehensive to involve the measurement on rotor movement orbit to help observe the dynamic behaviors of double-blade centrifugal pump.
Author Contributions
Funding
Institutional Review Board Statement
Informed Consent Statement
Data Availability Statement
Conflicts of Interest
Nomenclature
Qd | Flow rate at design point |
nq | Specific speed (3.65nQd0.5/Hd0.75) |
cp | Unsteady pressure pulsation coefficient |
μp | Intensity of pressure pulsation |
u2 | Circumferential velocity at impeller outlet |
pi | Transient pressure |
Averaged pressure | |
N | Sample number per revolution |
ρ | Density |
f | Frequency |
fn | Rotational frequency of impeller |
Fx | Radial force along x axe |
Fy | Radial force along y axe |
A | Vibration amplitude |
BPF | Blade passing frequency |
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Parameter | Value |
---|---|
Design operation condition | |
Flow rate Qd/(m3·h−1) | 100 |
Total head Hd/(m) | 15 |
Rotation speed n/(r·min−1) | 2900 |
Rotation frequency fn/(Hz) | 48.33 |
Specific speed nq | 231.5 |
Reynolds number Re (u22D22/υ) | 3.06 × 106 |
Pump geometrical parameters | |
Impeller inlet diameter D1/(mm) | 100 |
Impeller outlet diameter D2/(mm) | 142 |
Blade outlet width b2/(mm) | 68 |
Blade outlet angle β2/(°) | 21 |
Number of blades z | 2 |
Basic circle diameter D3/(mm) | 150 |
Volute inlet width b3/(mm) | 80 |
Tongue placement angle φ0/(°) | 25 |
Tongue flow angle α0/(°) | 20 |
Throat area A8/(mm2) | 5000 |
Tongue radius Rt/(mm) | 6 |
Pump discharge diameter Do/(mm) | 80 |
Pump suction diameter Di/(mm) | 100 |
Turbulence Model | H (m) | ΔH = |HCFD−HEXP.|/HEXP. (%) |
---|---|---|
Standard k-ε | 16.21 | 1.64 |
RNG k-ε | 16.14 | 2.06 |
EARSM k-ε | 16.30 | 1.09 |
Standard k-ω | 16.95 | 2.85 |
BSL k-ω | 16.76 | 1.69 |
SST k-ω | 16.74 | 1.57 |
Exp. | 16.48 | - |
Sensor | Model | Sensitivity | Calibration Temperature | Position |
---|---|---|---|---|
Acceleration sensor 1# | 1A111E | 10.44 mV (m·s−2) | 25 °C | Top of pump housing (Z direction) |
Acceleration sensor 2# | 1A111E | 10.03 mV (m·s−2) | 25 °C | Side wall of pump housing (Y direction) |
Acceleration sensor 3# | 1A111E | 10.23 mV (m·s−2) | 25 °C | Foot of pump housing (Z direction) |
Acceleration sensor 4# | 1A111E | 10.01 mV (m·s−2) | 25 °C | Bearing housing (Z direction) |
Acceleration sensor 5# | 1A111E | 10.05 mV (m·s−2) | 25 °C | Bearing housing (Y direction) |
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Wu, D.; Yao, S.; Lin, R.; Ren, Y.; Zhou, P.; Gu, Y.; Mou, J. Dynamic Instability Analysis of a Double-Blade Centrifugal Pump. Appl. Sci. 2021, 11, 8180. https://doi.org/10.3390/app11178180
Wu D, Yao S, Lin R, Ren Y, Zhou P, Gu Y, Mou J. Dynamic Instability Analysis of a Double-Blade Centrifugal Pump. Applied Sciences. 2021; 11(17):8180. https://doi.org/10.3390/app11178180
Chicago/Turabian StyleWu, Denghao, Songbao Yao, Renyong Lin, Yun Ren, Peijian Zhou, Yunqing Gu, and Jiegang Mou. 2021. "Dynamic Instability Analysis of a Double-Blade Centrifugal Pump" Applied Sciences 11, no. 17: 8180. https://doi.org/10.3390/app11178180
APA StyleWu, D., Yao, S., Lin, R., Ren, Y., Zhou, P., Gu, Y., & Mou, J. (2021). Dynamic Instability Analysis of a Double-Blade Centrifugal Pump. Applied Sciences, 11(17), 8180. https://doi.org/10.3390/app11178180