# Investigation on Pressure Fluctuation of the Impellers of a Double-Entry Two-Stage Double Suction Centrifugal Pump

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## Abstract

**:**

## 1. Introduction

## 2. Physical Configuration and Numerical Model

#### 2.1. Calculation Domain

#### 2.2. Grid and Boundary Conditions

^{+}< 300, which means the calculation is reliable.

^{−5}. The cases are run in the High-Performance Computing Center of Hohai University, using 256 GB of memory and 128 cores for parallel computing. The numerical calculation is carried out on ANSYS CFX 2020.

#### 2.3. Monitoring Points

## 3. Results and Discussion

#### 3.1. Pump General Performance

#### 3.2. Characteristics of Pressure Fluctuation of First-Stage Single Suction Impeller

^{−5}at the eighth loop. The data were chosen from the ninth loop to the tenth loop.

_{r}= 12.5 Hz). Among the monitoring points of the blade suction side, the dominant frequency amplitude of point SS3 is the highest, while the frequency of point SS4 is the smallest. The dominant frequency amplitude of SS3 is 1.2 times that of point SS6 while it is 2 times that of point SS4. For all monitoring points on the blade pressure side, the dominant frequency amplitude at SP9 is the maximum while point SP4 is the smallest. The numerical value of point SP9 is 1.6 times that of SP3, while it is about 2.8 times that of point SP4. Comparing the values of the blade, the maximum amplitude on the pressure side is 1.3 times that on the suction side.

#### 3.3. Comparison of Pressure Fluctuation of Two Single-Suction Impellers

#### 3.4. Characteristics of Pressure Fluctuation of Second-stage Double-Suction Impeller

## 4. Conclusions

- (1)
- The pressure fluctuation characteristics of the first-stage single-suction impeller are obtained. In the first-stage single-suction impeller, the pressure fluctuation changes periodically with time. The dominant frequency of the impeller regions is 2 times the rotational frequency. The dominant frequency amplitude increases from the blade inlet to the blade outlet. The value of the blade outlet is about 2 times that of the blade inlet. Among the three typical conditions, the dominant frequency amplitude at 0.6 Q is the maximum, which is about three times that of 1.0 Q.
- (2)
- The effects of a taper pipe suction chamber and semi-spiral suction chamber on the pressure pulsation of a single-suction impeller are compared. Both the impellers show that along the streamline direction, the dominant frequency amplitude of pressure fluctuation increases. The dominant frequency amplitude of the same region reaches a maximum when the flow rate is low. Different from the straight chamber of the single-stage single-suction centrifugal pump, the semi-spiral suction chamber of the pump affects the dominant frequency amplitude of the first-stage single-suction impeller.
- (3)
- The pressure fluctuation characteristics of the second-stage double-suction impeller are obtained. In the second-stage double-suction impeller, the dominant frequency is twice that of the rotational frequency. It increases from the blade entrance to the blade outlet. At 0.6 Q, the dominant frequency amplitude is about twice that at 1.0 Q. The dominant frequency amplitude of the blade pressure side inlet is about 5 times that of the first-stage single-suction impeller due to the differences of the suction chambers.

## Author Contributions

## Funding

## Conflicts of Interest

## Nomenclature

D_{1} | Outer diameter of first-stage single suction impeller, mm |

D_{2} | Outer diameter of second-stage double suction impeller, mm |

Z_{1} | Blades number of first-stage single suction impeller |

Z_{2} | Blades number of second-stage double suction impeller |

H | Pump head, m |

Q | Design flow rate, m^{3}/s |

n | Dated rotational speed, r/min |

H | Pump efficiency, % |

${y}^{+}$ | Dimensionless distance between the center of mass of the first layer of the grid to the wall |

Cp | Pressure coefficient |

$\Delta p$ | The difference between the pressure and its average, Pa |

$\rho $ | Density, m^{3}/s |

$u$ | Circumferential velocity of impeller outlet, m/s |

D | Outer diameter of impeller, mm |

SS | Single suction impeller Suction side |

SP | Single suction impeller Pressure side |

DS | Double suction impeller Suction side |

DP | Double suction impeller Pressure side |

DTDCP | double-entry two-stage double-suction centrifugal pump |

f | Rotating frequency, Hz |

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**Figure 1.**Calculation domain of DTDCP. (

**1**) water inlet (

**2**) suction chamber (

**3**) first-stage single suction impeller, (

**4**) inter-stage flow channel (

**5**) second-stage double suction impeller (

**6**) double-volute.

**Figure 3.**Flowchart of study process. (

**a**) suction chamber (

**b**) inter-stage flow channel (

**c**) second-stage double-suction impeller (

**d**) double-volute.

**Figure 9.**Frequency domain diagram of single-suction impeller at design flow rate condition. (

**a**) Blade Suction Side, (

**b**) Blade Pressure Side.

**Figure 10.**Time domain diagram of point sp6 at three typical flow rate conditions. (

**a**) 0.6 Q, (

**b**) 1.0 Q, (

**c**) 1.1 Q.

**Figure 11.**Frequency domain diagram of single-suction impeller at three typical flow rate conditions. (

**a**) SP4, (

**b**) SP5, (

**c**) SP6.

**Figure 12.**Highest amplitude of two single-suction impellers. (

**a**) Single-suction impeller in reference [36], (

**b**) Single-suction impeller in this paper.

**Figure 13.**Static pressure distribution in the mid-section of the positive passage at three typical flow rate conditions. (

**a**) 0.6 Q, (

**b**) 1.0 Q, (

**c**) 1.1 Q.

**Figure 14.**Velocity distribution of inter-stage flow channel at three typical flow rate conditions. (

**a**) 0.6 Q, (

**b**) 1.0 Q, (

**c**) 1.1 Q.

**Figure 15.**Frequency domain diagram of second-stage double-suction impeller at 1.0 Q. (

**a**) Monitoring points of blade suction side, (

**b**)Monitoring points of blade pressure side.

**Figure 17.**Static pressure near outlet of second stage impeller at three typical flow rate conditions. (

**a**) 0.6 Q, (

**b**) 1.0 Q, (

**c**) 1.1 Q.

Parameters | Values |
---|---|

D_{1} | 1050 mm |

Z_{1} | 6 |

D_{2} | 1000 mm |

Z_{2} | 6 |

n | $750\mathrm{r}\cdot {\mathrm{min}}^{-1}$ |

Q | $8640{\mathrm{m}}^{3}\cdot {\mathrm{h}}^{-1}$ |

H | 158 m |

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**MDPI and ACS Style**

Yan, H.; Heng, Y.; Zheng, Y.; Tao, R.; Ye, C.
Investigation on Pressure Fluctuation of the Impellers of a Double-Entry Two-Stage Double Suction Centrifugal Pump. *Water* **2022**, *14*, 4065.
https://doi.org/10.3390/w14244065

**AMA Style**

Yan H, Heng Y, Zheng Y, Tao R, Ye C.
Investigation on Pressure Fluctuation of the Impellers of a Double-Entry Two-Stage Double Suction Centrifugal Pump. *Water*. 2022; 14(24):4065.
https://doi.org/10.3390/w14244065

**Chicago/Turabian Style**

Yan, Hongyeyu, Yaguang Heng, Yuan Zheng, Ran Tao, and Changliang Ye.
2022. "Investigation on Pressure Fluctuation of the Impellers of a Double-Entry Two-Stage Double Suction Centrifugal Pump" *Water* 14, no. 24: 4065.
https://doi.org/10.3390/w14244065