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Research Papers

Rotordynamic Force Coefficients of Volutes and Diffusers for Prediction of Turbomachinery Vibration

[+] Author and Article Information
Farzam Mortazavi

Mem. ASME
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77843
e-mail: farzam.mortazavi@tamu.edu

Alan Palazzolo

James J. Cain Professor I
Fellow ASME
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77843
e-mail: a-palazzolo@tamu.edu

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received July 28, 2017; final manuscript received March 12, 2018; published online April 27, 2018. Assoc. Editor: Costin Untaroiu.

J. Vib. Acoust 140(5), 051015 (Apr 27, 2018) (12 pages) Paper No: VIB-17-1344; doi: 10.1115/1.4039725 History: Received July 28, 2017; Revised March 12, 2018

The American Petroleum Institute (API) level II vibration stability analysis for impellers requires higher fidelity models to predict the dynamic forces of the whirling impeller. These forces are in turn required to predict the vibration stability, critical speeds, and steady-state vibration response of the shaft-bearing-seal-impeller system. A transient computational fluid dynamics (CFD)-based approach is proposed which is applicable to nonaxisymmetric turbomachinery components, such as the volute and/or diffuser vanes, unlike its predecessor models like the bulk-flow or the quasi-steady model. The key element of this approach is the recent advancements in mesh deformation techniques which permit less restrictive motion boundary conditions to be imposed on the whirling impeller. The results quantify the contributions of the volute and/or the diffuser to the total forces which guides the analyst on whether to include these components in the model. The numerical results obtained by this approach are shown to agree well with experimental measurements and to be superior to the earlier quasi-steady alternative in terms of accuracy. Furthermore, several volute shapes were designed and analyzed for the sensitivity of the solution to the geometrical properties of the volute. The design flow rotordynamic forces show a significant dependence on the presence of the volutes in the model, with the specific shape of the volute having a lesser influence. The dimensionless forces are shown to be almost independent of the spin speed.

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Figures

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Fig. 4

Exploded view of the computational domains

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Fig. 3

Volute designs from CFTurbo: (a) circular, (b) radius based, (c) rectangular, (d) round asymmetric, and (e) trapezoidal

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Fig. 2

Pump dimensions: (a) main dimensions and (b) narrow versus wide clearance

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Fig. 1

Schematic of gap A configurations

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Fig. 5

Mesh deformation boundary conditions: (a) blade to blade view and (b) meridional view

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Fig. 6

Sample fast Fourier transform (FFT) of the dimensionless forces in the stationary frame at FR=−0.6

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Fig. 13

Dimensionless normal and tangential forces, predictions versus experiments. QS and Trn correspond to quasi-steady and transient, respectively.

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Fig. 7

Zero frequency ratio force extraction

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Fig. 8

Fictitious force due to the fixed axis of spin

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Fig. 9

Quasi-steady dimensionless normal and tangential forces with centered and off-centered spinning motion (eccentricity e=1.26mm)

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Fig. 10

Grid independency results

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Fig. 11

Dimensionless dynamic forces from various grid densities

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Fig. 12

Experimental and numerical pump characteristics

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Fig. 15

Total dimensionless normal and tangential forces of the same impeller working with various volutes

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Fig. 16

Contributions of the impeller and various volutes to the total normal and tangential forces

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Fig. 14

The trapezoidal volute rotordynamic forces versus the impeller for the wide clearance configuration

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Fig. 20

Gap A influence on the dynamic forces

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Fig. 21

Independency of the dimensionless normal and tangential forces from the spin speed

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Fig. 17

Contributions of the diffuser and the volute to the total normal and tangential forces

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Fig. 18

The quasi-steady model predictions follow the transient results closely for the narrow clearance configuration. Trapezoidal volute is included in both cases.

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Fig. 19

Transient force predictions of the narrow versus wide clearance. Trapezoidal volute is included in both cases.

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