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Research Papers

Proper Orthogonal Decomposition and Extended- Proper Orthogonal Decomposition Analysis of Pressure Fluctuations and Vortex Structures Inside a Steam Turbine Control Valve

[+] Author and Article Information
Peng Wang, Hongyu Ma

Key Lab of Education Ministry for Power
Machinery and Engineering,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China;
Gas Turbine Research Institute,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China

Yingzheng Liu

Key Lab of Education Ministry for Power
Machinery and Engineering,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China;
Gas Turbine Research Institute,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: yzliu@sjtu.edu.cn

1Corresponding author.

Manuscript received July 6, 2018; final manuscript received July 8, 2018; published online December 12, 2018. Editor: Jerzy T. Sawicki.

J. Eng. Gas Turbines Power 141(4), 041035 (Dec 12, 2018) (11 pages) Paper No: GTP-18-1455; doi: 10.1115/1.4040903 History: Received July 06, 2018; Revised July 08, 2018

In steam turbine control valves, pressure fluctuations coupled with vortex structures in highly unsteady three-dimensional flows are essential contributors to the aerodynamic forces on the valve components, and are major sources of flow-induced vibrations and acoustic emissions. Advanced turbulence models can capture the detailed flow information of the control valve; however, it is challenging to identify the primary flow structures, due to the massive flow database. In this study, state-of-the-art data-driven analyses, namely, proper orthogonal decomposition (POD) and extended-POD, were used to extract the energetic pressure fluctuations and dominant vortex structures of the control valve. To this end, the typical annular attachment flow inside a steam turbine control valve was investigated by carrying out a detached eddy simulation (DES). Thereafter, the energetic pressure fluctuation modes were determined by conducting POD analysis on the pressure field of the valve. The vortex structures contributing to the energetic pressure fluctuation modes were determined by conducting extended-POD analysis on the pressure–velocity coupling field. Finally, the dominant vortex structures were revealed conducting a direct POD analysis of the velocity field. The results revealed that the flow instabilities inside the control valve were mainly induced by oscillations of the annular wall-attached jet and the derivative flow separations and reattachments. Moreover, the POD analysis of the pressure field revealed that most of the pressure fluctuation intensity comprised the axial, antisymmetric, and asymmetric pressure modes. By conducting extended-POD analysis, the incorporation of the vortex structures with the energetic pressure modes was observed to coincide with the synchronous, alternating, and single-sided oscillation behaviors of the annular attachment flow. However, based on the POD analysis of the unsteady velocity fields, the vortex structures, buried in the dominant modes at St = 0.017, were found to result from the alternating oscillation behaviors of the annular attachment flow.

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References

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Figures

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Fig. 1

Schematic illustration of the control valve configuration and corresponding annular attachment flow

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Fig. 2

Wall pressure fluctuations monitored during the numerical simulation

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Fig. 3

Contour plot of instantaneous vortex structures characterized by Q-criterion and time-averaged vorticity: (a) q-criterion and (b) vorticity

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Fig. 4

Time-mean and time-variant flow distributions inside the steam turbine control valve: velocity vectors and Mach number contour: (a) time averaged, (b) t1, (c) t2, and (d) t3

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Fig. 5

Contour plot of the statistical quantities of steam turbine control valve: (a) fluctuation intensity of streamwise velocity component, (b) reverse-flow intermittency, and (c) pressure fluctuation intensity

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Fig. 6

Normalized eigenvalues corresponding to the pressure POD eigenmodes and their cumulative distributions

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Fig. 7

Spatial features for the pressure POD eigenmodes

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Fig. 8

Spectral power density of mode coefficients for the pressure POD eigenmodes: (a) mode 1, (b) mode 2, (c) mode 3, (d) mode 4, (e) mode 5, and (f) mode 6

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Fig. 9

Spatial features for the extended-POD modes for the pressure–velocity coupling field of the control valve

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Fig. 10

Normalized eigenvalues corresponding to the velocity POD eigenmodes and their cumulative distributions

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Fig. 11

Spatial features for the velocity POD eigenmodes

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Fig. 12

Spectral power density of mode coefficients for the velocity POD eigenmodes: (a) mode 1, (b) mode 2, (c) mode 3, (d) mode 4, (e) mode 5, and (f) mode 6

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Fig. 13

Reconstructed streamwise velocity distribution with mode 1 of the velocity fields of the control valve: (a) without averaged flow field and (b) with averaged flow field

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