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Research Papers

Experimental Investigation of Heat Transfer in Cavities of Steam Turbine Casings Under Generic Test Rig Conditions

[+] Author and Article Information
David Spura

Chair of Thermal Power Machinery and Plants,
Institute of Power Engineering,
Technische Universität Dresden,
Dresden 01062, Germany
e-mail: david.spura@tu-dresden.de

Gunter Eschmann, Wieland Uffrecht

Chair of Magnetofluiddynamics,
Measuring and Automation Technology,
Institute of Fluid Mechanics,
Technische Universität Dresden,
Dresden 01062, Germany

Uwe Gampe

Chair of Thermal Power Machinery and Plants,
Institute of Power Engineering,
Technische Universität Dresden,
Dresden 01062, Germany

1Corresponding author.

Manuscript received August 15, 2018; final manuscript received August 21, 2018; published online April 8, 2019. Editor: Jerzy T. Sawicki.

J. Eng. Gas Turbines Power 141(5), 051021 (Apr 08, 2019) (11 pages) Paper No: GTP-18-1569; doi: 10.1115/1.4041452 History: Received August 15, 2018; Revised August 21, 2018

This paper presents the first experimental results of the systematic investigation of forced convection heat transfer in scaled generic models of steam turbine casing side spaces with varied geometric dimensions under fully turbulent air flow. Data were obtained by two redundant low-heat measuring methods. The results from the steady-state inverse method are in good agreement with the data from the local overtemperature method, which was applied via a novel miniaturized heat transfer coefficient (HTC) sensor concept. All experiments were conducted at the new side space test rig “SiSTeR” at TU Dresden. The dependencies of the HTC distributions on the axial widths of the cavity and its inlet and on the eccentricity between them were investigated for Reynolds numbers from Re=40,000 to 115,000 in the annular main flow passage. The measured HTC distributions showed a maximum at the stagnation point where the induced jet impinges on the wall surface, and decreasing values toward the cavity corners. Local values scaled roughly with the main flow Reynolds number. The HTC distributions thereby differed considerably depending on the dimensions and the form of the cavity, ranging from symmetric T-shape to asymmetric L-shape, with upstream or downstream shifted sidewalls.

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References

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Figures

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Fig. 1

Side spaces between guide vane carriers and outer casing of an industrial steam turbine [13]

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Fig. 2

Piping scheme of the pressurized air facility: 1—screw compressors; 2—pressure vessel; 3—pressure reducing valve; 4—three-way bypass valve; 5—orifice plate; 6—test rig; 7—exhaust control valve

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Fig. 3

Test rig concept: 1—inflow; 2—main flow passage (annulus); 3—variable guide vane (optional); 4—calming section; 5—inlet side wall (right side axially shiftable); 6—cavity side wall (axially shiftable); 7—cavity outer wall with HTC instrumentation (axially shiftable, revolvable); 8—cavity; 9—cavity inlet; 10—outer pipe/outliner; 11—displacement body/inliner; 12—outflow

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Fig. 4

Dimensions of the cavity and the annular main flow passage

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Fig. 5

Cavity outer wall consisting of eight identical ring-shaped HTC measuring modules

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Fig. 6

Side space module with side wall adjustment mechanism and insulated outer wall

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Fig. 7

Mesh and boundary conditions of the 2D FE model

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Fig. 8

Convergence of the design optimization for inverse determination of HTC with the FE model: (a) objective function dTopt; (b) differences between simulated and measured temperatures ΔTk; and (c) iterated values of HTC interval averages α¯j

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Fig. 9

Resulting HTC distribution at the outer cavity wall for the converged FE model. Vertical bars denote the standard deviation from the probabilistic analysis. Horizontal bars symbolize the “wetted” ring surfaces being in contact with the fluid in the cavity.

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Fig. 10

Temperature field of the side space structures for the converged FE model

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Fig. 11

Resolution of the data acquisition system as function of HTC and fluid temperature

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Fig. 12

Comparison between local HTC distributions from both measuring methods: (a) s=46.3 mm, b=146.3 mm, e=0; (b) s=20 mm, b=120 mm, e=0

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Fig. 13

Influence of inlet width on HTC distribution: (a) s=46.3 mm, (b) s=40 mm, (c) s=30 mm, (d) s=20 mm, (e) s=10 mm; b=s+100 mm, e=0

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Fig. 14

Influence of cavity width on HTC distribution: (a) b=146.3 mm, (b) b=121.3 mm, (c) b=96.3 mm, (d) b=71.3 mm, (e) b=46.3 mm; s=46.3 mm, e=0

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Fig. 15

Influence of eccentricity on HTC distribution: (a) e=25mm, (b) e=12.5mm, (c) e=0mm, (d) e=−12.5mm, (e) e=−25mm; s=46.3mm, b=96.3mm

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