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UTSR Presentation
Heat Transfer Development
Andrew ChenAugust, 2017
Mentor: Yong Kim
Group Manager: Michael Fox
Department Manager: Daniel Burnes
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Presentation Outline
Personal Background
Projects
I. Pressure Side Trailing Edge Slot Discharge Coefficient Study
II. Labyrinth Seal Flow Parameter Study
III. Labyrinth Seal CFD Simulation
Takeaways
Q&A
2
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Background
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B.S. degree from National Taiwan University
M.S. degree from Texas A&M University
Research on Gas Turbine Heat
Transfer/Film Cooling
Pursuing Ph.D. degree at Texas A&M University
Research on Gas Turbine Film Cooling and Internal
Cooling under Stationary or Rotating Conditions)
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Experience
Research assistant at
Foxconn Communication Technology Corp.
Institute of Atomic and Molecular Sciences, Academia Sinica.
National Synchrotron Radiation Research Center, Taiwan.
4
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PS Slot Discharge Coeff.─
Introduction
5
Why cooling?
Engine operates under mainstream temp. > metal yielding temp.
Use cooling air to cool the turbine blade both internally and
externally.
External (film) cooling.
Credit: Je-Chin Han, 2013, “Fundamental Gas Turbine Heat Transfer”
Trailing edge slot ejection
For a gas turbine vane or blade,
a thin trailing edge is usually
preferred from the aerodynamic
point of view.
Pressure side (PS) slots are
ideal for providing adequate
cooling in this thin-wall region.
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PS Slot Discharge Coeff.─
Introduction
A trailing edge slot rig was built to study the heat transfer as
well as flow behavior.
Mainstream flow acceleration was achieved by an adjustable
door (inclined top wall).
6
Mainstream
Coolant
6 in2.85 in
9.4 in
21.9 in
3.8 in
3.9 in
0.83 in
Vin = 65 ft/s
Coolant mass flow rate
= 0.03 ~ 0.15 lb/s
Pout = 14.5 psi
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PS Slot Discharge Coeff.─
Background
7
Discharge coefficient:
𝐶𝑑 =𝐴𝑐𝑡𝑢𝑎𝑙 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒
𝐼𝑑𝑒𝑎𝑙 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒≤ 1
Important for estimating the actual coolant flow rate
𝐴𝑐𝑡𝑢𝑎𝑙 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 = C𝑑 × 𝐼𝑑𝑒𝑎𝑙 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒
Provide adequate cooling with less amount of coolant.
Increase power, efficiency and durability.
Orifice or Slot
Pup Pdown
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PS Slot Discharge Coeff.─
Finesse Model
Finesse is an in-house 1-D fluid network solver with
specialized components specifically for turbomachinery.
Used for engine hot-gas-path heat/mass predictions.
A 1-D flow simulation network was built for the PS slot.
Mass flow rate, pressures, and velocities are fairly close to the
experimental data.
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PS Slot Discharge Coeff.─
Results
Existing experimental results showed:
Cd higher than one.
Cd drops abruptly at higher coolant blowing ratios (M).
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Blowing ratio M =
𝐶𝑜𝑜𝑙𝑎𝑛𝑡 𝑚𝑎𝑠𝑠 𝑓𝑙𝑢𝑥
𝑀𝑎𝑖𝑛𝑠𝑡𝑟𝑒𝑎𝑚 𝑚𝑎𝑠𝑠 𝑓𝑙𝑢𝑥
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PS Slot Discharge Coeff.─
Results
CFD result showed Cd gradually increases with blowing ratio
up to around 1.
Discrepancy between CFD and experimental results.
10
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PS Slot Discharge Coeff.─
Results
Tried to use different reference pressures.
No significant change in results.
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Ref. 1
Ref. 2
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PS Slot Discharge Coeff.─
Results
Three different mainstream flow conditions were investigated:
Accelerated (baseline case)
Accelerated, door was shifted 1.8” downstream (DS)
Non-accelerated (NA)
Nearly no effect on Cd.12
Baseline
Door-Shifted (DS)
Non-accelerated (NA)
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PS Slot Discharge Coeff.─
Slot Inlet Static Pressure
Slot inlet static pressure was examined. An abrupt change in
slope was identified in the experimental data.
13
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PS Slot Discharge Coeff.─
Mainstream Static Pressure
Use Bernoulli’s equation, the -0.07 psi static pressure
difference corresponds to a velocity of 96 ft/s, which is far
higher than the specified mainstream inlet velocity of 65 ft/s.
Higher than expected uncertainties in pressure measurement
may be responsible for the discrepancies between
experimental and CFD results.
14
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PS Slot Discharge Coeff.─
Conclusions
CFD Showed that Cd increases with increasing coolant flow
rate up to around 1.
Different reference pressures will lead to different results.
The mainstream acceleration, or the door (top wall) location,
has minimal effect on the discharge coefficient.
Uncertainty in the pressure measurement may be responsible
for the discrepancies between the experimental and CFD
results.
15
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Labyrinth Seal Flow Coeff. Study
Background
An accurate prediction of flow parameters of labyrinth seals is
important to the resultant coolant consumption,
pressure/temperature distributions, and engine performance.
Based on engine test data, the leakage mass flow rate of the
labyrinth seal was found ~10% higher than the value
predicted by Finesse.
Objectives:
Compare Finesse with available NASA data.
Check if Finesse is working properly.
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Labyrinth Seal Flow Coeff. Study
Straight Seal Test Matrix
The NASA test data [1] includes the following cases. There
are three clearances: CL = 0.02”, 0.01” and 0.005”
Cases include smooth land and honeycomb land.
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Test # Kϴ (°) KN KT (in) KP (in) CL (in) X (in)
1 90 5 0.010 0.100 0.005 0.031
2 90 5 0.010 0.100 0.005 0.062
3 90 5 0.010 0.100 0.005 0.125
4 90 5 0.010 0.100 0.005 Solid
5 90 5 0.010 0.100 0.010 0.031
6 90 5 0.010 0.100 0.010 0.062
7 90 5 0.010 0.100 0.010 0.125
8 90 5 0.010 0.100 0.010 Solid
9 90 5 0.010 0.100 0.020 0.031
10 90 5 0.010 0.100 0.020 0.062
11 90 5 0.010 0.100 0.020 0.125
12 90 5 0.010 0.100 0.020 Solid
[1] Donald L. Tipton, Thomas E. Scott, and Rodney E. Vogel, 1986, “Volume III – Analytical and Experimental
Development of a Design Model for Labyrinth Seals”, Technical Report by Allison Gas Turbine.
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Labyrinth Seal Flow Coeff. Study
NASA vs. Finesse
Comparison between NASA data and Finesse model showed
significant discrepancies at CL = 0.01”.
Finesse model is around 9% lower than the NASA data.
18
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Labyrinth Seal Flow Coeff. Study
Vermes Model
Vermes model [2] is an improved version from the Martin’s
formula [3] and is the theory base of Finesse.
The mass flow through a labyrinth seal is expressed by:
The result is dependent on the clearance factor K value [4]:
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𝑊 = 5.76𝐾𝐴𝑔
𝑅𝑇0
𝑃0
1 − 𝛼𝛽
L/C
K
• Smaller K variation when
0.4 < L/C < 1
[2] Vermes G. “A Fluid Mechanics Approach to the
Labyrinth Seal Leakage Problem”, ASME. J. Eng.
Power. 1961;83(2):161-169. doi:10.1115/1.3673158.
[3] H. M. Martin, “Labyrinth Packings,” Engineering,
January 10, 1908, pp. 35-36.
[4] Myer Kutz, “Mechanical Engineers' Handbook,
Volume 3: Manufacturing and Management”, John Wiley
& Sons, 2015
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Labyrinth Seal Flow Coeff. Study
Vermes vs. Finesse
Comparison between Finesse and Vermes model was done
and the results suggest that the Finesse outputs are correct.
20
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Labyrinth Seal Flow Coeff. Study
NASA vs. Vermes
NASA data was converted into weight flow (lb/s) and
overlapped with the figure in Vermes paper [2] .
Vermes model under-predicts at CL = 0.01” to 0.015”
21
lb/s
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Labyrinth Seal Flow Coeff. Study
Conclusions
The results confirmed that there is no internal error of
Finesse.
Both Vermes paper and the comparison with NASA data
suggest that the Vermes model may under predict the flow at
a clearance level between 0.01” to 0.015”.
The clearance factor (K) directly affects the outcome of the
prediction. It seems that having 0.4 < L/C < 1.0 will be a more
conservative way in the design point of view due to smaller
variations of the K value.
According to Bell and Bergelin (1957): “For the flows in the
transition region (40 < Re < 4000), experimental values
should be used whenever possible.”
Further study is needed.
22
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Labyrinth Seal CFD Simulation
Background
CFD models using two different reference frame setups were
run using STAR CCM+. Different results were obtained.
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Setup 1
Rotate_wall
Setup 2
Rotate_fluid
stationary
rotating
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Labyrinth Seal CFD Simulation
Challenges
Complex geometry with tiny gaps and high losses.
Convergence is challenging.
Issues remained even with higher mesh densities:
Mass imbalance
High residual values
Occasional floating point errors
24
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Labyrinth Seal CFD Simulation
Simplified Model
To rule out other factors that might affect the CFD calculation
with such complex geometry, a half cylinder fluid domain was
generated.
Similar boundary conditions were applied.
25
Periodic
1
Periodic
2
Ω
stator
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Labyrinth Seal CFD Simulation
Results
Static pressures are almost identical.
Simulation on the cylinder model using different reference
settings showed different total temperature results.
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inlet middle outlet inlet middle outlet
2000 rpm
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Labyrinth Seal CFD Simulation
Results
Run at higher rpms.
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2k rpm
2k rpm
5k rpm
5k rpm
10k rpm
10k rpm
Rotate fluid
Rotate wall
Residuals
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Labyrinth Seal CFD Simulation
Conclusions
Both results from the full model and the simplified model
showed significant difference in total temperature.
Total temperature from either setup may be questionable.
Some observations:
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Rotate fluid Rotate wall
CPU time >
Residual level >
Stability <
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Takeaways
STAR CCM+
Finesse
Labyrinth seal models and theories
Work in a company
Connections inside/outside company
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