Experimental and Numerical Investigation of Forced Convection in a Double Skin Façade
Abstract
:1. Introduction
2. Experimental Study
Calibration and Uncertainty
3. Experimental Results
4. Numerical Study
4.1. Governing Equations
4.2. Numerical Method
- The flow is steady, fully turbulent and three dimensional,
- The realizable k-epsilon turbulent model was used,
- SIMPLE algorithm was applied in the solution of the governing equations,
- Standard method was used for the separation of the pressure term,
- Second Order Upwind separation scheme was applied for the other transport equations
4.3. Geometrical Setup and Boundary Conditions
5. Results and Discussions
5.1. Velocity Changes at the Horizontal Lines in the Middle of the Cavity
5.2. Temperature Changes at the Top Horizontal Line in the Middle of the Cavity
5.3. Velocity Distributions and the Streamlines at the Vertical Section in the Middle of the Cavity
5.4. The Average Pressure Drop at the Vertical Section in the Middle of the Cavity
5.5. Temperature Distributions at the Vertical Section in the Middle of the Cavity
5.6. Non-Dimensional Correlation Construction between Reynolds and Nusselt Numbers
6. Conclusions
- Forced flow through the DSF cavity were in the thermal and hydrodynamic entrance region for almost all numerical experiments. Thus, convection heat transfer coefficient values for each case were found to be relatively higher in the entrance region except of the inlet and outlet sections. This situation can be considered for the energy analysis of DSF.
- Design of cross section area of air inlet and outlet was significant. Sharp turns created significant pressure drops which increased fan capacity and its energy consumption. This sharp-edged inlet of the cavity behaved like an air flow constriction.
- Recirculating flows around the inlet section created pressure drop and the circulation zone took the form a larger loop as the velocity of the air in the cavity increased.
- Extended data sets from the nine experimental studies under steady-state conditions were collected. These data can be used by the validation of the different numerical studies for a double skin façade with an external airflow mode.
- A correlation based on a Nu-Re analysis of the numerical results was developed to predict the Nusselt numbers with the Reynolds number ranging from 28,000 to 56,500 approximately for a box window type of DSF with an external airflow mode for aspect ratios of 0.10–0.16.
- This non-dimensional correlation could be used to evaluate the energy performance of the double skin façade using climatic data from different locations as a future study.
Acknowledgments
Author Contributions
Conflicts of Interest
Nomenclature
CA | cavity air |
C, Cμ, C1ε, C2ε, C3ε | constants |
cp | specific heat, J/kg K |
CFD | computational fluid dynamics |
Dh | hydraulic diameter, m |
DSF | double skin façade |
E | energy transfer rate, W |
Gb | generation of turbulence kinetic energy due to buoyancy |
Gk | generation of turbulence kinetic energy due to mean velocity gradients |
h | Convection heat transfer coefficient, W/m2K |
H | geometric height, m |
k | thermal conductivity, W/mK; local turbulence kinetic energy |
L | geometric width, m |
mass flow rate, kg/s | |
Nu | Nusselt number |
p | pressure, Pa |
PF | primary façade |
Re | Reynolds number |
Q | heat transfer rate, W |
SK, Sε | user-defined source terms |
SF | secondary façade |
t | time, s |
T | temperature, °C |
u | velocity component, x-direction, m/s |
v | velocity component, y-direction, m/s |
V | velocity, m/s |
w | velocity component, z-direction, m/s |
W | geometric depth, m |
YM | contribution of fluctuating dilatation in compressible turbulence to overall dissipation rate |
x, y, z | cartesian coordinates |
Greek Symbols | |
ε | diffusion rate |
μ | dynamic viscosity, kg/m s |
ρ | density, kg/m3 |
σk, σε | turbulent Prandtl numbers for k and ε |
Δ | differential element |
Subscripts | |
avg | average |
i, j | tensors |
t | turbulence |
Superscript | |
m | constant |
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Exp. # | Cavity Depth (cm) | Flow | (°C) | (m/s) | PF (°C) | SF (°C) | ||||
---|---|---|---|---|---|---|---|---|---|---|
Tinlet | Vinlet | T1,2avg | T3,4avg | T5,6avg | T1,2avg | T3,4avg | T5,6avg | |||
1 | 25.0 | low | 4.40 | 1.25 | 6.28 | 8.41 | 9.45 | 3.79 | 4.41 | 4.73 |
2 | med | 4.52 | 1.81 | 5.84 | 7.83 | 8.60 | 3.53 | 4.01 | 4.31 | |
3 | high | 3.34 | 2.34 | 4.53 | 6.45 | 7.13 | 2.30 | 2.56 | 2.89 | |
4 | 32.5 | low | 5.71 | 1.23 | 7.45 | 9.22 | 10.41 | 4.95 | 5.44 | 5.78 |
5 | med | 5.03 | 1.67 | 6.31 | 7.98 | 9.06 | 3.84 | 4.11 | 4.49 | |
6 | high | 3.78 | 2.15 | 5.03 | 6.76 | 7.76 | 2.66 | 2.78 | 3.20 | |
7 | 40.0 | low | 6.40 | 1.40 | 8.30 | 10.14 | 11.34 | 5.53 | 5.95 | 6.33 |
8 | med | 6.36 | 1.92 | 7.86 | 9.58 | 10.58 | 5.15 | 5.29 | 5.63 | |
9 | high | 5.89 | 2.35 | 7.18 | 8.84 | 9.76 | 4.75 | 4.60 | 4.92 |
Exp. # | (K) | Q (W) | Pascal | ṁ (kg/s) | |||||
---|---|---|---|---|---|---|---|---|---|
Toutlet | PF | SF | ΔEair | ΔEerror | Δp | ṁinlet | ṁoutlet | Δṁ | |
1 | 277.82 | 119.900 | −1.017 | 118.573 | −0.310 | 1.753 | 0.44204980 | 0.44204962 | 1.788 × 10−7 |
2 | 277.83 | 124.700 | 19.994 | 104.285 | −0.421 | 3.152 | 0.64110140 | 0.64110191 | −5.364 × 10−7 |
3 | 276.62 | 142.023 | −30.802 | 110.551 | −0.670 | 4.608 | 0.83308649 | 0.83308619 | 2.980 × 10−7 |
4 | 279.06 | 94.339 | −7.224 | 86.773 | −0.342 | 1.878 | 0.43359959 | 0.43359985 | −2.682 × 10−7 |
5 | 278.30 | 98.098 | −25.357 | 72.265 | −0.477 | 2.635 | 0.59128022 | 0.59128016 | 5.960 × 10−8 |
6 | 277.05 | 120.811 | −29.322 | 90.900 | −0.589 | 3.867 | 0.76466095 | 0.76466018 | 7.749 × 10−7 |
7 | 279.73 | 100.283 | −10.254 | 89.612 | −0.418 | 1.937 | 0.49215615 | 0.49215606 | 8.941 × 10−8 |
8 | 279.63 | 108.603 | −26.712 | 81.446 | −0.445 | 2.780 | 0.67640877 | 0.67640847 | 2.980 × 10−7 |
9 | 279.14 | 116.771 | −34.663 | 81.458 | −0.650 | 3.565 | 0.83000046 | 0.83000070 | −2.384 × 10−7 |
Exp. # | #1 | #2 | #3 | #4 | #5 | #6 | #7 | #8 | #9 |
---|---|---|---|---|---|---|---|---|---|
C. Depth (cm) | 25.0 | 32.5 | 40.0 | ||||||
Re | 30,190 | 43,720 | 56,530 | 28,150 | 38,540 | 49,650 | 31,010 | 42,520 | 52,050 |
Nu | 134.29 | 169.45 | 206.59 | 148.17 | 177.88 | 220.39 | 184.10 | 231.38 | 272.10 |
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İnan, T.; Başaran, T.; Erek, A. Experimental and Numerical Investigation of Forced Convection in a Double Skin Façade. Energies 2017, 10, 1364. https://doi.org/10.3390/en10091364
İnan T, Başaran T, Erek A. Experimental and Numerical Investigation of Forced Convection in a Double Skin Façade. Energies. 2017; 10(9):1364. https://doi.org/10.3390/en10091364
Chicago/Turabian Styleİnan, Tuğba, Tahsin Başaran, and Aytunç Erek. 2017. "Experimental and Numerical Investigation of Forced Convection in a Double Skin Façade" Energies 10, no. 9: 1364. https://doi.org/10.3390/en10091364