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ABSTRACT
The air-side heat transfer and pressure drop characteristics of an H-type finned tube bank in the turbulent periodically fully developed region are investigated numerically. The effects of seven geometric parameters and Reynolds number are examined. It is found that when the number of tube rows is equal to and larger than 25, the heat transfer and fluid flow approach the fully developed state. Among the seven geometric parameters spanwise tube pitch has the most important effect. Based on the numerical results, the correlations of heat transfer and pressure drop of the H-type finned tube bank for the fully developed region are presented.
Nomenclature
| A | = | area, m2 |
| D | = | tube outside diameter, m |
| f | = | friction factor |
| Fp | = | fin pitch, m |
| Ft | = | fin thickness, m |
| h | = | heat transfer coefficient, W · m−2 · K−1 |
| H | = | fin height, m |
| k | = | turbulent kinetic energy, m2 · s−2 |
| Nu | = | average Nusselt number |
| p | = | pressure, Pa |
| P | = | pumping power, W |
| AP | = | pressure drop, Pa |
| Re | = | Reynolds number |
| S1 | = | spanwise tube pitch, m |
| S2 | = | longitudinal tube pitch, m |
| T | = | temperature, K |
| ΔT | = | the log mean temperature difference, K |
| u | = | velocity, m · s−1 |
| W | = | slit width, m |
| Greek alphabet | = | |
| Φ | = | heat transfer rate, W |
| λ | = | thermal conductivity, W · m−1 · K−1 |
| ν | = | kinematic viscosity, m2 · s−1 |
| ρ | = | density, kg · m−3 |
| θ | = | local intersection angle, Deg. |
| ε | = | turbulent energy dissipation rate, m2 · s−3 |
| Subscripts | = | |
| in | = | inlet |
| out | = | outlet |
| w | = | tube wall |
| m | = | module average |
| f | = | frontal area |
Nomenclature
| A | = | area, m2 |
| D | = | tube outside diameter, m |
| f | = | friction factor |
| Fp | = | fin pitch, m |
| Ft | = | fin thickness, m |
| h | = | heat transfer coefficient, W · m−2 · K−1 |
| H | = | fin height, m |
| k | = | turbulent kinetic energy, m2 · s−2 |
| Nu | = | average Nusselt number |
| p | = | pressure, Pa |
| P | = | pumping power, W |
| AP | = | pressure drop, Pa |
| Re | = | Reynolds number |
| S1 | = | spanwise tube pitch, m |
| S2 | = | longitudinal tube pitch, m |
| T | = | temperature, K |
| ΔT | = | the log mean temperature difference, K |
| u | = | velocity, m · s−1 |
| W | = | slit width, m |
| Greek alphabet | = | |
| Φ | = | heat transfer rate, W |
| λ | = | thermal conductivity, W · m−1 · K−1 |
| ν | = | kinematic viscosity, m2 · s−1 |
| ρ | = | density, kg · m−3 |
| θ | = | local intersection angle, Deg. |
| ε | = | turbulent energy dissipation rate, m2 · s−3 |
| Subscripts | = | |
| in | = | inlet |
| out | = | outlet |
| w | = | tube wall |
| m | = | module average |
| f | = | frontal area |
Acknowledgments
We gratefully acknowledge the support of this work by the National Key Basic Research Program of China (973 Program) (No. 2013CB228304).