Near-Wall Thermal Processes in an Inclined Impinging Jet: Analysis of Heat Transport and Entropy Generation Mechanisms
Abstract
:1. Introduction
2. Configuration and Numerical Procedure
2.1. Inclined Jet Impinging on a Heated Solid Surface
2.2. Numerical Procedure
3. Summary of the Previous Study
4. Near-Wall Thermal Characteristics
4.1. First and Second Order Thermal Moments
4.2. Turbulent Thermal Processes
4.3. Heat Transport
4.4. Wall Heat Transfer
5. Entropy Generation Mechanisms
6. Concluding Remarks
- I
- Examining near-wall thermal statistics within the -inclined impinging jet configuration, it turned out that the peak heat transfer does not appear directly at the stagnation point as is usually the case in jets impinging normally on a heated surface. Instead, the highest Nusselt numbers, the minimum of thermal boundary layer thickness and largest wall-normal heat transport are slightly shifted towards the compression side of the inclined jet (). Thereby, turbulent intensity is high, while temperature variance exhibits a local minimum at this location.
- II
- Based on the analysis of the budget contributions of different terms in the temperature variance and turbulence kinetic energy equations, it appears that turbulent thermal and fluid flow transport processes around the stagnation point of the inclined impinging jet are considerably different from those found in other wall-bounded flows. Dissipation is relatively small, while molecular and pressure-related diffusion dominate. In the case of turbulent kinetic energy, the production term is prevailing negative.
- III
- It is observed that heat is transported counter to the gradient from low to high temperature regions at the location of maximal heat transfer (). The reason for such a paradoxical behavior is that the dissipation of temperature fluctuations is too small to balance the diffusional sources (see also [77]).
- IV
- Regarding turbulent heat transport, it turned out that fluxes are predominantly isotropic very close to the wall, become highly anisotropic with increasing wall distance and finally return to the isotropic state at the edge of the thermal boundary layer. Furthermore, the heat fluxes behave most anisotropically on the compression side. Both, the counter gradient heat flux and the inherently anisotropic nature of heat fluxes in the thermal boundary layer of the inclined impinging jet suggest that tensorial heat diffusivity models might be appropriate for such kinds of thermo-viscous flows, especially in the context of RANS.
- V
- The ratio of mechanical and thermal time scales deviates considerably from the equilibrium value of in the thermal boundary layer of the inclined impinging jet. In particular around the stagnation point, the time-scale ratio exceeded 1.5, indicating strong non-equilibrium effects in heat and fluid flow transport.
- VI
- Especially the heated wall acts as a strong source of reversibility in the case of impinging cooling arrangements. This holds for both entropy production due to viscous dissipation and heat conduction. Thereby, the entropy production contribution of mean gradients dominates that of the fluctuating gradients. This suggests that the design of the impinged plate (surface roughness, corrugation, chevron angle, etc.) is particularly important for efficient use of energy in such thermal arrangements that may exhibit intensification of turbulence in the vicinity of the wall.
- VII
- Regarding the conceptional engineering design of such thermal devices, this study confirms that the estimation of the turbulent part of the entropy production based on turbulence dissipation rates in non-reacting, non-isothermal fluid flows represents a reliable approximation for second law analysis, likewise in the context of computationally less expensive simulation techniques like RANS and/or LES.
Author Contributions
Acknowledgments
Conflicts of Interest
Appendix A. Solution Verification
Appendix A.1. Test Case
Appendix A.2. Solution Verification Results
References
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Property | Description | Value |
---|---|---|
inclination angle of the plate | ||
D | nozzle exit diameter | 40 mm |
H | jet-to-plate distance | 40 mm |
velocity at the contraction entrance | m/s | |
temperature at the contraction entrance | 290 K | |
wall temperature of the heated surface | 330 K | |
p | ambient pressure | bar |
Reynolds-number based on nozzle exit diameter | 5000 | |
molecular Prandtl number |
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Ries, F.; Li, Y.; Klingenberg, D.; Nishad, K.; Janicka, J.; Sadiki, A. Near-Wall Thermal Processes in an Inclined Impinging Jet: Analysis of Heat Transport and Entropy Generation Mechanisms. Energies 2018, 11, 1354. https://doi.org/10.3390/en11061354
Ries F, Li Y, Klingenberg D, Nishad K, Janicka J, Sadiki A. Near-Wall Thermal Processes in an Inclined Impinging Jet: Analysis of Heat Transport and Entropy Generation Mechanisms. Energies. 2018; 11(6):1354. https://doi.org/10.3390/en11061354
Chicago/Turabian StyleRies, Florian, Yongxiang Li, Dario Klingenberg, Kaushal Nishad, Johannes Janicka, and Amsini Sadiki. 2018. "Near-Wall Thermal Processes in an Inclined Impinging Jet: Analysis of Heat Transport and Entropy Generation Mechanisms" Energies 11, no. 6: 1354. https://doi.org/10.3390/en11061354