|Contributions||University of Brighton. Department of Mechanical and Manufacturing Engineering., Delphi Technical Centre Luxembourg.|
This paper presents a detailed evaluation of two- and three-dimensional numerical models of flow and heat transfer over louvred fin arrays in compact heat exchangers. Two 3-D models are described, both of which incorporate the effects of tube surface area and fin resistance on the overall heat transfer by: The numerical simulation on the other augment surfaces, such as perforated fins, louvered fins in compact heat exchangers, can be found in these literatures,,,. In this study, the heat transfer Colburn factor j and the friction factor f characteristics of the serrated fins in PFHE are investigated both experimentally and by: Numerical model The numerical simulation was done with the commercial software Fluent. In order to be able to mesh the louver-fin transition adequately, a zero fin thickness model is used. The heat transfer in the fin material is modelled used the conduction equations in a single layer of cells conforming to theCited by: 7. Experimental investigations were conducted to understand the air flow and heat transfer in louver-fin round-tube two-row two-pass cross-counterflow heat exchangers. The Colburn factor j and friction factor f were obtained by using the ε-NTU approach. A three-dimensional computational fluid dynamics model was developed based on a representative unit cell with Cited by: 9.
The present 3D numerical model of a fin and tube heat exchanger design includes conjugate heat transfer that corresponds to the combination of heat transfer phenomenon in fin, tube and gas domains simultaneously. To simplify the model and computation, following assumptions are made: Steady state flow and heat transfer. FLOW PHENOMENA IN LOUVERED FINS As stated in the introduction, very few performance data are available in the literature. However, a number of authors have considered the operating mechanisms of louvered heat transfer surfaces. Beauvais  used flow visualization on large-scale models. mensional numerical analysis of heat transfer on the air side of a wavy fin and tube heat ex-changer. The three dimensional local flow and thermal fields are well characterized by the numerical analysis. The developed and presented model demonstrated good heat transfer pre-diction. It could provide guidelines for the design optimization of a Cited by: 9. Numerical models for the heat transfer rate and flow friction derived from the microscopic analysis are then used for simulations of the full radiator model in semimicroscopic analysis. In the semimicroscopic analysis, conjugate heat transfer is analyzed for the domain with the radiator whose louver fin area is replaced by a porous by: 9.
The study is performed for different louver angles varying from θ L = 12 to 60 deg, and optimal heat transfer rate is obtained at louver angle of θ L = 28 deg . Also, it is found that increasing the louver number, N L , on the fin surface enhances the heat transfer by: 3. 8 of The present study numerically investigates the thermal hydraulic performance of multi- louvered fin and flat tube heat exchangers using 36 heat exchanger models with different louver angles (19°°), flow depths (16, 20, 24 mm) and ≤ Lp/Fp ≤ over a Reynolds number range of 30 to File Size: 5MB. The characteristics of physical phenomena for the fluid flow and heat transfer inside a heat exchanger are investigated by changing geometric and flow parameters such as louver angle of the fin(0), the ratio of louver pitch to fin pitch(F P /L P) and Reynolds number(Re=UL p /v). Computational results are graphically visualized and many Author: C. S. Kang, J. L. Sohn, T. M. Choi, J. H. Lee. Several studies of the louvered fin heat exchanger have already been done. Both experimental and numerical studies are available. Investigations to the optimal louver angle have been performed, many times in combination with other fin parameters such as louver pitch and fin thickness. Most studies assume a single louver angle for all the louvers in the heat by: 7.