|Series||Atomic Energy of Canada Limited. AECL -- 8271|
|Contributions||Rhodes, D., Carlucci, L.|
A numerical study of the two-dimensional isothermal steady flow distribution of an incompressible fluid in the shell side of an experimental heat exchanger is described. Computations are performed with and without tubes present in the model, for Reynolds numbers up to 10, Baffles and tube bundles are modelled by incorporating the “porous medium” concept into the governing by: 8. Ling, JPCW, Ireland, PT, & Harvey, NW. "Measurement of Heat Transfer Coefficient Distributions and Flow Field in a Model of a Turbine Blade Cooling Passage With Tangential Injection." Proceedings of the ASME Turbo Expo Power for Land, Sea, and Air. Volume 3: Heat Transfer, Parts A and B. Barcelona, Spain. May 8–11, pp. ASME. From inside the book. exchanger heat transfer coefficient helium in-line increase inlet interface laminar length liquid film louvred mass flow rate mass transfer mass velocity measured method nucleate boiling Nusselt Nusselt number operating parameters Volume 15 of Proceedings of the International Centre for Heat and Mass Transfer. The actual maximum velocity for this application varies with heat exchanger diameter and nozzle opening sizes. Some copper tube selections may have maximum velocities as high as feet per second (FPS) while others have a maximum as low as FPS. Stainless steel and Cupro-Nickle (CuNi) velocities may go as high as 11 FPS.
Predicted results from both a network flow model and a turbulent flow model were compared with measured results from an air flow test on a half-scale model of the auxiliary heat exchanger for a high temperature gas cooled reactor. Measurements of both velocity and pressure were made within the heat exchanger shell side flow field. These measurements were compared with calculated results from. In other words, fluid velocity in a heat exchanger is normally of secondary importance - except where it can cause serious tube vibration or metal erosion. For further basic and useful information on heat exchangers (including a mention of velocity values), go to the following page on this Website, which, I believe was written by Chris Haslego. pressure drop across the heat exchanger. U-tube mercury manometers are used to measure the pressure drop across the heat exchanger. Calibration of the orifice plate has been done as per ASME standards and it is found that the average coefficient of discharge is The plate heat exchanger consists of 26 plates, which forms 25 number of cold. Heat transfer/pressure drop for different in stocks used in. The design of a heat exchanger is a complex task and requires attention to many parameters. Of utmost im portance for a liquid to air heat exchanger are the power requirements and size of the pump and fan. The design might not be practical if it results in a very low overall.
A computational fluid dynamics code is used to study the heat and moisture transfer distribution in the heat exchanger using sensible- latent effectiveness ratio Due to concerns over indoor air. HT-7 ∂ ∂−() = −= f TT kA L 2 AB TA TB 0. () In equation (), k is a proportionality factor that is a function of the material and the temperature, A is the cross-sectional area and L is the length of the bar. In the limit for any temperature difference ∆T across a length ∆x as both L, T A - . Six air flow conditions were constructed: average frontal air velocity of , , and m s −1 with uniform and non-uniform velocity distributions. The six heat exchanger test specimens in Fig. 2 were simulated in these air conditions. The simulation results are presented in Fig. 7. The heat transfer capacity decreased and the pressure. The velocity vectors and temperature distribution for a platform height m and a wind speed of m/s are shown in Figs. 2 and 3 respectively. The corresponding velocity vectors and temperature distribution for a wind speed of m/s are shown in Figs. 4 and 5 respectively. In both cases the flow through the heat exchanger was taken as uniform.