CFD ANALYSIS OF TURBULENT THERMAL MIXING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT
|
|
- Norman Baker
- 5 years ago
- Views:
Transcription
1 ISTP-6, 005, PRAGUE 6 TH INTERNATIONAL SYMPOSIUM ON TRANSPORT PHENOMENA CFD ANALYSIS OF TURBULENT THERMAL MIING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT Hideo Asano ((, Kazuhiko Suga (3, Masafumi Hirota (, Hiroshi Nakayama (, Shunsaku Hirayama ( and Yasuhiro Mizuno ( ( DENSO CORPORATION, Kariya , Japan. ( Nagoya University, Nagoya , Japan. (3 Toyota Central R & D Labs., Inc., Nagakute, Aichi 480-9, Japan. Corresponding author: hirota@mech.nagoya-u.ac.jp Phone: Fax: Keywords: Automobile air-conditioning, Turbulent thermal mixing, Planar shear layer, Second moment closure, heat flux model, Abstract The results of numerical simulations on turbulent flow and thermal mixing of hot and cold airflows in the HVAC unit used in automobile air-conditioning system are presented, and their reliability is examined by comparing them with experimental data. To simplify the problems, the thermal mixing in the HVAC unit has been modeled by the twodimensional planar turbulent mixing layer. Three turbulence models have been tested; namely, standard linear k-ε model, low-re cubic nonlinear k-ε model, and two-component-limit second moment closure (TCL SMC. For turbulent heat fluxes, prescribed turbulent Prandtl numbers are applied along with the k-ε models. TCL SMC is coupled with a generalized gradient diffusion hypothesis ( or its higher order version ( model. The results suggest that TCL SMC + ( model can predict the distributions of turbulent heat fluxes and mean temperature of the mixed flow successfully. Introduction Turbulent mixing of two flows with different velocities, temperatures and/or concentrations is encountered in many engineering applications, such as chemical reactor, piping system in power plant, combustion chamber, etc. One of the typical examples can be also found in the HVAC (Heating, Ventilating and Air- Conditioning unit used in the automobile airconditioning system []. Figure shows a schematic of the HVAC unit, in which a fan, an evaporator and a heater-core are packaged. In this unit, all air taken by the fan is once cooled down by the evaporator to reduce humidity, and a part of this cold air is heated by the heatercore. Then, hot and cold air is mixed at appropriate flow-rate ratios to control the air temperature blown into the compartment of an automobile. The temperature of the mixed airflow is determined by the flow-rate ratio of the hot and cold air, and it is controlled by the opening of the air-mix door that is settled between the evaporator and the heater-core. Thus it follows that, in the HVAC unit, the hot and cold airflows meet at various angles and various velocity ratios depending on the air temperature required in the automobile compartment. Nowadays it is strongly desired that the HVAC unit be designed virtually by making the most use of CAE to reduce the developing time. This digital engineering requires the numerical simulations of turbulent mixing of hot and cold airflows. At the present stage, however, the reliability of the calculated velocity and temperature distributions in the mixed airflow is not high enough to be directly applicable to the
2 Blower Evaporator Air-Mix Door Cold Air Cold Air Hot Air Heater Core Defroster Duct Foot Duct Face Duct Fig.. Conceptual illustration of HVAC unit design of the HVAC unit. This is because the velocity field of the mixed flow usually shows complex features, and the present turbulence models are not designed to predict it with sufficient accuracy. In addition to the problems of turbulence models, the modeling of the turbulent heat fluxes is also a key issue for improving the performance of numerical simulations of the turbulent thermal mixing encountered in the HVAC unit []. Detailed data on the flow and temperature fields in the HVAC unit are, however, quite scarce, and thus the suitability of turbulence and turbulent heat flux models for the simulation of thermal mixing process encountered in the HVAC unit has not been examined in detail yet. With these points as background, in this study, we have made numerical simulations on turbulent thermal mixing of hot and cold airflows in the HVAC unit, and examined their reliability by comparing the results with experimental data. The turbulent thermal mixing in HVAC unit has been modeled by the mixing of simple two parallel flows with different velocities and temperatures, i.e., twodimensional planar turbulent mixing layer, as shown in Fig.. We have tested three turbulence models for velocity field and they have been coupled with three turbulent heat flux models; the first turbulence model is the standard linear k-ε model and the second one is the low-reynoldsnumber cubic nonlinear k-ε model [], both of which have been coupled with prescribed turbulent Prandtl numbers for turbulent heat fluxes. The third turbulence model is the twocomponent-limit second moment closure (TCL SMC [3], which is coupled with a generalized gradient diffusion hypothesis ( [4] or its higher order version ( [5] for turbulent heat fluxes. TCL SMC is the latest version of the Reynolds stress transport model, and its usefulness has been confirmed for a few complex flows. The tested cases are, however, wall turbulence and its performance in the application to the mixing layer is not clarified yet. In this study, we compare the simulated results with measured ones [6], and evaluate the performance and suitability of these models in the application to the turbulent thermal mixing in the HVAC unit. Flow geometry As described above, in this study, the turbulent thermal mixing in the HVAC unit has been modeled by the two-dimensional planar turbulent mixing layer. Figure shows the schematic of the flow geometry. Cold airflow at T c = 30 C and hot airflow at T h = 80 C are mixed in the test section after flowing through the settling chambers, flow nozzles and developing regions. Each developing region has a cross section of 00 mm 97.5 mm, and the splitter plate that divides the hot and cold flows is 5 mm thick. The mixing section has a cross section of 00 mm 00 mm. These dimensions of the test channel were determined referring to the practical HVAC unit []. The velocity of the cold flow U c was kept at 4 m/s, and that of the hot flow U h was set at m/s and 4 m/s (velocity ratio r = U h = and, respectively. Under both velocity ratios, cold air flows in the upper half of the test channel and hot air flows in the lower half. It was confirmed that in the cold flow side a turbulent boundary layer about 5 mm thick was formed at the end of the splitter plate. The Reynolds number based on the momentum thickness of this boundary layer is about 380. Under these experimental conditions, the Richardson number is as small as , thus the influence of the buoyancy force is negligibly small. We confirmed that the velocity distribution measured under this non-isothermal condition agreed well with that obtained under the
3 CFD ANALYSIS OF TURBULENT THERMAL MIING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT Nozzle Cold air Uc, Tc Hot air Uh, Th enlarged view 5 Fig.. Test channel used in the experiment (-D mixing layer Fig. 3 Grid system used around the tip of the splitter plate isothermal condition. The coordinate system is also shown in Fig.. The mean and fluctuating velocity components in each direction are denoted as U, U and, u, respectively. T and t denote the mean and fluctuating temperatures. Details of the experiments are described in a reference [6]. In the numerical simulation, two-dimensional calculation has been made in this study. The exit of the calculation region is set at 000 mm downstream from the tip of the splitter plate to avoid the influence of the exit condition on the simulated flow field. In order to calculate the flow field just after the flow merging accurately, quite a fine grid system is formed around the tip of the splitter plate. Figure 3 shows the grid system near the splitter-plate tip used in the present numerical simulation. The number of the grid points has been changed from 5,000 to 5,000 depending on the turbulence models. The flow parameters measured at 35 mm upstream from the tip of the splitter plate have been used as the initial values of the numerical simulations Splitter plate 00 3 Turbulence models 3. Flow field Considering the computation time allowed in the practical design of HVAC unit, three kinds of RANS turbulence models for flow field have been tested in this study. The first model is the standard linear k-ε model that has been widely used in various engineering applications. The second model is the low-reynolds-number cubic nonlinear k-ε model []. This model can reproduce the anisotropy of turbulent stresses accurately and thus it is expected that the reliability of predictions of complex turbulent flows be improved. The third model is the two-component-limit second moment closure (TCL SMC [3]. This is the latest Reynolds stress transport model, and can predict the turbulence anisotropy more successfully than other models. Although its usefulness has been confirmed for a few complex flows, such as 3-D curved duct flow and turbulent obstacle flow, the tested cases are still limited to wall turbulence and its performance in the application to the free turbulence is not fully clarified yet. Recently, Suga applied this model to the turbulent mixing layer and obtained satisfactory results. Since these turbulence models need lengthy expressions, details of each turbulence model are not described in this paper: see the references for details of these models. 3. Turbulent heat fluxes The standard k-ε models and the low- Reynolds-number cubic nonlinear k-ε model adopted in this study have been combined with prescribed turbulent Prandtl numbers Pr t. This is the simplest way to express the turbulent heat fluxes. Pr t is assumed to be 0.9 for the low-re nonlinear k-ε model. Three values of Pr t, 0., and 0.9 are tested with the standard k-ε model to examine the influence of Pr t -values on the mean temperature distributions. As for TCL SMC, two turbulent heat flux models have been tested. One is a generalized gradient diffusion 3
4 hypothesis ( model [4], and the other is its high-order version (. These models are expressed as follows [5]. Pr t model: ν t Θ uiθ = ( Pr x model: Θ uiθ = cθ τ uiu j, x t i j k τ = ( ε model: Θ uiθ = cθ kτ ( σ ij + α ij (3 x uiu j uiul ulu j σ il = cσ + cσ (4 k k u lu j u jul α = Ω + Ω ij cα τ il li (5 k k U U i j Ω ij = (6 x j xi See the reference for details of the model coefficients [5]. In general, Pr t model cannot predict the turbulent heat fluxes reasonably in complex turbulent flows that have mean temperature and velocity gradients in multiple directions. In other words, this model cannot reproduce the streamwise turbulent heat flux under the fully developed thermal condition. This is because Pr t model assumes that turbulent heat flux in the i -direction u i t is generated only by the contribution of the mean temperature gradient in the i -direction, although u i t is generated by the mean temperature gradients not only in the i - direction but also in the j -directions (i j. heat flux model is generally successful in the computation of complex thermal field. It is, however, known that cannot predict the streamwise heat flux component reasonably well [5] though it is much better than Pr t. The high order version of mode, i.e., model, was developed by expanding with extra terms including a quadratic product of the Reynolds stress tensor to improve the j performance of the model. It is more effective to predict the streamwise turbulent heat flux. In general, the streamwise turbulent heat flux does not exert important influences on the mean temperature distribution in a fully developed flow. The flow in a practical HVAC unit is, however, so complex accompanied by frequent changes of its direction that the streamwise turbulent heat flux can become as important as transverse one to predict the mean temperature distribution. Since the performance of the -type heat flux models relies on the accuracy of the predicted turbulence anisotropy, and have been coupled with TCL SMC in this study. 4 Results and discussion In this paper, the results obtained with k-ε models coupled with Pr t are presented at first. Then the results of TCL SMC + ( models are shown and their performance on the prediction of thermal field in the plane turbulent mixing layer is examined in detail. 4. Flow field with k-ε models Figure 4 shows the distributions of the streamwise mean velocity U (left and the turbulent shear stress u (right obtained at the velocity ratio r = U h =. The solid line shows the results calculated by the standard (STD k-ε model, and the broken line shows those by low-reynolds-number nonlinear (LRN k-ε model. The experimental results are shown by open symbols. In this paper, the results obtained at three streamwise locations, =,.0 and.0, are presented, where D denotes a half of the side length of the mixing cross section (= 00 mm. These locations have been determined considering the size of practical HVAC units, at which the flow does not attain the self-similar state [7]. As shown in Fig. 4, the distributions of U obtained by model agree well with those by model at all, and these simulated results are in good agreement with experimental ones at all. The distributions of u are also successfully reproduced by these k-ε models, although their peak values are 4
5 CFD ANALYSIS OF TURBULENT THERMAL MIING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT = =.0 = U = =.0 =.0-0 Fig. 4. Mean velocity and turbulent shear stress distributions predicted by k-ε models (r = = r = =.0 = U Fig. 5. Mean velocity and turbulent shear stress distributions predicted by k-ε models (r = somewhat underpredicted at =. These results suggest that, at r =, the model as well as the model is good enough for predicting the flow field in the planar turbulent mixing layer. At the velocity ratio of r = shown in Fig. 5, however, the reliability of the simulated results becomes much lower than that for r =. From the U distributions shown in Fig. 5 (left, it is found that the thickness of the mixing layer is overpredicted with model and that the recovery of the velocity deficit region at =.0 is delayed in both k-ε models. As for u distributions, model generally overpredicts the experimental results, and the locations of the peak values are not well predicted by both models. As a whole, the reliability of the results obtained by model is lower than that of model under the velocity ratio of r = u *00 = =.0 =.0 r = u *00 4. Thermal field with k-ε + Pr t models At first, we show the results of the thermal fields calculated with a prescribed turbulent Prandtl number of 0.9; the flow field is calculated with two k-ε models. The results at r = are presented in Fig. 6; distributions of mean temperature (T, streamwise turbulent heat flux (T h and transverse turbulent heat flux u (T h are shown from the top of this figure. The transverse component of turbulent heat flux u t, which dominates the heat transport in the mixing layer, is underpredicted over all. Moreover, the streamwise component t, which is in almost the same level as u t in the experiment, is nearly zero in the simulations. As a result of such underpredictions of the turbulent heat fluxes, the simulation with Pr t = 0.9 tends to underpredict the development of the thermal mixing layer. The difference between the measured mean temperature and calculated one becomes larger in the region further downstream from the origin of the mixing layer. Quite similar results are obtained at r = shown in Fig. 7 and the difference between the experimental results and numerical ones is increased in comparison with the case of r =. It is thought that such an underprediction of u t as observed above can be improved by assuming smaller turbulent Prandtl number. Hence, in this study, we made the calculations with three turbulent Prantdl numbers of Pr t = 0., and 0.9. In these calculations, the standard k-ε model has been coupled with Pr t, because the reliability of the flow field predicted by model is higher than that of LRN k- ε model. Figures 8 and 9 show the results for r = and, respectively. At r =, the reliability of u t prediction is much improved with the turbulent Prandtl number of. In free turbulence, Pr t is often assumed to be in the range of 5-0.7: the result of r = supports this assumption about Pr t -value. On the other hand, at r =, the reliability of u t prediction is not improved so much by decreasing Pr t. This suggests that Pr t changes depending on the velocity field even in the relatively simple planar thermal mixing layer. 5
6 = =.0 =.0 = r = =.0 =.0 = Prt= =.0 =.0 = r = Prt= =.0 = (T = =.0 = (T = =.0 =.0 r = (T = =.0 = (T = =.0 =.0 r = = =.0 =.0 = =.0 =.0 r = Prt= = =.0 =.0.0 Prt= = =.0 =.0 r = u u Fig. 6. Thermal field Fig. 7. Thermal field by Pr t model (r = by Pr t model (r = From the results described above, it is thought that the reliability of u t prediction may be improved by giving the Pr t distributions with some appropriate functions. As for the streamwise component t, however, Pr t given by functions cannot improve the reliability of the simulated result because the streamwise temperature gradient T/, to which t is assumed to be proportional, is almost zero in the present thermal mixing layer. In order to examine the reason for such complex t distributions as obtained in the measurement, Prt= Prt= u u Fig. 8. Thermal field Fig. 9. Thermal field with different Pr t with different Pr t (r = (r = the production terms in the transport equation of t have been evaluated based on the experimental data. Figure 0 shows the distributions of each term of t production, which is expressed as follows, measured at = [6]. P T D = uu U T A, c P U ut D B = c U T U D P C = ut (7 U T c 6
7 CFD ANALYSIS OF TURBULENT THERMAL MIING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT = TCL =.0 =.0 = =.0 =.0 TCL (a r = U u *00 Fig.. Mean velocity and turbulent shear stress distributions predicted by TCL SMC (r = = r = TCL =.0 =.0 = =.0 =.0 TCL (b r = Fig. 0. Production of t It is found that the distributions of the sum of these production terms are qualitatively similar to those of t shown above. In particular, the contributions of P A and P C, both of which include the gradient of mean quantity in the transverse ( direction, are much larger than that of P B. The term including T/ was smaller than P B and its contribution to t production was negligible. From these results, it follows that the influences of U / and T/ must be included to reproduce reasonably the complex distributions of t. This is a reason for the selection of -type turbulent heat flux models to calculate the thermal field of the present mixing layer. 4.3 Results of calculation with TCL SMC + ( models In this section, the results of the velocity and temperature fields calculated by TCL SMC + ( models are compared with the experimental data. Figure shows the distributions of U and u calculated for r = with TCL SMC. The calculated results agree U u *00 Fig.. Mean velocity and turbulent shear stress distributions predicted by TCL SMC (r = well with the experimental ones, although a slight delay of the recovery of the velocity deficit region is observed in U distributions. Figure shows the results for r =. The difference between the calculated distributions of u and measured ones is increased in comparison with that for r = ; in particular, u is underpredicted in a downstream region. From a comparison of Fig. with Fig. 5, however, it is understood that the reliability of the flow field calculated by TCL SMC is improved in comparison with the k-ε models. Thus, it follows that the difference between the numerical results of the thermal field shown below and those shown in Figs. 6-9 reflects the performance of both the turbulence model and turbulent heat flux model. Next, the thermal field is examined. Similar to Figs. 6-9, the distributions of the mean temperature, turbulent heat fluxes t and u t are compared with the experimental results. Figure 3 shows the results at r =. The values of t 7
8 = =.0 = (T (T = =.0 = = =.0 =.0 = r = =.0 = u u Fig. 3. Thermal field Fig. 4. Thermal field by ( model by ( model (r = (r = calculated with are slightly smaller than the experimental results at =, but they agree well with the measured values in a further downstream region. The higher-order version of, i.e.,, generally overpredicts t. These results show that model can predict the t distribution far more successfully than Pr t model. This is because -type turbulent heat flux model can incorporate the contribution of T/ into the formulation of t. As to u t, the difference = r = =.0 =.0 = =.0 =.0 r = between and is quite smaller than that for t. Both models underpredict the values of u t near the origin of the mixing layer, but the difference between the measured and calculated values becomes smaller in the downstream region. The reliability of u t calculated by and models is higher than that obtained with the prescribed Pr t model. As a result of such improvement in the calculation of turbulent heat fluxes, the distributions of the mean temperature at r =, shown at the top of Fig. 3, are more successfully reproduced by ( models than the Pr t model. Figure 4 shows the results at r =. Although the qualitative features of t distributions are well captured by both type models, generally overpredicts t as is the case with r = while underpredicts it. On the other hand, u t is underpredicted by both -type models in the region of > ; the disagreement between the experimental and numerical results is increased than the case of r =. This tendency is similar to that calculated with k-ε + Pr t models, but as a whole ( models can reproduce the distributions of u t with higher accuracy than the prescribed Pr t model. Similar to the case of r =, the reliability of the mean temperature distributions predicted by ( models is improved in comparison with the Pr t model, although the difference between measured and calculated values is somewhat increased in comparison with that for r =. Here it should be noted that the TCL SMC and ( models tested in this study were originally developed to the prediction of turbulent heat transfer in complex wall shear flows such as 3-D curved duct [5]. Thus, the model coefficients were optimized referring to the experimental data or DNS results in those flows. In the present study, the original models are used without any modifications. Since the characteristics of the present flow geometry are quite different from those of the wall turbulence, the performance of the predictions may be improved by adjusting the model coefficients to the mixing layer. In the numerical simulations 8
9 CFD ANALYSIS OF TURBULENT THERMAL MIING OF HOT AND COLD AIR IN AUTOMOBILE HVAC UNIT of turbulent thermal mixing in the HVAC unit, another important point is the computation time. It should be noted that the CPU time needed to attain the final result by TCL SMC + model was about three times as long as that for standard k-ε + Pr t model; this is within the scope of practical use. 4 Conclusions The numerical simulations of turbulent thermal mixing in a planar shear layer have been conducted, which simulates the mixing of hot and cold airflows in the HVAC unit used for automobile air-conditioning system. We have tested three turbulence models: standard k-ε model, low-re nonlinear k-ε model and TCL SMC. The first two k-ε models have been coupled with prescribed Pr t, and TCL SMC has been combined with model and its higher-order version for turbulent heat fluxes. By optimizing the Pr t -values, the k-ε + Pr t models can predict the distributions of u t with a sufficient accuracy at r =, but the reliability of u t prediction becomes lower at r =. The Pr t model cannot reproduce the t distributions in principle, and the reliability of the predicted mean temperature distributions is insufficient. TCL SMC + ( models can reasonably reproduce the turbulent heat fluxes and successfully predict the mean temperature distributions in the mixing layer. These results suggest that TCL SMC + ( models have high potential to the prediction of turbulent thermal mixing encountered in the HVAC unit for automobiles. [5] Suga, K. Predicting Turbulence and Heat Transfer in 3-D Curved Ducts by Near-Wall Second Moment Closures, Int. J. Heat Mass Transfer, Vol. 46, pp. 6 73, 003. [6] Asano, H., Hirota, M., Nakayama, H., Mizuno, Y. and Hirayama, S. Turbulent Thermal Mixing of Hot and Cold Air in Planar Shear Layer (Thermal Mixing in Automobile HVAC Unit, Proc. 6th World Conf. Exp. Heat Transfer, Fluid Mech., Thermodynamics, 3-a-3, Matsushima, Japan, 005 (in CD-ROM. [7] Abdul Asim, M. and Sadrul Islam, A. K. M. Plane Mixing Layers from Parallel and Non-Parallel Merging of Two Streams, Exp. in Fluids, Vol. 34, pp. 0-6, 003. References [] Kitada, M., Asano, H., Kanbara, M. and Akaike, S. Development of Automotive Air-Conditioning System Basic Performance Simulator: CFD Technique Development. JSAE Review, Vol., pp. 9-96, 000. [] Craft, T.J., Launder, B.E. and Suga, K. Development and Application of a Cubic Eddy-Viscosity Model of Turbulence. Int. J. Heat Fluid Flow, Vol. 7, pp. 08-5, 996. [3] Suga, K. Modeling Pressure-Transport for Turbulent Wake Flows. Proc. Turbulence Shear Flow Phenomena-3, Sendai, Japan, pp , 003. [4] Daly, B.J. and Harlow, F.H. Transport equation in turbulence. Phys. Fluid, Vol. 3, pp ,
Journal of Fluid Science and Technology
Bulletin of the JSME Vol.9, No.3, 24 Journal of Fluid Science and Technology Promotion and control of turbulent mixing of hot and cold airflows in T-junction Takuya MATSUDA*, Masafumi HIROTA*, Hideo ASANO**,
More informationConjugate heat transfer from an electronic module package cooled by air in a rectangular duct
Conjugate heat transfer from an electronic module package cooled by air in a rectangular duct Hideo Yoshino a, Motoo Fujii b, Xing Zhang b, Takuji Takeuchi a, and Souichi Toyomasu a a) Fujitsu Kyushu System
More informationNUMERICAL AND EXPERIMENTAL INVESTIGATIONS OF AIR FLOW AND TEMPERATURE PATTERNS OF A LOW VELOCITY DIFFUSER
NUMERICAL AND EXPERIMENTAL INVESTIGATIONS OF AIR FLOW AND TEMPERATURE PATTERNS OF A LOW VELOCITY DIFFUSER M Cehlin and B Moshfegh Division of Energy and Mechanical Engineering, Department of Technology,
More informationThe Effect of Endplates on Rectangular Jets of Different Aspect Ratios
The Effect of Endplates on Rectangular Jets of Different Aspect Ratios M. Alnahhal *, Th. Panidis Laboratory of Applied Thermodynamics, Mechanical Engineering and Aeronautics Department, University of
More informationLarge Eddy Simulation as a Powerful Engineering Tool for Predicting Complex Turbulent Flows and Related Phenomena
29 Review Large Eddy Simulation as a Powerful Engineering Tool for Predicting Complex Turbulent Flows and Related Phenomena Masahide Inagaki Abstract Computational Fluid Dynamics (CFD) has been applied
More informationTurbulence Modeling I!
Outline! Turbulence Modeling I! Grétar Tryggvason! Spring 2010! Why turbulence modeling! Reynolds Averaged Numerical Simulations! Zero and One equation models! Two equations models! Model predictions!
More informationRANS simulations of rotating flows
Center for Turbulence Research Annual Research Briefs 1999 257 RANS simulations of rotating flows By G. Iaccarino, A. Ooi, B. A. Pettersson Reif AND P. Durbin 1. Motivation and objectives Numerous experimental
More informationA TURBULENT HEAT FLUX TWO EQUATION θ 2 ε θ CLOSURE BASED ON THE V 2F TURBULENCE MODEL
TASK QUARTERLY 7 No 3 (3), 375 387 A TURBULENT HEAT FLUX TWO EQUATION θ ε θ CLOSURE BASED ON THE V F TURBULENCE MODEL MICHAŁ KARCZ AND JANUSZ BADUR Institute of Fluid-Flow Machinery, Polish Academy of
More informationNONLINEAR FEATURES IN EXPLICIT ALGEBRAIC MODELS FOR TURBULENT FLOWS WITH ACTIVE SCALARS
June - July, 5 Melbourne, Australia 9 7B- NONLINEAR FEATURES IN EXPLICIT ALGEBRAIC MODELS FOR TURBULENT FLOWS WITH ACTIVE SCALARS Werner M.J. Lazeroms () Linné FLOW Centre, Department of Mechanics SE-44
More informationNumerical simulations of heat transfer in plane channel flow
Numerical simulations of heat transfer in plane channel flow Najla EL GHARBI 1, 3, a, Rafik ABSI 2, b and Ahmed BENZAOUI 3, c 1 Renewable Energy Development Center, BP 62 Bouzareah 163 Algiers, Algeria
More informationTheoretical and Experimental Studies on Transient Heat Transfer for Forced Convection Flow of Helium Gas over a Horizontal Cylinder
326 Theoretical and Experimental Studies on Transient Heat Transfer for Forced Convection Flow of Helium Gas over a Horizontal Cylinder Qiusheng LIU, Katsuya FUKUDA and Zheng ZHANG Forced convection transient
More informationDIRECT NUMERICAL SIMULATION OF SPATIALLY DEVELOPING TURBULENT BOUNDARY LAYER FOR SKIN FRICTION DRAG REDUCTION BY WALL SURFACE-HEATING OR COOLING
DIRECT NUMERICAL SIMULATION OF SPATIALLY DEVELOPING TURBULENT BOUNDARY LAYER FOR SKIN FRICTION DRAG REDUCTION BY WALL SURFACE-HEATING OR COOLING Yukinori Kametani Department of mechanical engineering Keio
More informationCFD Analysis for Thermal Behavior of Turbulent Channel Flow of Different Geometry of Bottom Plate
International Journal Of Engineering Research And Development e-issn: 2278-067X, p-issn: 2278-800X, www.ijerd.com Volume 13, Issue 9 (September 2017), PP.12-19 CFD Analysis for Thermal Behavior of Turbulent
More informationNumerical Simulation of Turbulent Buoyant Helium Plume by Algebraic Turbulent Mass Flux Model
Numerical Simulation of Turbulent Buoyant Helium Plume by Algebraic Turbulent Mass Flux Model Hitoshi Sugiyama 1),Naoto Kato 1), Masahiro Ouchi 1) 1) Graduate School of Engineering,Utsunomiya University
More informationCOMPUTATIONAL FLUID DYNAMICS ANALYSIS OF A V-RIB WITH GAP ROUGHENED SOLAR AIR HEATER
THERMAL SCIENCE: Year 2018, Vol. 22, No. 2, pp. 963-972 963 COMPUTATIONAL FLUID DYNAMICS ANALYSIS OF A V-RIB WITH GAP ROUGHENED SOLAR AIR HEATER by Jitesh RANA, Anshuman SILORI, Rajesh MAITHANI *, and
More informationInternational Journal of Scientific & Engineering Research, Volume 6, Issue 5, May ISSN
International Journal of Scientific & Engineering Research, Volume 6, Issue 5, May-2015 28 CFD BASED HEAT TRANSFER ANALYSIS OF SOLAR AIR HEATER DUCT PROVIDED WITH ARTIFICIAL ROUGHNESS Vivek Rao, Dr. Ajay
More informationTable of Contents. Foreword... xiii. Preface... xv
Table of Contents Foreword.... xiii Preface... xv Chapter 1. Fundamental Equations, Dimensionless Numbers... 1 1.1. Fundamental equations... 1 1.1.1. Local equations... 1 1.1.2. Integral conservation equations...
More informationBOUNDARY LAYER FLOWS HINCHEY
BOUNDARY LAYER FLOWS HINCHEY BOUNDARY LAYER PHENOMENA When a body moves through a viscous fluid, the fluid at its surface moves with it. It does not slip over the surface. When a body moves at high speed,
More informationPrinciples of Convection
Principles of Convection Point Conduction & convection are similar both require the presence of a material medium. But convection requires the presence of fluid motion. Heat transfer through the: Solid
More informationNumerical investigation of swirl flow inside a supersonic nozzle
Advances in Fluid Mechanics IX 131 Numerical investigation of swirl flow inside a supersonic nozzle E. Eslamian, H. Shirvani & A. Shirvani Faculty of Science and Technology, Anglia Ruskin University, UK
More informationComputation of turbulent natural convection with buoyancy corrected second moment closure models
Computation of turbulent natural convection with buoyancy corrected second moment closure models S. Whang a, H. S. Park a,*, M. H. Kim a, K. Moriyama a a Division of Advanced Nuclear Engineering, POSTECH,
More informationComparison of Turbulence Models in the Flow over a Backward-Facing Step Priscila Pires Araujo 1, André Luiz Tenório Rezende 2
Comparison of Turbulence Models in the Flow over a Backward-Facing Step Priscila Pires Araujo 1, André Luiz Tenório Rezende 2 Department of Mechanical and Materials Engineering, Military Engineering Institute,
More information2.3 The Turbulent Flat Plate Boundary Layer
Canonical Turbulent Flows 19 2.3 The Turbulent Flat Plate Boundary Layer The turbulent flat plate boundary layer (BL) is a particular case of the general class of flows known as boundary layer flows. The
More informationConvective Mass Transfer
Convective Mass Transfer Definition of convective mass transfer: The transport of material between a boundary surface and a moving fluid or between two immiscible moving fluids separated by a mobile interface
More informationProblem 4.3. Problem 4.4
Problem 4.3 Problem 4.4 Problem 4.5 Problem 4.6 Problem 4.7 This is forced convection flow over a streamlined body. Viscous (velocity) boundary layer approximations can be made if the Reynolds number Re
More informationLarge eddy simulation of turbulent flow over a backward-facing step: effect of inflow conditions
June 30 - July 3, 2015 Melbourne, Australia 9 P-26 Large eddy simulation of turbulent flow over a backward-facing step: effect of inflow conditions Jungwoo Kim Department of Mechanical System Design Engineering
More informationThe mean shear stress has both viscous and turbulent parts. In simple shear (i.e. U / y the only non-zero mean gradient):
8. TURBULENCE MODELLING 1 SPRING 2019 8.1 Eddy-viscosity models 8.2 Advanced turbulence models 8.3 Wall boundary conditions Summary References Appendix: Derivation of the turbulent kinetic energy equation
More informationAER1310: TURBULENCE MODELLING 1. Introduction to Turbulent Flows C. P. T. Groth c Oxford Dictionary: disturbance, commotion, varying irregularly
1. Introduction to Turbulent Flows Coverage of this section: Definition of Turbulence Features of Turbulent Flows Numerical Modelling Challenges History of Turbulence Modelling 1 1.1 Definition of Turbulence
More informationFINITE ELEMENT ANALYSIS OF MIXED CONVECTION HEAT TRANSFER ENHANCEMENT OF A HEATED SQUARE HOLLOW CYLINDER IN A LID-DRIVEN RECTANGULAR ENCLOSURE
Proceedings of the International Conference on Mechanical Engineering 2011 (ICME2011) 18-20 December 2011, Dhaka, Bangladesh ICME11-TH-014 FINITE ELEMENT ANALYSIS OF MIXED CONVECTION HEAT TRANSFER ENHANCEMENT
More informationCHAPTER 7 NUMERICAL MODELLING OF A SPIRAL HEAT EXCHANGER USING CFD TECHNIQUE
CHAPTER 7 NUMERICAL MODELLING OF A SPIRAL HEAT EXCHANGER USING CFD TECHNIQUE In this chapter, the governing equations for the proposed numerical model with discretisation methods are presented. Spiral
More informationOn the transient modelling of impinging jets heat transfer. A practical approach
Turbulence, Heat and Mass Transfer 7 2012 Begell House, Inc. On the transient modelling of impinging jets heat transfer. A practical approach M. Bovo 1,2 and L. Davidson 1 1 Dept. of Applied Mechanics,
More informationProcess Chemistry Toolbox - Mixing
Process Chemistry Toolbox - Mixing Industrial diffusion flames are turbulent Laminar Turbulent 3 T s of combustion Time Temperature Turbulence Visualization of Laminar and Turbulent flow http://www.youtube.com/watch?v=kqqtob30jws
More informationASSESSMENT OF ANISOTROPY IN THE NEAR FIELD OF A RECTANGULAR TURBULENT JET
TUR-3 ExHFT-7 8 June 03 July 009, Krakow, Poland ASSESSMENT OF ANISOTROPY IN THE NEAR FIELD OF A RECTANGULAR TURBULENT JET Α. Cavo 1, G. Lemonis, T. Panidis 1, * 1 Laboratory of Applied Thermodynamics,
More informationLARGE EDDY SIMULATION OF MASS TRANSFER ACROSS AN AIR-WATER INTERFACE AT HIGH SCHMIDT NUMBERS
The 6th ASME-JSME Thermal Engineering Joint Conference March 6-, 3 TED-AJ3-3 LARGE EDDY SIMULATION OF MASS TRANSFER ACROSS AN AIR-WATER INTERFACE AT HIGH SCHMIDT NUMBERS Akihiko Mitsuishi, Yosuke Hasegawa,
More informationA Discussion of Low Reynolds Number Flow for the Two-Dimensional Benchmark Test Case
A Discussion of Low Reynolds Number Flow for the Two-Dimensional Benchmark Test Case M. Weng, P. V. Nielsen and L. Liu Aalborg University Introduction. The use of CFD in ventilation research has arrived
More informationNUMERICAL SIMULATION OF CONJUGATE HEAT TRANSFER FROM MULTIPLE ELECTRONIC MODULE PACKAGES COOLED BY AIR
Proceedings of IPACK03 International Electronic Packaging Technical Conference and Exhibition July 6 11 2003 Maui Hawaii USA InterPack2003-35144 NUMERICAL SIMULATION OF CONJUGATE HEAT TRANSFER FROM MULTIPLE
More informationNUMERICAL SIMULATION OF LDI COMBUSTOR WITH DISCRETE-JET SWIRLERS USING RE-STRESS MODEL IN THE KIVA CODE
NUMERICAL SIMULATION OF LDI COMBUSTOR WITH DISCRETE-JET SWIRLERS USING RE-STRESS MODEL IN THE KIVA CODE S. L. Yang, C. Y. Teo, and Y. K. Siow Department of Mechanical Engineering Engineering Mechanics
More informationcompression corner flows with high deflection angle, for example, the method cannot predict the location
4nd AIAA Aerospace Sciences Meeting and Exhibit 5-8 January 4, Reno, Nevada Modeling the effect of shock unsteadiness in shock-wave/ turbulent boundary layer interactions AIAA 4-9 Krishnendu Sinha*, Krishnan
More informationIntroduction to Turbulence and Turbulence Modeling
Introduction to Turbulence and Turbulence Modeling Part I Venkat Raman The University of Texas at Austin Lecture notes based on the book Turbulent Flows by S. B. Pope Turbulent Flows Turbulent flows Commonly
More informationOn stably stratified homogeneous shear flows subjected to rotation
Center for Turbulence Research Proceedings of the Summer Program 2000 241 On stably stratified homogeneous shear flows subjected to rotation By B. A. Pettersson Reif, A.Ooi AND P. A. Durbin Theoretical
More informationO. A Survey of Critical Experiments
O. A Survey of Critical Experiments 1 (A) Visualizations of Turbulent Flow Figure 1: Van Dyke, Album of Fluid Motion #152. Generation of turbulence by a grid. Smoke wires show a uniform laminar stream
More informationNumerical Heat and Mass Transfer
Master Degree in Mechanical Engineering Numerical Heat and Mass Transfer 15-Convective Heat Transfer Fausto Arpino f.arpino@unicas.it Introduction In conduction problems the convection entered the analysis
More informationExplicit algebraic Reynolds stress models for internal flows
5. Double Circular Arc (DCA) cascade blade flow, problem statement The second test case deals with a DCA compressor cascade, which is considered a severe challenge for the CFD codes, due to the presence
More informationLES of wind turbulence and heat environment around dense tall buildings
EACWE 5 Florence, Italy 19 th 23 rd July 2009 LES of wind turbulence and heat environment around dense tall buildings Flying Sphere image Museo Ideale L. Da Vinci Tsuyoshi Nozu 1, Takeshi Kishida 2, Tetsuro
More informationPerformance characteristics of turbo blower in a refuse collecting system according to operation conditions
Journal of Mechanical Science and Technology 22 (2008) 1896~1901 Journal of Mechanical Science and Technology www.springerlink.com/content/1738-494x DOI 10.1007/s12206-008-0729-6 Performance characteristics
More informationComputation of turbulent natural convection at vertical walls using new wall functions
Computation of turbulent natural convection at vertical alls using ne all functions M. Hölling, H. Herig Institute of Thermo-Fluid Dynamics Hamburg University of Technology Denickestraße 17, 2173 Hamburg,
More informationNumerical Modelling of the Interaction Between Water Sprays and Hot Air Jets - Part I: Gas Phase Large Eddy Simulations
Numerical Modelling of the Interaction Between Water Sprays and Hot Air Jets - Part I: Gas Phase Large Eddy Simulations Tarek Beji, Georgios Maragkos, Setareh Ebrahimzadeh, Bart Merci Department of Flow,
More informationBoundary-Layer Theory
Hermann Schlichting Klaus Gersten Boundary-Layer Theory With contributions from Egon Krause and Herbert Oertel Jr. Translated by Katherine Mayes 8th Revised and Enlarged Edition With 287 Figures and 22
More informationHeat Transfer from An Impingement Jet onto A Heated Half-Prolate Spheroid Attached to A Heated Flat Plate
1 nd International Conference on Environment and Industrial Innovation IPCBEE vol.35 (1) (1) IACSIT Press, Singapore Heat Transfer from An Impingement Jet onto A Heated Half-Prolate Spheroid Attached to
More informationAIJ COOPERATIVE PROJECT FOR PRACTICAL APPLICATIONS OF CFD TO URBAN VENTILATION
The Seventh Asia-Pacific Conference on Wind Engineering, November 8-2, 29, Taipei, Taiwan AIJ COOPERATIVE PROJECT FOR PRACTICAL APPLICATIONS OF CFD TO URBAN VENTILATION Ryuichiro Yoshie, Akashi Mochida
More informationAn alternative turbulent heat flux modelling for gas turbine cooling application
TRANSACTIONS OF THE INSTITUTE OF FLUID-FLOW MACHINERY No. 3, 23, 2-?? MICHAŁ KARCZ and JANUSZ BADUR An alternative turbulent heat flux modelling for gas turbine cooling application Institute of Fluid-Flow
More informationOn modeling pressure diusion. in non-homogeneous shear ows. By A. O. Demuren, 1 M. M. Rogers, 2 P. Durbin 3 AND S. K. Lele 3
Center for Turbulence Research Proceedings of the Summer Program 1996 63 On modeling pressure diusion in non-homogeneous shear ows By A. O. Demuren, 1 M. M. Rogers, 2 P. Durbin 3 AND S. K. Lele 3 New models
More informationTurbulent Natural Convection in an Enclosure with Colliding Boundary Layers
Turbulent Natural Convection in an Enclosure with Colliding Boundary Layers Abstract Mutuguta John Wanau 1* 1. School of Pure and Applied Sciences, Murang a University of Technology, P.O box 75-10200,
More informationComputation of turbulent Prandtl number for mixed convection around a heated cylinder
Center for Turbulence Research Annual Research Briefs 2010 295 Computation of turbulent Prandtl number for mixed convection around a heated cylinder By S. Kang AND G. Iaccarino 1. Motivation and objectives
More informationTurbulence - Theory and Modelling GROUP-STUDIES:
Lund Institute of Technology Department of Energy Sciences Division of Fluid Mechanics Robert Szasz, tel 046-0480 Johan Revstedt, tel 046-43 0 Turbulence - Theory and Modelling GROUP-STUDIES: Turbulence
More informationarxiv: v1 [physics.flu-dyn] 11 Oct 2012
Low-Order Modelling of Blade-Induced Turbulence for RANS Actuator Disk Computations of Wind and Tidal Turbines Takafumi Nishino and Richard H. J. Willden ariv:20.373v [physics.flu-dyn] Oct 202 Abstract
More informationTurbulent Boundary Layers & Turbulence Models. Lecture 09
Turbulent Boundary Layers & Turbulence Models Lecture 09 The turbulent boundary layer In turbulent flow, the boundary layer is defined as the thin region on the surface of a body in which viscous effects
More informationProbability density function (PDF) methods 1,2 belong to the broader family of statistical approaches
Joint probability density function modeling of velocity and scalar in turbulence with unstructured grids arxiv:6.59v [physics.flu-dyn] Jun J. Bakosi, P. Franzese and Z. Boybeyi George Mason University,
More informationTutorial School on Fluid Dynamics: Aspects of Turbulence Session I: Refresher Material Instructor: James Wallace
Tutorial School on Fluid Dynamics: Aspects of Turbulence Session I: Refresher Material Instructor: James Wallace Adapted from Publisher: John S. Wiley & Sons 2002 Center for Scientific Computation and
More informationUNIT II CONVECTION HEAT TRANSFER
UNIT II CONVECTION HEAT TRANSFER Convection is the mode of heat transfer between a surface and a fluid moving over it. The energy transfer in convection is predominately due to the bulk motion of the fluid
More informationChapter 3 NATURAL CONVECTION
Fundamentals of Thermal-Fluid Sciences, 3rd Edition Yunus A. Cengel, Robert H. Turner, John M. Cimbala McGraw-Hill, 2008 Chapter 3 NATURAL CONVECTION Mehmet Kanoglu Copyright The McGraw-Hill Companies,
More informationCalculations on a heated cylinder case
Calculations on a heated cylinder case J. C. Uribe and D. Laurence 1 Introduction In order to evaluate the wall functions in version 1.3 of Code Saturne, a heated cylinder case has been chosen. The case
More information6.2 Governing Equations for Natural Convection
6. Governing Equations for Natural Convection 6..1 Generalized Governing Equations The governing equations for natural convection are special cases of the generalized governing equations that were discussed
More informationConvection. forced convection when the flow is caused by external means, such as by a fan, a pump, or atmospheric winds.
Convection The convection heat transfer mode is comprised of two mechanisms. In addition to energy transfer due to random molecular motion (diffusion), energy is also transferred by the bulk, or macroscopic,
More informationStudy of Forced and Free convection in Lid driven cavity problem
MIT Study of Forced and Free convection in Lid driven cavity problem 18.086 Project report Divya Panchanathan 5-11-2014 Aim To solve the Navier-stokes momentum equations for a lid driven cavity problem
More informationNumerical modeling of complex turbulent flows
ISTP-16, 5, PRAGUE 16 TH INTERNATIONAL SYMPOSIUM ON TRANSPORT PHENOMENA Numerical modeling of complex turbulent flows Karel Kozel Petr Louda Jaromír Příhoda Dept. of Technical Mathematics CTU Prague, Karlovo
More informationarxiv:physics/ v2 [physics.flu-dyn] 3 Jul 2007
Leray-α model and transition to turbulence in rough-wall boundary layers Alexey Cheskidov Department of Mathematics, University of Michigan, Ann Arbor, Michigan 4819 arxiv:physics/6111v2 [physics.flu-dyn]
More informationNUMERICAL SIMULATION OF TRANSITIONAL FLOWS WITH LAMINAR KINETIC ENERGY
Engineering MECHANICS, Vol. 20, 2013, No. 5, p. 379 388 379 NUMERICAL SIMULATION OF TRANSITIONAL FLOWS WITH LAMINAR KINETIC ENERGY JiříFürst* The article deals with the numerical solution of transitional
More informationSTRESS TRANSPORT MODELLING 2
STRESS TRANSPORT MODELLING 2 T.J. Craft Department of Mechanical, Aerospace & Manufacturing Engineering UMIST, Manchester, UK STRESS TRANSPORT MODELLING 2 p.1 Introduction In the previous lecture we introduced
More informationAdvanced near-wall heat transfer modeling for in-cylinder flows
International Multidimensional Engine Modeling User s Group Meeting at the SAE Congress April 20, 2015 Detroit, MI S. Šarić, B. Basara AVL List GmbH Advanced near-wall heat transfer modeling for in-cylinder
More informationInclined slot jet impinging on a moving wall
Ninth International Conference on Computational Fluid Dynamics (ICCFD9), Istanbul, Turkey, July -, ICCFD9-xxxx Inclined slot et impinging on a moving wall Benmouhoub Dahbia & Mataoui Amina USTHB, Laboratoire
More informationFluid Mechanics. Chapter 9 Surface Resistance. Dr. Amer Khalil Ababneh
Fluid Mechanics Chapter 9 Surface Resistance Dr. Amer Khalil Ababneh Wind tunnel used for testing flow over models. Introduction Resistances exerted by surfaces are a result of viscous stresses which create
More informationFluid Flow and Heat Transfer of Combined Forced-Natural Convection around Vertical Plate Placed in Vertical Downward Flow of Water
Advanced Experimental Mechanics, Vol.2 (2017), 41-46 Copyright C 2017 JSEM Fluid Flow and Heat Transfer of Combined Forced-Natural Convection around Vertical Plate Placed in Vertical Downward Flow of Water
More informationAn evaluation of a conservative fourth order DNS code in turbulent channel flow
Center for Turbulence Research Annual Research Briefs 2 2 An evaluation of a conservative fourth order DNS code in turbulent channel flow By Jessica Gullbrand. Motivation and objectives Direct numerical
More informationStudies on flow through and around a porous permeable sphere: II. Heat Transfer
Studies on flow through and around a porous permeable sphere: II. Heat Transfer A. K. Jain and S. Basu 1 Department of Chemical Engineering Indian Institute of Technology Delhi New Delhi 110016, India
More informationTurbulence Laboratory
Objective: CE 319F Elementary Mechanics of Fluids Department of Civil, Architectural and Environmental Engineering The University of Texas at Austin Turbulence Laboratory The objective of this laboratory
More informationLecture 30 Review of Fluid Flow and Heat Transfer
Objectives In this lecture you will learn the following We shall summarise the principles used in fluid mechanics and heat transfer. It is assumed that the student has already been exposed to courses in
More information+ = + t x x x x u. The standard Smagorinsky model has been used in the work to provide the closure for the subgridscale eddy viscosity in (2):
International Conference on Methods of Aerophysical Research, ICMAR 008 LARGE EDDY SIMULATION OF TURBULENT ROUND IMPINGING JET B.B. Ilyushin, D.V. Krasinsky Kutateladze Institute of Thermophysics SB RAS
More informationUncertainty quantification for RANS simulation of flow over a wavy wall
Uncertainty quantification for RANS simulation of flow over a wavy wall Catherine Gorlé 1,2,3, Riccardo Rossi 1,4, and Gianluca Iaccarino 1 1 Center for Turbulence Research, Stanford University, Stanford,
More informationCFD STUDIES IN THE PREDICTION OF THERMAL STRIPING IN AN LMFBR
CFD STUDIES IN THE PREDICTION OF THERMAL STRIPING IN AN LMFBR K. Velusamy, K. Natesan, P. Selvaraj, P. Chellapandi, S. C. Chetal, T. Sundararajan* and S. Suyambazhahan* Nuclear Engineering Group Indira
More informationSimultaneous Velocity and Concentration Measurements of a Turbulent Jet Mixing Flow
Simultaneous Velocity and Concentration Measurements of a Turbulent Jet Mixing Flow HUI HU, a TETSUO SAGA, b TOSHIO KOBAYASHI, b AND NOBUYUKI TANIGUCHI b a Department of Mechanical Engineering, Michigan
More informationHEAT TRANSFER IN A RECIRCULATION ZONE AT STEADY-STATE AND OSCILLATING CONDITIONS - THE BACK FACING STEP TEST CASE
HEAT TRANSFER IN A RECIRCULATION ZONE AT STEADY-STATE AND OSCILLATING CONDITIONS - THE BACK FACING STEP TEST CASE A.K. Pozarlik 1, D. Panara, J.B.W. Kok 1, T.H. van der Meer 1 1 Laboratory of Thermal Engineering,
More informationTurbulence and its modelling. Outline. Department of Fluid Mechanics, Budapest University of Technology and Economics.
Outline Department of Fluid Mechanics, Budapest University of Technology and Economics October 2009 Outline Outline Definition and Properties of Properties High Re number Disordered, chaotic 3D phenomena
More informationNumerical Simulations And Laboratory Measurements In Hydraulic Jumps
City University of New York (CUNY) CUNY Academic Works International Conference on Hydroinformatics 8-1-2014 Numerical Simulations And Laboratory Measurements In Hydraulic Jumps Luis G. Castillo José M.
More informationNumerical simulations of the edge tone
Numerical simulations of the edge tone I. Vaik, G. Paál Department of Hydrodynamic Systems, Budapest University of Technology and Economics, P.O. Box 91., 1521 Budapest, Hungary, {vaik, paal}@vizgep.bme.hu
More informationSecondary vortices in turbulent square duct flow
Secondary vortices in turbulent square duct flow A. Bottaro, H. Soueid & B. Galletti DIAM, Università di Genova & DIASP, Politecnico di Torino Goal: hydrodynamic stability based approach to make progress
More informationConvection in Three-Dimensional Separated and Attached Flow
Convection in Three-Dimensional Separated and Attached Flow B. F. Armaly Convection Heat Transfer Laboratory Department of Mechanical and Aerospace Engineering, and Engineering Mechanics University of
More informationmeters, we can re-arrange this expression to give
Turbulence When the Reynolds number becomes sufficiently large, the non-linear term (u ) u in the momentum equation inevitably becomes comparable to other important terms and the flow becomes more complicated.
More informationBefore we consider two canonical turbulent flows we need a general description of turbulence.
Chapter 2 Canonical Turbulent Flows Before we consider two canonical turbulent flows we need a general description of turbulence. 2.1 A Brief Introduction to Turbulence One way of looking at turbulent
More informationNumerical Simulation of Rocket Engine Internal Flows
Numerical Simulation of Rocket Engine Internal Flows Project Representative Masao Furukawa Authors Taro Shimizu Nobuhiro Yamanishi Chisachi Kato Nobuhide Kasagi Institute of Space Technology and Aeronautics,
More informationVALIDATION OF LES FOR LOCAL HEAT ENVIRONMENT IN TOKYO -COMPARISON WITH FIELD MEASUREMENT DATA-
The Seventh Asia-Pacific Conference on Wind Engineering, November 8-12, 29, Taipei, Taiwan VALIDATION OF LES FOR LOCAL HEAT ENVIRONMENT IN TOKYO -COMPARISON WITH FIELD MEASUREMENT DATA- Tsuyoshi Nozu 1,
More informationA Computational Investigation of a Turbulent Flow Over a Backward Facing Step with OpenFOAM
206 9th International Conference on Developments in esystems Engineering A Computational Investigation of a Turbulent Flow Over a Backward Facing Step with OpenFOAM Hayder Al-Jelawy, Stefan Kaczmarczyk
More informationAir Flow Modeling in a Mechanically Ventilated Room
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2008 Air Flow Modeling in a Mechanically Ventilated Room T. P. Ashok Babu National
More informationModeling Complex Flows! Direct Numerical Simulations! Computational Fluid Dynamics!
http://www.nd.edu/~gtryggva/cfd-course/! Modeling Complex Flows! Grétar Tryggvason! Spring 2011! Direct Numerical Simulations! In direct numerical simulations the full unsteady Navier-Stokes equations
More informationAvailable online at ScienceDirect. Procedia Engineering 90 (2014 )
Available online at www.sciencedirect.com ScienceDirect Procedia Engineering 9 (214 ) 599 64 1th International Conference on Mechanical Engineering, ICME 213 Validation criteria for DNS of turbulent heat
More informationLarge eddy simulation of a forced round turbulent buoyant plume in neutral surroundings
Center for Turbulence Research Annual Research Briefs 1999 239 Large eddy simulation of a forced round turbulent buoyant plume in neutral surroundings By A. J. Basu AND N. N. Mansour 1. Motivation and
More informationENGINEERING MECHANICS 2012 pp Svratka, Czech Republic, May 14 17, 2012 Paper #195
. 18 m 2012 th International Conference ENGINEERING MECHANICS 2012 pp. 309 315 Svratka, Czech Republic, May 14 17, 2012 Paper #195 NUMERICAL SIMULATION OF TRANSITIONAL FLOWS WITH LAMINAR KINETIC ENERGY
More informationA NUMERICAL ANALYSIS OF COMBUSTION PROCESS IN AN AXISYMMETRIC COMBUSTION CHAMBER
SCIENTIFIC RESEARCH AND EDUCATION IN THE AIR FORCE-AFASES 2016 A NUMERICAL ANALYSIS OF COMBUSTION PROCESS IN AN AXISYMMETRIC COMBUSTION CHAMBER Alexandru DUMITRACHE*, Florin FRUNZULICA ** *Institute of
More informationGÖRTLER VORTICES AND THEIR EFFECT ON HEAT TRANSFER
ISTP-6, 2005, PRAGUE 6 TH INTERNATIONAL SYMPOSIUM ON TRANSPORT PHENOMENA GÖRTLER VORTICES AND THEIR EFFECT ON HEAT TRANSFER Petr Sobolík*, Jaroslav Hemrle*, Sadanari Mochizuki*, Akira Murata*, Jiří Nožička**
More informationEVALUATION OF FOUR TURBULENCE MODELS IN THE INTERACTION OF MULTI BURNERS SWIRLING FLOWS
EVALUATION OF FOUR TURBULENCE MODELS IN THE INTERACTION OF MULTI BURNERS SWIRLING FLOWS A Aroussi, S Kucukgokoglan, S.J.Pickering, M.Menacer School of Mechanical, Materials, Manufacturing Engineering and
More information