INTRODUCTION
Turbulence flows are characterized by fluctuating components, which have three dimensional behaviors and a large spectrum of length scales. The special stochastic characteristics of turbulent elements, together with flow unsteadiness and three dimensional nonlinear oscillations, add to the complexity of the problem. The governing equations of turbulence are the NavierStokes equations. Due to numerous unknowns and nonlinearity of these equations, up to now, no analytical solution except for a few simple homogeneous, isotropic situations, has been proposed. So, the numerical approaches are the only available tools to be implemented in computational codes.
Engineering CFD calculations are largely based on the solution of the RANS equations in conjunction with a turbulence model. During last decades, many different turbulence models have been proposed by different researchers.
The models proposed so far are often based on theoretical principles, dimensional analysis, asymptotic analysis of the Navier Stokes equations and experimental observations.
Until now despite the efforts and available assessments and general consensus there is no single theory and a dominantly superior turbulent model which can be used reliably and universally. Often, turbulent models are developed and tested for limited classes of flow. The first turbulence models of which, the prandtls mixing length hypothesis is the most well known example, related the turbulent transport terms uniquely to local mean quantities. These models could only be applied to a self similar special flow groups, which the partial differential equations expressing mass and momentum conservation can be reduced to ordinary ones. Even for the few simple flows which the zero equation models could be applied, the early models lacked the universality in that they required different empirical constants for different flows. The mixing length model is not suitable when turbulent convective transport is an important part of the physics, examples are rapidly developing flows, heat transfer across planes with zero velocity gradients and flows with recirculation. Also due to the great difficulties in specifying the mixing length (L), the model is of limited use in complex flows.
In order to overcome the above mentioned limitations of the mixing length hypothesis, turbulence models were developed which account to the transport of turbulence equations by solving differential transport equations for them. Among these models the one equation model of KolmogorovPrandtl, which was introduced by Kolmogrov (1942) and Prandtl (1925) independently, is well known.
The more advanced models developed in 1940 s, give up direct algebraic link between the turbulent transport terms and the mean flow quantities and employ differential transport equations for turbulence quantities such as kinetic energy of the turbulent motion. In 1960 s computers became sufficiently powerful and shortly after, numerical techniques developed to allow partial differential equations to be solved for many flow situations.
The most popular turbulent models which have been developed since 1980 s, are the standard Kε model proposed by Launder and Spalding (1972), Realizeable Kε model of Shih et al. (1998), RNG Kε model introduced by Choudhury (1993), standard Kω model of Wilcox (1988) and its shear transport version of Menter (1994). All of the above models have some limitations. For example, the widely used Kε turbulence model fails to predict flow near a solid boundary. It also fails to predict the experimentally observed differences between the spreading rates of a plane jet and a round jet. In experiments the spreading rate of round jet is 15% lower than a plane jet, but in the simulations with the standard Kε model, the round jet spreading rate is 15% higher (Wilcox, 1988). Wilcox proposed that the dissipation rate equation of the Kε model be replaced by an equation for a specific dissipation rate defined as ω = K/ε. This Kω model predicts the behavior of attached boundary layers in adverse pressure gradients more accurately than Kε model, but performs weakly in free shear flows.
In 1982, Sinder (1982) compared the application of common turbulent models and proposed some corrections for the coefficients of the Kε model. Kooronaki et al. (2001) investigated the effect of the kind of turbulent model on the results obtained for velocity and turbulent distribution. Cole et al. (2003) simulated axisymmetric submerged jets numerically using FLUENT CFD code and pointed out that the results obtained for velocity distribution profiles match well with experimental data.
One of the most ambiguous categories of flow is the confined jet with back pressure. The flow separation phenomena with recirculating eddies, make the problem too intricate. The present work is concerned with a comprehensive assessment of five common two equation turbulent models, namely: standard Kε, RNG Kε, Realizable Kε, standard Kω and SST Kω implemented in general purpose FLUENT V6 CFD code. Each model is run with its standard set of constants. The numerical method is based on a cellcentered, unstructured finite volume discritization and a SIMPLE type segregated solution procedure. All simulations are carried out to use as second order upwind scheme for the convective terms.
Figure 1 shows the model geometry, which is a two dimensional axisymmetric sudden pipe expansion. Inlet velocity and outlet pressure are chosen as boundary conditions. The diameter of the inlet jet and the expanded pipe diameter are 7.62 and 28 cm, respectively, which produce an expansion ratio of D2/Dj = 3.675. A circular orifice with a diameter of 19.5 cm is provided at the outlet inorder to ensure flow submergence. A uniform rectangular grid, consisting of 13250 quadrilateral element cells, is implemented in the numerical procedures.
EXPERIMENTAL RIG AND INSTRUMENTATION
The expansion used here was located 2.5 m from the inlet of the test section
and was preceded by a short, smooth contraction converting upstream pipe diameter
of 300 mm to downstream diameter of 76.2 mm. The pipe diameter at the inlet
to the expansion was D_{J }= 76.2 mm and its length was 1 m, which ensured
formation of fully developed flow at the jet inlet. The main body of the sudden
expansion, the key dimensions of which are shown in Fig. 1
and 2, was made of Perspex. The smooth contraction was fabricated
form stainless steel. Measurements of pressure and velocity distribution were
possible form 11 axial locations corresponding to X values of 6, 6, 12, 18,
24, 30, 42, 54, 66, 78, 114 cm, measured from the efflux section. Also, pressure
tappings of 2 mm diameter were provided along the bottom of the pipe to allow
the wall pressure distribution to be measured.

Fig. 1: 
Sketch of the physical model 

Fig. 2: 
Defition of flow parameters 
The tapings were connected to differential pressure transducer and the measurements
were carried out using a data logger. The pressure transducers used, were able
to measure gage pressures between 1 bar and +1 bar with a natural frequency
of 1 KHz. Figure 3 shows the photograph of the rig.

Fig. 3: 
Photograph of the physical model 
COMPARISON OF THE RESULTS
Figure 4 compares the results obtained from CFD models for spread of the jet, with experiments. It seems that realizable Kε model (R K ε) gives the best prediction for the spread of the jet, while with the RNG Kε model, the spreading of the jet for the zones near reattachment point is 10% lower, however for the zone of flow establishment the results are approximately identical to simulations with the R K ε model. In simulations with the standard Kε model and Kω model, the spreading rate of the jet is higher than experimental measurement. This deviation from measurements is more sensible for the zone of flow establishment.
In Fig. 4, both the inner and outer limit of diffusion is
illustrated. Comparison of the curves, shows that the family of Kω models
approximate the length of the potential core much less than measurements. Figure
5 shows the results obtained for centerline velocity distribution. As it
is obvious, predictions of the RNG model and standard Kε model for center
line velocity distribution match reasonably well with measurement, while the
predictions of other models differ considerably from experiments. It is interesting
that the simulations with the standard Kε model provide the closest results
to the experiments, for centerline velocity distribution. Distribution of axial
velocity at three different sections is shown in Fig. 6. It
is seen that the standard Kε model performs weak in recirculation zone.

Fig. 4: 
Comparison of the CFD results for the spread of the jet 

Fig. 5: 
Distribution of maximum velocity along the pipe (Centerline
velocity), RKE: Realizeable Kε model, RNG KE: Renormalization group
Kε model, SKE: Standard Kε model, SKW: Standard Kω model,
SST KW: Shear Stress Transport Kω model 

Fig. 6: 
Axial velocity distribution at three distinct locations 

Fig. 7: 
Distribution of mean static pressure 

Fig. 8: 
Comparison of the CFD results for turbulence kinetic energy
with experimental results 
The mean static pressure distribution is shown in Fig. 7.
It is clear that the RK ε model gives the best prediction of static pressure
distribution along the jet axis. Finally the comparison of turbulence kinetic
energy is presented in Fig. 8. It seems that the RK ε
model approximates the trend of the turbulence kinetic energy much better than
the other models, while the standard Kε model and the RNG model predictions
of peak kinetic energy match with experimental data, much better than the predictions
of other models. On the other hand in simulations with the family of Kω
models, the peak kinetic energy is much lower than experiments.
CONCLUSIONS AND FUTURE WORK
The comparative analysis of the performance of five common 2equations turbulence models for simulations of axisymmetric confined jets dominated by flow separation has been presented. The objective was to evaluate the overall accuracy of each model to prediction different flow parameters at different flow zones. The results indicate that each model has some limitations and the authors hesitate to introduce a definite model as the best applicable model for simulations of this kind of flow but believes that, overall, the accuracy of the RKε model and RNG Kε model appears to be superior to other models. Of course, the RNG Kε model in comparison to the RKε model needs more computational efforts per iteration and for the convergence of the solutions, which is due to the strong nonlinear terms existing in its transformed equations.
The sensitivity of the models to the choice of boundary type and the Reynolds number are the topics which need further investigation and will be the future work of the author.
ACKNOWLEDGMENT
The physical model was constructed in the laboratory of Iran^{’}s Water Research Center and special tanks are given to Dr. Nasiri, Head of the Institute for his valuable help.