# Reynolds-Averaged Navier-Stokes (RANS) Simulations

For incompressible turbulent flow the instantaneous velocity field can be decomposed into a time averaged velocity and its corresponding fluctuation.

- ${u}_{i}$ : instantaneous velocity,
- $\overline{{u}_{i}}=\frac{1}{\Delta t}\underset{t}{\overset{t+\Delta t}{{\displaystyle \int}}}{u}_{i}dt$ : time averaged velocity over $\Delta t$ ,
- ${u}_{i}^{\text{'}}$ velocity fluctuation.

where $p$ is the instantaneous pressure.

- $\overline{{S}_{ij}}=\frac{1}{2}\left(\frac{\partial \overline{{u}_{i}}}{\partial {x}_{j}}+\frac{\partial \overline{{u}_{j}}}{\partial {x}_{i}}\right)$ is the mean strain rate tensor,
- ${\tau}_{ij}^{R}=-\rho \overline{{u}_{i}^{\text{'}}{u}_{j}^{\text{'}}}$ is the Reynolds stress tensor.

It is noted that the momentum equation has an unsteady term (the first term in the left hand side of the momentum equation). Wegner et al. (2004) argued that the RANS equations with the time term (unsteady RANS) can be applied to simulate unsteady flows when a time scale (T2) for large scale motions is larger than a time averaging period for RANS (T1) (see Figure 2). It is worth mentioning that RANS time averaging period (T1) should be considerably larger than the largest turbulence (integral) time scale, as URANS can only give a time averaged mean value for the velocity field, not solving turbulence. Thus, a representative URANS solution is demonstrated by the smoothed red line in the image below. Whereas the blue line represents the velocity profile with instantaneous fluctuations.

Although Reynolds-averaging eliminates a need to compute the instantaneous flow field, it introduces a new unknown term in comparison to the Navier-Stokes equations. This unknown term is referred to as the Reynolds stress tensor, which represents an added stress due to the turbulent motions. This term arises from the decomposition of the convective term using the Reynolds decomposition. Since your goal is to eliminate any dependence on the instantaneous flow field in these simplified equations, this term should be modeled in terms of the mean flow. This challenge is known as the closure problem of turbulence.

- ${\mu}_{t}$ : the eddy viscosity,
- $k=\frac{1}{2}\overline{{u}_{i}^{\text{'}}{u}_{j}^{\text{'}}}$ : the turbulent kinetic energy per unit mass,
- ${\delta}_{ij}$ : the Kronecker delta.

- Mixing length model
- Spalart-Allmaras model
- $k-\epsilon $ model, RNG (Renormalized Group) $k-\epsilon $ model, Realizable $k-\epsilon $ model
- $k-\omega $ model, SST (Shear Stress Transport) model
- $v2f$ model, zeta-f model

This approach is valid for many turbulent flows, for example, boundary layer, channel flow, round jets, turbulent shear flow and mixing layer, but not for all, for example, impinging flow and swirling flow. Under these circumstances, a model that is capable of predicting anisotropic Reynolds stresses is more appropriate. This can include a full Reynolds stress model (RSM), which determines the turbulent stresses by solving a transport equation for each stress component, or an eddy viscosity model that uses a non linear stress strain relationship to compute each Reynolds stress component separately. Although the improvement in accuracy achieved from this type of modeling is appealing, the introduction of anisotropic stresses is often accompanied by increased compute cost and a decrease in robustness.

The following section provides a review of some commonly used RANS models, ranging from algebraic models (zero equation models) up to the seven equation Reynolds Stress Model.