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development The stress transport equations are again written in density-weighted form but now additional terms appear for combusting flows which require modelling Of the available models, that described in (11) appears to be one of the most reliable and has produced good results for reacting flow The scalar fluxes must again be modelled and this may be done using the second-moment closure also described in (11) This level of closure allows us to capture effects such as counter-gradient diffusion observed in premixed flames which cannot be represented by lower order closures The Reynolds stress and scalar flux closures described represent the current best practice for application to practical gas turbine combustor calculations, since they balance physical realism with computational economy However, we are still limited by the fundamental assumptions of all Reynolds averaging methods whereby we have characterized the turbulence field by a single length and time scale.

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This is likely to be a significant compromise particularly in flows where the effects of solid walls are important, such as the modelling of cooling films or diffuser performance In such cases we may wish to move to a more comprehensive treatment of the turbulence structure that captures at least some of the range of eddy scales and so the energy cascade The only method currently offering promise in this area for engineering flows at high Reynolds number is the Large Eddy Simulation (LES) approach Here, we perform an unsteady calculation on a grid sufficiently fine to resolve the large eddy structures and simulate only those that cannot be resolved on the grid (which should be that part of the flow within the turbulence inertial subrange).

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This method is attractive for a number of reasons for calculating the flows in combustion systems: The inherently unsteady nature of the calculation and capture of multiple length and time scales should allow the calculation of structures such as cooling films which are poorly predicted by many Reynolds-averaged techniques The decay of the cooling film is controlled by the rate of mixing between the film and the hot mainstream; this mixing process is governed by large-scale vortex motions in the interface leading to entrainment of hot gas into the film These processes should be more amenable to prediction by LES than by Reynolds-averaged methods which should improve the data that can be supplied to combustor life calculations LES allows us to directly simulate the larger turbulence scales which will be most influenced by the geometry and boundary conditions.

This listing results in the following:

The smaller, modelled, scales are assumed to be more universal and therefore may be more properly approximated by simple 'universal' models This should further improve diffuser predictions where small changes in the geometry may lead to significant changes in performance and the flow characteristics are dominated by the structure of the near-wall flow In attempting to reduce emissions from the combustion system, most approaches now favour use of a fuel-lean flame This introduces issues of flame stability and the possible generation of destructive acoustic waves in the chamber These can contain sufficient energy to damage the combustion system These instabilities take the form of largescale unsteady motions in the combustion chamber which should be better captured by LES thus allowing investigation of potential acoustic problems at the design stage instead of using expensive rig testing However, we should not underestimate the challenges involved in making LES a design tool.

Relatively little work has been performed on LES for combustion, some exceptions being for example (1), (5), and (7) and so issues remain over the precise treatment of combustion in an LES framework While we assume that the unresolved subgrid turbulence scales are represented by relatively simple universal models, there has been little comparative testing of different subgrid scale models in complex engineering flows We also need the calculations to.

With the pdf of,S , , at hand and noting that N L I M = 1, the average normalized aggregated rate is obtained from (6.6) and (6.7) as

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