# Evaluating Performance of Steam Turbine using CFD

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2 The available energy in the hot and high pressure steam is first converted into kinetic energy by the expansion of steam in a suitably shaped passage known as nozzle from which it issues as a high velocity jet having a high tangential component. Then a part of this kinetic energy and sometimes part of the pressure energy are converted into mechanical energy by directing the jet at a proper angle, against curved blades mounted on a rotating disc. The rotor coupled to generator produces the electricity. Fig 1: Typical Arrangement for Large Power Station Turbine A. Working Principle of Operation The motive power in a steam turbine is obtained by the rate of change in momentum of a high velocity jet of steam impinging on a curved blade which is free to rotate [2,3,6]. The steam from the boiler is expanded in a nozzle, resulting in the emission of a high velocity jet. This jet of steam impinges on the moving vanes or blades, mounted on a shaft. Here it undergoes a change of direction of motion which gives rise to a change in momentum and therefore a force. Steam Turbines are widely used for the generation of electricity in a number of different cycles, such as Rankine cycle, Reheat cycle, Regenerative cycle and Combined cycle. Consider the steam turbine shown in the cycle above. The output power of the turbine at steady flow condition is: P = m (h 1 -h 2 ) Where m is the mass flow of the steam through the turbine and h1 and h2 are specific enthalpy of the steam at inlet and outlet of the turbine respectively. An ideal steam turbine is considered to be an isentropic process or constant entropy process, in which the entropy of the steam entering the turbine is equal to the entropy of the steam leaving the turbine. The efficiency of the steam turbine is often described by the isentropic efficiency for expansion process. No steam turbine is truly isentropic, however, with typical isentropic efficiencies ranging from 20%-90% based on the applications of the turbine. The presence of water droplets in the steam will reduce the efficiency of the turbine and cause physical erosion of the blades. Therefore the dryness fraction of the steam at the outlet of the turbine should not be less than 0.9. Steam Turbine consists of several stages. Each stage can be described by analyzing the expansion of steam from a higher pressure to a lower pressure. The steam may be wet, dry saturated or superheated. IV. RESULTS AND DISCUSSION The analysis is carried out in two stages. First, individual stage analysis is done and later combined analysis for all the 5 stages has been carried out. The stage analysis has been carried out for the turbine stages with the constant mass flow and it consists of stator, rotor, and seals. The various performance parameters like pressure, temperature distribution and velocity profiles on the blades, isentropic efficiencies, Power have been computed using the CFX Macros and with the help of Mollier Chart. As the eight stages consisting of Guide blade, Moving blade with a stage interface between the blades is simulated, and the solution is obtained with high resolution convergence up to 1e- 5.The analysis is carried out without and with seals for 8 th stage. Vol. 4 Issue 2 July ISSN: X

3 Fig 2: 8th stage with seal Fig 3: 8th stage vector plot without seal shows the variation of the velocity across the eighth stage without seals. This vectors plot, which is a collection of vectors drawn to show the direction and magnitude of a vector variable on a collection of points are defined by arrows. From the figure, it is obvious that the velocity is minimum at the entrance which is of m/sec and maximum at the blade throat of the stage which is around m/sec. Vol. 4 Issue 2 July ISSN: X

4 Fig 4: Views for 8th stage guide blade The figure shows the variation of Mach number across the 8 th stage without seals. From the figure it is obvious that Mach number is increasing from the entry to exit and Mach number is minimum of the order of occurred at the entrance of the guide blade and is maximum of is occurred at the blade throat of guide and moving blade. The variation of pressure across the stage is seen in the figure, the pressure contour plot which is a series of lines linking points with equal values of a given variable pressure. The variable values can quickly be associated with the colored regions of the plot. It is shown in the figure that the pressure goes on decreasing from entry to exit of the stage. At the entrance the maximum of bar is observed and a minimum of bar is obtained at the exit is obtained. In the pre processing the following fluid domains and boundary conditions are specified for the eight stage analysis. 1. Boundary Conditions: Inlet : Guide blade inlet Outlet : Moving blade outlet Inlet Mass Flow : kg/sec Inlet Static Temperature : K Wall : smooth Outlet Static Pressure : bar Rotational Speed : rpm Reference pressure : 0 bar 2. Fluid Properties: Working Fluid : Steam5 (Dry steam) Dynamic Viscosity : e-6 Pa s Thermal Conductivity : W/m. ºc 3. Turbulence Model: Turbulence Model : Standard k-epsilon Model Heat transfer Model : Total Energy 4. Interface between Guide and Moving Blade: Type : Fluid -Fluid Frame Change Option : Stage Interface(G8M8 Blade stage interface) 5. Pitch Change: Option: Specified Pitch Angle Pitch angle side 1: Vol. 4 Issue 2 July ISSN: X

5 Pitch angle side 2: Fig 5: Convergece Graph for with seal Fig 6: Convergece Graph for with out seal Table 1 : Table showing different physical parameters Torque (one blade row) kg m^2 s^-2 Torque (all blades) kg m^2 s^-2 Power (all blades) kg m^2 s^-3 Total-to-total isen. efficiency Total-to-static isen. efficiency Total-to-total poly. efficiency Total-to-static poly. efficiency V. CONCLUSION The results are analyzed for mass flow rates, temperature and pressure distributions on blades, power developed by stage and isentropic efficiency of the stage. The results are compared with Two-Dimensional program validated by experimentally and found to be in agreement with the 2D analysis. The CFD analysis of the Intermediate Pressure turbine module has helped in predicting the turbine performance and comparing with experimentally verified values. The analysis provided insight in to the flow field of the turbine blade path. Though the stage s performance is reasonable scope exists for further improving the performance by reducing the leakage Vol. 4 Issue 2 July ISSN: X

6 losses and modification of the blade profiles. The analysis also helps to carry out low pressure turbine blade path which uses cylindrical and twisted blades. REFERENCES [1] John D. Anderson. Jr, "Computational Fluid Dynamics, the basics with applications", Inc. New York St. LOlliS San Ffancisco Auckland [2] Dr. R. K. Bansal, "Fluid Mechanics and hydraulic machines", Tata Mc Graw Hill, 2006 [3] C.W. Haldeman, R.M. Mathison; Aerodynamic and Heat Flux Measurements in a Single-Stage Fully Cooled Turbine Part II, Journal of Turbomachinery, vol. 130/021016, April [4] X.Yan, T.Takinuka; Aerodynamic Design Model Test and CFD Analysis for a Multistage Axial Helium Compressor, Journal of Turbomachinery, ASME paper,. [5] Arun K.Saha, Sumanta Acharya, Computations of Turbulent Flow and Heat Tansfer Through a Three-Dimensional Nonaxisymmetric Blade Passage, Journal of turbomachinery, ASME paper, Vol. 130/031008, July [6] Horloc, J.H., The Thermodynamics Efficiency of the Field Cycle, ASME paper Vol. no. 57.A.44, Vol. 4 Issue 2 July ISSN: X

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