3 d flow analysis of an annular diffuser with and without struts
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The document summarizes a study on the 3D flow analysis of an annular diffuser with and without struts. Numerical simulations were conducted for an annular exhaust diffuser model at different inlet velocities and with or without struts. The results show that pressure recovery within the diffuser increases as flow proceeds, with pressure increasing and velocity decreasing. The presence of struts decreases the pressure recovery coefficient slightly due to increased losses, with velocity increasing along the strut portion where pressure decreases. Contour plots illustrate the velocity and pressure distributions through the diffuser.
![Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014
INTERNATIONAL JOURNAL OF MECHANICAL ENGINEERING
17 – 19, July 2014, Mysore, Karnataka, India
AND TECHNOLOGY (IJMET)
ISSN 0976 – 6340 (Print)
ISSN 0976 – 6359 (Online)
Volume 5, Issue 9, September (2014), pp. 222-231
© IAEME: www.iaeme.com/IJMET.asp
Journal Impact Factor (2014): 7.5377 (Calculated by GISI)
www.jifactor.com
IJMET
© I A E M E
3D FLOW ANALYSIS OF AN ANNULAR DIFFUSER WITH AND WITHOUT
STRUTS
Pramod B A1, Dr. B Sadashive Gowda2
1(M.Tech Student, Department ofMechanical Engineering, Vidyavardaka college of Engineering, Mysore, Karnataka)
2(Principal, VVCE, Mysore 570002, Vidyavardaka college of Engineering, Mysore, Karnataka)
222
ABSTRACT
Numerical investigations have been carried out for an annular type gas turbine exhaust diffuser with inlet
guidevanes and with and without struts. Numerical simulations were carried out to determine the pressure recovery
coefficient, for a divergence angle 13o by keeping the diffusion length constant. The flow conditions at the inlet are
varied to evaluate how they affect the flow development in the passage. The velocity at inlet is varied from 80 m/s to 160
m/s in the steps of 40 m/s. In the present study a (1/6)th part of the model is considered for the analysis, due to symmetry.
The results for with and without struts indicates how the pressure recovery coefficient affects the efficiency of the
turbine.
Keywords: Annular diffuser, Exhaust diffuser, Gas turbine, Numerical simulations, Pressure recovery coefficient.
1. INTRODUCTION
A diffuser is a device that increases the pressure of a fluid at the expense of its kinetic energy [1]. The cross
section area of diffuser increases in the direction of flow, therefore fluid is decelerated as it flows through it, causing a
rise in static pressure along the stream. Annular diffusers are extensively used in axial flow compressors and turbines to
convert the kinetic energy of the exhaust flow into pressure. This makes the diffuser a critical element in the performance
of the turbine, which is often neglected.
The exhaust diffuser of an industrial gas turbine recovers the static pressure by decelerating the turbine
discharge flow. In the modern turbine the Mach number at the exhaust is around 0.4-0.45 and the total energy produced
by the turbine is approximately 350KJ/kg, in consequence, a 10% of the total energy of the turbine which is 35KJ/Kg is
being wasted or loss at the exhaust by entering into atmosphere[9]. Only a very few studies on experimental and
numerical investigations on simple diffusers are available [2], [3], [4] and the factors influencing their performance are
predominantly the area ratio and the length of the flow path over which diffusion occurs. At diffusers inlet, the intensity
of the turbulence is usually very high due to the swirl nature of the flow. It is a well known fact that, within diffusers the
flows are characterized by strong adverse pressure gradients which tends to flow to separate from the walls. In the
literature a very few researches are available on experimental analysis concerning on annular diffusers downstream to the
turbine [5], [6] or a compressor [7], [8]. In an annular diffuser, a number of different geometric variables can influence
the variation of pressure recovery and inlet condition of flow.
Struts are structural members which serve as both load bearings support and as passages for cooling air and
lubricating oil. The overall performance of the diffuser is highly influenced by the presence of struts. In the present study
the geometrical details of the struts are taken from NACA-0021 profile, which is one of the NACA four-digit wing
section series.](https://image.slidesharecdn.com/3dflowanalysisofanannulardiffuserwithandwithoutstruts-141023092634-conversion-gate02/85/3-d-flow-analysis-of-an-annular-diffuser-with-and-without-struts-1-320.jpg)
![Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM
-2014
17 – 19, July 2014, Mysore, Karnataka, India
2. GEOMETRICAL DETAILS AND MATHEMATICAL FORMULATION
Diffuser Geometry Numerical investigations have been carried out in a gas turbine
Diffuser) to study the effect of the divergence angle and the Reynolds number. A series of 24 guide vanes and 6 struts
have been used, which provides a means of introducing swirl and aerodynamic blockage into the test section. The
Diffuser assembly of the scaled down gas turbine exhaust diffuser with and without strut is as shown in Fig. 1. The
geometrical details of 35% scaled down gas turbine exhaust diffuser is shown in Fig. 2, where the diffusing length is
450mm, inlet and outlet diameters are 190mm and 320mm, respectively and half cone angle is 13
Fig. 1: Diffuser assembly with and without struts
Fig. 2: Geometry of 35% Gas Turbine Exhaust Diffuser [9, 10]
3. GRID INDEPENDENCE STUDY
A commercially available meshing tool is used to generate tetrahedral grids. An unstructured mesh is
generated with the Gambit (Ver. 2.3.16) software meshing tool. The mesh density is increased near the surface of the
blades and struts to ensure accuracy, as velocity changes in th
highly concentrated at the surface of the blades. This is done by performing a number of simulations with different
mesh sizes, starting from a coarse mesh and refining it until physical results a
The tetrahedral cells are retained to have good discretization accuracy. Four mesh refinements of 1159917, 1645161,
2099319 and 2475980 cells are tested and compared with a velocity which is a physical parameter of th
cross section of the annular diffuser as shown in Fig. 3. For good accuracy of the results, the case with 2099319 cells
can be employed as this gives no significant difference compared to that with 2475980 cells. A fine mesh of 2099319
cells is chosen for further analysis.
223
exhaust diffuser (Annular
et o.
the fluid are expected to occur in these regions. The mesh is
are no more dependent on the mesh size.
e re the fluid for each](https://image.slidesharecdn.com/3dflowanalysisofanannulardiffuserwithandwithoutstruts-141023092634-conversion-gate02/85/3-d-flow-analysis-of-an-annular-diffuser-with-and-without-struts-2-320.jpg)
![Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM
The turbulence generation term G is written as:
The effective viscosity μeff is calculated from
The five emperical model constant are assigned
5. BOUNDARY CONDITIONS
the following values:
There are four types of boundary conditions to specify for the computation in annular exhaust diffuser, they
are Inlet, Outlet, Wall and d Symmetry boundary conditions.
Fluent code uses the finite volume method for
discretization. The governing steady-state equations for mass and momentum conservation are solved with a segregated
approach. In this approach, the equations are sequentially solved with implicit linearization
interpolation scheme is used in the analysis in order to get the accurate results. The pressure
implemented using iterative correction procedure (SIMPLEC algorithm).
Inlet: The present analysis involves the velocity as the inlet boundary condition and is varied from 80m/s to 160m/s in
the steps of 40m/s. Turbulence intensity is specified as Medium Turbulence i.e 5% with respect to the equivalent flow
diameter.
Outlet: Atmospheric pressure condition is applie
is set to Atmospheric.
Wall: The no slip condition and smooth surface conditions are used for all walls (except side walls).
Symmetry: Symmetry boundary conditions are applied to
considered (1/6)th part of geometry for the analysis.
In the present analysis numerical simulations are carried out by choosing k
target of 1×10-6 is set to ensure the convergence of the equations.
6. FLUID PROPERTIES
The material which is used for the analysis is Air at 25
tabulated in Table. 1.
Table.1:
Thermodynamic
Thermal Expansion coefficient
Dynamic Viscosity
Thermal Conductivity
Density
17 – 19, July 2014, Mysore, Karnataka, India
225
linearization. A second
pressure-velocity coupling is
elocity applied at the outlet boundary where in the pressure at the exit of the diffuser
the model at the either walls of the diffuser, because we
k- turbulence model. The residual
nsure oC. The material properties of the Air at 25
Properties of the Air at 25oC
State Gas
0.003356 [k^-1]
1.831×10-5 [Kg m^-1 s^-1]
2.61×10-2 [W m^-1 k^-1]
1.185 [Kg m^-3]
-2014
. second- order upwind
d oC are
(7)
(8)](https://image.slidesharecdn.com/3dflowanalysisofanannulardiffuserwithandwithoutstruts-141023092634-conversion-gate02/85/3-d-flow-analysis-of-an-annular-diffuser-with-and-without-struts-4-320.jpg)
![Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM
7. CODE VALIDATION
-2014
17 – 19, July 2014, Mysore, Karnataka, India
The problem is solved using Fluent CFD code, the existing code is validated with the results of Vaddin Chethan
[11] for accuracy and correctness. For the modeling of annular diffuser, the values of diffusion length, casing angle, hub
length and boundary conditions are retained same as Vaddin Chethan [11] and validation is carried for velocity of 80 m/s,
It is found to agree well with the results of published works.
8. RESULTS AND DISCUSSION
This paper presents the performance of gas tur
measured in the scaled down model. In the graphs and contour plots, it is referred that the position of measuring point in
terms of axial position, considering that:
Axial position of 0 mm is the leading edge of inlet of diffuser.
Results are produced in the diffuser model with and without struts for various section from inlet to outlet.
The diffusers performances have been also determined by the following parameters:
• Pressure Recovery coefficient(Cp)
An ideal pressure recovery can be defined if the flow is assumed to be isentropic. Then, by employing the
conservation of mass, this relation can be converted to an area ratio for incompressible flow.
Where,
Vav1 represents the average velocity at the inlet.
P is the pressure at the point at which pressure coefficient is being evaluated.
is the pressure in the free stream.
A is the cross sectional area, and
R is the universal gas constant.
8.1 Analysis of the annular diffuser for 13
The pressure recovery coefficient and velocity distribution for with and without struts along the length of the
diffuser are shown in Fig. 5 (a, c, e) and Fig. 5 (b, d, f) respe
diffuser, the velocity continuously decreases towards the outlet because of the diffusion. From the Fig. 5(a), we can
notice that the pressure recovery coefficient is slightly reduced in the c
struts. This is because, as the fluid comes in contact with the strut interface, the pressure recovery coefficient decreases
226
tained Fig 4: Velocity v/s X/L
turbine annular diffuser in terms of pressure recovery coefficient
)
resents 0 casing angle with and without struts:
respectively, at different values of velocity. From the inlet of the
case of struts compared to the diffuser without
bine ctively, ase (9)
(10)](https://image.slidesharecdn.com/3dflowanalysisofanannulardiffuserwithandwithoutstruts-141023092634-conversion-gate02/85/3-d-flow-analysis-of-an-annular-diffuser-with-and-without-struts-5-320.jpg)
![Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014
17 – 19, July 2014, Mysore, Karnataka, India
Fig. 8(d): Pressure contour for 130 casing angle without strut and velocity at 160m/sec
231
9. CONCLUSION
Numerical investigations have been carried out to investigate the static pressure development and pressure
recovery coefficient through an industrial gas turbine exhaust diffuser with and without struts.
From the above discussion the following conclusions can be made:
1. The pressure recovery within the diffuser increases as the flow proceeds, consequently the pressure also increases
with the decrease in velocity level.
2. With increase in area ratio pressure recovery increases due to higher rate of diffusion but pressure recovery loss
also increases.
3. With increases in inlet velocity, there is increase in pressure recovery, since the entrance losses increases marginal
with velocity.
4. Comparing the two cases, with and without the struts, it is clear that the overall diffuser loss is significantly
increased by the struts and this loss rise mainly occurs in the axial region of the struts and in the endwall regions,
where flow separates from the hub and the casing.
REFERENCES
[1]. Ackert J, Aspect of Internal Flow, Fluid Mechanics of Internal Flow, Ed. Sovran G., Elsevier Amsterdam,
pp.1, 1967.
[2]. Sovran. G and Klomp E. D., Experimentally determined optimum geometries for rectilinear diffusers with
rectangular, conical or annular cross-section, Fluid Mechanics of Internal Flow (Ed. G. Sovran) (Elsevier,
Amsterdam) pp. 270–312, 1967.
[3]. R.K. Singh, R.S. Azada,Measurements of instantaneous flow reversals and velocity field in a conical diffuser,
Experimental Thermal and Fluid science, Vol. 17, pp. 100- 106, 1995.
[4]. P.W. Runstadler, F.X. Dolan, R.C. Dean, Diffuser data book, Creare, TB-186, 1975.
[5]. U. Desideri, G. Manfrida, Flow and turbulence survey for a model of gas turbine exhaust diffuser, ASME
paper 95-GT- 139, 1995.
[6]. B. Djebedjian, J. Renaudeaux, Numerical and experimental investigation of the flow in annular diffuser,
Proceedings of FEDSM98, Washington, DC, FEDSM98-4967, 1998.
[7]. H. Pfeil, M. Going, Measurements of the turbulent boundary layer in the diffuser behind an axial compressor,
ASME Journal of Turbo machinery, Vol. 109, 405-412, 1987.
[8]. H. Harris, I. Pineiro, T. Norris, A performance evaluation of three splitter diffuser and vaneless diffuser
installed on the power turbine exhaust of a TF40B gas turbine, ASME paper 98-GT-284, 1998.
[9]. S. Ubertini, U. Desideri, Flow development and turbulence length scales within an annular gas turbine exhaust
diffuser, Experimental Thermal and Fluid Science, Vol. 22, Issue 1-2, pp. 55-70, August 2000.
[10]. Stefano Ubertini, Umbert Desideri, Experimental performance analysis of an annular diffuser with and without
struts, Experimental Thermal and Fluid Science, vol. 22, pp. 183-195, 2000.
[11]. Vaddin Chetan, D V Satish, Dr. Prakash S Kulkarni, “Numerical Investigations of PGT10 Gas Turbine
Exhaust Diffuser Using Hexahedral Dominant Grid”, International Journal of Engineering and Innovative
Technology (IJEIT) Volume 3, Issue 1, July 2013.](https://image.slidesharecdn.com/3dflowanalysisofanannulardiffuserwithandwithoutstruts-141023092634-conversion-gate02/85/3-d-flow-analysis-of-an-annular-diffuser-with-and-without-struts-10-320.jpg)
3 d flow analysis of an annular diffuser with and without struts
- 1. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 INTERNATIONAL JOURNAL OF MECHANICAL ENGINEERING 17 – 19, July 2014, Mysore, Karnataka, India AND TECHNOLOGY (IJMET) ISSN 0976 – 6340 (Print) ISSN 0976 – 6359 (Online) Volume 5, Issue 9, September (2014), pp. 222-231 © IAEME: www.iaeme.com/IJMET.asp Journal Impact Factor (2014): 7.5377 (Calculated by GISI) www.jifactor.com IJMET © I A E M E 3D FLOW ANALYSIS OF AN ANNULAR DIFFUSER WITH AND WITHOUT STRUTS Pramod B A1, Dr. B Sadashive Gowda2 1(M.Tech Student, Department ofMechanical Engineering, Vidyavardaka college of Engineering, Mysore, Karnataka) 2(Principal, VVCE, Mysore 570002, Vidyavardaka college of Engineering, Mysore, Karnataka) 222 ABSTRACT Numerical investigations have been carried out for an annular type gas turbine exhaust diffuser with inlet guidevanes and with and without struts. Numerical simulations were carried out to determine the pressure recovery coefficient, for a divergence angle 13o by keeping the diffusion length constant. The flow conditions at the inlet are varied to evaluate how they affect the flow development in the passage. The velocity at inlet is varied from 80 m/s to 160 m/s in the steps of 40 m/s. In the present study a (1/6)th part of the model is considered for the analysis, due to symmetry. The results for with and without struts indicates how the pressure recovery coefficient affects the efficiency of the turbine. Keywords: Annular diffuser, Exhaust diffuser, Gas turbine, Numerical simulations, Pressure recovery coefficient. 1. INTRODUCTION A diffuser is a device that increases the pressure of a fluid at the expense of its kinetic energy [1]. The cross section area of diffuser increases in the direction of flow, therefore fluid is decelerated as it flows through it, causing a rise in static pressure along the stream. Annular diffusers are extensively used in axial flow compressors and turbines to convert the kinetic energy of the exhaust flow into pressure. This makes the diffuser a critical element in the performance of the turbine, which is often neglected. The exhaust diffuser of an industrial gas turbine recovers the static pressure by decelerating the turbine discharge flow. In the modern turbine the Mach number at the exhaust is around 0.4-0.45 and the total energy produced by the turbine is approximately 350KJ/kg, in consequence, a 10% of the total energy of the turbine which is 35KJ/Kg is being wasted or loss at the exhaust by entering into atmosphere[9]. Only a very few studies on experimental and numerical investigations on simple diffusers are available [2], [3], [4] and the factors influencing their performance are predominantly the area ratio and the length of the flow path over which diffusion occurs. At diffusers inlet, the intensity of the turbulence is usually very high due to the swirl nature of the flow. It is a well known fact that, within diffusers the flows are characterized by strong adverse pressure gradients which tends to flow to separate from the walls. In the literature a very few researches are available on experimental analysis concerning on annular diffusers downstream to the turbine [5], [6] or a compressor [7], [8]. In an annular diffuser, a number of different geometric variables can influence the variation of pressure recovery and inlet condition of flow. Struts are structural members which serve as both load bearings support and as passages for cooling air and lubricating oil. The overall performance of the diffuser is highly influenced by the presence of struts. In the present study the geometrical details of the struts are taken from NACA-0021 profile, which is one of the NACA four-digit wing section series.
- 2. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India 2. GEOMETRICAL DETAILS AND MATHEMATICAL FORMULATION Diffuser Geometry Numerical investigations have been carried out in a gas turbine Diffuser) to study the effect of the divergence angle and the Reynolds number. A series of 24 guide vanes and 6 struts have been used, which provides a means of introducing swirl and aerodynamic blockage into the test section. The Diffuser assembly of the scaled down gas turbine exhaust diffuser with and without strut is as shown in Fig. 1. The geometrical details of 35% scaled down gas turbine exhaust diffuser is shown in Fig. 2, where the diffusing length is 450mm, inlet and outlet diameters are 190mm and 320mm, respectively and half cone angle is 13 Fig. 1: Diffuser assembly with and without struts Fig. 2: Geometry of 35% Gas Turbine Exhaust Diffuser [9, 10] 3. GRID INDEPENDENCE STUDY A commercially available meshing tool is used to generate tetrahedral grids. An unstructured mesh is generated with the Gambit (Ver. 2.3.16) software meshing tool. The mesh density is increased near the surface of the blades and struts to ensure accuracy, as velocity changes in th highly concentrated at the surface of the blades. This is done by performing a number of simulations with different mesh sizes, starting from a coarse mesh and refining it until physical results a The tetrahedral cells are retained to have good discretization accuracy. Four mesh refinements of 1159917, 1645161, 2099319 and 2475980 cells are tested and compared with a velocity which is a physical parameter of th cross section of the annular diffuser as shown in Fig. 3. For good accuracy of the results, the case with 2099319 cells can be employed as this gives no significant difference compared to that with 2475980 cells. A fine mesh of 2099319 cells is chosen for further analysis. 223 exhaust diffuser (Annular et o. the fluid are expected to occur in these regions. The mesh is are no more dependent on the mesh size. e re the fluid for each
- 3. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM Fig. 3: Variation of velocity for annular diffuser with different mesh cells for 13 4. GOVERNING EQUATIONS The calculation procedure is based on the solution of the equations governing the c -2014 momentum in the time averaged form for a steady incompressible flow. These equations can be written in tensor notation as: The quantities ( ) represent the turbulent Reynolds stresses. The k- model: The Reynolds stresses are linearly related to the mean rate strain as, The turbulent viscosity μt is expressed as (1) Where k and are the turbulence kinetic energy and dissipation rate of turbulence, the values of which are obtained from the solution of the following transport equations: 17 – 19, July 2014, Mysore, Karnataka, India 224 o degree casing angle conservation of mass and onservation (2) (3) (4) (5) (6)
- 4. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM The turbulence generation term G is written as: The effective viscosity μeff is calculated from The five emperical model constant are assigned 5. BOUNDARY CONDITIONS the following values: There are four types of boundary conditions to specify for the computation in annular exhaust diffuser, they are Inlet, Outlet, Wall and d Symmetry boundary conditions. Fluent code uses the finite volume method for discretization. The governing steady-state equations for mass and momentum conservation are solved with a segregated approach. In this approach, the equations are sequentially solved with implicit linearization interpolation scheme is used in the analysis in order to get the accurate results. The pressure implemented using iterative correction procedure (SIMPLEC algorithm). Inlet: The present analysis involves the velocity as the inlet boundary condition and is varied from 80m/s to 160m/s in the steps of 40m/s. Turbulence intensity is specified as Medium Turbulence i.e 5% with respect to the equivalent flow diameter. Outlet: Atmospheric pressure condition is applie is set to Atmospheric. Wall: The no slip condition and smooth surface conditions are used for all walls (except side walls). Symmetry: Symmetry boundary conditions are applied to considered (1/6)th part of geometry for the analysis. In the present analysis numerical simulations are carried out by choosing k target of 1×10-6 is set to ensure the convergence of the equations. 6. FLUID PROPERTIES The material which is used for the analysis is Air at 25 tabulated in Table. 1. Table.1: Thermodynamic Thermal Expansion coefficient Dynamic Viscosity Thermal Conductivity Density 17 – 19, July 2014, Mysore, Karnataka, India 225 linearization. A second pressure-velocity coupling is elocity applied at the outlet boundary where in the pressure at the exit of the diffuser the model at the either walls of the diffuser, because we k- turbulence model. The residual nsure oC. The material properties of the Air at 25 Properties of the Air at 25oC State Gas 0.003356 [k^-1] 1.831×10-5 [Kg m^-1 s^-1] 2.61×10-2 [W m^-1 k^-1] 1.185 [Kg m^-3] -2014 . second- order upwind d oC are (7) (8)
- 5. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM 7. CODE VALIDATION -2014 17 – 19, July 2014, Mysore, Karnataka, India The problem is solved using Fluent CFD code, the existing code is validated with the results of Vaddin Chethan [11] for accuracy and correctness. For the modeling of annular diffuser, the values of diffusion length, casing angle, hub length and boundary conditions are retained same as Vaddin Chethan [11] and validation is carried for velocity of 80 m/s, It is found to agree well with the results of published works. 8. RESULTS AND DISCUSSION This paper presents the performance of gas tur measured in the scaled down model. In the graphs and contour plots, it is referred that the position of measuring point in terms of axial position, considering that: Axial position of 0 mm is the leading edge of inlet of diffuser. Results are produced in the diffuser model with and without struts for various section from inlet to outlet. The diffusers performances have been also determined by the following parameters: • Pressure Recovery coefficient(Cp) An ideal pressure recovery can be defined if the flow is assumed to be isentropic. Then, by employing the conservation of mass, this relation can be converted to an area ratio for incompressible flow. Where, Vav1 represents the average velocity at the inlet. P is the pressure at the point at which pressure coefficient is being evaluated. is the pressure in the free stream. A is the cross sectional area, and R is the universal gas constant. 8.1 Analysis of the annular diffuser for 13 The pressure recovery coefficient and velocity distribution for with and without struts along the length of the diffuser are shown in Fig. 5 (a, c, e) and Fig. 5 (b, d, f) respe diffuser, the velocity continuously decreases towards the outlet because of the diffusion. From the Fig. 5(a), we can notice that the pressure recovery coefficient is slightly reduced in the c struts. This is because, as the fluid comes in contact with the strut interface, the pressure recovery coefficient decreases 226 tained Fig 4: Velocity v/s X/L turbine annular diffuser in terms of pressure recovery coefficient ) resents 0 casing angle with and without struts: respectively, at different values of velocity. From the inlet of the case of struts compared to the diffuser without bine ctively, ase (9) (10)
- 6. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India till the length of the strut. However, in the case of velocity distribution, the velocity increases with decrease in pressure along the strut portion. This scenario is shown in the zoomed portion of the Figures. 5(a) to 5(f). The above explained scenario is applicable for the remaining figures with different velocities. Fig. 5(a) Fig. 5 (b) Fig. 5: (a b) Variation of pressure recovery coefficient velocityfor the diffuser with and without struts at V=80m/s Fig. 5(c) Fig. 5(d) Fig. 5(c d) Variation of pressure recovery coefficient velocityfor the diffuser with and without struts at V=120m/s Fig. 5(e) Fig. 5(f) Fig. 5: (e f) Variation of pressure recovery coefficient velocityfor the diffuser with and without struts at V=160m/s 227
- 7. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India Fig. 6, Fig. 7 and Fig. 8 shows the contour plots for velocity and pressure distribution for both with and without struts for different velocity cases. In these figures fluid characteristics like velocity, pressure are shown by different color. Due to the change of kinetic energy into pressure energy there is continuous increase in the magnitude of pressure from inlet to outlet, and also due to the change in cross sectional area, the velocity increases along the length of guidevanes and struts, and goes on decreases till the outlet of the diffuser. Fig. 6(a): Velocity contour for 130 casing angle with strut and velocity at 80m/s Fig. 6(b): Pressure contour for 130 casing angle with strut and velocity at 80m/sec Fig. 6(c): Velocity contour for 130 casing angle without strut and velocity at 80m/s 228
- 8. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India Fig. 6(d): Pressure contour for 130 casing angle without strut and velocity at 80m/sec Fig. 7(a): Velocity contour for 130 casing angle with strut and velocity at 120m/s Fig. 7(b): Pressure contour for 130 casing angle with strut and velocity at 120m/sec Fig. 7(c): Velocity contour for 130 casing angle without strut and velocity at 120m/s 229
- 9. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India Fig. 7(d): Pressure contour for 130 casing angle without strut and velocity at 120m/sec Fig. 8(a): Velocity contour for 130 casing angle with strut and velocity at 160m/s. Fig. 8(b): Pressure contour for 130 casing angle with strut and velocity at 160m/sec Fig. 8(c): Velocity contour for 130 casing angle without strut and velocity at 160m/s 230
- 10. Proceedings of the 2nd International Conference on Current Trends in Engineering and Management ICCTEM -2014 17 – 19, July 2014, Mysore, Karnataka, India Fig. 8(d): Pressure contour for 130 casing angle without strut and velocity at 160m/sec 231 9. CONCLUSION Numerical investigations have been carried out to investigate the static pressure development and pressure recovery coefficient through an industrial gas turbine exhaust diffuser with and without struts. From the above discussion the following conclusions can be made: 1. The pressure recovery within the diffuser increases as the flow proceeds, consequently the pressure also increases with the decrease in velocity level. 2. With increase in area ratio pressure recovery increases due to higher rate of diffusion but pressure recovery loss also increases. 3. With increases in inlet velocity, there is increase in pressure recovery, since the entrance losses increases marginal with velocity. 4. Comparing the two cases, with and without the struts, it is clear that the overall diffuser loss is significantly increased by the struts and this loss rise mainly occurs in the axial region of the struts and in the endwall regions, where flow separates from the hub and the casing. REFERENCES [1]. Ackert J, Aspect of Internal Flow, Fluid Mechanics of Internal Flow, Ed. Sovran G., Elsevier Amsterdam, pp.1, 1967. [2]. Sovran. G and Klomp E. D., Experimentally determined optimum geometries for rectilinear diffusers with rectangular, conical or annular cross-section, Fluid Mechanics of Internal Flow (Ed. G. Sovran) (Elsevier, Amsterdam) pp. 270–312, 1967. [3]. R.K. Singh, R.S. Azada,Measurements of instantaneous flow reversals and velocity field in a conical diffuser, Experimental Thermal and Fluid science, Vol. 17, pp. 100- 106, 1995. [4]. P.W. Runstadler, F.X. Dolan, R.C. Dean, Diffuser data book, Creare, TB-186, 1975. [5]. U. Desideri, G. Manfrida, Flow and turbulence survey for a model of gas turbine exhaust diffuser, ASME paper 95-GT- 139, 1995. [6]. B. Djebedjian, J. Renaudeaux, Numerical and experimental investigation of the flow in annular diffuser, Proceedings of FEDSM98, Washington, DC, FEDSM98-4967, 1998. [7]. H. Pfeil, M. Going, Measurements of the turbulent boundary layer in the diffuser behind an axial compressor, ASME Journal of Turbo machinery, Vol. 109, 405-412, 1987. [8]. H. Harris, I. Pineiro, T. Norris, A performance evaluation of three splitter diffuser and vaneless diffuser installed on the power turbine exhaust of a TF40B gas turbine, ASME paper 98-GT-284, 1998. [9]. S. Ubertini, U. Desideri, Flow development and turbulence length scales within an annular gas turbine exhaust diffuser, Experimental Thermal and Fluid Science, Vol. 22, Issue 1-2, pp. 55-70, August 2000. [10]. Stefano Ubertini, Umbert Desideri, Experimental performance analysis of an annular diffuser with and without struts, Experimental Thermal and Fluid Science, vol. 22, pp. 183-195, 2000. [11]. Vaddin Chetan, D V Satish, Dr. Prakash S Kulkarni, “Numerical Investigations of PGT10 Gas Turbine Exhaust Diffuser Using Hexahedral Dominant Grid”, International Journal of Engineering and Innovative Technology (IJEIT) Volume 3, Issue 1, July 2013.