Page 152 - Fluid Mechanics and Thermodynamics of Turbomachinery
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Axial-flow Turbines: Two-dimensional Theory 133
Mallinson, D. H. and Lewis, W. G. E. (1948). The part-load performance of various gas-
turbine engine schemes. Proc. Instn. Mech. Engrs., 159.
Raghunathan, S. Setoguchi, T. and Kaneko, K. (1991). The Wells air turbine subjected to
inlet flow distortion and high levels of turbulence. Heat and Fluid Flow, 8, No. 2.
Raghunathan, S., Setoguchi, T. and Kaneko, K. (1991). Aerodynamics of monoplane Wells
turbine a review. Proc. Conf. on Offshore Mechanics and Polar Engineering., Edinburgh.
Raghunathan, S., Curran, R. and Whittaker, T. J. T. (1995). Performance of the Islay Wells
air turbine. Proc. Instn Mech. Engrs., 209,55 62.
Raghunathan, S. (1995). A methodology for Wells turbine design for wave energy conversion.
Proc. Instn Mech. Engrs., 209, 221 32.
Shapiro, A. H., Soderberg, C. R., Stenning, A. H., Taylor, E. S. and Horlock, J. H. (1957).
Notes on Turbomachinery. Department of Mechanical Engineering, Massachusetts Institute
of Technology. Unpublished.
Smith, G. E. (1986). Vibratory stress problems in turbomachinery. Advanced Topics in Turbo-
machine Technology. Principal Lecture Series, No. 2. (David Japikse, ed.) pp. 8 1to8 23,
Concepts ETI.
Soderberg, C. R. (1949). Unpublished note. Gas Turbine Laboratory, Massachusetts Institute
of Technology.
Stenning, A. H. (1953). Design of turbines for high energy fuel, low power output applica-
tions. D.A.C.L. Report 79, Massachusetts Institute of Technology.
Stodola, A. (1945). Steam and Gas Turbines, (6th edn). Peter Smith, New York.
Wells, A. A. (1976). Fluid driven rotary transducer. British Patent 1595700.
Wilde, G. L. (1977). The design and performance of high temperature turbines in turbofan
engines. 1977 Tokyo Joint Gas Turbine Congress, co-sponsored by Gas Turbine Soc. of
Japan, the Japan Soc. of Mech. Engrs and the Am. Soc. of Mech. Engrs., pp. 194 205.
Wilson, D. G. (1987). New guidelines for the preliminary design and performance prediction
of axial-flow turbines. Proc. Instn. Mech. Engrs., 201, 279 290.
Problems
1. Show, for an axial flow turbine stage, that the relative stagnation enthalpy across the
rotor row does not change. Draw an enthalpy entropy diagram for the stage labelling all
salient points.
Stage reaction for a turbine is defined as the ratio of the static enthalpy drop in the rotor
to that in the stage. Derive expressions for the reaction in terms of the flow angles and draw
velocity triangles for reactions of zero, 0.5 and 1.0.
2. (a) An axial flow turbine operating with an overall stagnation pressure of 8 to 1 has a
polytropic efficiency of 0.85. Determine the total-to-total efficiency of the turbine.
(b) If the exhaust Mach number of the turbine is 0.3, determine the total-to-static efficiency.
(c) If, in addition, the exhaust velocity of the turbine is 160 m/s, determine the inlet total
temperature.
Assume for the gas that C P D 1.175 kJ/(kg K) and R D 0.287 kJ/(kg K).
3. The mean blade radii of the rotor of a mixed flow turbine are 0.3 m at inlet and 0.1 m
at outlet. The rotor rotates at 20,000 rev/min and the turbine is required to produce 430 kW.
The flow velocity at nozzle exit is 700 m/s and the flow direction is at 70 ° to the meridional
plane.
Determine the absolute and relative flow angles and the absolute exit velocity if the gas
flow is 1 kg/s and the velocity of the through-flow is constant through the rotor.

