Aerodynamic Radial Inflow Turbine Rotors

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Aerodynamic Radial Inflow Turbine Rotors ( aerodynamic-radial-inflow-turbine-rotors )

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Three configurations were tested: rotor I with stator I; rotor I with stator II (stator I closed down to reduce the throat area); and rotor II with stator II only. The nozzle was restag- gered after the first test showed a higher-than-design mass flow rate at the design stage pressure ratio. Tests were conducted in warm air at an inlet total tempera- ture of 860 R and over an inlet total pressure range of 45 to 50 psia. The test program consisted of measuring the overall stage performance and conducting radial and circumferential flow field surveys at various operating conditions at the tur- bine inlet and exit and in the vaneless space. The flow surveys measured fluid temperature, pressure, and flow angle. Meas- ured performance results are compared with conventional radial inflow turbine performance found in the literature. Symbols D rotor diameter, in. g conversion constant, 32.174 lbm-ft/lbf-sec 2 r torque, in.-lb Subscripts: bx axial length of the turbine blade cr conditions at Mach 1.0 eq equivalent conditions L based on torque p pressure side s suction side t tip 0 station upstream of stator at inlet 1 station at stator leading edge 2 station at rotor inlet 3 station at rotor exit 4 station downstream of rotor (rotor exit survey plane) Superscripts: total state condition * U.S. standard sea-level conditions (temperature, 518.67 R; pressure, 4.696 lbf/in. 2) Turbine Design and Research Hardware The significant difference between this radial turbine design and that of a conventional radial turbine is the greatly short- ened rotor axial length, achieved by shortening the exducer portion of the rotor blade and redistributing the blade aerody- namic loading forward. A three-dimensional, multiblade-row, Euler design code (ref. I) was utilized to design the airfoil geometry. The final blade shapes were selected based on aero- dynamic performance and rotor stress levels. Figure 1com- pares the two compact rotors with a conventional baseline rotor having an equal power requirement. The length and diameter reductions specified for the compact rotors are rela- tive to a number of high-work radial inflow turbines found in the literature (refs. 5 to 11). The comparison reveals a 40- to 52-percent reduction in axial length and a 4-percent reduction in diameter of the compact rotor relative to conventional tur- bines scaled to a 3119-hp requirement. The single stator designed for both rotors has 36 constant- section stator vanes and is shown in figure 2. The vanes have tran- sonic exit velocities. The two compact rotors are shown in the photographs of figure 3: rotor I (3(a)) and rotor II (3(b)). Both rotors had 14 blades with elliptical leading edges. The inducer portion of rotor I had radial elements whereas the leading edge of rotor II had a slight sweep to minimize a leading edge over- speed condition associated with the reduced tip speed. h specific work, Btu/lb m J conversion constant, 778 ft-lbt4Btu ' mass flow, lbm/sec N rotor speed, rpm P pressure, lbf/in. 2 Re Reynolds number, m/pD t T absolute temperature, R U blade speed, ft/sec V absolute velocity, ft/sec VR velocity ratio, [Ut/(2gJAh' t )1/2] W relative velocity, (2gJAh') 1/2,ft/sec WF work factor, gJAh'/U 2 _x absolute flow angle, deg fl relative flow angle, deg 7 ratio of specific heats ratio of inlet total pressure to U.S. standard sea-level pressure, P[/P* e specific-heat-ratio correction, 0.740/{712/(7+I)]7/(7-1)} r/ efficiency 0 squared ratio of critical velocity at turbine inlet to critical velocity at U.S. standard sea-level temperature, (Vcr, lNc r )2 /2 viscosity lb/sec-ft

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