Rotary kinetic fluid motors or pumps – Working fluid passage or distributing means associated with... – Plural distributing means immediately upstream of runner
Reexamination Certificate
1999-11-05
2001-11-06
Look, Edward K. (Department: 3745)
Rotary kinetic fluid motors or pumps
Working fluid passage or distributing means associated with...
Plural distributing means immediately upstream of runner
C416S22300B
Reexamination Certificate
active
06312219
ABSTRACT:
BACKGROUND OF THE INVENTION
The present invention relates generally to gas turbine engines, and, more specifically, to compressors or fans therein.
In a turbofan aircraft gas turbine engine, air is pressurized in a fan and compressor during operation. The fan air is used for propelling an aircraft in flight. The air channeled through the compressor is mixed with fuel in a combustor and ignited for generated hot combustion gases which flow through turbine stages that extract energy for powering the fan and compressor.
A typical turbofan engine includes a multistage axial flow compressor which pressurizes the air sequentially to produce high pressure air for combustion. The compressed air is diffused and decelerates as it is compressed. Compressor airfoils must therefore be designed to reduce undesirable flow separation which would adversely affect stall margin and efficiency.
Conversely, combustion gases are accelerated through the turbine stages, and the turbine blades have different aerodynamic designs for maximizing efficiency of energy extraction.
Fundamental in compressor design is efficiency in compressing the air with sufficient stall margin over the entire flight envelope of operation from takeoff, cruise, and landing.
However, compressor efficiency and stall margin are normally inversely related, with increasing efficiency typically corresponding with decrease in stall margin. The conflicting requirements of stall margin and efficiency are particularly demanding in high performance military engine applications, as opposed to less demanding commercial applications, which require high level of stall margin typically at the expense of compressor efficiency.
Maximizing efficiency of compressor airfoils is primarily effected by optimizing the velocity distributions over the pressure and suction sides of the airfoil. However, efficiency is typically limited in conventional compressor design by the requirement for a suitable stall margin. Any further increase in efficiency typically results in a reduction in stall margin, and, conversely, further increase in stall margin results in decrease in efficiency.
High efficiency is typically obtained by minimizing the wetted surface area of the airfoils for a given stage to correspondingly reduce airfoil drag. This is typically achieved by reducing airfoil solidity or the density of airfoils around the circumference of a rotor disk, or by increasing airfoil aspect ratio of the chord to span lengths.
For a given rotor speed, this increase in efficiency reduces stall margin. To achieve high levels of stall margin, a higher than optimum level of solidity may be used, along with designing the airfoils at below optimum incidence angles. This reduces axial flow compressor efficiency.
Increased stall margin may also be obtained by increasing rotor speed, but this in turn reduces efficiency by increasing the airfoil Mach numbers, which increases airfoil drag.
Compressor performance is also affected by the cooperation of compressor rotor blades and stator vanes. A row of blades extends radially outwardly from a supporting rotor disk and rotates during operation within a surrounding stator casing. A corresponding row of stator vanes is disposed directly upstream from the blades for controlling airflow thereto.
The stator vanes typically have radially outer tips mounted in an annular outer band, and radially inner roots suitably mounted in a radially inner band which typically supports an inner seal. Such mounting is typically effected by stabbing the individual vanes through complementary apertures in the bands, and securing the vanes thereto by brazing or welding for example. The individual vanes are typically straight and rigid for undergoing this manufacturing process without distortion.
However, typical vanes have relatively uniform radial profiles from root to tip and limit efficiency of operation and stall margin. The bands define endwalls along which boundary layers of air form during operation and affect performance. Aerodynamic or diffusion loading of the vanes is higher near the endwalls than the midspan regions of the vanes, and the vane-endwall interfaces are subject to flow separation along the vane suction sides near the trailing edges as the air diffuses during operation.
Accordingly, typical compressor design necessarily includes a compromise between efficiency and stall margin favoring one over the other. And, differences in blade and vane designs additionally complicate compressor design. It is, therefore, desired to further improve both compressor efficiency and stall margin by enhancing compressor vanes and improving cooperation with corresponding compressor blades.
BRIEF SUMMARY OF THE INVENTION
A compressor stator vane includes pressure and suction sides extending chordally between leading and trailing edges, and longitudinally between a root and a tip. The vane narrows in chord to a waist between the root and tip. The vane may also be bowed at its trailing edge in cooperation with the narrow waist.
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Decker John J.
Mielke Mark J.
Seitzer Kenneth E.
Steinmetz Gregory T.
Wood Peter J.
General Electric Company
Hess Andrew C.
Look Edward K.
McAleenan James
Young Rodney M.
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