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Fouling Mechanisms in Axial Compressors
Volume 4: Cycle Innovations; Fans and Blowers; Industrial and Cogeneration; Manufacturing Materials and Metallurgy; Marine; Oil and Gas Applications, 2011Fouling of compressor blades is an important mechanism leading to performance deterioration in gas turbines over time. Fouling is caused by the adherence of particles to airfoils and annulus surfaces. Particles that cause fouling are typically smaller than 2 to 10 microns. Smoke, oil mists, carbon, and sea salts are common examples.
Rainer Kurz, Klaus Brun
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Rotating stall in axial compressors
Zeitschrift für angewandte Mathematik und Physik ZAMP, 1955The phenomenon known as ‘rotating stall’ is described. Basically, it involves a nonuniform pattern of flow, steadily rotating relative to both the fixed and the rotating blades of axial-flow compressors. Attempts to analyze the phenomenon by means of small-perturbation theories are reviewed.
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Axial Compressor Stator Aerodynamics
Journal of Engineering for Gas Turbines and Power, 1985Axisymmetric, through-flow calculations, currently the “backbone” of most multistage turbomachinery design systems, are being pushed to their limit. This is due to the difference between the complex, three-dimensional flows that actually occur in turbomachinery and the two-dimensional flow assumed in this type of analysis.
H. D. Joslyn, R. P. Dring
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1981
The axial flow compressor is the second type of dynamic compressor, whose general nature and capabilities were introduced in section 1.3. It absorbs energy from an external power source, raising the pressure of a continuous flow of working fluid by means of its blading geometry and motion.
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The axial flow compressor is the second type of dynamic compressor, whose general nature and capabilities were introduced in section 1.3. It absorbs energy from an external power source, raising the pressure of a continuous flow of working fluid by means of its blading geometry and motion.
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Axial Compressors and Turbines
2012With the definition of the work coefficient in (6.4a) and (6.4b), we can now write from (4.22a) to (4.22d) the nondimensional azimuthal velocity component expressions as follows: $$ \frac{{{{c}_{\rm{u1}}}}}{u} = \left( {1 - \hat{r}} \right) - \frac{\Psi}{4} $$ $$ \frac{{{{c}_{\rm{u2}}}}}{u} = \left( {1 - \hat{r}} \right) + \frac{\Psi}{4} $$
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Stall control for axial compressors *
IFAC Proceedings Volumes, 1999Abstract Rotating stall is a primary constraint for the performance of flow compressors. This paper establishes a necessary and sufficient condition for a feedback controller to locally stabilize the critical equilibrium of the uniform flow at the inception of rotating stall.
Siva S. Banda +3 more
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Dynamic control of axial compressors
Proceedings of the 1997 IEEE International Conference on Control Applications, 2002Several control laws have been formulated by other authors to stabilize the low-order nonlinear state-space model of an axial compression system developed by Moore and Greitzer (1986). Using static nonlinear feedback, these control laws extend the stable operating range of the compressor system. This paper considers the merits of using dynamic feedback
B. D. Coller +3 more
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Axial Compressor Performance Maintenance
Volume 4: Turbo Expo 2005, 2005Methods of compressor performance maintenance for large utility combustion turbines continue to evolve. On-line water wash systems used to recover performance loss due to fouling are evolving that use less water. This paper derives a water wash model based on a thin film of water covering the airfoil surfaces.
Philip Levine, Leonard Angello
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Centrifugal and Axial Compressors
2016This chapter and Chap. 10 treat the rotating modules of both aero engines and gas turbines. These modules are compressible turboachinery (or turbomachines). Let us first introduce a definition for turbomachines. The word (turbo) or (turbines) is of Latin origin, meaning “that which spins or whirls around.” Though compressible turbomachines may be fans,
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1979
The only additional material here over that in chapter 4 is that it is convenient in the velocity diagrams to specify angles δ and γ for trigonometric purposes and polytropic stage efficiency is of importance since axial compressors, which are usually multistage machines are mostly designed on the basis of one stage with an assumed constant stage ...
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The only additional material here over that in chapter 4 is that it is convenient in the velocity diagrams to specify angles δ and γ for trigonometric purposes and polytropic stage efficiency is of importance since axial compressors, which are usually multistage machines are mostly designed on the basis of one stage with an assumed constant stage ...
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