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Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001](https://image.slidesharecdn.com/random-240902064228-57806802/75/Introduction-pdf-9-2048.jpg)
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Introduction ℙ𝕦𝕞𝕡𝕚𝕟𝕘 𝕄𝕒𝕔𝕙𝕚𝕟𝕖𝕣𝕪.pdf
- 1. Pumping Machinery 2001 ASMEFluids Engineering Division Summer Meeting Dr. Adiel Guinzburg
- 2. What is Turbomachinery? Usingworking fluids to Boost output, either increase or decrease pressure by using Machinery Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 3. High Pressure FuelTurbopump Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 4. High Pressure OxygenTurbopump Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 5. Turbomachine Classification • Turbines.Pumps and Compressors • Incompressible. Compressible • Axial-flow, Mixed-flow, Radial-flow geometry • Single stage. Multi-stage • Turbo-pump. Turbo-compressor. Torque-converter • Impulse. Reaction Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 6. From Customer Requirementsto Final Product • Specification • Preliminary Design, Conceptual design, ... • Component Design • Component Test, Analysis • Acceptance Test • ..... Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 7. Design Trade-offs • Performance •Weight • Cost • Life • Reliability • Structural Strength • Maintainability • Envelope Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 8. Design Process • In-housedesign database - scale • Detail design – (2D, Quasi 3D, CFD <=> stress analysis • Test Data Evaluation Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 9. Turbomachine ] gz) 2 v (h gz) 2 v [(h m Ps in 2 out 2 + + − + + = & FluidsEngineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 10. Turbines • Impart KineticEnergy to rotor as Mechanical Energy of rotation • Impulse – high Pressure, low Flow • Reaction – low Pressure, high Flow Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 11. Pump Classification Fluids EngineeringDivision Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 12. Centrifugal Pump • rotor,stator – accelerate flow by imparting kinetic energy – decelerate (diffuse) in stator – results in increase in fluid pressure Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 13. Elements of aCentrifugal Flow Pump • From Huzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 14. Rotor • Inducer • Impeller •Bearings • Shaft Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 15. Inducer • Axial flow •Increase total pressure • permits non cavitating operation in impeller • used as boost pump, permits main pump to operate at higher speeds • e.g. LPOTP is only inducer Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 16. Inducer Fluids Engineering DivisionAnnual Summer Meeting, New Orleans, LA, 29 May 2001
- 17. Stator • Casing • Diffuservanes • Volute • Seals Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 18. Vane Island Diffuser (shownwithout shroud) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 19. Impeller Profiles • Axial Flow MixedFlow Radial Flow From BWIP pump pocket book Ns Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 20. Pump Configurations • FromHuzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 21. Velocity Triangle • FromHuzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 22. Velocity Triangle • FromHuzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 23. Impeller Loss Components •Skin Friction • Blade Loading • Incidence • Wake Mixing • Impeller-shroud Clearance Leakage • Disk Friction • Recirculation Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 24. Flow Variables PT =P + ρv2 PT = P + ρ (vθ 2 + vm 2) hT = h + ρv2 + gz 2 2 1 2 1 1 Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 25. Dimensionless Quantities • Headcoefficient • Flow Coefficient 2 2 R gH Ω = Ψ R A Q Ω = Φ Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 26. Head rise ) v (v g u H 1 2θ θ − = Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 27. Isentropic Enthalpy Rise ∆H=144.∆p/ρ ∆P(psi) ∆H (ft) ρ(lb/ft3) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 28. Affinity Laws • Q~ ΩD3 • H ~ Ω2D2 • T ~ ρΩ2D5 • P ~ ρΩ3D5 Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 29. Engine System Resistanceand Pump Characteristics • From Huzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 30. Specific speed 4 3 2 1 (gH) Q s Ω = Ω • Consistentunits – Ω (rad/s) – Q (m3/s) – H (m) • US 2734.6 Ns s = Ω 4 3 2 1 (ft.) RPM.(GPM) Ns = Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 31. Impeller Profiles • Axial Flow MixedFlow Radial Flow From BWIP pump pocket book Ns Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 32. Effect of Nson H-Q curve • From Cameron Hydraulic Data Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 33. Profiles and EfficienciesBased on Specific Speed Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 34. Issues • H-Q instability •Stall • Cavitation induced dynamic pressure • Radial loads • Discharge and suction recirculation Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 35. Separation and Stall Jetand wake observed in each impeller passage. The eddying wake is seen on the suction side of the channel from Fischer and Thoma, 1932 Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 36. Recirculation Secondary flows ina centrifugal pump from Brennen (1994) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 37. Recirculation Sudden increase inpressure pulsation from Fraser (1981) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 38. Stator Effect onHead Characteristics (steepens H-Q curve) • reduce impeller inlet Cu at low flow • increase impeller inlet Cu at high flow • provide stability over wide operating range • increase stator and impeller incidence angle at off design • reduces inception of stall with negative incidence Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 39. Vaned Diffuser Effecton Head Characteristics (flattens H-Q curve) • convert kinetic energy of fluid leaving the impeller into static pressure rise • flow incidence sensitive • leading edge stall phenomenon believed to be cause of loss of diffuser performance • rapid head falloff at low flow Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 40. 0 0.2 0.4 0.6 0.8 1 1.2 1.4 0.3 0.4 0.50.6 0.7 0.8 0.9 1 1.1 1.2 1.3 Flow/Flow des Pump Head/Pump Head des WFR no stall no diffuser stall no stator stall Stator stall Diffuser stall Impeller stall Stall Characteristics Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 41. Two-Dimensional Diffuser Map FlowRegimes in Straight Wall, Two-Dimensional Diffusers from Moore and Kline, 1955. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 42. Slot Optimization Slot geometryconfiguration optimization from Gostelow and Watson, 1972. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 43. Blade Loading From Guinzburget al. (1997) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 44. CFD as aTool • Before using a particular CFD code in a rotating machinery component design process, it is important to bracket the accuracy of the code results for that particular type of component. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 45. Interpretation of CFD •Another important issue is how accurately the component inlet flow boundary conditions have to be known (pre- computation) to get results that are consistent with test data. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 46. CFD Process • Validatea computational fluid dynamic code for integration into the impeller design process. • The validation process consists of computing the impeller flow for a range of inlet conditions. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 47. Accuracy of theCFD Results • number of nodes used to discretize the flow domain • accuracy of the numerical discretization scheme • type of turbulence model used. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 48. CFD Capabilities • TransientAnalysis • Two Phase Flow • Heat Transfer • Temperature Dependent Properties • Moving Mesh • Non-inertial Reference Frames • Selection of Turbulence Models • Wall Function Models Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 49. Diffusion The diffusion factorD, can be adapted for pumps from Lieblein (1965) as follows: 1 1 2 1 2 1 2 W 2 V r r V + W W - 1 = D σ θ θ − Duncombe (1964) explicitly examined the diffusion on both the suction (s) and pressure (p) sides of the blade and expressed the result as follows: W W - 1 + W W - 1 = D 1 min p, max s, 2 Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 50. Cavitation Typical cavity configurationwithin an impeller. Flowrate is half that of BEP; so, the cavity is broken up by recirculating flow. From Sloteman et al (1995). Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 51. Cavitation • Thoma number,cavitation number 2 2 1 v v p - p ρ σ = Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 52. Suction Specific speed 4 3 2 1 (gNPSH) Q ss Ω = Ω •Consistent units – Ω (rad/s) – Q (m3/s) – NPSH (m) • US 2734.6 Nss ss = Ω 4 3 2 1 (ft.) RPM.(GPM) Nss = Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 53. Pump Suction Performance •From Huzel, D. K. and Huang, D. H. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 54. Bucket Curve 0 1 2 3 4 5 6 7 8 9 10 0 0.20.4 0.6 0.8 1 1.2 1.4 1.6 φ/φd NPSH/NPSH d design point Predicted Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 55. Experimental Inducer Cavitation FluidsEngineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 56. Leading Edge CavitationDamage Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 57. Typical Pump performancecurve, showing NPSH required a) to maintain hydraulic performance or pump head (NPSHR), b) to limit cavitation damage and therefore maintain pump life (NPSHd), c) to prevent bubble formation entirely (NPSHi) from Cooper and Antunes(1983) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 58. Pump Losses • mechanical •hydraulic • disk friction • leakage Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 59. Radial Load Fluids EngineeringDivision Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 60. Radial Load Profilesfor Volutes of Different Specific Speed Pumps Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 61. Axial Calculation Fluids EngineeringDivision Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 62. Axial Load BalancingSchemes • Seal Leakage Return Path • Pump out ribs or vanes • Balance Drum • Balance Disk Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 63. Pump Balance Piston FluidsEngineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 64. Rotordynamics Relationship between theforces in the pump frame and the rotordynamic forces from Brennen (1994) Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 65. Impact Testing Fluids EngineeringDivision Annual Summer Meeting, New Orleans, LA, 29 May 2001
- 66. References • Anderson, H.H. Centrifugal pumps. The Trade and Technical Press Ltd., England • Balje, O. E. (1981). Turbomachines. A guide to selection and theory. John Wiley and Sons, New York. • BWIP Pump Pocket Book. • Brennen, C. E. 1994. Hydrodynamics of Pumps. Concepts ETI, Inc. and Oxford University Press. New York. • Brennen, C. E. 1995. Cavitation and Bubble Dynamics. Oxford University Press. New York. • Cameron Hydraulic Data. (1988) Ingersoll-Rand Company. • Cooper, P. and Antunes, F. F. 1983. “Cavitation damage in boiler feed pumps.” Symposium Proceedings on: Power Plant Feed Pumps - The State of the Art, EPRI CS-3158, Cherry Hill, New Jersey, pp. 2.24-2.29. • Csanady, G. T. (1964) Theory of turbomachines. McGraw-Hill, New York. • Duncombe, E., 1964, “Aerodynamic Design of Axial Flow Turbines,” in Aerodynamics of Turbines and Compressors, W. R. Hawthorne, Ed., Princeton University Press, p. 512. • Fraser, W. H. 1981. “Recirculation in Centrifugal Pumps,” Materials of Construction of Fluid Machinery and Their Relationship to Design and Performance, ASME Nov. 15-20. Pp. 65-86. • Fischer, K. and Thoma, D. 1932. “Investigation of flow conditions in a centrifugal pump,” Transactions of the ASME, Vol. 54, pp. 141-155. • Furst, R B. (1973) Liquid Rocket Engine Centrifugal Flow Turbopumps. NASA SP-8109. • Karassik, I. J. And Carter, R. (1960) Centrifugal pumps. F. W. Dodge Corporation, New York • Huzel, D. K. and Huang, D. H. Modern Engineering for Design of Liquid-Propellant Rocket Engines. AIAA, Washington D. C. • Katsanis, T., and McNally, W. D., 1969, “Revised Fortran Program for Calculating Velocities and Streamlines on a Blade-to-Blade Stream Surface of a Turbomachine,” NASA TM X-1764. • Katsanis, T., and McNally, W. D., 1977, “Revised Fortran Program for Calculating Velocities and Streamlines on the Hub-Shroud Stream Surface of an Axial-, Radial-, or Mixed-Flow Turbomachine or Annular Duct,” NASA TN D-8430. • Lazarkiewicz, S. And Troskolanski, A. T. (1965) Impeller pumps. Pergamon Press, New York • Leiblein, S., “Experimental Flow in Two-Dimensional Cascades,” in Aerodynamic Design of Axial-Flow Compressors, NASA SP-36, p. 203. • Macaluso, S B. (1974) Liquid Rocket Engine Centrifugal Flow Turbopumps. NASA SP-8110. • Sloteman, D. P., Wotring, T. L., March, P., McBee, D, and Moody, L. 1995. “Experimental evaluation of high energy pump improvements including effects of upstream piping,” Proceedings of the 12th International Pump Users Symposium, Houston, Texas. • Stepanoff, A. J. (1973) Centrifugal and axial flow pumps. John Wiley and Sons, New York. Fluids Engineering Division Annual Summer Meeting, New Orleans, LA, 29 May 2001