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Andrew L. Banka, P.E. Airflow Sciences Corpora1on [email protected] D. Sco4 MacKenzie, PhD, FASM Houghton Interna1onal, Inc [email protected]
Parameters Effec?ng Submerged Plumes in Quench Systems
2
Agenda
• Introduc1on ▲ Background ▲ Overview
• Simula1on Study ▲ System Descrip1on ▲ CFD Model
• Results • Discussion • Conclusions
3
Introduc1on -‐ Background
• Agita1on is cri1cal ▲ Purpose is uniform heat transfer
▲ Low distor1on ▲ Reduce thermal gradients
• Agita1on achieved ▲ Impellers ▲ Pumps and Nozzles ▲ Both commonly used
4
Introduc1on -‐ Background
• Impellers • Pumps
▲ OMen used ♦ Centrifugal pumps
■ Low ini1al cost ■ Low wear
▲ Applica1ons ♦ Quench Chutes ♦ Open tanks
• Lack of significant literature on nozzles for quenching applica1ons
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Introduc1on -‐ Overview
• Goal ▲ Objec1ve assessment of quench tank parameters and nozzle performance ♦ Nozzle size (diameter)
♦ Nozzle length
▲ Performance characterized using CFD
▲ Water as quenching medium
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Simula1on Study – System Descrip1on
• Typical Quench Tank ▲ Size 3.65m x 1.83m x 2.44m
(L x W x D)
▲ Single nozzle header along tank centerline 300mm above tank boaom.
▲ Header is 100mm OD pipe
▲ 5 nozzles on 600mm centers
▲ Two return openings for return flow to the pump
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Simula1on Study – System Descrip1on
• Nozzles ▲ Diameter
♦ 25.40, 23.86, 20.32 mm ▲ Extensions
♦ 1” Schedule 40 pipe (1.315” OD)
♦ 0, 25.4, 50.8 and 76.2 mm long
▲ Five nozzles ▲ Flow
♦ 31.5 Liters per second total flow (500 GPM)
♦ 6.3 Liters per second each nozzle (100 GPM)
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Simula1on Study – CFD Model
• Assumed ▲ Standard water proper1es at ambient (25°C) ▲ All surfaces hydraulically smooth (except
upper liquid surface) ▲ Upper surface had symmetry boundary
condition to approximate a free surface ▲ Flow into nozzle header specified as
uniform velocity profile ▲ Water returns at constant pressure
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Simula1on Study – CFD Model
• Computa1onal Grid ▲ Used GAMBIT for gridding
▲ Hexahedral cells – interior of header and direct vicinity of nozzles ♦ Smaller cells near nozzle exits to provide greater resolu1on
▲ Balance of grid is polyhedral cells ▲ Total of 8.5 million cells
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Results
• CFD simula1ons using AZORE®
▲ 12 cases ♦ 3 nozzle diameters ♦ 4 extension lengths
▲ Due to symmetry, plumes lie on centerline
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Results – Header Sta1c Pressure
• Nozzle Size ▲ Pressure loss strongly affected
by nozzle diameter ▲ Longer extension length
resulted in lower pressure loses
• Extensions ▲ Provide more ver1cal flow ▲ More even mass flow split ▲ Lower overall system pressure
loss
• Predominate pressure losses occur at header nozzle interface
Bulk of Pressure losses occur at the nozzles
17
Results – Jet Core Velocity Drop
• Velocity Decay ▲ 75% decay corresponds to
14 nozzles diameters
▲ Can be used to design effec1ve “throw”
▲ Directed flow range is limited but can be used to bulk fluid movement.
• Nozzle Diameters ▲ Smaller nozzle diameters
exhibit greater penetra1on
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Results – Ver1cal Velocity
• Upwards flow shows similar results ▲ 2% difference between cases ▲ No systemic varia1on ▲ Integra1on shows average
mass flows of 705 kg/s • 22X amplifica1on in flow rate • Velocity spread
▲ Width of nozzle flow achieving 1 m/s velocity is about 190 mm (all cases)
▲ Suggests smaller spacing should be used ♦ Assuming used to direct flow ♦ Not bulk fluid mo1on
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Conclusions
• From the results of the analysis, the following can be concluded: ▲ Open holes in the header show momentum effects reducing the
overall width of the flow field. ▲ Nozzle extensions, straighten the flow, and provide a more even
mass flow split between nozzles at a lower total supply pressure. ▲ Nozzle extensions provide for more even flow between the
nozzles. ▲ The effec1ve “throw” at 75% of maximum velocity of nozzles is
approximately 14 nozzle diameters. ▲ Within the range of nozzle sizes tested, smaller nozzles with
higher exit veloci1es did not appear to have any advantages • Results apply to an empty quench tank and could vary
significantly for cases where a load is present
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References
• [1] GAMBIT Users Guide. • [2] ANSYS-‐Fluent 15 Users Guide. • [3] Azore® Users Guide, 2011, Azore® Technologies,
LLC. • [4] “Houghton on Quenching”, Houghton
Interna1onal, Valley Forge Interna1onal, Inc., 1992. • [5] D.S. MacKenzie, B. Lynn Ferguson, ICPMCS 2010,
May 31-‐June 01, Shanghai, China. • [6] B. Liscic, H. Tensi, L. Canale, G. Toaen,
“Quenching Theory and Technology”, CRC Press, Boca Raton FL (2010) p.477.
• [7] G.E. Toaen, C.E. Bates, N.A. Clinton, “Handbook of Quenchants and Quenching Technology, ASM
• Interna1onal, Metals Park, OH, (1993). • [8] S. W. Han, S.H. Kang, G.E. Toaen, G. E. Webster,
“Principles and Applica1ons of Immersion Time Quenching Systems in Batch and Con1nuous Furnaces”, Heat Trea1ng: Equipment and Processes,
• ASM Interna1onal, (1994) 337-‐345. • [9] Michael Volk, “Pump Characteris1cs and
Applica1ons”, CRC Press, Boca Raton, FL, (2013).
• [10]Frank, M. W., Fluid Mechanics, Fourth Edi1on, McGraw-‐Hill Series in Mechanical Engineering, University of Rhode Island, (2001).
• [11] Bloomer. J. J., Prac1cal Fluid Mechanics For Engineering Applica1ons, Marcel Dekker Inc., New York, (2000).
• [12] Krause, E., Fluid Mechanics, Springer Berlin Heidelberg New York, (2005).
• [13] Lewis, W. R., Nithiarasu, P., Seetharamu, N. K., Fundamentals of the Finite Element Method for Heat and Fluid Flow, John Wiley & Sons, New York, (2004).
• [14] Ionel Olaru, “The Fluid Flow Simula1on through a Venturi Nozzle”, Journal of Engineering Studies and Research – Volume 19 (2013) No. 1, pp 42-‐46.
• [15] A. Bernstein, W. H. Heiser, C. Hevenor, Compound-‐ Compressible Nozzle Flow”, Trans. ASME, September (1967), pp 548-‐554.
• [16] A. Banka, T. Lee, “Comparison of Nozzle Vs. Impeller Agita1on in Quench Systems”, ASM Heat Treat 2013, September 16-‐18, Indianapolis, Indiana.