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. ) ( mm/m ) mm/m( . . . . . Evapcool ( kwh/yr ) ( . ) REFERENCES 1. Bahadori, M. ‘Natural cooling in Hot arid regions’ in Solar Energy Applications in Buildings. (Bahadori, M., Sayigh, A.), New York Academic Press, 1978. 2. Bahadori, M., ‘An Improved design of wind towers for natural ventilation and passive cooling’, in Solar Energy, Vol. 35, No. 2, pp119-129. Pergamon Press, 1985. 3. Konya, A. ‘Design Primer for Hot Climates’. The Architectural Press, London, 1980. 4. Cain, A., Ashfar, F., and Norton, J. ‘Indigenous Building and the Third World’. Architectural Design, Vol. 45, No. 4., April, 1975, pp 207-224. 5. Grosso, M. ‘Il Raffrescamento passivo negli edifici’, Maggioli Editore, Rimini, 1997, pp. 163, 164. 6. WSP Environmental Ltd., London, UK; Axima Lab., Winterthur, CH.7. Meteonorm 4.0, 2000.
Evapcool CFD )(
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Dan Int-Hout, Leon Kloostra :
:
habibahmady@hotmail.com
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Figure 1: Vertical jet projection, effect of T.T50 throw distance.
Figure 3: Throw and drop for outlet without ceiling. 20° vertical
Figure 2: Throw and drop for outlet 2 to 4 ft (0.6 to 1.3 m) below
deflection, 0° spread.
ceiling. 20° upward vertical deflection, 0° spread.
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Figure 4: Throw and drop for outlet 1 ft below ceiling. 0°
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Figure 6: Throw and drop for outlet 1.5 ft below ceiling. 20° vertical, 45° spread.
Figure 7: Throw and drop for outlet 2 to 4 ft below ceiling. 0° vertical deflection, 45° spread.
Figure 8: Specific airflow characteristics at high and low airflow rates.
Figure 9: Circular ceiling pattern diffuser.
Figure 10: Cross-flow pattern diffuser.
Figure 11: Spreading horizontal projection.
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Figure 12: Displacement ventilation.
Table 1: Summarizes Figures 2 through 7.
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AMCA 210 ASHRAE FUNDAMENTAL 32 (1) CENTRIFUGAL FAN)S( (2) SYSTEM EFFECT (3)AMCA: AIR MOVEMENT ASSOCIATION (4) UNIFORM (5) fpm: FEET PER MINUTE (6) SYSTEM EFFECT FACTOR
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. . ) ( ) ( . . . . . CFM ASHRAE . . CFM . CFM ) ( CFM CFM . . CFM . ( . CFM ) . ) HVI( CFM . CFM CFM CFM . . ) ( . ) ( . CO )CPSC(
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Figure 1. A fan curve illustrates the effect of static pressure on the performance of the fan. As the pressure (imposed by the resistance of the hood, exhaust duct, and tightness of the house) increases, the flow decreases.
. .) ( CFM CFM . .) ( .
Figure 2. A house will become more depressurized as its tightness increases or as the size of the kitchen fan is increased.
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1- Bruce Manclark is co-owner of Delta-T, an energy services company in Eugene, Oregon. He has spent 20 years in energy conservation. Reference: www.HOMEENERGY.org
. . .
: : . . . . CFM . : : . . . : : . .
)... ( H. Kotani, T. Yamanaka, Y. Momoi :
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of airflow in room with complex shaped diffuserpart 2 .Proc .Technical Meetin of Kinki Branch of AIJJapan :245248)in Japanese(. 8 .Sftware Cradle Co .Ltd .2000 .STREAM for Windows version 4 User Guide Osaka. 9 .Srevric J .Q .Chen .2001 .A method of testto obtain diffuser data for CFD modeling of room airflow ASHRAE Trans .Vol .107)2(: 108116.
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1 .Gosman A.D. P.V. Nielsen A. Restivo and J.H.Whitelaw 1980. The flow properties o f rooms with small ventilation openings Transactions of ASME Vol. 102: 316323. 2 .HiranoT. R. Sato T. Yamanaka H.Kotani and K. Miyamoto. 1997. Measurement of the airflow velocity and turvulent energy around anemostat type diffuser to patch onto CFD. Proc. Technical Meeting of SHASEJapan: 509512)in Japanese( 3 .Kondo Y.Y .NagasawaT. Moriya M.Sekiguchi and K .Harimoto. 2001. Modeling of complex ceiling diffuser in CFD part1 and 2.Proc. Technical Meeting of SHASEJapan: 717724 )in Japanese( 4 .NielsenP.V. A. Restivo and J.H.Whitelaw.1978.The velocity characteristics of ventilated rooms journal of Fluid Engineering Vol. 100:291298. 5 .Nielsen P.V.1992 .Description of supply openings in numerical models for room air distribution ASHRAE Transactions Vol.98)1(: 963971. 6 .Okaichi A.T.Yamanaka H .Kotani and M.Kato.2000.Study on CFD of rooms with anemostat type diffuserpart 2 .Proc .Technical Meeting of Kinki branch of AIJJapan :245248 )in Japanese(. 7 .Okaichi A.T.YamanakaH.Kotaniand Y .Momori .2001.CFD
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Farshid momeni@yahoo.com
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