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风量试验台在不同送风方式下整流效果分析.pdf

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1、37 1 2009 M 1 S / v (1 S)J. Huazhong Univ. of Sci. p V S “(20060487036). ANSI/AMCA STANDARD 210-85, ANSI/ASHRAE STANDARD 51-85, Laboratory methods of testing fansfor rating purposes, 1985. k Z T/ rTs周 拨1 游 斌1,2 谢军龙1 吴克启1(1华中科技大学能源与动力工程学院, 湖北武汉430074;2广东美的空调公司博士后工作站, 广东顺德528311)K1: N-SZSk-EZ 1 !9 k d

2、 ZT( / )/ rT s,TV )s ,iBYYV M I ( ,KY Z T .YV Z T rT1 ,) k d F a .T + ? k !9# ,4 G I.1 o M: ; k ; I “d; ; = +ms |: TK21 DS M : A cI|: 1671-4512(2009)01-0126-04Rectification effects of orifice plate unit in the air volumetesting equipment at two typed-sendingZhou Bo1 You B in 1, 2 X ie J unlong1 Wu K

3、 eqi1(1 College of Energy and Power Engineering, Huazhong University of Science and Technology, Wuhan430074, China;2 PostdoctoralResearch Center, Midea Air Conditioner Co. , Shunde 528311, Guangdong China)Abstract: The rectification effect of orifice plate unit in the self designed air volume test a

4、pparatus attwo kindsof send (the side send/ the up send) was simulatednumerically based on three-dimensionalNavier-Stokes (N-S) equations coupledwith standard k-Eturbulence model. The result indicates thatthe separating flow at the turning jams the measuring flow passage and affects the coming flow

5、un-iformity relative to the nozzles, at last affects the measurement accuracy of the equipment at the upsend. Through comparing the rectification effect at two kinds of sending, the rectification mechanismthat the orifice plate unit accelerates mainstream anddissipatesvortex isdiscussed. Thethesisai

6、ms tomake a contribution for designing the similar external characteristics service test and further evalua-ting the equipment precision.Key words: orifice plate unit; air volume testing equipment; mult-inozzle measurement system; flowmeasurement; internal flow characteristicsY+ ? VY!9. = 4G 1 . I“d

7、 , kaz+,y/Y+ ? n . + ? wL,A g |“ LB#I - V L.Fluid qGvM1S1 !930 000 m3/h I“d k = E,1 g 2 ZT/ rT, 2 Z T k.) k d .T V + k 2 5 !9# 4G N I.1 rTs1 5F130000 m3/h k“d k !9 a#9 sWnD6.m1 Kv !9 30 000 m3/h H2m1 30000 m3/h O m Z T = O m.Vm1(a) V A Z_V g g ,m1(b) AC2Q|,2 Z TQ uZ$ 8Bv 7.m1(a) Z T, 8 -, 8 ;m1(b) Z

8、 T, 8 -, ? 3|), L1 u A I HZ_,i OY1 2 W u . k d Z T/ rTs, L= 9 ) ( Y.+ ? L s i isYb m2 U3 , I4 ( / . 9 F7,W 0. 1 , Z_Y 1sY60 %,50%45 %,V0.5 %.m2 Uimm3YV3 L#3 sm.m3(a) Z T 8v,19 ,y7M , Z T Z T,14 ? .YV I - ,M I ( ,8CH ( s, I - | V L, Z TI 7 f /, 0s ( ;7 Z T, sB 0,y7 I - L= M Z Tv.8 V / :a.5 Z T, i A Z

9、 T, ? A rT; Z T 8YV /11 Z TvBt, Z T v,14S ? X .YV1 Z T rT,) dF a .b. Z T,1i Q !9, P |“ g LM.c.1 Z T I - | s,v , Z T, |“sCBd ( ;7 Z T s ( .V Z T I -|“ iB ,V7Y k. ID1 EckI B. Fans: design andoperations of centrifugal,axia-l flow and cross-flow fansM. New York: Perg-amum Press, 1973.2 , , X ,. b ? k“d

10、!9 LCJ. 8, 2002, 30(1): 51-53.3,.l + k J. 8, 1994, 22(1): 25-30.4 , F, . b ? k L b ZEJ. L/ 5 ,2002, 19(5): 38-41.5 ,3,A(.V g: + kTYsJ./ , 1999(2):9-11.6 m, , + C,. 8+ ? k = J. , 2006(S1): 137-140.5 S/v(1 S)6/=Sn S/ 0|2008 M1122 25 ,Sn1 S12Q M/=Sn #+ S/ 0vyK .1 Sn S/ 600Vp.s S/ ,Sn1 S 7Z /=Sn #+ S/ 0 1.N 1 S/ 76, S/ 118,+ S/ 53,n5 S/v(1 S)6 /Sn S/ 0|.#129#1 m: k Z T/ rTs

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