浙江大学学报(工学版)
浙江大學學報(工學版)
절강대학학보(공학판)
JOURNAL OF ZHEJIANG UNIVERSITY(ENGINEERING SCIENCE)
2015年
2期
309-314
,共6页
董永申%王定标%向飒%夏春杰
董永申%王定標%嚮颯%夏春傑
동영신%왕정표%향삽%하춘걸
倾斜螺旋片%计算流体力学%火积耗散
傾斜螺鏇片%計算流體力學%火積耗散
경사라선편%계산류체역학%화적모산
oblique helical fins%computational fluid dynamics%entransy dissipation
为了减小螺旋片强化的套管换热器的摩擦阻力系数 f ,提出倾斜螺旋片强化的方法.基于RNG k‐ε模型对倾斜螺旋片强化的套管换热器进行模拟;将 Re=2362~16860的螺旋升角α=35°,螺旋片倾斜角β=5°、10°、15°时的传热性能与光滑管以及α=35°的普通螺旋片强化管的传热性能进行对比;考察 f、N u和综合传热性能PEC值的变化规律;并运用火积耗散理论对传热性能进行分析.结果表明:模拟结果与实验结果吻合较好,证明模拟方法是可行的;普通螺旋片和倾斜螺旋片均有强化传热的作用,与普通螺旋片相比,倾斜螺旋片能够有效地减小 f,且对 f的减小程度随着β的增大呈现先增大后减小的趋势,分别减小了1.7%~3.3%、12.5%~14.5%和6.3%~7.8%;N u随着β的增大呈现先减小后增大的趋势,但变化不大;倾斜螺旋片的 PEC值均高于普通螺旋片,当β=10°时PEC值最高,相对于普通螺旋片的1.26~1.62,增大到1.38~1.71;采用倾斜螺旋片强化的火积耗散率均低于采用普通螺旋片强化的火积耗散率,当β=10°时,火积耗散率最小,与等泵功条件下所得出的结论吻合.
為瞭減小螺鏇片彊化的套管換熱器的摩抆阻力繫數 f ,提齣傾斜螺鏇片彊化的方法.基于RNG k‐ε模型對傾斜螺鏇片彊化的套管換熱器進行模擬;將 Re=2362~16860的螺鏇升角α=35°,螺鏇片傾斜角β=5°、10°、15°時的傳熱性能與光滑管以及α=35°的普通螺鏇片彊化管的傳熱性能進行對比;攷察 f、N u和綜閤傳熱性能PEC值的變化規律;併運用火積耗散理論對傳熱性能進行分析.結果錶明:模擬結果與實驗結果吻閤較好,證明模擬方法是可行的;普通螺鏇片和傾斜螺鏇片均有彊化傳熱的作用,與普通螺鏇片相比,傾斜螺鏇片能夠有效地減小 f,且對 f的減小程度隨著β的增大呈現先增大後減小的趨勢,分彆減小瞭1.7%~3.3%、12.5%~14.5%和6.3%~7.8%;N u隨著β的增大呈現先減小後增大的趨勢,但變化不大;傾斜螺鏇片的 PEC值均高于普通螺鏇片,噹β=10°時PEC值最高,相對于普通螺鏇片的1.26~1.62,增大到1.38~1.71;採用傾斜螺鏇片彊化的火積耗散率均低于採用普通螺鏇片彊化的火積耗散率,噹β=10°時,火積耗散率最小,與等泵功條件下所得齣的結論吻閤.
위료감소라선편강화적투관환열기적마찰조력계수 f ,제출경사라선편강화적방법.기우RNG k‐ε모형대경사라선편강화적투관환열기진행모의;장 Re=2362~16860적라선승각α=35°,라선편경사각β=5°、10°、15°시적전열성능여광활관이급α=35°적보통라선편강화관적전열성능진행대비;고찰 f、N u화종합전열성능PEC치적변화규률;병운용화적모산이론대전열성능진행분석.결과표명:모의결과여실험결과문합교호,증명모의방법시가행적;보통라선편화경사라선편균유강화전열적작용,여보통라선편상비,경사라선편능구유효지감소 f,차대 f적감소정도수착β적증대정현선증대후감소적추세,분별감소료1.7%~3.3%、12.5%~14.5%화6.3%~7.8%;N u수착β적증대정현선감소후증대적추세,단변화불대;경사라선편적 PEC치균고우보통라선편,당β=10°시PEC치최고,상대우보통라선편적1.26~1.62,증대도1.38~1.71;채용경사라선편강화적화적모산솔균저우채용보통라선편강화적화적모산솔,당β=10°시,화적모산솔최소,여등빙공조건하소득출적결론문합.
Oblique helical fins was proposed to reduce f ,the frictional Resistance coefficient ,of double‐pipe heat exchanger enhanced by helical fins ,and RNG k‐e epsilon model was used to simulate double‐pipe heat exchanger enhanced by oblique helical fins .With Re ,the Reynolds number ,varying from 2 362 to 16 860 ,the heat transfer performance of double‐pipe heat exchanger w hose α,the helix angle ,equals 35° and β,the oblique angle of helical fins ,equals 5° ,10° and 15° was compared with that of smooth double‐pipe heat exchanger and double‐pipe heat exchanger enhanced by ordinary helical fins w hose αequals 35° , and the change rule of f ,Nu and PEC ,the comprehensive heat transfer performance with the same pump power ,were analyzed . Also , the entransy dissipation theory was used to analyze the heat transfer performance .Results show that the ordinary helical fins ,w hoseβequals 0 ,and oblique helical fins both have the effect of enhancement .Compared with ordinary helical fins ,oblique helical fins can effectively decrease f ,and its degree of decrease on f decreases after increasing with the increase of β,respectively a reduce of 1 .7%‐3 .3% ,12 .5%‐14 .5% and 6 .3%‐7 .8% . Nu firstly decreases then increases with the increase of β,but the change is not big .The PEC values of oblique helical fins are higher than that of ordinary helical fins .When βequals 10 ° ,PEC ,relative to ordinary helical fins ,increases to 1 .38‐1 .71 from 1 .26‐1 .62 .The entransy dissipation rate of oblique helical fins is lower than that of ordinary helical fins ,and the entransy dissipation rate is the lowest when βequals 10 ° ,which is identical with the conclusion obtained with the same pump power .