锯齿螺旋翅片管束强化换热特性研究
|
摘要
与传统的连续螺旋翅片管相比，锯齿螺旋翅片管制作简便、翅化比大且换热更强，已在联合循环余热锅炉等大型烟气热能回收装置中得到应用。但当前对其强化换热特性的基础研究较少，以往相关研究中不同研究者所得结论也不尽一致，制约了该换热管型的有效使用与广泛应用。本文在分析锯齿螺旋翅片管束强化换热机理的基础上，对锯齿螺旋翅片管错列管束的强化换热特性进行了较为全面的实验与数值模拟研究。
在高温回流传热风洞中对12个锯齿螺旋翅片管束进行了实验研究，获得了横向管距、纵向管距及翅片间距在Re=4000~30000范围对管束换热特性和阻力特性的影响，并提出了相应的管束换热及阻力计算关联式，为相关工程提供了大量基础数据和设计依据。利用Fluent软件对10个实验管束的翅侧流动与换热特性进行了数值模拟，并根据实验结果对本文数值模拟方法及模拟结果进行了检验，结果表明二者相符较好。设计了28个模拟管束，在Re=10000~40000范围就相关结构因素对管束强化换特性的影响进行了数值模拟研究。其中，锯齿高度、锯齿宽度和锯齿扭角是锯齿螺旋翅片管特有的结构参数，本文首次对上述结构参数的影响进行了研究。此外，还通过数值模拟方法对翅片结构不同的4类钢质螺旋翅片管进行了比较。
在紧凑式换热器换热表面综合性能比较方法的基础上，针对气流横掠管束换热的场合，提出了比较管束迎风面积、换热面积和空间体积的3种管束综合性能评价方法。本文不仅分析和比较了各结构因素对管束换热及阻力特性的影响，还比较了各结构因素对管束迎风面积、换热面积及空间体积的影响，所得结论为换热管束的结构优化提供了清晰的指导方向。
通过本文实验与数值模拟研究，发现在相同换热量和流体输运功耗下各结构因素对管束综合性能的影响为：
(1)在相同纵向管距下，减小横向管距可减少管束换热面积和管束体积，但同时也使管束迎风面积增大；在相同横向管距下，存在最佳纵向管距使得管束迎风面积和换热面积最小，但管束体积随纵向管距增大而增大。
(2)随横向管距与纵向管距等比例增大，管束迎风面积减小，换热面积增大，管束体积明显增大。管距紧密布置可减少管束换热面积和管束体积，但同时迎风面积增大，换热管束外形趋于迎风面积大流道长度短的扁平状。
(3)在相同斜向管距下随管束横向/斜向流通面积之比增大，管束迎风面积先减小后增大，管束换热面积和管束体积均趋于增大。较小的横向/斜向流通面积之比有利于减少管束换热面积和管束体积，但需注意横向/斜向流通面积之比过小会使管束迎风面积明显增大。
(4)管束迎风面积随翅片高度增大而增大；管束换热面积随翅片高度减小而减小，但考虑到翅片与基管的成本差异，一定翅片间距下存在一最佳翅片高度使得换热管投资最小；管束体积随翅片高度增大而减小，但这种影响随翅片高度增大而逐渐减弱。随着翅片间距增大，管束迎风面积稍有增大，管束换热面积基本不变，管束体积明显增大。
(5)随着锯齿高度增大，管束迎风面积明显增大，换热面积略微减小；在翅片管制作工艺允许的范围内，适度减小锯齿高度可进一步减小设备体积。锯齿宽度对管束迎风面积，换热管投资及管束体积均影响不大。
(6)管束迎风面积在0°~60°范围随锯齿扭角增大而增大，在实际工程应用的锯齿扭角范围15°~30°，扭齿螺旋翅片管束的迎风面积较锯齿螺旋翅片管束增大约8%~12%；管束换热面积与管束体积在0°~30°范围均随锯齿扭角增大而减小（约5%），但在扭角30°~60°范围基本不变。
(7)在相同的管间距和换热管结构下与连续螺旋翅片管束相比，I型锯齿螺旋翅片管、L型锯齿螺旋翅片管和扭齿螺旋翅片管的管束迎风面积分别增大约10%、23%和30%，管束换热面积分别减少约9%、6%和12%。连续螺旋翅片管、I型锯齿螺旋翅片管和扭齿螺旋翅片管在管束体积方面无明显差异，但L型锯齿螺旋翅片管的管束体积增大约18%。
Serrated fin tubes have the advantages of easy manufacturing, the larger finnedratio and the enhanced heat transfer in comparison with the conventional solid fintubes, and have been applied in various large scale heat exchangers with flue gasemissions, such as the combined cycle heat recovery steam generators (HRSGs), etc.However, the number of the published researches on the heat transfer and pressuredrop of serrated fin tube banks is very limited, and the experimental results of thedifferent researchers are mostly inconsistent on the effects of various structure factors.Such status quo hampers the efficient use and widespread application of serrated fintube. Based on the theoretically analyses of the principles of the heat transferenhancement of serrated fin tube banks, this paper performed a comprehensiveinvestigation on the thermal and hydraulic characteristics of serrated fin tube bankswith staggered layouts by means of a lot of experiments and numerical simulations.
Twelve tube banks with different tube spacing and fin pitch were tested in a hightemperature circulating wind tunnel, resultingly obtained the respective effects oftransversal tube spacing, longitudinal tube spacing and fin pitch on the thermal andhydraulic characteristics of serrated fin tube banks in the range of Renolds numberfrom4000to30000. Based on the test data from this paper, a set of heat transfer andpressure drop correlations were presented for the related engineering design orcalculation. Then, ten testing banks were simulated using the Fluent software tovalidate the numerical methods of this paper by means of comparing the numericalresults of the heat transfer and pressure drop of tube banks, respectively, with thecorresponding experimental results. The comparison results show that the numericalresults coincided with the experimental results satisfactorily. Afterwards, twenty-eighttube banks were designed and simulated in the range of Renolds number from10000to40000, resultingly obtained the effects of almost all related structure factors on thethermal and hydraulic characteristics of serrated fin tube banks. Among which thesegment height, segment width and segment twist-angle are the particular structureparameters of serrated fin tube, this paper studied the effects of those structure factorson the thermal and hydraulic characteristics of tube banks for the first time. Moreover,this paper compared four types of helically finned tube banks by means of numericalsimulation, they were the solid fin, serrated I-foot fin, serrated L-foot fin and serratedtwist-fin tube banks, respectively.
Based on the evaluation methodologies of the overall thermal-hydraulicperformances for the compact heat exchangers, this paper presented three evaluationmethodologies of the overall thermal-hydraulic performances for the heat exchangerswith crossflow tube banks, to compare the frontal flow areas, heat transfer areas andspatial volumes of tube banks, respectively, in a certain heat duty and transportingpower consumption of the tube outside gas. In this paper, the effects of structurefactors were compared and analyzed not only on the heat transfer and pressure drop oftube banks, but also on the overall thermal-hydraulic performances of tube banks,hence the conclusions drawn by this paper can directly guide the structureoptimization of serrated fin tube banks.
From the experimental and numerical investigations of this paper, the effects ofvarious structure factors on the overall thermal-hydraulic performances of the serratedfin tube banks with staggered layouts were founded as follow:
(1) In certain longitudinal tube spacing, a decrease in transversal tube spacingcould result in a decrease in the heat transfer areas and spatial volumes of tube banks,while would increase the frontal flow areas of tube banks simultaneously. In certaintransversal tube spacing, there would be an optimal longitudinal tube spacing tominimize the frontal flow areas and heat transfer areas of tube banks, while the spatialvolumes of tube banks always increased as the longitudinal tube spacing increased.
(2) An equal propotional increase in the transversal and longitudinal tube spacingwould result in a moderate decrease and increase in the frontal flow areas and heattransfer areas of tube banks, respectively, but a significant increase in the spatialvolumes of tube banks. It means that the compact tube layouts is of benefit todecreasing the heat transfer areas and spatial volumes of tube banks, while the shapesof tube banks will tend to a pancake having a large frontal flow area and a short flowlength due to the accompanying increase in the frontal flow areas of tube banks.
(3) In certain diagnol tube spacing, an increase in the ratios of transversal-diagnolfree flow areas of tube banks would result in an increase in the heat transfer areas andspatial volumes of tube banks, while the frontal flow areas of tube banks were firstlydecreased and then increased as the ratios of transversal-diagnol free flow areasincreased. So a small ratios of transversal-diagnol free flow areas is of benefit todecreasing the heat transfer areas and spatial volumes of tube banks, but it should beconcerned that the spatial volumes of tube banks will be increased dramatically as the ratio of transversal-diagnol free flow areas is very small.
(4) An increase in fin height would result in an increase in the frontal flow areasand heat transfer areas of tube banks; there would be an optimal fin height tominimize the cost of finned tubes in view of the cost deffierence between fin and basetube. The spatial volumes of tube banks tended to decrease as the fin height increased,whereas the decrease extents were decreasing as the fin height increased. Thevariation of fin pitch had an insignificant effect on the frontal flow areas and heattransfer areas of tube banks, while the spatial volumes of tube banks would increasedistinctly with an increase in fin pitch.
(5) An increase in segment height would result in an obvious increase in thefrontal flow areas and a slightly decrease in the heat transfer areas of tube banks.Within the allowable limits of the manufacturing process of serrated fin tube, themoderate decrease in segment height could make a further decrease in the spatialvolumes of tube banks. The variation of segment width had an insignificant effect onthe frontal flow areas, heat transfer areas and spatial volumes of tube banks.
(6) In the range of segment twist-angle from0°to60°, an increase in segmenttwist-angle would result in an increase in the frontal flow areas of tube banks. In thepractical range of segment twist-angle from15°to30°, the frontal flow areas ofserrated twist-fin tube banks would be increased approximately8%~12%incomparison with the serrated fin tube banks without fin twisting. Both the heattransfer areas and spatial volumes of serrated twist-fin tube banks decreasedapproximately5%as the segment angles increased from0°to30°, and then basicallyremained unchanged as the the segment angles increased from30°to60°.
(7) Compared with the solid fin tube bank in a certain tube spacing and thestructural parameters of finned tube, the frontal flow areas of serrated I-foot fin,serrated L-foot fin and serrated twist-fin tube banks increased approximately10%,23%and30%, respectively; and the heat transfer areas of those corresponding tubebanks decreased approximately9%,6%and12%, respectively. The spatial volumes ofthe solid fin, serrated I-foot fin and serrated twist-fin tube banks were almost same,while the spatial volumes of the serrated L-foot fin tube bank increased approximately18%relative to the solid fin tube bank.
在高温回流传热风洞中对12个锯齿螺旋翅片管束进行了实验研究，获得了横向管距、纵向管距及翅片间距在Re=4000~30000范围对管束换热特性和阻力特性的影响，并提出了相应的管束换热及阻力计算关联式，为相关工程提供了大量基础数据和设计依据。利用Fluent软件对10个实验管束的翅侧流动与换热特性进行了数值模拟，并根据实验结果对本文数值模拟方法及模拟结果进行了检验，结果表明二者相符较好。设计了28个模拟管束，在Re=10000~40000范围就相关结构因素对管束强化换特性的影响进行了数值模拟研究。其中，锯齿高度、锯齿宽度和锯齿扭角是锯齿螺旋翅片管特有的结构参数，本文首次对上述结构参数的影响进行了研究。此外，还通过数值模拟方法对翅片结构不同的4类钢质螺旋翅片管进行了比较。
在紧凑式换热器换热表面综合性能比较方法的基础上，针对气流横掠管束换热的场合，提出了比较管束迎风面积、换热面积和空间体积的3种管束综合性能评价方法。本文不仅分析和比较了各结构因素对管束换热及阻力特性的影响，还比较了各结构因素对管束迎风面积、换热面积及空间体积的影响，所得结论为换热管束的结构优化提供了清晰的指导方向。
通过本文实验与数值模拟研究，发现在相同换热量和流体输运功耗下各结构因素对管束综合性能的影响为：
(1)在相同纵向管距下，减小横向管距可减少管束换热面积和管束体积，但同时也使管束迎风面积增大；在相同横向管距下，存在最佳纵向管距使得管束迎风面积和换热面积最小，但管束体积随纵向管距增大而增大。
(2)随横向管距与纵向管距等比例增大，管束迎风面积减小，换热面积增大，管束体积明显增大。管距紧密布置可减少管束换热面积和管束体积，但同时迎风面积增大，换热管束外形趋于迎风面积大流道长度短的扁平状。
(3)在相同斜向管距下随管束横向/斜向流通面积之比增大，管束迎风面积先减小后增大，管束换热面积和管束体积均趋于增大。较小的横向/斜向流通面积之比有利于减少管束换热面积和管束体积，但需注意横向/斜向流通面积之比过小会使管束迎风面积明显增大。
(4)管束迎风面积随翅片高度增大而增大；管束换热面积随翅片高度减小而减小，但考虑到翅片与基管的成本差异，一定翅片间距下存在一最佳翅片高度使得换热管投资最小；管束体积随翅片高度增大而减小，但这种影响随翅片高度增大而逐渐减弱。随着翅片间距增大，管束迎风面积稍有增大，管束换热面积基本不变，管束体积明显增大。
(5)随着锯齿高度增大，管束迎风面积明显增大，换热面积略微减小；在翅片管制作工艺允许的范围内，适度减小锯齿高度可进一步减小设备体积。锯齿宽度对管束迎风面积，换热管投资及管束体积均影响不大。
(6)管束迎风面积在0°~60°范围随锯齿扭角增大而增大，在实际工程应用的锯齿扭角范围15°~30°，扭齿螺旋翅片管束的迎风面积较锯齿螺旋翅片管束增大约8%~12%；管束换热面积与管束体积在0°~30°范围均随锯齿扭角增大而减小（约5%），但在扭角30°~60°范围基本不变。
(7)在相同的管间距和换热管结构下与连续螺旋翅片管束相比，I型锯齿螺旋翅片管、L型锯齿螺旋翅片管和扭齿螺旋翅片管的管束迎风面积分别增大约10%、23%和30%，管束换热面积分别减少约9%、6%和12%。连续螺旋翅片管、I型锯齿螺旋翅片管和扭齿螺旋翅片管在管束体积方面无明显差异，但L型锯齿螺旋翅片管的管束体积增大约18%。
Serrated fin tubes have the advantages of easy manufacturing, the larger finnedratio and the enhanced heat transfer in comparison with the conventional solid fintubes, and have been applied in various large scale heat exchangers with flue gasemissions, such as the combined cycle heat recovery steam generators (HRSGs), etc.However, the number of the published researches on the heat transfer and pressuredrop of serrated fin tube banks is very limited, and the experimental results of thedifferent researchers are mostly inconsistent on the effects of various structure factors.Such status quo hampers the efficient use and widespread application of serrated fintube. Based on the theoretically analyses of the principles of the heat transferenhancement of serrated fin tube banks, this paper performed a comprehensiveinvestigation on the thermal and hydraulic characteristics of serrated fin tube bankswith staggered layouts by means of a lot of experiments and numerical simulations.
Twelve tube banks with different tube spacing and fin pitch were tested in a hightemperature circulating wind tunnel, resultingly obtained the respective effects oftransversal tube spacing, longitudinal tube spacing and fin pitch on the thermal andhydraulic characteristics of serrated fin tube banks in the range of Renolds numberfrom4000to30000. Based on the test data from this paper, a set of heat transfer andpressure drop correlations were presented for the related engineering design orcalculation. Then, ten testing banks were simulated using the Fluent software tovalidate the numerical methods of this paper by means of comparing the numericalresults of the heat transfer and pressure drop of tube banks, respectively, with thecorresponding experimental results. The comparison results show that the numericalresults coincided with the experimental results satisfactorily. Afterwards, twenty-eighttube banks were designed and simulated in the range of Renolds number from10000to40000, resultingly obtained the effects of almost all related structure factors on thethermal and hydraulic characteristics of serrated fin tube banks. Among which thesegment height, segment width and segment twist-angle are the particular structureparameters of serrated fin tube, this paper studied the effects of those structure factorson the thermal and hydraulic characteristics of tube banks for the first time. Moreover,this paper compared four types of helically finned tube banks by means of numericalsimulation, they were the solid fin, serrated I-foot fin, serrated L-foot fin and serratedtwist-fin tube banks, respectively.
Based on the evaluation methodologies of the overall thermal-hydraulicperformances for the compact heat exchangers, this paper presented three evaluationmethodologies of the overall thermal-hydraulic performances for the heat exchangerswith crossflow tube banks, to compare the frontal flow areas, heat transfer areas andspatial volumes of tube banks, respectively, in a certain heat duty and transportingpower consumption of the tube outside gas. In this paper, the effects of structurefactors were compared and analyzed not only on the heat transfer and pressure drop oftube banks, but also on the overall thermal-hydraulic performances of tube banks,hence the conclusions drawn by this paper can directly guide the structureoptimization of serrated fin tube banks.
From the experimental and numerical investigations of this paper, the effects ofvarious structure factors on the overall thermal-hydraulic performances of the serratedfin tube banks with staggered layouts were founded as follow:
(1) In certain longitudinal tube spacing, a decrease in transversal tube spacingcould result in a decrease in the heat transfer areas and spatial volumes of tube banks,while would increase the frontal flow areas of tube banks simultaneously. In certaintransversal tube spacing, there would be an optimal longitudinal tube spacing tominimize the frontal flow areas and heat transfer areas of tube banks, while the spatialvolumes of tube banks always increased as the longitudinal tube spacing increased.
(2) An equal propotional increase in the transversal and longitudinal tube spacingwould result in a moderate decrease and increase in the frontal flow areas and heattransfer areas of tube banks, respectively, but a significant increase in the spatialvolumes of tube banks. It means that the compact tube layouts is of benefit todecreasing the heat transfer areas and spatial volumes of tube banks, while the shapesof tube banks will tend to a pancake having a large frontal flow area and a short flowlength due to the accompanying increase in the frontal flow areas of tube banks.
(3) In certain diagnol tube spacing, an increase in the ratios of transversal-diagnolfree flow areas of tube banks would result in an increase in the heat transfer areas andspatial volumes of tube banks, while the frontal flow areas of tube banks were firstlydecreased and then increased as the ratios of transversal-diagnol free flow areasincreased. So a small ratios of transversal-diagnol free flow areas is of benefit todecreasing the heat transfer areas and spatial volumes of tube banks, but it should beconcerned that the spatial volumes of tube banks will be increased dramatically as the ratio of transversal-diagnol free flow areas is very small.
(4) An increase in fin height would result in an increase in the frontal flow areasand heat transfer areas of tube banks; there would be an optimal fin height tominimize the cost of finned tubes in view of the cost deffierence between fin and basetube. The spatial volumes of tube banks tended to decrease as the fin height increased,whereas the decrease extents were decreasing as the fin height increased. Thevariation of fin pitch had an insignificant effect on the frontal flow areas and heattransfer areas of tube banks, while the spatial volumes of tube banks would increasedistinctly with an increase in fin pitch.
(5) An increase in segment height would result in an obvious increase in thefrontal flow areas and a slightly decrease in the heat transfer areas of tube banks.Within the allowable limits of the manufacturing process of serrated fin tube, themoderate decrease in segment height could make a further decrease in the spatialvolumes of tube banks. The variation of segment width had an insignificant effect onthe frontal flow areas, heat transfer areas and spatial volumes of tube banks.
(6) In the range of segment twist-angle from0°to60°, an increase in segmenttwist-angle would result in an increase in the frontal flow areas of tube banks. In thepractical range of segment twist-angle from15°to30°, the frontal flow areas ofserrated twist-fin tube banks would be increased approximately8%~12%incomparison with the serrated fin tube banks without fin twisting. Both the heattransfer areas and spatial volumes of serrated twist-fin tube banks decreasedapproximately5%as the segment angles increased from0°to30°, and then basicallyremained unchanged as the the segment angles increased from30°to60°.
(7) Compared with the solid fin tube bank in a certain tube spacing and thestructural parameters of finned tube, the frontal flow areas of serrated I-foot fin,serrated L-foot fin and serrated twist-fin tube banks increased approximately10%,23%and30%, respectively; and the heat transfer areas of those corresponding tubebanks decreased approximately9%,6%and12%, respectively. The spatial volumes ofthe solid fin, serrated I-foot fin and serrated twist-fin tube banks were almost same,while the spatial volumes of the serrated L-foot fin tube bank increased approximately18%relative to the solid fin tube bank.
引文
[1]赵毅.我国发电企业节能现状与技术措施.热力透平,2008,37(2):71-76.
[2] http://www.cec.org.cn
[3]吕学勤,刘刚,黄自元.电力调峰方式及其存在的问题.电站系统工程，2007,23(5):37-40.
[4]闫廷满.燃气联合循环的新发展.东方电气评论，2003,17(1):15-19.
[5] Pilavachi P A. Power generation with gas turbine systems and combine heat andpower. Applied Thermal Engineering,2000,20(15):105-108.
[6]焦树建.燃气－蒸汽联合循环的理论基础.北京:清华大学出版社,2003.
[7]徐明.燃气－蒸汽联合循环发电装置的热力特性及燃气轮机热经济性分析.能源技术,2003,24(3):100-102.
[8]李为华,朱庚富.燃气－蒸汽联合循环发电机组的清洁生产特性.电力环境保护,2003,19(4):20-22.
[9]陈孙艺.高频焊螺旋翅片管的缺陷形式及成因分析.锅炉制造,2008(1):54-57.
[10] Reid D R, Taborek J. Selection Criteria for Plain and Segmented Fined Tubes forHeat Recovery Systems. ASME Journal of Engineering for Gas Turbines andPower,1994,116(4):406-410.
[11] Briggs D E, Young E H. Convective heat transfer and pressure drop of air flowingacross triangular pitch banks of finned tubes. Chemical Engineering ProgressSymposium Series.1963,59(41):1-10.
[12] Robinson K K, Briggs D E. Pressure drop of air flowing across triangular pitchbanks of finned tubes. Chemical Engineering Progress Symposium Series.1966,62(64):177-184.
[13] Mirkovic Z. Heat Transfer and Flow Resistance Correlation for Helically Finnedand Staggered Tube Banks in Cross-flow, Heat Exchangers: Design and TheorySource Book, edited by Afgan and Schlunder, USA: Hemisphere,1974,559-584.
[14] Zukauskas A A.换热器内的对流传热.北京:科学出版社,1986.
[15]曹家甡.高频焊接螺旋翅片管的换热和阻力特性.东方电气评论,1996,8(2):78-81.
[16] Khavin A A. Thermal and Aerodynamic Characteristics of Tube Banks withSpiral-Welded Ribbon Fins. Heat Transfer Research,1999,30(4):375-384.
[17]何法江,曹伟武,匡江红等.螺旋翅片管束传热和阻力特性的试验研究.动力工程学报,2009,29(5):460-464.
[18] Norris R H, Spofford W A. High-performance fins for heat transfer. Transactions ofASME,64:489-496.
[19] Schryber E A, Brooklyn N Y. Heat transfer coefficients and other data on individualserrated-finned surface. Transactions of the ASME.1945,67(8):683-686.
[20] Weierman C. Pressure Drop Data for Heavy-duty Finned Tubes. ChemicalEngineering Progress,1977,73(2):69-72.
[21] Weierman C, Taborek J, Marner W J. Comparison of the Performance of In-lineand Staggered Banks of Tubes with Segmented Fins. AIChE Symposium Series,San Francisco, Natl Heat Transfer Conf,15th, Heat Transfer, Res and App,1978,74(174):39-46.
[22] Rabas T J, Myers G A, Eckels P W. Comparison of the Thermal Performance ofSerrated High-finned Tubes Used in Heat-recovery Systems. ASME, Heat TransferDivision, Anaheim, Heat Transfer in Waste Heat Recovery and Heat RejectionSystems.1986,59:33-40.
[23] Martinez E, Vicente W, Salinas M, etc. Single-phase experimental analysis of heattransfer in helically finned heat exchanger. Applied Thermal Engineering,2009,29:2205-2210.
[24] Martinez E, Vicente W, Soto G, etc. Comparative analysis of heat transfer andpressure drop in helically segmented finned tube heat exchangers. Applied ThermalEngineering,2010,30:1470-1476.
[25]程贵兵,陈远国.齿型翅片管束传热及流阻性能实验研究.中国工程热物理学会传热传质学学术会议论文集.合肥,1998,47-52.
[26] Kawaguchi K, Okui K, Kashi T. Heat Transfer and Pressure Drop Characteristics ofFinned Tube Banks in Forced Convection (Comparison of the Pressure DropCharacteristics between Spiral Fin and Serrated Fin). Heat Transfer-AsianResearch,2004,33(7):431-444.
[27] Kawaguchi K, Okui K, Kashi T. Heat Transfer and Pressure Drop Characteristics ofFinned Tube Banks in Forced Convection (Comparison of the Heat TransferCharacteristics between Spiral Fin and Serrated Fin). Heat Transfer-AsianResearch,2005,34(2):120-133.
[28] Kawaguchi K, Okui K, Asai T, etc. The Heat Transfer and Pressure DropCharacteristics of the Finned Tube Banks in Forced Convection (Effects of FinHeight on Pressure Drop Characteristics). Heat Transfer-Asian Research,2006,35(3):179-193.
[29] Kawaguchi K, Okui K, Asai T, etc. The Heat Transfer and Pressure DropCharacteristics of the Finned Tube Banks in Forced Convection (Effects of FinHeight on Heat Transfer Characteristics). Heat Transfer-Asian Research,2006,35(3):194-208.
[30] N ss E. Experimental investigation of heat transfer and pressure drop inserrated-fin tube bundles with staggered tube layouts. Applied ThermalEngineering,2010,30:1531-1537.
[31] Weierman C. Correlations ease the selection of fin tubes. Oil and Gas Journal,1976,74(6):94-100.
[32] ESCOA Corp. ESCOA Fintube Manual. Tulsa, OK: ESCOA,1979.
[33] Ganapathy V. Industrial boilers and heat recovery steam generators. Marcel Dekker,Inc.,2003:419-428.
[34] Annaratone D. Steam generators. Springer,2008:410-418.
[35] Engineering Data Book (Twelfth Edition-FPS). Gas Processors SuppliersAssociation,2004:8.1-8.10.
[36] Nir A. Heat transfer and friction factor correlations for cross-flow over staggeredfinned tube banks. Heat Transfer Engineering,1991,12(1):43-58.
[37] VDI Heat Atlas,2nd edition. Springer,2010.
[38] Weierman C. Pressure Drop Data for Heavy-duty Finned Tubes. ChemicalEngineering Progress,1977,73(2):69-72.
[39] Sparrow E M, Myrum T A. Crossflow heat transfer for tubes with periodicallyinterrupted annular fins. International Journal of Heat and Mass Transfer.1985,28(2):509-512.
[40]卓宁,蒋伟元,王坚,等.齿型螺旋翅片管束传热及通风特性试验研究.华东工业大学学报,1996,18(1):23-26.
[41] Holman J P. Heat Transfer,9th ed. New York: McGraw Hill,2001.
[42]马义伟.空冷器设计与应用.哈尔滨:哈尔滨工业大学出版社,1998.
[43] Shah R K, Sekulic D P. Fundamentals of heat exchanger design. John Wiley&Sons, Inc.,2003:700-702.
[44] London A L, Compact heat exchangers, Part2, Surface geometry, Mech. Eng.,1964,86, June:31-34.
[45] Shah R K. Compact heat exchanger surface selection methods, Heat Transfer1978,Proc.6th Int. Heat Transfer Conf.,1978,4:193-199.
[46] Kays W M, London A L. Compact heat exchangers,3rd ed. New York: McGrawHill,1984.
[47] Webb R L, Kim N. Principles of Enhanced Heat Transfer,2nd ed. New York:Taylor&Francis,2005.
[48] Gardner K A. Efficiency of extended surface. Trans. ASME,1945,67:621-631.
[49] Kraus A D, Aziz A, Welty J. Extended surface heat transfer. John Wiley&Sons,Inc.,2001.
[50] Schmidt Th E. Improved methods for calculation of heat transfer on finned surfaces.K ltetech Klim [in Germany].1966,18(4):135-138.
[51] Hong K T, Webb R L. Calculation of fin efficiency for wet and dry fins. Journal ofHVAC&R Research,1996,2(1):27-41.
[52] Acosta-Iborra A, Campo A. Approximate analytic temperature distribution andefficiency for annular fins of uniform thickness. International Journal of ThermalSciences,2009,48:773-780.
[53] Bahadori A, Vuthaluru H. Predictive tool for estimation of convection heat transfercoefficients and efficiencies for finned tubular sections. International Journal ofThermal Sciences,2010,49:1477-1483.
[54] Esmail M A. Heat transfer from extended surfaces subject to variable heat transfercoefficient. International Journal of Heat and Mass Transfer,2003,39:131-138.
[55] Lymer A, Ridal B F. Finned tubes in a crossflow of gas. Journal of British nuclearenergy conference,1961,307-313.
[56] Huang L J, Shah R K. Assessment of calculation methods for efficiency of straightfins of rectangular profile. International Journal of Heat and Fluid Flow,1992,13(3):282-293.
[57] Yudin V F, Tokhtarova L S. Investigation of the correction factor psi for thetheoretical effectiveness of a round fin. Thermal Engineering,1973,20(3):65-68.
[58] Shah R K, Sekulic D P. Fundamentals of heat exchanger design. John Wiley&Sons, Inc.,2003:283-286.
[59] Hashizume K, Morikawa R, Koyama T, etc. Fin efficiency of serrated fins. HeatTransfer Engineering,2002,23(2):6-14.
[60] Eckert E R G, Drake R M. Analysis of heat and mass transfer, New York: McGrawHill,1972.
[61]李之光.相似与模化（理论及应用）.北京:国防工业出版社,1982.
[62]庄礼贤,尹协远,马晖扬.流体力学（第2版）.合肥:中国科学技术大学出版社,2009.
[63] Lu C W, Huang J M, Nien W C, et al. A numerical investigation of the geometriceffects on the performance of plate finned-tube heat exchanger. Energy Conversionand Management,2011,52(3):1638-1643.
[64] Tao Y B, He Y L, Huang J, et al. Three-dimensional numerical study of wavyfin-and-tube heat exchangers and field synergy principle analysis. InternationalJournal of Heat and Mass Transfer,2007,50(5-6):1163-1175.
[65]于新娜,袁益超,马有福,等. H形翅片管束传热和阻力特性的试验与数值模拟.动力工程学报,2010,30(6):433-438.
[66]陶文铨等.传热与流动问题的多尺度数值模拟:方法与应用.北京:科学出版社,2008.
[67] He Y L, Han H, Tao W Q, et al. Numerical study of heat-transfer enhancement bypunched winglet-type vortex generator arrays in fin-and-tube heat exchangers.International Journal of Heat and Mass Transfer,2012, in press.
[68] Malapure V P, Mitra S K, Bhattachary A. Numerical investigation of fluid flow andheat transfer over louvered fins in compact heat exchanger. International Journal ofThermal Sciences,2007,46:199–211.
[69] Mi Sandar Mon, Ulrich Gross. Numerical study of fin-spacing effects inannular-finned tube heat exchangers. International Journal of Heat and Mass Transfer,2004,47:1953–1964.
[70] Rao Y, Xu Y M, Wan C Y. An experimental and numerical study of flow and heattransfer in channels with pin fin-dimple and pin fin arrays. Experimental Thermal andFluid Science,2012,38:237–247.
[71] Kalaiselvam S, Karthik P, Ranjit Prakash S. Numerical investigation of heattransfer and pressure drop characteristics of tube–fin heat exchangers in ice slurryHVAC system, Applied Thermal Engineering,2009,29:1831–1839.
[72] Sheik Ismail L, Ranganayakulu C, Shah Ramesh K. Numerical study of flowpatterns of compact plate-fin heat exchangers and generation of design data for offsetand wavy fins..International Journal of Heat and Mass Transfer,2009,52:3972–3983.
[73] Dogan M, Sivrioglu M. Experimental and numerical investigation of clearance gapeffects on laminar mixed convection heat transfer from fin array in a horizontalchannel-A conjugate analysis. Applied Thermal Engineering,2012,40:102-113.
[74] Levent Bilira, Zafer Ilken, Aytun Erek. Numerical optimization of a fin-tube gasto liquid heat exchanger. International Journal of Thermal Sciences,2012,52:59-72.
[75] Tang L H, Zeng M, Wang Q W. Experimental and numerical investigation onair-side performance of fin-and-tube heat exchangers with various fin patterns.Experimental Thermal and Fluid Science,2009,33:818–827.
[76] Dong J Q, Chen J P, Zhang W F, et al. Experimental and numerical investigation ofthermal-hydraulic performance in wavy fin-and-flat tube heat exchangers. AppliedThermal Engineering,2010,30:1377-1386.
[77] Song K W, Wang Y, Zhang Q, et al. Numerical study of the fin efficiency and amodified fin efficiency formula for flat tube bank fin heat exchanger. InternationalJournal of Heat and Mass Transfer,2011,54:2661–2672.
[78] Borrajo-Peláez R, Ortega-Casanova J, Cejudo-López J M. A three-dimensionalnumerical study and comparison between the air side model and the air/water sidemodel of a plain fin-and-tube heat exchanger. Applied Thermal Engineering,2010,30:1608-1615.
[79] Sahin H M, Dal A R, Baysal E.3-D Numerical study on the correlation betweenvariable inclined fin angles and thermal behavior in plate fin-tube heat exchanger.Applied Thermal Engineering,2007,27:1806–1816.
[80] Song W M, Meng J A, Li Z X. Numerical study of air-side performance of a finnedflat tube heat exchanger with crossed discrete double inclined ribs. Applied ThermalEngineering,2010,30:1797-1804.
[81] Tiwari S, Chakraborty D, Biswas G, et al. Numerical prediction of flow and heattransfer in a channel in the presence of a built-in circular tube with and without anintegral wake splitter. International Journal of Heat and Mass Transfer,2005,48:439–453.
[82] Islamoglu Y. Numerical analysis of the influence of a circular fin with differentprofiles on the thermal characteristics in a ceramic tube of heat transfer equipment.International Journal of Pressure Vessels and Piping,2004,81:583–587.
[83] Vessakosol P, Charoensuk J. Numerical analysis of heat transfer and flow fieldaround cross-flow heat exchanger tube with fouling. Applied Thermal Engineering,2010,30:1170–1178.
[84] Chang L M, Wang L B, Song K W. Numerical study of the relationship betweenheat transfer enhancement and absolute vorticity flux along main flow direction in achannel formed by a flat tube bank fin with vortex generators. International Journal ofHeat and Mass Transfer,2009,52:1794–1801.
[85] Perrotin T, Clodic D. Thermal-hydraulic CFD study in louvered fin-and-flat-tubeheat exchangers. International Journal of Refrigeration,2004,27:422–432.
[86] Zhang J H, Kundu J, Manglik R M. Effect of fin waviness and spacing on thelateral vortex structure and laminar heat transfer in wavy-plate-fin cores. InternationalJournal of Heat and Mass Transfer,2004,47:1719–1730.
[87] Tian L T, He Y L, Tao Y B, et al. A comparative study on the air-side performanceof wavy fin-and-tube heat exchanger with punched delta winglets in staggered andin-line arrangements. International Journal of Thermal Sciences,2009,48:1765–1776.
[88] Xie G N, Wang Q W, Sunden B. Parametric study and multiple correlations onair-side heat transfer and friction characteristics of fin-and-tube heat exchangers withlarge number of large-diameter tube rows. Applied Thermal Engineering,2009,29:1–16.
[89] Sahin B, Ozturk N A, Gurlek C. Horseshoe vortex studies in the passage of a modelplate-fin-and-tube heat exchanger. International Journal of Heat and Fluid Flow,2008,29:340–351.
[90] Sahiti N, Durst F, Geremia P. Selection and optimization of pin cross-sections forelectronics cooling. Applied Thermal Engineering,2007,27:111–119.
[91]王福军.计算流体动力学分析.北京:清华大学出版社,2004.
[92] Fluent6.0Users Guide. Lebanon, NH: Fluent Inc.,2001.
[93] Anderson D. Introduction to Computational Fluid Dynamics.北京:清华大学出版社,2004.
[94]陶文铨.数值传热学（第2版）.西安:西安交通大学出版社,2001.
[95] Pletcher R, Tannehill J, Anderson D. Computational Fluid Mechanics and HeatTransfer,3rd Edition. Taylor&Francis,2011.
[96] Lemouedda A, Schmid A, Franz E, etc. Numerical investigations for theoptimization of serrated finned-tube heat exchangers. Applied ThermalEngineering,2011,31:1393-1401.
[2] http://www.cec.org.cn
[3]吕学勤,刘刚,黄自元.电力调峰方式及其存在的问题.电站系统工程，2007,23(5):37-40.
[4]闫廷满.燃气联合循环的新发展.东方电气评论，2003,17(1):15-19.
[5] Pilavachi P A. Power generation with gas turbine systems and combine heat andpower. Applied Thermal Engineering,2000,20(15):105-108.
[6]焦树建.燃气－蒸汽联合循环的理论基础.北京:清华大学出版社,2003.
[7]徐明.燃气－蒸汽联合循环发电装置的热力特性及燃气轮机热经济性分析.能源技术,2003,24(3):100-102.
[8]李为华,朱庚富.燃气－蒸汽联合循环发电机组的清洁生产特性.电力环境保护,2003,19(4):20-22.
[9]陈孙艺.高频焊螺旋翅片管的缺陷形式及成因分析.锅炉制造,2008(1):54-57.
[10] Reid D R, Taborek J. Selection Criteria for Plain and Segmented Fined Tubes forHeat Recovery Systems. ASME Journal of Engineering for Gas Turbines andPower,1994,116(4):406-410.
[11] Briggs D E, Young E H. Convective heat transfer and pressure drop of air flowingacross triangular pitch banks of finned tubes. Chemical Engineering ProgressSymposium Series.1963,59(41):1-10.
[12] Robinson K K, Briggs D E. Pressure drop of air flowing across triangular pitchbanks of finned tubes. Chemical Engineering Progress Symposium Series.1966,62(64):177-184.
[13] Mirkovic Z. Heat Transfer and Flow Resistance Correlation for Helically Finnedand Staggered Tube Banks in Cross-flow, Heat Exchangers: Design and TheorySource Book, edited by Afgan and Schlunder, USA: Hemisphere,1974,559-584.
[14] Zukauskas A A.换热器内的对流传热.北京:科学出版社,1986.
[15]曹家甡.高频焊接螺旋翅片管的换热和阻力特性.东方电气评论,1996,8(2):78-81.
[16] Khavin A A. Thermal and Aerodynamic Characteristics of Tube Banks withSpiral-Welded Ribbon Fins. Heat Transfer Research,1999,30(4):375-384.
[17]何法江,曹伟武,匡江红等.螺旋翅片管束传热和阻力特性的试验研究.动力工程学报,2009,29(5):460-464.
[18] Norris R H, Spofford W A. High-performance fins for heat transfer. Transactions ofASME,64:489-496.
[19] Schryber E A, Brooklyn N Y. Heat transfer coefficients and other data on individualserrated-finned surface. Transactions of the ASME.1945,67(8):683-686.
[20] Weierman C. Pressure Drop Data for Heavy-duty Finned Tubes. ChemicalEngineering Progress,1977,73(2):69-72.
[21] Weierman C, Taborek J, Marner W J. Comparison of the Performance of In-lineand Staggered Banks of Tubes with Segmented Fins. AIChE Symposium Series,San Francisco, Natl Heat Transfer Conf,15th, Heat Transfer, Res and App,1978,74(174):39-46.
[22] Rabas T J, Myers G A, Eckels P W. Comparison of the Thermal Performance ofSerrated High-finned Tubes Used in Heat-recovery Systems. ASME, Heat TransferDivision, Anaheim, Heat Transfer in Waste Heat Recovery and Heat RejectionSystems.1986,59:33-40.
[23] Martinez E, Vicente W, Salinas M, etc. Single-phase experimental analysis of heattransfer in helically finned heat exchanger. Applied Thermal Engineering,2009,29:2205-2210.
[24] Martinez E, Vicente W, Soto G, etc. Comparative analysis of heat transfer andpressure drop in helically segmented finned tube heat exchangers. Applied ThermalEngineering,2010,30:1470-1476.
[25]程贵兵,陈远国.齿型翅片管束传热及流阻性能实验研究.中国工程热物理学会传热传质学学术会议论文集.合肥,1998,47-52.
[26] Kawaguchi K, Okui K, Kashi T. Heat Transfer and Pressure Drop Characteristics ofFinned Tube Banks in Forced Convection (Comparison of the Pressure DropCharacteristics between Spiral Fin and Serrated Fin). Heat Transfer-AsianResearch,2004,33(7):431-444.
[27] Kawaguchi K, Okui K, Kashi T. Heat Transfer and Pressure Drop Characteristics ofFinned Tube Banks in Forced Convection (Comparison of the Heat TransferCharacteristics between Spiral Fin and Serrated Fin). Heat Transfer-AsianResearch,2005,34(2):120-133.
[28] Kawaguchi K, Okui K, Asai T, etc. The Heat Transfer and Pressure DropCharacteristics of the Finned Tube Banks in Forced Convection (Effects of FinHeight on Pressure Drop Characteristics). Heat Transfer-Asian Research,2006,35(3):179-193.
[29] Kawaguchi K, Okui K, Asai T, etc. The Heat Transfer and Pressure DropCharacteristics of the Finned Tube Banks in Forced Convection (Effects of FinHeight on Heat Transfer Characteristics). Heat Transfer-Asian Research,2006,35(3):194-208.
[30] N ss E. Experimental investigation of heat transfer and pressure drop inserrated-fin tube bundles with staggered tube layouts. Applied ThermalEngineering,2010,30:1531-1537.
[31] Weierman C. Correlations ease the selection of fin tubes. Oil and Gas Journal,1976,74(6):94-100.
[32] ESCOA Corp. ESCOA Fintube Manual. Tulsa, OK: ESCOA,1979.
[33] Ganapathy V. Industrial boilers and heat recovery steam generators. Marcel Dekker,Inc.,2003:419-428.
[34] Annaratone D. Steam generators. Springer,2008:410-418.
[35] Engineering Data Book (Twelfth Edition-FPS). Gas Processors SuppliersAssociation,2004:8.1-8.10.
[36] Nir A. Heat transfer and friction factor correlations for cross-flow over staggeredfinned tube banks. Heat Transfer Engineering,1991,12(1):43-58.
[37] VDI Heat Atlas,2nd edition. Springer,2010.
[38] Weierman C. Pressure Drop Data for Heavy-duty Finned Tubes. ChemicalEngineering Progress,1977,73(2):69-72.
[39] Sparrow E M, Myrum T A. Crossflow heat transfer for tubes with periodicallyinterrupted annular fins. International Journal of Heat and Mass Transfer.1985,28(2):509-512.
[40]卓宁,蒋伟元,王坚,等.齿型螺旋翅片管束传热及通风特性试验研究.华东工业大学学报,1996,18(1):23-26.
[41] Holman J P. Heat Transfer,9th ed. New York: McGraw Hill,2001.
[42]马义伟.空冷器设计与应用.哈尔滨:哈尔滨工业大学出版社,1998.
[43] Shah R K, Sekulic D P. Fundamentals of heat exchanger design. John Wiley&Sons, Inc.,2003:700-702.
[44] London A L, Compact heat exchangers, Part2, Surface geometry, Mech. Eng.,1964,86, June:31-34.
[45] Shah R K. Compact heat exchanger surface selection methods, Heat Transfer1978,Proc.6th Int. Heat Transfer Conf.,1978,4:193-199.
[46] Kays W M, London A L. Compact heat exchangers,3rd ed. New York: McGrawHill,1984.
[47] Webb R L, Kim N. Principles of Enhanced Heat Transfer,2nd ed. New York:Taylor&Francis,2005.
[48] Gardner K A. Efficiency of extended surface. Trans. ASME,1945,67:621-631.
[49] Kraus A D, Aziz A, Welty J. Extended surface heat transfer. John Wiley&Sons,Inc.,2001.
[50] Schmidt Th E. Improved methods for calculation of heat transfer on finned surfaces.K ltetech Klim [in Germany].1966,18(4):135-138.
[51] Hong K T, Webb R L. Calculation of fin efficiency for wet and dry fins. Journal ofHVAC&R Research,1996,2(1):27-41.
[52] Acosta-Iborra A, Campo A. Approximate analytic temperature distribution andefficiency for annular fins of uniform thickness. International Journal of ThermalSciences,2009,48:773-780.
[53] Bahadori A, Vuthaluru H. Predictive tool for estimation of convection heat transfercoefficients and efficiencies for finned tubular sections. International Journal ofThermal Sciences,2010,49:1477-1483.
[54] Esmail M A. Heat transfer from extended surfaces subject to variable heat transfercoefficient. International Journal of Heat and Mass Transfer,2003,39:131-138.
[55] Lymer A, Ridal B F. Finned tubes in a crossflow of gas. Journal of British nuclearenergy conference,1961,307-313.
[56] Huang L J, Shah R K. Assessment of calculation methods for efficiency of straightfins of rectangular profile. International Journal of Heat and Fluid Flow,1992,13(3):282-293.
[57] Yudin V F, Tokhtarova L S. Investigation of the correction factor psi for thetheoretical effectiveness of a round fin. Thermal Engineering,1973,20(3):65-68.
[58] Shah R K, Sekulic D P. Fundamentals of heat exchanger design. John Wiley&Sons, Inc.,2003:283-286.
[59] Hashizume K, Morikawa R, Koyama T, etc. Fin efficiency of serrated fins. HeatTransfer Engineering,2002,23(2):6-14.
[60] Eckert E R G, Drake R M. Analysis of heat and mass transfer, New York: McGrawHill,1972.
[61]李之光.相似与模化（理论及应用）.北京:国防工业出版社,1982.
[62]庄礼贤,尹协远,马晖扬.流体力学（第2版）.合肥:中国科学技术大学出版社,2009.
[63] Lu C W, Huang J M, Nien W C, et al. A numerical investigation of the geometriceffects on the performance of plate finned-tube heat exchanger. Energy Conversionand Management,2011,52(3):1638-1643.
[64] Tao Y B, He Y L, Huang J, et al. Three-dimensional numerical study of wavyfin-and-tube heat exchangers and field synergy principle analysis. InternationalJournal of Heat and Mass Transfer,2007,50(5-6):1163-1175.
[65]于新娜,袁益超,马有福,等. H形翅片管束传热和阻力特性的试验与数值模拟.动力工程学报,2010,30(6):433-438.
[66]陶文铨等.传热与流动问题的多尺度数值模拟:方法与应用.北京:科学出版社,2008.
[67] He Y L, Han H, Tao W Q, et al. Numerical study of heat-transfer enhancement bypunched winglet-type vortex generator arrays in fin-and-tube heat exchangers.International Journal of Heat and Mass Transfer,2012, in press.
[68] Malapure V P, Mitra S K, Bhattachary A. Numerical investigation of fluid flow andheat transfer over louvered fins in compact heat exchanger. International Journal ofThermal Sciences,2007,46:199–211.
[69] Mi Sandar Mon, Ulrich Gross. Numerical study of fin-spacing effects inannular-finned tube heat exchangers. International Journal of Heat and Mass Transfer,2004,47:1953–1964.
[70] Rao Y, Xu Y M, Wan C Y. An experimental and numerical study of flow and heattransfer in channels with pin fin-dimple and pin fin arrays. Experimental Thermal andFluid Science,2012,38:237–247.
[71] Kalaiselvam S, Karthik P, Ranjit Prakash S. Numerical investigation of heattransfer and pressure drop characteristics of tube–fin heat exchangers in ice slurryHVAC system, Applied Thermal Engineering,2009,29:1831–1839.
[72] Sheik Ismail L, Ranganayakulu C, Shah Ramesh K. Numerical study of flowpatterns of compact plate-fin heat exchangers and generation of design data for offsetand wavy fins..International Journal of Heat and Mass Transfer,2009,52:3972–3983.
[73] Dogan M, Sivrioglu M. Experimental and numerical investigation of clearance gapeffects on laminar mixed convection heat transfer from fin array in a horizontalchannel-A conjugate analysis. Applied Thermal Engineering,2012,40:102-113.
[74] Levent Bilira, Zafer Ilken, Aytun Erek. Numerical optimization of a fin-tube gasto liquid heat exchanger. International Journal of Thermal Sciences,2012,52:59-72.
[75] Tang L H, Zeng M, Wang Q W. Experimental and numerical investigation onair-side performance of fin-and-tube heat exchangers with various fin patterns.Experimental Thermal and Fluid Science,2009,33:818–827.
[76] Dong J Q, Chen J P, Zhang W F, et al. Experimental and numerical investigation ofthermal-hydraulic performance in wavy fin-and-flat tube heat exchangers. AppliedThermal Engineering,2010,30:1377-1386.
[77] Song K W, Wang Y, Zhang Q, et al. Numerical study of the fin efficiency and amodified fin efficiency formula for flat tube bank fin heat exchanger. InternationalJournal of Heat and Mass Transfer,2011,54:2661–2672.
[78] Borrajo-Peláez R, Ortega-Casanova J, Cejudo-López J M. A three-dimensionalnumerical study and comparison between the air side model and the air/water sidemodel of a plain fin-and-tube heat exchanger. Applied Thermal Engineering,2010,30:1608-1615.
[79] Sahin H M, Dal A R, Baysal E.3-D Numerical study on the correlation betweenvariable inclined fin angles and thermal behavior in plate fin-tube heat exchanger.Applied Thermal Engineering,2007,27:1806–1816.
[80] Song W M, Meng J A, Li Z X. Numerical study of air-side performance of a finnedflat tube heat exchanger with crossed discrete double inclined ribs. Applied ThermalEngineering,2010,30:1797-1804.
[81] Tiwari S, Chakraborty D, Biswas G, et al. Numerical prediction of flow and heattransfer in a channel in the presence of a built-in circular tube with and without anintegral wake splitter. International Journal of Heat and Mass Transfer,2005,48:439–453.
[82] Islamoglu Y. Numerical analysis of the influence of a circular fin with differentprofiles on the thermal characteristics in a ceramic tube of heat transfer equipment.International Journal of Pressure Vessels and Piping,2004,81:583–587.
[83] Vessakosol P, Charoensuk J. Numerical analysis of heat transfer and flow fieldaround cross-flow heat exchanger tube with fouling. Applied Thermal Engineering,2010,30:1170–1178.
[84] Chang L M, Wang L B, Song K W. Numerical study of the relationship betweenheat transfer enhancement and absolute vorticity flux along main flow direction in achannel formed by a flat tube bank fin with vortex generators. International Journal ofHeat and Mass Transfer,2009,52:1794–1801.
[85] Perrotin T, Clodic D. Thermal-hydraulic CFD study in louvered fin-and-flat-tubeheat exchangers. International Journal of Refrigeration,2004,27:422–432.
[86] Zhang J H, Kundu J, Manglik R M. Effect of fin waviness and spacing on thelateral vortex structure and laminar heat transfer in wavy-plate-fin cores. InternationalJournal of Heat and Mass Transfer,2004,47:1719–1730.
[87] Tian L T, He Y L, Tao Y B, et al. A comparative study on the air-side performanceof wavy fin-and-tube heat exchanger with punched delta winglets in staggered andin-line arrangements. International Journal of Thermal Sciences,2009,48:1765–1776.
[88] Xie G N, Wang Q W, Sunden B. Parametric study and multiple correlations onair-side heat transfer and friction characteristics of fin-and-tube heat exchangers withlarge number of large-diameter tube rows. Applied Thermal Engineering,2009,29:1–16.
[89] Sahin B, Ozturk N A, Gurlek C. Horseshoe vortex studies in the passage of a modelplate-fin-and-tube heat exchanger. International Journal of Heat and Fluid Flow,2008,29:340–351.
[90] Sahiti N, Durst F, Geremia P. Selection and optimization of pin cross-sections forelectronics cooling. Applied Thermal Engineering,2007,27:111–119.
[91]王福军.计算流体动力学分析.北京:清华大学出版社,2004.
[92] Fluent6.0Users Guide. Lebanon, NH: Fluent Inc.,2001.
[93] Anderson D. Introduction to Computational Fluid Dynamics.北京:清华大学出版社,2004.
[94]陶文铨.数值传热学（第2版）.西安:西安交通大学出版社,2001.
[95] Pletcher R, Tannehill J, Anderson D. Computational Fluid Mechanics and HeatTransfer,3rd Edition. Taylor&Francis,2011.
[96] Lemouedda A, Schmid A, Franz E, etc. Numerical investigations for theoptimization of serrated finned-tube heat exchangers. Applied ThermalEngineering,2011,31:1393-1401.