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Article(id=1319293033217118942, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1319293032650887902, articleNumber=null, orderNo=null, doi=10.3969/j.issn.1005-0329.2025.03.001, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1723824000000, receivedDateStr=2024-08-17, revisedDate=1733328000000, revisedDateStr=2024-12-05, acceptedDate=null, acceptedDateStr=null, onlineDate=1792473570397, onlineDateStr=2026-10-20, pubDate=1743264000000, pubDateStr=2025-03-30, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1792473570397, onlineIssueDateStr=2026-10-20, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1792473570397, creator=13701087609, updateTime=1792473570397, updator=13701087609, issue=Issue{id=1319293032650887902, tenantId=1146029695717560320, journalId=1316781260334530699, year='2025', volume='53', issue='3', pageStart='1', pageEnd='118', issueExtLink='null', onlineDate='null', pubDate='1743264000000', pubDateStr='2025-03-30', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1792473570263, creator='13701087609', updateTime=1792473570263, updator='13701087609', preIssue=null, nextIssue=null, articleTotal=null, ext=null, issueFiles=null, downloadFileDto=null}, startPage=1, endPage=8, ext={EN=ArticleExt(id=1319293033389085407, articleId=1319293033217118942, tenantId=1146029695717560320, journalId=1316781260334530699, language=EN, title=Study on the thermal performance test of diffusion‑bonded hybrid heat exchangers, columnId=null, journalTitle=Fluid Machinery, columnName=null, runingTitle=null, highlight=null, articleAbstract=

This study investigates the thermal performance of diffusion‑bonded hybrid heat exchangers through wind tunnel experiments and numerical simulations. Comparative analysis was conducted on the adaptability of heat transfer and friction factor correlations obtained by different methods for stainless steel plain fins. Results indicate that the thermal load of the heat exchanger increases with rising air‑side velocity，while the pressure loss grows more significantly. When air velocity increases from 8.1 m/s to 28.2 m/s，the thermal load increases by 2.9 times，and the pressure loss escalates by 9.82 times. Within the air‑side Reynolds number range of 2 440≤Re≤8 502，the theoretical thermal load calculated using statistically derived Colburn factor correlations deviates by 0.34%~16.55% from numerical and experimental results. Theoretical pressure loss predictions show less than 3% deviation from measured values. The study verifies the accuracy of the heat transfer/friction factor correlations and numerical models，providing practical guidance for thermal design of single‑phase diffusion‑bonded hybrid heat exchangers.

, authors=Gaige YU, Yongdong CHEN, Bingchuan HAN, Xiaogen LIU, authorsList=Gaige YU, Yongdong CHEN, Bingchuan HAN, Xiaogen LIU, authorCompany=null, correspAuthors=null, authorNote=null, correspAuthorsNote=null, copyrightStatement=null, copyrightOwner=null, extLink=null, articleAbsUrl=null, sourceXml=null, magXml=null, pdfUrl=null, pdf=null, pdfFileSize=null, pdfExtLink=null, richHtmlUrl=null, mobilePdfUrl=null, reviewReport=null, pdfFirstPage=null, abstractGraph=null, abstractGraphContent=null, abstractVideo=null, citation=null, cebUrl=null, magXmlContent=null, mapNumber=null, fund=null), CN=ArticleExt(id=1319293037994431229, articleId=1319293033217118942, tenantId=1146029695717560320, journalId=1316781260334530699, language=CN, title=扩散焊混合式换热器热工性能试验研究, columnId=1317484286475883136, journalTitle=流体机械, columnName=试验研究, runingTitle=null, highlight=null, articleAbstract=

为了研究扩散焊混合式换热器热工性能，基于风洞试验平台开展了扩散焊混合式换热器传热与流动性能试验，并与数值仿真结果进行对比，分析了不同方法获取的传热因子和摩擦因子准则方程对不锈钢平直翅片的适应性。结果表明，扩散焊混合式换热器热负荷随空气侧流速增大而增大，阻力损失增加更为显著，当空气侧流速从8.1 m/s增加至28.2 m/s，热负荷增加了2.9倍，阻力损失增加了9.82倍；在空气侧2 440≤Re≤8 502范围内，基于统计方法获取的传热因子准则方程计算获得的热负荷与数值仿真、试验结果三者之间偏差为0.34%~16.55%，阻力损失理论计算与试验测值偏差均小于3%。试验验证了传热因子、摩擦因子准则方程及数值仿真的模型准确可靠。研究结果可用于指导单相工质扩散焊混合式换热器的热工设计。

, authors=于改革, 陈永东, 韩冰川, 刘孝根, authorsList=于改革, 陈永东, 韩冰川, 刘孝根, authorCompany=null, correspAuthors=null, authorNote=

于改革（1986），男，高级工程师，主要从事高效紧凑式换热器设计开发工作，通信地址：230031 安徽省合肥市长江西路888号合肥通用机械研究院有限公司，E-mail：。

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于改革（1986），男，高级工程师，主要从事高效紧凑式换热器设计开发工作，通信地址：230031 安徽省合肥市长江西路888号合肥通用机械研究院有限公司，E-mail：。

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于改革（1986），男，高级工程师，主要从事高效紧凑式换热器设计开发工作，通信地址：230031 安徽省合肥市长江西路888号合肥通用机械研究院有限公司，E-mail：。

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Computers and Applied Chemistry，2015，32 （8）： 977-981., articleTitle=null, refAbstract=null), Reference(id=1319293053765014376, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, doi=null, pmid=null, pmcid=null, year=null, volume=null, issue=null, pageStart=null, pageEnd=null, url=null, language=null, rfNumber=32, rfOrder=40, authorNames=null, journalName=null, refType=null, unstructuredReference=HASELER L E，MILLER K M，WADEKAR V V. Friction factors and j‑factors for plate fin surfaces［R］. Aspen HTFS Handbook，YM12，2006., articleTitle=null, refAbstract=null)], funds=null, companyList=[AuthorCompany(id=1319293038350947070, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, xref=null, ext=[AuthorCompanyExt(id=1319293038392890111, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, companyId=1319293038350947070, language=EN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=Hefei General Machinery Research Institute Co.，Ltd.，Hefei 230031，China), AuthorCompanyExt(id=1319293038451610368, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, companyId=1319293038350947070, language=CN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=合肥通用机械研究院有限公司，合肥 230031)])], figs=[ArticleFig(id=1319293042356507422, tenantId=1146029695717560320, 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Characteristic sizes of hybrid heat exchanger

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半圆通道侧
参数		数值翅片侧
参数		数值
通道直径D/mm1.5翅片高度h/mm5.5
间隔宽度δ1/mm2.40翅片宽度δ2/mm4.2
流道长度l1/mm721流道长度l2/mm286
板片厚度tD/mm1.5翅片厚度 tp/mm0.5
换热面积As/m22.4换热面积Ap/m23.8
流道形式zig-zag15°翅片层数20
板片层数20单层翅片数46
单板片通道数32
), ArticleFig(id=1319293046827635513, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=CN, label=表1, caption=

混合式换热器特征尺寸

, figureFileSmall=null, figureFileBig=null, tableContent=
半圆通道侧
参数		数值翅片侧
参数		数值
通道直径D/mm1.5翅片高度h/mm5.5
间隔宽度δ1/mm2.40翅片宽度δ2/mm4.2
流道长度l1/mm721流道长度l2/mm286
板片厚度tD/mm1.5翅片厚度 tp/mm0.5
换热面积As/m22.4换热面积Ap/m23.8
流道形式zig-zag15°翅片层数20
板片层数20单层翅片数46
单板片通道数32
), ArticleFig(id=1319293046911521594, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=EN, label=Tab.2, caption=

Test measuring instrument parameters

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仪表名称型号规格不确定度仪表量程
铂热电阻Pt1000.1%~0.15%0~200 ℃
涡轮流量计LWGY-25/M/C/P/L/B10.13%~0.15%1~10 m3/h
微压计testo 5120.3%0~20 hPa
风速仪testo 4800~3 m/s：0.01 m/s；
3~30 m/s：0.1 m/s		0~30 m/s
压力变送器0~200 kPa0.5%0~200 kPa
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试验测量仪表参数

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仪表名称型号规格不确定度仪表量程
铂热电阻Pt1000.1%~0.15%0~200 ℃
涡轮流量计LWGY-25/M/C/P/L/B10.13%~0.15%1~10 m3/h
微压计testo 5120.3%0~20 hPa
风速仪testo 4800~3 m/s：0.01 m/s；
3~30 m/s：0.1 m/s		0~30 m/s
压力变送器0~200 kPa0.5%0~200 kPa
), ArticleFig(id=1319293047083488060, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=EN, label=Tab.3, caption=

Thermal performance test results

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工况热侧进口
温度/℃		热侧出口
温度/℃		热侧流量/(m3·h-1)冷侧进口
温度/℃		冷侧出口
温度/℃		冷侧流量/(m3·h-1)
167.7266.352.7429.0252.42561
267.6465.532.7029.2053.22852
368.3365.452.6629.7352.901 135
468.0164.712.7329.9951.951 390
567.8863.922.6730.0450.971 688
668.1663.812.7030.0050.361 954
), ArticleFig(id=1319293047167374141, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=CN, label=表3, caption=

热工性能试验结果

, figureFileSmall=null, figureFileBig=null, tableContent=
工况热侧进口
温度/℃		热侧出口
温度/℃		热侧流量/(m3·h-1)冷侧进口
温度/℃		冷侧出口
温度/℃		冷侧流量/(m3·h-1)
167.7266.352.7429.0252.42561
267.6465.532.7029.2053.22852
368.3365.452.6629.7352.901 135
468.0164.712.7329.9951.951 390
567.8863.922.6730.0450.971 688
668.1663.812.7030.0050.361 954
), ArticleFig(id=1319293047251260222, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=EN, label=Tab.4, caption=

Verification results of grid independence

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项目主体区域网格尺寸/mm
0.300.200.15
出口温度（热侧/冷侧）/℃64.54/52.8165.39/52.8465.41/52.85
压降（热侧/冷侧）/kPa0.47/25.800.52/26.100.53/26.10
), ArticleFig(id=1319293047356117823, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293033217118942, language=CN, label=表4, caption=

网格无关性验证结果

, figureFileSmall=null, figureFileBig=null, tableContent=
项目主体区域网格尺寸/mm
0.300.200.15
出口温度（热侧/冷侧）/℃64.54/52.8165.39/52.8465.41/52.85
压降（热侧/冷侧）/kPa0.47/25.800.52/26.100.53/26.10
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扩散焊混合式换热器热工性能试验研究
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于改革 , 陈永东 , 韩冰川 , 刘孝根
流体机械 | 试验研究 2025,53(3): 1-8
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流体机械 |试验研究 2025 , 53 (3) : 1 -8
扩散焊混合式换热器热工性能试验研究
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于改革 , 陈永东, 韩冰川, 刘孝根
作者信息
  • 合肥通用机械研究院有限公司，合肥 230031
作者简介:

于改革（1986），男，高级工程师，主要从事高效紧凑式换热器设计开发工作，通信地址：230031 安徽省合肥市长江西路888号合肥通用机械研究院有限公司，E-mail：。

Study on the thermal performance test of diffusion‑bonded hybrid heat exchangers
Gaige YU , Yongdong CHEN, Bingchuan HAN, Xiaogen LIU
Affiliations
  • Hefei General Machinery Research Institute Co.，Ltd.，Hefei 230031，China
出版时间: 2025-03-30 doi: 10.3969/j.issn.1005-0329.2025.03.001
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为了研究扩散焊混合式换热器热工性能，基于风洞试验平台开展了扩散焊混合式换热器传热与流动性能试验，并与数值仿真结果进行对比，分析了不同方法获取的传热因子和摩擦因子准则方程对不锈钢平直翅片的适应性。结果表明，扩散焊混合式换热器热负荷随空气侧流速增大而增大，阻力损失增加更为显著，当空气侧流速从8.1 m/s增加至28.2 m/s，热负荷增加了2.9倍，阻力损失增加了9.82倍；在空气侧2 440≤Re≤8 502范围内，基于统计方法获取的传热因子准则方程计算获得的热负荷与数值仿真、试验结果三者之间偏差为0.34%~16.55%，阻力损失理论计算与试验测值偏差均小于3%。试验验证了传热因子、摩擦因子准则方程及数值仿真的模型准确可靠。研究结果可用于指导单相工质扩散焊混合式换热器的热工设计。

扩散焊  /  混合式换热器  /  板翅  /  zig-zag通道

This study investigates the thermal performance of diffusion‑bonded hybrid heat exchangers through wind tunnel experiments and numerical simulations. Comparative analysis was conducted on the adaptability of heat transfer and friction factor correlations obtained by different methods for stainless steel plain fins. Results indicate that the thermal load of the heat exchanger increases with rising air‑side velocity，while the pressure loss grows more significantly. When air velocity increases from 8.1 m/s to 28.2 m/s，the thermal load increases by 2.9 times，and the pressure loss escalates by 9.82 times. Within the air‑side Reynolds number range of 2 440≤Re≤8 502，the theoretical thermal load calculated using statistically derived Colburn factor correlations deviates by 0.34%~16.55% from numerical and experimental results. Theoretical pressure loss predictions show less than 3% deviation from measured values. The study verifies the accuracy of the heat transfer/friction factor correlations and numerical models，providing practical guidance for thermal design of single‑phase diffusion‑bonded hybrid heat exchangers.

diffusion bonding  /  hybrid heat exchanger  /  plate‑fin  /  zig‑zag channel
于改革, 陈永东, 韩冰川, 刘孝根. 扩散焊混合式换热器热工性能试验研究. 流体机械, 2025 , 53 (3) : 1 -8 . DOI: 10.3969/j.issn.1005-0329.2025.03.001
Gaige YU, Yongdong CHEN, Bingchuan HAN, Xiaogen LIU. Study on the thermal performance test of diffusion‑bonded hybrid heat exchangers[J]. Fluid Machinery, 2025 , 53 (3) : 1 -8 . DOI: 10.3969/j.issn.1005-0329.2025.03.001
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扩散焊换热器按照传热元件组合可以分为3种类型［1-2］：由蚀刻板片构成的扩散焊换热器 （printed circuit heat exchanger，PCHE）、由成型翅片构成的扩散焊换热器（formed plate heat exchangers，FPHE）和由蚀刻板片和成型翅片组合而成的混合式换热器（hybrid heat exchanger，H2X）。混合式换热器特别适用于四代核能钠冷快堆、铅铋快堆、烟气余热回收等场景［3-4］。
关于PCHE的传热与流动特性已经开展了大量数值仿真和试验研究［5-19］。因扩散焊混合式换热器两侧通道在制造工艺上存在较大差异，成型后的几何特征参数的差异性使得扩散焊过程中存在变形不协调问题，且因应用场景多为高温、腐蚀等苛刻条件，其研究多集中于制造工艺和机械结构完整性方面，如文献［20-21］中研究了翅片结构特征参数对扩散焊芯体结构应力分布影响规律。SARANAM等［22-23］提出一种混合式换热器扩散焊工艺模型并完成试验验证，可以准确预测扩散焊工艺门槛值。SIMANJUNTAK等［24］深入分析了混合式换热器两侧错位偏差对应力分布的影响规律。
扩散焊混合式换热器材料为奥氏体不锈钢，其翅片侧特征参数如翅片厚度、翅片高度、翅片间距与传统的铝制翅片规格差异较大，但不论是不锈钢翅片的传热因子与摩擦因子准则方程研究，还是关于混合式结构扩散焊换热器的传热与流动试验研究都鲜有报道［25］。本文针对半圆形通道和平直翅片通道组合式结构，在风洞试验平台进行热工性能测试，分析不同方法获得传热因子与摩擦因子准则方程对不锈钢平直翅片的适应性，并采用数值仿真、理论计算与试验相结合的方法，开展混合式换热器的传热与流动特性研究，为扩散焊混合式换热器的设计提供借鉴。
1　扩散焊混合式换热器样机
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目前，国内奥氏体不锈钢薄板常用厚度有1.0，1.5，2.0 mm，化学蚀刻通道深度通常≤1.0 mm。不锈钢薄板冲压成型的厚度通常≤0.5 mm，成型翅片高度≤6.0 mm。结合扩散焊工艺要求，本文研制的扩散焊混合换热器试验样机实物、样机蚀刻通道和翅片通道几何特征参数如图1所示。
混合式换热器样机翅片通道为直进直出，微通道侧为侧进侧出。芯体通道布置方式按蚀刻通道板片-翅片-中间隔板-蚀刻通道板片顺序堆叠。混合式换热器样机详细几何尺寸见表1。
2　扩散焊混合式换热器热工性能试验
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2.1　风洞-水试验装置
空气-水热工性能试验系统主要由热水循环系统、风洞系统、测试样机及测量仪表组成，其原理如图2所示。
热水循环系统主要由电加热水箱、热水循环泵、体积流量计、调节阀等组成。空气侧为开式风洞，主要由进口整流段、前测量段、后测量段、风机及测控系统构成，该装置取得了CNAS，CMA认证。混合式换热器测试样机与测试段安装实物如图3所示。
2.2　混合式换热器热工性能试验
扩散焊混合式换热器样机的空气侧为平直翅片，水侧为半圆形截面zig-zag15°通道。工程经验表明，空气侧传热系数与水侧传热系数相差2个数量级，试验过程改变水侧带来总传热系数变化不明显，可以忽略不计。因此，项目试验过程主要研究空气侧流量变化对传热与流动的影响。基于前期对zig-zag15°通道水-水试验，试验过程固定水侧流量2.7 m3/h，进口温度（68.0±0.5） ℃，空气侧进口温度（29.5±1） ℃。通过改变空气侧流量进行热工性能试验，空气侧流量从561~1954 m3/h逐渐增加，雷诺数Re范围2 440~8 502，主要处于湍流和层流-湍流转变区。试验测量用仪表参数见表2。考虑到冷侧小温差下温度测量值对数据计算结果影响较大，通过现场校验的方法，对所有温度测量仪表进行实际工况点校验，温度测量仪表校正后的最大误差控制在±0.05 ℃，校正后的仪表精度完全能够满足后续试验工况的要求。
为确保测量数据的准确可靠，按照下式对测量不确定度［26］进行计算：
δRR=∑i=1n∂R∂Xiδx0.5
式中，R=RX1,X2,X3,⋯,XN；∂R，∂Xi分别为相应变量的绝对误差值。
试验过程按照JB/T 10379—2022《热交换器热工性能和流体阻力特性通用测试方法》要求，每个测试工况在热平衡误差小于5%，稳定30 min后开始采集样机冷、热侧进出口温度、进口流量和压降数据，获得差异化流道扩散焊换热器热工性能试验测试数据如表3所示。
3　扩散焊混合式换热器数值仿真
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3.1　仿真模型
扩散焊混合式换热器芯体换热区域冷热两侧为交替分布，冷侧平直翅片通道直进直出，热侧采用了3次曲折的侧进侧出型式，冷热换热过程存在复杂的错逆流，无法在冷热侧各选取1个通道进行模型简化。建立的几何计算单元见图4，包含1层蚀刻半圆形通道的板片与1层成型翅片。本文假设流道内流体为稳态流动，板片上各流道内流体分布均匀，则可以选取一冷一热1组换热单元研究水-空气的换热与流动特性。此外，从表3可看出，水和空气的进出口温度变化范围都在较小的区间内，且都是单相状态，实际计算过程中可认为其物性为常数。固体材料为SUS31603，其密度为7 930 kg/m3，比热为450 J/（kg⋅K），导热率为15 W/（m⋅K）。
3.2　控制方程和边界条件
质量守恒方程：
∇⋅ρu⃗=0
式中，ρ为密度，kg/m3；u⃗为速度矢量。
动量守恒方程：
∂ρu⃗∂τ+∇⋅ρu⃗u⃗=-∇p+∇⋅μ∇u⃗+∇u⃗T
式中，p为压力，MPa。
能量守恒方程：
∂ρE∂τ+∇⋅u⃗ρE+p=∇⋅λ∇T
式中，E为能量，m2/s2；λ为导热系数，W/（m⋅K）。
根据试验工况操作参数及前期PCHE数值模拟经验［27］，选择SST k-ω模型。边界条件设置如下：水侧（热侧）、空气侧（冷侧）入口为速度入口，依据试验参数确定其流速与温度，水侧（热侧）、空气侧（冷侧）出口为压力出口；计算单元内两板片接触面为传热面，对应侧面设置为周期性边界；同时，忽略动量方程中重力及浮升力的影响。
3.3　网格独立性验证
计算区域采用六面体网格，为消除网格对计算结果的影响，对其进行网格无关性验证。以工况3为例，对流道壁面附近网格进行了局部加密，流体与固体接触界面附近施加边界层。
流道壁面处y+≈10，主体区域网格尺寸分别为0.30，0.20，0.15 mm，网格独立性验证结果见表4，其中通过改变线段上的节点数来改变网格数量和网格疏密程度，最终网格设置以冷侧出口温度和热侧出口温度为参考。当网格尺寸由0.2 mm细化至0.15 mm时，热侧/冷侧出口温度与压降计算值变化均小于0.2%，如表4所示；网格数量由1 513万增加至1 967万。为了在减少计算成本的同时获得合理的计算结果，将换热单元的计算模型中网格尺寸定为0.2 mm。网格划分如图5所示。
3.4　数值仿真结果
以工况1为例，空气侧沿流动方向的温度分布如图6所示。
图6中右侧为进口，温度为29.02 ℃，左侧为空气出口，出口的总平均温度约为53.94 ℃，与样机测试结果52.42 ℃偏差不大。固体区域的温度分布基本一致，流体在固体壁面的传热下逐渐升温。空气侧平直翅片通道尺寸3.7 mm×5 mm，但是在图6上下边缘处的通道宽度为翅片通道尺寸的1/2，其出口呈现出较高的温度，即窄通道可以获得更大的温升。
水侧的温度分布如图7所示。图中左下角为热侧进口，存在明显的高温区，右上角为热侧出口，与图6所示空气侧温度分布对比分析，水侧为换热强侧；在最右侧中部存在较低的温度区域，其是受冷侧空气进口的影响。当进口温度为67.72 ℃时，出口平均温度为66.11 ℃，略低于试验测量值66.35 ℃。
采用同样数值模拟方法获取6种不同工况下冷热侧出口温度。6种不同工况下，水侧和空气侧出口温度数值模拟值与试验值对比如图8、图9所示。
对于空气侧出口温度，数值模拟的结果略低于试验值，最大偏差约为3 ℃（工况6），工况6的进口温度为30 ℃，相对偏差约为14.3%。水侧最大偏差也是在工况6，数值模拟与试验偏差约为0.68 ℃，相对偏差约为15%。
4　试验结果与分析
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4.1　理论计算准则式对比分析
在前期工作中，单相水在PCHE半圆形通道侧传热与流动准则方程已进行了试验验证［28］，文中关于水侧传热与流动特性不再赘述。
针对单相气体在不锈钢平直翅片的传热与流动特性，对比分析了不同方法获取的传热因子和摩擦因子方程。
由日本神户制钢［29］“ALEX”铝制平直翅片性能曲线拟合得到的j因子和f因子准则方程（适用范围：400≤Re≤10 000）如下：
lnj=0.103 109lnRe2-1.910 91lnRe+3.221
lnf=0.106 566lnRe2-2.121 58lnRe+5.825 05
董军启等［30］通过试验拟合，得到的铝制平直翅片j因子和f因子准则方程（适用范围：600≤Re≤7 000）如下：
j=0.27Re-0.334 5LDe-0.441hfDe0.14tfDe-0.127
f=3.621 94Re-0.389 6LDe-0.395 5hfDe0.113tfDe0.219 4
式中，L为翅片长度，mm；De为通道当量直径，mm；hf为翅片高度，mm；tf为翅片厚度，mm。
徐赛等［31］基于CFD模拟数据拟合，得到铝制平直翅片j因子和f因子准则方程（适用范围：Re≥2 000）如下：
j=0.026Re-0.182pfDe0.501hfDe-0.018 9tfDe0.059 3
f=0.421Re-0.303 1pfDe-0.4hfDe-0.023 4tfDe0.292
式中，pf为翅片间距。
基于统计方法获得的具有普适性的平直翅片传热因子和摩擦因子准则方程［32］如下。
（1）不同流动状态下传热因子j准则方程。
①层流区域（Re≤1 000）：
jl=K4+13.03Gz4/31/4/(RePr1/3)
其中，K=（3.65+C1）/2，Gz=（πDeRePr）/（4L），
C1=8.2-16.3/（1.5+r+1/r），r=（hf-tf）/（pf-tf）
②湍流区域（Re≥5 000）：
jt=C2MaxRe,5  0000.2
其中，C2=0.017+0.04/(r+1/r)。
③层流-湍流转变区域（1 000＜Re＜5 000）：
jl-t=jl4+jt41/4
（2）不同流动状态下摩擦因子f准则方程。
①层流区域（Re≤1 000）：
fl=A/Re
其中，A=25-19/(r+1/r)。
②湍流区域（Re≥5 000）：
ft=0.056/Re0.2
③层流-湍流转变区域（1 000＜Re＜5 000）：
fl-t=fl4+ft41/4
式（11）~（16）中，j，f分别为传热因子和摩擦因子；下标l为层流，t为湍流，l‑t为层流-湍流转变区；Pr为普朗特数。
基于表1和表3数据，采用以上不同准则式获取的传热因子j和摩擦因子f如图10、图11所示。
从图10可以看出，由神户制钢“ALEX”翅片性能曲线拟合得到的传热因子准则式（5）与基于大量数据统计获得准则式（12）（13）计算结果相当接近，偏差均小于5%。而基于CFD模拟的传热因子准则式（9）的计算结果与其他准则式偏差均较大，相对于准则式（12）（13）偏差在20%以上，推测主要是由CFD模拟采用的铝制翅片高度（8，10，15 mm）和翅片厚度（0.15，0.20 mm）与本次试验不锈钢翅片高度和翅片厚度差异性较大导致。基于试验获得准则式（7）的翅片高度（8，10，15 mm）和翅片厚度（0.15，0.20 mm）存在类似情况，即准则式的外推适用性不确定性较大。
从图11可以看出，与传热因子准则式类似，由式（6）得到的摩擦因子与由式（15）（16）的偏差范围为5%~22%。而由式（9）（10）得到的摩擦因子，相对于式（15）（16）的偏差范围为53%~94%。
根据以上对试验准则式的分析，拟选用式（11）~（16）进行试验结果分析。
4.2　试验结果分析
理论计算热负荷是以试验工况两侧的入口温度、压力、流量为输入条件，以换热面积余量为0为约束条件，通过迭代计算获取最终两侧出口温度，进而获得理论计算热负荷。试验热负荷Q由下式获得：
Q=mCpΔT
式中，Q为理论计算热负荷，kW；m为质量流量，kg/h；Cp为进出口比热平均值；ΔT为进出口温差，℃。
图12示出热负荷随风速的变化规律。
从图可以看出，理论计算、数值仿真和试验所得热负荷与风速均似呈线性关系，当空气侧风速从8.1 m/s增加至28.2 m/s，热负荷增加了2.9倍。数值模拟与试验偏差范围为0.34%~11.89%，最大偏差均出现在空气侧风速最小处。式（7）（9）计算所得热负荷与试验偏差较大，最大偏差约28.44%。式（5）（12）（13）理论计算结果较为接近，其中，式（12）（13）与试验偏差范围为5.98%~16.55%，可以较好地预测样机传热特性。
由于试验测试阻力损失包含了试验样机前后的过渡段，即试验值包含了测试样机芯体部分阻力损失和过渡段部分阻力损失。扩散焊混合式换热器试验样机前过渡段由250 mm×250 mm矩形截面，过渡至191.5 mm×250 mm，过渡段长度369.5 mm；样机后过渡段长度与入口段相同，形状与入口对称。其中，过渡段的阻力损失ΔPTS：
ΔPTS=G22Kc+1-σ2ρin+4fLρmDe-Ke+1-σ2ρout
式中，G为质量流速，kg/（m2⋅s），Kc，Ke分别为经验入口、出口阻力损失因子；ρin，ρout，ρm分别为流体的入口、出口、平均温度下的密度，kg/m3；f为范宁摩擦因子；L为过渡段沿程长度，m；σ为过渡段大端和小端之比。
图13示出阻力损失随风速的变化规律。从图可以看出，理论计算和试验阻力损失随着风速增加不断增加，当空气侧风速从8.1 m/s增加至28.2 m/s，阻力损失增加了9.82倍。式（6）计算结果与试验值偏差4.0%~17.56%，式（8）（10）计算结果与试验值偏差超过了30%，式（15）（16）计算结果与试验值偏差范围为0.21%~2.96%，可以较好地进行阻力损失预测。
5　结论
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（1）扩散焊混合式换热器热负荷随空气侧风速增大而增大，阻力损失的增加更为显著。当空气侧风速从8.1 m/s增加至28.2 m/s，热负荷增加了2.9倍，阻力损失增加了9.82倍。
（2）在空气侧2 440≤Re≤8 502范围内，基于传热因子准则式（12）（13）计算的热负荷与数值仿真、试验结果偏差较小，三者之间最小偏差为0.34%，最大偏差约16.55%。
（3）空气侧不同流速情况下，各工况点基于摩擦因子准则式（15）（16）的阻力损失与试验测试结果偏差均小于3%。
（4）试验验证了基于统计方法的单相工质传热因子、摩擦因子准则方程及数值仿真模型准确可靠，可用于指导单相工质扩散焊混合式换热器的热工设计。
为加速推进余热回收、四代核电领域混合式换热器工程设计开发进程，需进一步开展高温气体、液态金属、熔盐及超临界流体在扩散焊混合式换热器内传热与流动相关试验研究。

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doi: 10.3969/j.issn.1005-0329.2025.03.001
  • 接收时间：2024-08-17
  • 首发时间：2026-10-20
  • 出版时间：2025-03-30
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  • 收稿日期：2024-08-17
  • 修回日期：2024-12-05
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2种不同金属材料的力学参数
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Number of
species		 占总种数比例
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total species (%)		 属
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鹅膏菌科Amanitaceae 2 11 5.26 鹅膏菌属 Amanita 10 4.78
小菇科 Mycenaceae 2 12 5.74 丝盖伞属 Inocybe 5 2.39
多孔菌科 Polyporaceae 8 14 6.70 蜡蘑属 Laccaria 5 2.39
红菇科 Russulaceae 3 23 11.00 小皮伞属 Marasmius 6 2.87
小菇属 Mycena 11 5.26
光柄菇属 Pluteus 5 2.39
红菇属 Russula 17 8.13
栓菌属 Trametes 5 2.39
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