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Article(id=1320037933546058709, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037798686605953, articleNumber=null, orderNo=null, doi=10.3969/j.issn.1005-0329.2026.06.010, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1760284800000, receivedDateStr=2025-10-13, revisedDate=1780329600000, revisedDateStr=2026-06-02, acceptedDate=null, acceptedDateStr=null, onlineDate=1792651168476, onlineDateStr=2026-10-22, pubDate=1782748800000, pubDateStr=2026-06-30, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1792651168476, onlineIssueDateStr=2026-10-22, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1792651168476, creator=13701087609, updateTime=1792651168476, updator=13701087609, issue=Issue{id=1320037798686605953, tenantId=1146029695717560320, journalId=1316781260334530699, year='2026', volume='54', issue='6', pageStart='1', pageEnd='122', issueExtLink='null', onlineDate='null', pubDate='1782748800000', pubDateStr='2026-06-30', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1792651136322, creator='13701087609', updateTime=1792656254917, updator='13701087609', preIssue=null, nextIssue=null, articleTotal=null, ext={EN=IssueExt(id=1320059267693003413, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037798686605953, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1320059267693003414, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037798686605953, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null, downloadFileDto=null}, startPage=78, endPage=85, ext={EN=ArticleExt(id=1320037933864825814, articleId=1320037933546058709, tenantId=1146029695717560320, journalId=1316781260334530699, language=EN, title=Aerodynamic performance optimization of air‑conditioning scroll reversing centrifugal fan based on orthogonal experiment, columnId=null, journalTitle=Fluid Machinery, columnName=null, runingTitle=null, highlight=null, articleAbstract=

To address the issues of insufficient air volume and abnormal sound quality in the dual centrifugal fan system with reversing scroll，based on the single‑factor analysis method，the influence laws of blade profile，volute tongue structure，and collector form on the aerodynamic performance of the fan system were investigated，and structural optimization design of the air‑conditioning scroll reversing centrifugal fan was carried out to obtain the fan structure scheme with the best comprehensive performance.Orthogonal experiments were adopted to clarify the influence weights of structural parameters such as volute tongue inclination angle，anti‑swirl ring height，and guide ring outlet diameter on the performance of the optimized fan.The results show that the order of influence weights of each parameter on air volume is guide ring outlet diameter>volute tongue inclination angle>anti‑swirl ring height；the order of influence weights on sound quality is volute tongue inclination angle>guide ring outlet diameter>anti‑swirl ring height.Considering both air volume and sound quality indicators，the preferred scheme achieves an air volume of 1 223 m3/h，which is about 5% higher than the original scheme，and the noise peak is reduced by about 5 dB.This study can provide a reference for the design of air‑conditioning scroll reversing centrifugal fans.

, authors=Qianqian WANG, Feng JIANG, Yanyan WEI, authorsList=Qianqian WANG, Feng JIANG, Yanyan WEI, 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=1320037943058740208, articleId=1320037933546058709, tenantId=1146029695717560320, journalId=1316781260334530699, language=CN, title=基于正交试验的空调蜗旋换向离心风机气动性能优化, columnId=1317484287230853622, journalTitle=流体机械, columnName=设计计算, runingTitle=null, highlight=null, articleAbstract=

为解决双离心蜗旋换向风机系统存在的风量不足与音质异常问题，基于单因素分析法，探究叶型、蜗舌结构及集流器形式对风机系统气动性能的影响规律，并开展空调蜗旋换向离心风机的结构优化设计，以获得综合性能最优的风机结构方案。采用正交试验，明确蜗舌倾斜角度、防涡圈高度与导流圈出口直径等结构参数对优化后风机性能的影响权重。结果表明：各参数对风量的影响权重大小依次为导流圈出口直径>蜗舌倾斜角度>防涡圈高度；对音质的影响权重大小依次为蜗舌倾斜角度>导流圈出口直径>防涡圈高度。综合考虑风量与音质指标，优选方案的风量达1 223 m3/h，较原方案提升约5%，噪声峰值降低约5 dB。研究可为空调蜗旋换向离心风机的设计提供参考。

, authors=王千千, 蒋锋, 魏彦艳, authorsList=王千千, 蒋锋, 魏彦艳, authorCompany=null, correspAuthors=null, authorNote=

王千千（1990），女，硕士，高级工程师，主要从事空调风机平台开发和降噪技术研究工作，通信地址：519070广东省珠海市香洲区前山金鸡西路789号珠海格力电器股份有限公司，E-mail：。

, correspAuthorsNote=null, copyrightStatement=作者向本刊所投稿件一经本刊录用，则该论文的复制权、发行权、信息网络传播权、翻译权、汇编权等权利视为自动转让给本刊。本刊为国内各主要数据库收录期刊，本刊所发表的稿件将同时通过互联网进行网络出版或提供信息服务。, copyrightOwner=null, extLink=null, articleAbsUrl=null, sourceXml=k864qtSfKSpCj4mWsCbgqA==, magXml=rrvX/vC+Rbsi37lk7E/SNQ==, pdfUrl=null, pdf=null, pdfFileSize=null, pdfExtLink=null, richHtmlUrl=null, mobilePdfUrl=null, reviewReport=null, pdfFirstPage=null, abstractGraph=np68meay04qDu50HoRl6+Q==, abstractGraphContent=null, abstractVideo=null, citation=null, cebUrl=null, magXmlContent=UdCbNj/r1gpJ1tF/hcv3Nw==, mapNumber=null, fund=null)}, authors=[Author(id=1320037943532696565, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, orderNo=0, firstName=null, middleName=null, lastName=null, nameCn=null, orcid=null, stid=null, country=null, authorPic=null, dead=0, email=1569716778@qq.com, emailSecond=null, emailThird=null, correspondingAuthor=0, authorType=1, ext={EN=AuthorExt(id=1320037943616582647, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, authorId=1320037943532696565, language=EN, stringName=Qianqian WANG, firstName=Qianqian, middleName=null, lastName=WANG, prefix=null, suffix=null, authorComment=null, nameInitials=null, affiliation=null, department=null, xref=null, address=GREE Electric Appliances，Inc.of Zhuhai，Zhuhai 519070，China, bio=null, bioImg=null, bioContent=null, aboutCorrespAuthor=null), CN=AuthorExt(id=1320037943893406712, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, authorId=1320037943532696565, language=CN, stringName=王千千, firstName=null, middleName=null, lastName=null, prefix=null, suffix=null, authorComment=null, nameInitials=null, affiliation=null, department=null, xref=null, address=珠海格力电器股份有限公司，广东 珠海 519070, bio={"content":"

王千千（1990），女，硕士，高级工程师，主要从事空调风机平台开发和降噪技术研究工作，通信地址：519070广东省珠海市香洲区前山金鸡西路789号珠海格力电器股份有限公司，E-mail：。

"}, bioImg=null, bioContent=

王千千（1990），女，硕士，高级工程师，主要从事空调风机平台开发和降噪技术研究工作，通信地址：519070广东省珠海市香洲区前山金鸡西路789号珠海格力电器股份有限公司，E-mail：。

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near the volute tongue, figureFileSmall=Yz2HxAJrZelkAcdviT66ew==, figureFileBig=qVM8Rjcb+dphpmHVOuhKTg==, tableContent=null), ArticleFig(id=1320037951506067478, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=图7, caption=蜗舌附近湍动能对比, figureFileSmall=Yz2HxAJrZelkAcdviT66ew==, figureFileBig=qVM8Rjcb+dphpmHVOuhKTg==, tableContent=null), ArticleFig(id=1320037951577370647, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Fig.8, caption=Schematic diagram of the collector structure, figureFileSmall=G7uTcq9MzcNuSoGDFpORkA==, figureFileBig=ToeWzScP0n2hmwARqA9RTA==, tableContent=null), ArticleFig(id=1320037951648673816, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=图8, caption=集流器结构示意

（a）导流圈出口 （b）防涡圈与导流圈结构

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Main parameters of the scroll reversing centrifugalfan system

, figureFileSmall=null, figureFileBig=null, tableContent=
参数数值
叶轮外直径/mm246
叶轮内直径/mm196
叶轮高度/mm94
导流圈出口直径/mm226
风叶轴向间隙/mm10.5
叶轮叶片数63
蜗壳宽度/mm105
设计转数/（r·min-1）900
), ArticleFig(id=1320037952437202976, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表1, caption=

蜗旋换向离心风机系统主要参数

, figureFileSmall=null, figureFileBig=null, tableContent=
参数数值
叶轮外直径/mm246
叶轮内直径/mm196
叶轮高度/mm94
导流圈出口直径/mm226
风叶轴向间隙/mm10.5
叶轮叶片数63
蜗壳宽度/mm105
设计转数/（r·min-1）900
), ArticleFig(id=1320037952495923233, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.2, caption=

Structural parameters of different blade profiles and their simulated air volume

, figureFileSmall=null, figureFileBig=null, tableContent=
叶型进口直径D1/mm出口直径D2/mm进口安装角β1/（°）出口安装角β2/（°）风量Q/（m3·h-1）
原叶型1962461001521 183
叶型12072461001511 204
叶型22132461071551 237
), ArticleFig(id=1320037952563032098, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表2, caption=

不同叶型结构参数及其仿真风量

, figureFileSmall=null, figureFileBig=null, tableContent=
叶型进口直径D1/mm出口直径D2/mm进口安装角β1/（°）出口安装角β2/（°）风量Q/（m3·h-1）
原叶型1962461001521 183
叶型12072461001511 204
叶型22132461071551 237
), ArticleFig(id=1320037952739192867, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.3, caption=

Simulated air volume and sound quality perceptioneffects for different volute tongue structures

, figureFileSmall=null, figureFileBig=null, tableContent=
蜗舌结构风量/（m3∙h-1）音质评分旋转噪声
平蜗舌1 128.05有
阶梯蜗舌1 132.86有
倾斜蜗舌1 146.88无
), ArticleFig(id=1320037952810496036, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表3, caption=

不同蜗舌结构仿真风量及音质体验效果

, figureFileSmall=null, figureFileBig=null, tableContent=
蜗舌结构风量/（m3∙h-1）音质评分旋转噪声
平蜗舌1 128.05有
阶梯蜗舌1 132.86有
倾斜蜗舌1 146.88无
), ArticleFig(id=1320037952873410597, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.4, caption=

Structural parameters of different guide ring configurations and their simulated air volume

, figureFileSmall=null, figureFileBig=null, tableContent=
导流圈结构导流圈出口直径/mm风量/（m3∙h-1）
半包裹2261 165.6
全包裹2061 197.5
过度包裹1861 074.7
), ArticleFig(id=1320037954509189158, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表4, caption=

不同导流圈结构及其仿真风量

, figureFileSmall=null, figureFileBig=null, tableContent=
导流圈结构导流圈出口直径/mm风量/（m3∙h-1）
半包裹2261 165.6
全包裹2061 197.5
过度包裹1861 074.7
), ArticleFig(id=1320037954572103719, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.5, caption=

Orthogonal experiment results and simulated airvolume values

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组因素风量/（m3∙h-1）
蜗舌倾斜角度A/（°）防涡圈高度B/mm导流圈出口直径C/mm
1642001 233.1
2652061 252.2
3662121 212.7
4672181 197.2
51042061 261.2
61052121 220.5
71062181 209.6
81072001 242.7
91442121 230.2
101452181 222.4
111462001 255.3
121472061 266.5
131842181 232.6
141852001 274.3
151862061 286.9
161872121 242.2
), ArticleFig(id=1320037954672767016, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表5, caption=

正交试验结果及仿真风量数值

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组因素风量/（m3∙h-1）
蜗舌倾斜角度A/（°）防涡圈高度B/mm导流圈出口直径C/mm
1642001 233.1
2652061 252.2
3662121 212.7
4672181 197.2
51042061 261.2
61052121 220.5
71062181 209.6
81072001 242.7
91442121 230.2
101452181 222.4
111462001 255.3
121472061 266.5
131842181 232.6
141852001 274.3
151862061 286.9
161872121 242.2
), ArticleFig(id=1320037954752458793, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.6, caption=

Range analysis results for air volume

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组A/（°）B/mmC/mm
K14 895.24 957.15 005.4
K24 934.04 969.45 066.8
K34 974.44 964.54 905.6
K45 036.04 948.64 861.8
k11 223.81 239.31 251.4
k21 233.51 242.41 266.7
k31 243.61 241.11 226.4
k41 259.01 237.21 215.5
极差R35.25.251.3
最优水平A4B2C2
最优组合A4B2C2
), ArticleFig(id=1320037954819567658, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表6, caption=

风量极差分析结果

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组A/（°）B/mmC/mm
K14 895.24 957.15 005.4
K24 934.04 969.45 066.8
K34 974.44 964.54 905.6
K45 036.04 948.64 861.8
k11 223.81 239.31 251.4
k21 233.51 242.41 266.7
k31 243.61 241.11 226.4
k41 259.01 237.21 215.5
极差R35.25.251.3
最优水平A4B2C2
最优组合A4B2C2
), ArticleFig(id=1320037954907648043, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.7, caption=

Orthogonal experiment and sound quality scoring table

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试验组A/（°）B/mmC/mm音质评分
11452069
21462008
31852005
41862067
), ArticleFig(id=1320037955029282860, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表7, caption=

正交试验及音质评分表

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组A/（°）B/mmC/mm音质评分
11452069
21462008
31852005
41862067
), ArticleFig(id=1320037955096391725, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.8, caption=

Range analysis results for sound quality

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组A/（°）B/mmC/mm
K1171413
K2121516
k18.576.5
k267.58
极差R2.50.51.5
最优水平A1B2C2
最优组合A1B2C2
), ArticleFig(id=1320037955176083502, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表8, caption=

音质极差分析结果

, figureFileSmall=null, figureFileBig=null, tableContent=
试验组A/（°）B/mmC/mm
K1171413
K2121516
k18.576.5
k267.58
极差R2.50.51.5
最优水平A1B2C2
最优组合A1B2C2
), ArticleFig(id=1320037955238998063, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=EN, label=Tab.9, caption=

Comparison table of schemes and their results

, figureFileSmall=null, figureFileBig=null, tableContent=
方案蜗舌倾斜角度/（°）防涡圈高度/mm导流圈出口直径/mm风量/（m3∙h-1）正面噪声/dB噪声峰值/dB
原方案002261 16548.234.4
风量最优方案1852061 26147.932.3
音质最优方案1462061 22347.929.5
), ArticleFig(id=1320037955297718320, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037933546058709, language=CN, label=表9, caption=

方案及其结果对比表

, figureFileSmall=null, figureFileBig=null, tableContent=
方案蜗舌倾斜角度/（°）防涡圈高度/mm导流圈出口直径/mm风量/（m3∙h-1）正面噪声/dB噪声峰值/dB
原方案002261 16548.234.4
风量最优方案1852061 26147.932.3
音质最优方案1462061 22347.929.5
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基于正交试验的空调蜗旋换向离心风机气动性能优化
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王千千 , 蒋锋 , 魏彦艳
流体机械 | 设计计算 2026,54(6): 78-85
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流体机械 |设计计算 2026 , 54 (6) : 78 -85
基于正交试验的空调蜗旋换向离心风机气动性能优化
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王千千 , 蒋锋, 魏彦艳
作者信息
  • 珠海格力电器股份有限公司，广东 珠海 519070
作者简介:

王千千（1990），女，硕士，高级工程师，主要从事空调风机平台开发和降噪技术研究工作，通信地址：519070广东省珠海市香洲区前山金鸡西路789号珠海格力电器股份有限公司，E-mail：。

Aerodynamic performance optimization of air‑conditioning scroll reversing centrifugal fan based on orthogonal experiment
Qianqian WANG , Feng JIANG, Yanyan WEI
Affiliations
  • GREE Electric Appliances，Inc.of Zhuhai，Zhuhai 519070，China
出版时间: 2026-06-30 doi: 10.3969/j.issn.1005-0329.2026.06.010
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摘要
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为解决双离心蜗旋换向风机系统存在的风量不足与音质异常问题，基于单因素分析法，探究叶型、蜗舌结构及集流器形式对风机系统气动性能的影响规律，并开展空调蜗旋换向离心风机的结构优化设计，以获得综合性能最优的风机结构方案。采用正交试验，明确蜗舌倾斜角度、防涡圈高度与导流圈出口直径等结构参数对优化后风机性能的影响权重。结果表明：各参数对风量的影响权重大小依次为导流圈出口直径>蜗舌倾斜角度>防涡圈高度；对音质的影响权重大小依次为蜗舌倾斜角度>导流圈出口直径>防涡圈高度。综合考虑风量与音质指标，优选方案的风量达1 223 m3/h，较原方案提升约5%，噪声峰值降低约5 dB。研究可为空调蜗旋换向离心风机的设计提供参考。

蜗旋换向离心风机  /  正交试验  /  优化设计

To address the issues of insufficient air volume and abnormal sound quality in the dual centrifugal fan system with reversing scroll，based on the single‑factor analysis method，the influence laws of blade profile，volute tongue structure，and collector form on the aerodynamic performance of the fan system were investigated，and structural optimization design of the air‑conditioning scroll reversing centrifugal fan was carried out to obtain the fan structure scheme with the best comprehensive performance.Orthogonal experiments were adopted to clarify the influence weights of structural parameters such as volute tongue inclination angle，anti‑swirl ring height，and guide ring outlet diameter on the performance of the optimized fan.The results show that the order of influence weights of each parameter on air volume is guide ring outlet diameter>volute tongue inclination angle>anti‑swirl ring height；the order of influence weights on sound quality is volute tongue inclination angle>guide ring outlet diameter>anti‑swirl ring height.Considering both air volume and sound quality indicators，the preferred scheme achieves an air volume of 1 223 m3/h，which is about 5% higher than the original scheme，and the noise peak is reduced by about 5 dB.This study can provide a reference for the design of air‑conditioning scroll reversing centrifugal fans.

scroll reversing centrifugal fan  /  orthogonal experiment  /  optimization design
王千千, 蒋锋, 魏彦艳. 基于正交试验的空调蜗旋换向离心风机气动性能优化. 流体机械, 2026 , 54 (6) : 78 -85 . DOI: 10.3969/j.issn.1005-0329.2026.06.010
Qianqian WANG, Feng JIANG, Yanyan WEI. Aerodynamic performance optimization of air‑conditioning scroll reversing centrifugal fan based on orthogonal experiment[J]. Fluid Machinery, 2026 , 54 (6) : 78 -85 . DOI: 10.3969/j.issn.1005-0329.2026.06.010
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0　引言
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随着人民生活水平的提高，消费者对家电产品的舒适性和健康性要求越来越高［1］。国家与地方政府相继出台政策，支持并推动消费结构优化升级［2-4］。分布式送风空调具有沐浴式制冷和地毯式制热的特点［5］，能够提供较好的体感舒适度，广受消费者青睐。在开发新一代上下送风空调时，采用双离心蜗旋换向风机系统送风平台，可实现上出风、下出风和上下出风等多种送风模式。该系统对减少垂直温差、提高体感舒适度具有明显效果。然而，在产品化过程中发现，该风机系统存在风量不足与音质异常的问题，其气动性能亟待提高。
叶型优化是提升离心风机气动性能的常用手段。陈志涛等［6］通过对叶型结构的优化调整，在实现离心风机全压效率提升的同时，使整体噪声降低约3 dB。孟永哲等［7］通过数值模拟研究了叶轮与蜗壳的匹配对流场的影响，结果表明，叶轮与蜗壳的良好匹配能有效减少沿叶片吸力面的流动分离，减小旋涡尺度并降低强度。张弛等［8］采用仿真和实验的方法，对叶轮的叶型进行了参数化拟合构造和优化研究，优化后风机气动性能更好。刘燕潇等［9］通过数值模拟研究了倾斜蜗舌对风机流场与噪声特性的影响，结果表明，采用倾斜蜗舌后风机噪声降低了7.3 dB。徐韧等［10］针对多翼离心风机气动性能、噪声情况难以同时改进的问题，选取叶片进出口角、倾斜蜗舌的最大蜗舌半径、叶片切除角度作为设计变量，对风机进行了优化，优化后风机全压增加了34.79 Pa，效率提高了0.67%，噪声降低了1.73 dB。龚雪武等［11］采用阶梯蜗舌搭配后倾式离心风叶，相较于平蜗舌方案，使噪声总值降低3 dB以上，噪声峰值降低12 dB。刘小民等［12］研究了内凹式蜗舌对双吸多翼离心风机的影响，结果发现，该结构能有效减小蜗舌处压力梯度与旋涡强度，并抑制蜗舌区域噪声的叠加。刘江等［13］以多翼离心风机为研究对象,将蜗壳型线参数化,通过正交试验设计,针对蜗舌放置角、蜗舌半径、蜗壳周向面积、蜗舌与叶轮间隙4个因素,制定了16组参数组合方案，并确定了最优参数组合,优化后的风机出口风量提升7.3%,均匀度提升4.5%,全压效率提升5.9%，显著提升了风机的出风性能和出口风速分布均匀性。郑水华等［14］研究了集流圈圆弧半径对离心风机流场的影响，结果表明，该半径会影响叶轮中的旋涡回流现象，从而改变离心风机的流动特性。林静祥等［15］对某通用离心风机加装防涡圈后发现，通风机的全压和效率反而降低，这表明防涡圈的使用对离心风机不一定总能带来正向收益。上述研究表明，叶型、蜗舌形状及集流器形式均会对风机性能产生影响。因此，可基于叶型、蜗舌形状及集流器形式等因素，探寻最优耦合方案，以提高离心风机系统性能。
在此基础上，本文以双离心蜗旋换向风机系统为研究对象，采用单因素分析法，探究叶型、蜗舌结构及集流器形式对风机系统性能的影响，以确定最佳组合形式。采用正交试验法［16-18］，进一步考察上述结构核心参数对风机气动性能的影响权重。综合考虑风量与音质指标，寻找最优设计方案，以期提升双离心蜗旋换向风机系统的气动性能。
1　蜗旋换向离心风机系统
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1.1　研究对象
文中以某空调器室内机双离心蜗旋换向风机系统为研究对象。该系统包含2个结构相同的单吸离心风机，每个风机主要由蜗壳、电机、叶轮、运动蜗舌及蜗壳盖组成，如图1。风机系统的主要参数如表1所示。
1.2　数学模型及边界条件
为探究某空调器室内机双离心蜗旋换向风机系统的内部流场与压力场，提取该系统流体域并进行简化处理，建立如图2所示的三维流体域模型。
该模型主要包括进风区域、换热器区域、旋转区域和出风区域。与旋转区域相接触的面设置为interface面，其他区域通过interior面连接。湍流模型选用RNG k‑ε模型，壁面函数选用扩展壁面函数，采用SIMPLE算法进行压力修正。进、出风区域分别设置压力进口与压力出口条件，压力均设定为0 Pa（相对压力）；旋转区域采用MRF（多参考坐标系）模型；动量方程、湍动能及湍流耗散率方程均采用二阶迎风格式进行离散。
2　双离心蜗旋换向风机系统优化分析
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2.1　单因素分析
采用单因素分析法，分别改变叶型、蜗舌结构及集流器形式的参数，考察各因素对风机系统气动性能的影响。
2.1.1　叶型对风机性能的影响
风机系统存在风量不足的问题。原始风机竖直截面速度云图如图3所示。从图可以看出，风机出口处蜗舌附近存在低速区，出口截面流动受阻。
为提升风机风量，设计了2款优化风叶，其结构及参数分别如图4、表2所示。由表2可见，2款优化风叶的风量较原风叶均有提升，其中叶型2的提升幅度最大，约为50 m3/h。
图5示出3种叶型叶道内的速度矢量分布。可以看出，原叶型风机出口蜗舌侧的叶道内存在明显回流现象；叶型1在该处叶道内虽无回流，但仍有叶道涡；而叶型2则完全消除了叶道涡。综合比较不同叶型的风量及流场情况，叶型2为最佳方案。
2.1.2　蜗舌结构对风机性能的影响
蜗舌通过调控叶轮出口的气流方向、速度分布及压力脉动，进而影响离心风机的气动性能、效率与噪声水平。为改善整机气动性能，对比了平蜗舌、阶梯蜗舌与倾斜蜗舌对风机性能的影响，3种蜗舌结构如图6所示。
图7示出3种蜗舌结构下蜗舌附近湍动能的对比。采用平蜗舌与阶梯蜗舌时，蜗舌附近的湍动能分布非常相似，而阶梯蜗舌的湍动能较另外两者更小，表明其对气流的冲击作用更弱。采用3种不同蜗舌的风机系统仿真风量及音质表现如表3所示。由表可见，3种蜗舌的风量差异较小，但平蜗舌与阶梯蜗舌方案中均存在旋转噪声，而倾斜蜗舌无此问题，音质体验最佳。因此，本风机系统宜选用倾斜蜗舌。
2.1.3　集流器形式对风机性能的影响
集流器作为离心风机的进气部件，其结构参数显著影响气流进入叶轮前的流动状态，进而决定风机的风量特性、效率水平及噪声频谱特征。导流圈与叶轮的相对位置决定了进口气流的轴向均匀性与攻角分布。防涡圈一般布置在导流圈内侧根部，具有减少集流器前盘二次流的作用，其结构如图8（a）所示。
为验证防涡圈有无以及导流圈与叶轮相对位置对风机性能的影响，采用仿真方法进行分析。导流圈与叶轮的相对位置分为半包裹、全包裹和过度包裹3种情况，其中半包裹指导流圈出口直径位于叶轮内径与外径之间，全包裹指导流圈出口直径与叶轮内径相当，过度包裹指导流圈出口直径大于叶轮内径〔见图8（b）〕。
图9示出有无防涡圈时的局部速度矢量对比，由图可见，增加防涡圈后，可减少前盘回流所致的泄漏量及流动损失。图10示出不同导流圈结构下的压力云图对比，从图可以看出，全包裹与过度包裹方案的导流圈进口压力均较半包裹方案更小，进气条件得到改善。
不同导流圈方案的仿真风量如表4所示。可以看出，随着导流圈出口直径减小，风量呈先增后减趋势，其中最优方案为导流圈出口直径与叶轮内径相当的全包裹方案。综合上述分析，对本系统而言，集流器结构应包含防涡圈，且导流圈相对叶轮位置宜采用全包裹方式，即导流圈出口直径与叶轮内径相当较为理想。
2.2　正交分析
根据单因素分析结果，确定叶型结构为叶型2，蜗舌形状采用倾斜蜗舌。以蜗舌倾斜角度、防涡圈高度及导流圈出口直径为关键因素，设计正交表L16（43），如表5所示。其中，倾斜角度分别为6°，10°，14°，18°；防涡圈高度分别为4，5，6，7 mm；导流圈出口直径分别为200，206，212，218 mm。根据表中的参数建立相应模型并进行仿真计算。
以风量为评价指标，采用极差分析法，结果见表6。由表6可知，各因素极差大小排序为RC>RA>RB，即导流圈出口直径C对双离心蜗旋换向风机系统风量的影响最大，蜗舌倾斜角度A次之，防涡圈高度B的影响最小。同时可得最优参数组合为A4B2C2，即蜗舌倾斜角度18°、防涡圈高度5 mm、导流圈出口直径206 mm。
音质作为空调产品性能的关键评价指标之一，直接影响用户的使用体验。在保证测试有效性的前提下，为减少音质评估的样本数量，选择上述3个因素中风量较大的前两个水平，设计正交表L4（23），如表7所示。通过现场体验，对每个方案进行评分，音质评分区间为0~10分，评分越高表示音质越好。以音质为评价指标，极差分析结果见表8。可以看出，蜗舌倾斜角度A对双离心蜗旋换向风机系统音质的影响最大，导流圈出口直径C次之，防涡圈高度B的影响最小。同时可得最优组合为A1B2C2。综合考虑风量与音质指标，双离心蜗旋换向风机系统的最佳方案为蜗舌倾斜角度14°、防涡圈高度6 mm、导流圈出口直径206 mm。
3　试验验证
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在焓差试验室和半消声室内，对不同方案的手板样件进行了试验验证。分别测试原方案、风量最优方案及音质优化方案在相同噪声条件下的最大风量，并采集其噪声频谱图，测试方案及结果见表9，不同方案的噪声频谱如图11所示。
从图可以看出，风量最优方案的风量提升约8%，但存在旋转噪声问题；音质优化方案无音质异常，且风量提升约5%。
考虑到音质是空调产品更为重要的评价指标，而风量最优方案仍存在音质问题，因此最终选用蜗舌倾斜角度14°、防涡圈高度6 mm、导流圈出口直径206 mm的方案。与原方案相比，最终方案在噪声水平基本相同的条件下，风量提升约5%，且无音质异常问题，噪声峰值降低约5 dB。
4　结论
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（1）通过单因素分析可知，对于蜗旋换向风机系统而言，所设计的3种叶型中叶型2表现最佳；蜗舌结构采用倾斜蜗舌时音质体验最好；集流器建议采用带防涡圈且导流圈出口直径与叶轮内径相当的全包裹形式。
（2）通过正交试验分析，各因素对风量的影响权重依次为导流圈出口直径>蜗舌倾斜角度>防涡圈高度；对音质的影响权重依次为蜗舌倾斜角度>导流圈出口直径>防涡圈高度。
（3）权衡风量与音质指标的重要性后，最终选定方案为叶型2、蜗舌倾斜角度14°、导流圈出口直径206 mm、防涡圈高度6 mm。该方案风量可达1 223 m3/h，较原方案提升约5%，噪声峰值降低约5 dB，且音质体验良好。

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2026年第54卷第6期
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doi: 10.3969/j.issn.1005-0329.2026.06.010
  • 接收时间：2025-10-13
  • 首发时间：2026-10-22
  • 出版时间：2026-06-30
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  • 收稿日期：2025-10-13
  • 修回日期：2026-06-02
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    珠海格力电器股份有限公司，广东 珠海 519070
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鹅膏菌科Amanitaceae 2 11 5.26 鹅膏菌属 Amanita 10 4.78
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