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Article(id=1236611786414289811, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236611783876727231, articleNumber=null, orderNo=null, doi=10.19666/j.rlfd.202410226, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=null, receivedDateStr=null, revisedDate=1734364800000, revisedDateStr=2024-12-17, acceptedDate=null, acceptedDateStr=null, onlineDate=1772760825017, onlineDateStr=2026-03-06, pubDate=1753372800000, pubDateStr=2025-07-25, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1772760825017, onlineIssueDateStr=2026-03-06, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1772760825017, creator=13701087609, updateTime=1772760825017, updator=13701087609, issue=Issue{id=1236611783876727231, tenantId=1146029695717560320, journalId=1210938733613449225, year='2025', volume='54', issue='7', pageStart='1', pageEnd='159', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=0, createTime=1772760824412, creator=13701087609, updateTime=1772761154835, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1236613169855123924, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236611783876727231, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1236613169855123925, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236611783876727231, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=118, endPage=126, ext={EN=ArticleExt(id=1236611786682725273, articleId=1236611786414289811, tenantId=1146029695717560320, journalId=1210938733613449225, language=EN, title=Vibration mechanism of pipeline systems induced by butterfly valves and its suppression countemeasures, columnId=1211002409397129992, journalTitle=Thermal Power Generation, columnName=Power generation technology forum, runingTitle=null, highlight=null, articleAbstract=

Butterfly valves are widely used in industrial field, and under certain working conditions, strong unstable flow will occur in the butterfly valve and cause vibration in pipeline system. By taking the connecting pipe of the medium and low pressure cylinder of a 600 MW heating unit as the research object, the mechanism of unstable flow in the butterfly valve and the vibration of the connecting pipe was revealed through the combination of field measurement and steady numerical simulation. Then, based on the flow pattern optimization, a new type of butterfly valve with valve plate and diversion structure was designed, and the unsteady numerical simulation of the maximum vibration condition of the original butterfly valve and the optimized butterfly valve was carried out. The results show that, after adding the flow-guiding structure to the valve plate, most of the main steam flow moves along the middle of the steam inlet pipe of the low-pressure cylinder. This can effectively weaken the exciting force generated by unstable flow and suppress the vibration of the connecting pipe. The new butterfly valve proposed can be applied to suppress the vibration of the pipeline system with small opening of the butterfly valve.

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蝶阀在工业领域应用广泛，在某些工况，蝶阀内会产生较强的不稳定流动并引发管路系统振动。以某600 MW供热机组中低压连通管为研究对象，通过电厂实测与定常数值模拟相结合的方法揭示蝶阀内产生不稳定流动并导致连通管振动的机理。在此基础上，基于流型优化，设计了一种阀板加导流结构的新型蝶阀，并对原蝶阀和优化蝶阀进行振动最大工况的非定常数值模拟。结果表明，阀板加装导流结构后使大部分蒸汽主流沿低压缸进汽管中部流动，可有效减弱不稳定流动产生的激励力，抑制连通管振动。提出的新型蝶阀可应用于抑制存在蝶阀小开度工况管路系统的振动。

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王汀（1988），男，硕士，高级工程师，主要研究方向为电站节能、供热、灵活性等技术，。

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王汀（1988），男，硕士，高级工程师，主要研究方向为电站节能、供热、灵活性等技术，。

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王汀（1988），男，硕士，高级工程师，主要研究方向为电站节能、供热、灵活性等技术，。

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Xi’an: Xi’an Jiaotong University, 2020: 1., articleTitle=Design and noise level prediction of low noise valve for ship steam turbine, refAbstract=null)], funds=[Fund(id=1236611800612008504, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, awardId=HNKJ23-H54, language=EN, fundingSource=Science and Technology Project of China Huaneng Group Co., Ltd.(HNKJ23-H54), fundOrder=null, country=null), Fund(id=1236611800695894591, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, awardId=HNKJ23-H54, language=CN, fundingSource=中国华能集团有限公司总部科技项目(HNKJ23-H54), fundOrder=null, country=null)], companyList=[AuthorCompany(id=1236611791141269593, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, xref=1., ext=[AuthorCompanyExt(id=1236611791149658201, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, companyId=1236611791141269593, language=EN, 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tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.1, caption=Flow domain model of the connecting pipe and structure of the original butterfly valve, figureFileSmall=6lDLbObrvR/wxDH4k/4+Gw==, figureFileBig=savNFYQdPwZ043hl0dg16w==, tableContent=null), ArticleFig(id=1236611796518367642, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图1, caption=连通管流动域模型与原始蝶阀结构, figureFileSmall=6lDLbObrvR/wxDH4k/4+Gw==, figureFileBig=savNFYQdPwZ043hl0dg16w==, tableContent=null), ArticleFig(id=1236611796774220200, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.2, caption=Grid block partition diagram, figureFileSmall=Ej6YtjesaIdTNEPYVPorJw==, figureFileBig=0to+6AN2VQbWZfiMILMc1w==, tableContent=null), ArticleFig(id=1236611796916826544, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图2, caption=网格分块划分示意, figureFileSmall=Ej6YtjesaIdTNEPYVPorJw==, figureFileBig=0to+6AN2VQbWZfiMILMc1w==, tableContent=null), ArticleFig(id=1236611797025878453, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.3, caption=Grid division diagram of some components, figureFileSmall=7pQmcPsnZ0Z5rzHKCan+yw==, figureFileBig=EJz9ZBpnIx5bQEN2KeKNUQ==, tableContent=null), ArticleFig(id=1236611797130736060, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图3, caption=部分部件网格划分示意, figureFileSmall=7pQmcPsnZ0Z5rzHKCan+yw==, figureFileBig=EJz9ZBpnIx5bQEN2KeKNUQ==, tableContent=null), ArticleFig(id=1236611797214622142, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.4, caption=Test results of vibration of butterfly valve A at different opening degrees, figureFileSmall=15yY+1MHMhcI78BI0/DatQ==, figureFileBig=sU5KgB73mnGIJPL9Ms5UWg==, tableContent=null), ArticleFig(id=1236611797323674053, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图4, caption=蝶阀A不同开度时的振动实测结果, figureFileSmall=15yY+1MHMhcI78BI0/DatQ==, figureFileBig=sU5KgB73mnGIJPL9Ms5UWg==, tableContent=null), ArticleFig(id=1236611797424337353, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.5, caption=Test results of vibration of butterfly valve B at different opening degrees, figureFileSmall=ZCYDg0l19yPs3zip1M5m8A==, figureFileBig=MR8LL1YKXDd7C3OcKAOjvA==, tableContent=null), ArticleFig(id=1236611797512417741, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图5, caption=蝶阀B不同开度时的振动实测结果, figureFileSmall=ZCYDg0l19yPs3zip1M5m8A==, figureFileBig=MR8LL1YKXDd7C3OcKAOjvA==, tableContent=null), 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language=EN, label=Fig.9, caption=Flow structure and velocity vector diagram of butterfly valve B at 10° opening degree, figureFileSmall=DB3l8CxYFRouSqHxVfYA5A==, figureFileBig=FPqDXVdOgRYW2a3GSyxVKA==, tableContent=null), ArticleFig(id=1236611798317724136, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图9, caption=蝶阀B 10°开度时的通流结构和速度矢量图, figureFileSmall=DB3l8CxYFRouSqHxVfYA5A==, figureFileBig=FPqDXVdOgRYW2a3GSyxVKA==, tableContent=null), ArticleFig(id=1236611798451941869, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.10, caption=Schematic diagram of the optimized flow-guiding structure of the valve plate, figureFileSmall=QAGHkWuTwBiHaiHSJP7CCg==, figureFileBig=OGBiH3ToVICiq4aQ0g64ZA==, tableContent=null), ArticleFig(id=1236611798556799471, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图10, caption=阀板导流优化结构示意, figureFileSmall=QAGHkWuTwBiHaiHSJP7CCg==, figureFileBig=OGBiH3ToVICiq4aQ0g64ZA==, tableContent=null), ArticleFig(id=1236611798657462770, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.11, caption=The unbalance forces at different positions of the original butterfly valve at 10° opening degree, figureFileSmall=nubKYzcKHi0n+t0j6IJdCg==, figureFileBig=gBGUQVZKhzLgqFo35O7gFg==, tableContent=null), ArticleFig(id=1236611798787486196, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图11, caption=原始蝶阀10°开度时不同位置所受的不平衡力, figureFileSmall=nubKYzcKHi0n+t0j6IJdCg==, figureFileBig=gBGUQVZKhzLgqFo35O7gFg==, tableContent=null), ArticleFig(id=1236611798900732407, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.12, caption=Flow fields of butterfly valve at 10° opening degree, 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ArticleFig(id=1236611799374688779, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Fig.14, caption=The unbalance forces at different positions of the optimized butterfly valve at 10° opening degree, figureFileSmall=/8rRT2reiFTX6fMisZ3tIw==, figureFileBig=HJr2zatjLnh7WLNHrKurOA==, tableContent=null), ArticleFig(id=1236611799479546382, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=图14, caption=优化后蝶阀10°开度时不同位置所受的不平衡力, figureFileSmall=/8rRT2reiFTX6fMisZ3tIw==, figureFileBig=HJr2zatjLnh7WLNHrKurOA==, tableContent=null), ArticleFig(id=1236611799626347027, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Tab.1, caption=

The inlet and outlet boundary conditions for five working conditions

, figureFileSmall=null, figureFileBig=null, tableContent=
工况蝶阀开度/(°)进口总压/MPa进口温度/℃出口静压/MPa供热流量/(t·h–1)
150.725 0367.350.198 8482.8
2100.707 0363.630.364 6482.8
3150.737 5367.950.484 9362.2
4200.713 0366.520.573 5242.3
5400.720 0372.280.687 8108.2
), ArticleFig(id=1236611799764759063, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=表1, caption=

5个工况的进、出口边界条件

, figureFileSmall=null, figureFileBig=null, tableContent=
工况蝶阀开度/(°)进口总压/MPa进口温度/℃出口静压/MPa供热流量/(t·h–1)
150.725 0367.350.198 8482.8
2100.707 0363.630.364 6482.8
3150.737 5367.950.484 9362.2
4200.713 0366.520.573 5242.3
5400.720 0372.280.687 8108.2
), ArticleFig(id=1236611799861228058, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Tab.2, caption=

The maximum values of peak-to-peak of unbalanced forces in three directions at different positions

, figureFileSmall=null, figureFileBig=null, tableContent=
方向阀板阀壳蝶阀A后蝶阀B后
X1 350.02 710.08 785.010 295.0
Y995.02 770.09 870.011 400.0
Z3 500.0900.079.4110.6
), ArticleFig(id=1236611799999640098, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=表2, caption=

不同位置3个方向不平衡力最大峰峰值

, figureFileSmall=null, figureFileBig=null, tableContent=
方向阀板阀壳蝶阀A后蝶阀B后
X1 350.02 710.08 785.010 295.0
Y995.02 770.09 870.011 400.0
Z3 500.0900.079.4110.6
), ArticleFig(id=1236611800112886308, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Tab.3, caption=

The maximum values of the peak unbalanced forces in three directions at different positions after optimization

, figureFileSmall=null, figureFileBig=null, tableContent=
方向阀板阀壳蝶阀A后蝶阀B后
X1 100.02 920.07 734.08 710.0
Y9 70.02 193.08 410.09 290.0
Z2 900.01 100.064.974.8
), ArticleFig(id=1236611800221938216, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=表3, caption=

优化后不同位置3个方向不平衡力最大峰峰值

, figureFileSmall=null, figureFileBig=null, tableContent=
方向阀板阀壳蝶阀A后蝶阀B后
X1 100.02 920.07 734.08 710.0
Y9 70.02 193.08 410.09 290.0
Z2 900.01 100.064.974.8
), ArticleFig(id=1236611800310018605, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=EN, label=Tab.4, caption=

The maximum values of peak unbalanced forces at different positions before and after optimization

, figureFileSmall=null, figureFileBig=null, tableContent=
位置方向不平衡力最大峰峰值/N差值/%
优化前优化后
阀板Z3 500.02 900.0-17.10
阀壳内壁X2 710.02 920.07.75
Y2 770.02 192.7-20.80
连接管AX8 785.07 734.0-12.00
Y9 872.08 710.0-11.80
连接管BX10 295.08 710.0-15.40
Y11 400.09 290.0-18.50
), ArticleFig(id=1236611800427459120, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236611786414289811, language=CN, label=表4, caption=

优化前后不同位置不平衡力最大峰峰值比较

, figureFileSmall=null, figureFileBig=null, tableContent=
位置方向不平衡力最大峰峰值/N差值/%
优化前优化后
阀板Z3 500.02 900.0-17.10
阀壳内壁X2 710.02 920.07.75
Y2 770.02 192.7-20.80
连接管AX8 785.07 734.0-12.00
Y9 872.08 710.0-11.80
连接管BX10 295.08 710.0-15.40
Y11 400.09 290.0-18.50
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蝶阀引发管路系统振动机理及抑制措施
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王汀 1 , 彰金宝 2 , 翟鹏程 3 , 谢天 1 , 李毅刚 2 , 王耀文 1 , 穆祺伟 1 , 于龙文 3 , 邵建林 2 , 刘观伟 4
热力发电 | 发电技术论坛 2025,54(7): 118-126
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热力发电 | 发电技术论坛 2025, 54(7): 118-126
蝶阀引发管路系统振动机理及抑制措施
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王汀1 , 彰金宝2, 翟鹏程3, 谢天1, 李毅刚2, 王耀文1, 穆祺伟1, 于龙文3, 邵建林2, 刘观伟4
作者信息
  • 1.西安热工研究院有限公司，陕西　西安　710054
  • 2.国能三河发电有限责任公司，河北　廊坊　065201
  • 3.西安西热节能技术有限公司，陕西　西安　710054
  • 4.西安交通大学能源与动力工程学院，陕西　西安　710049

    • 王汀（1988），男，硕士，高级工程师，主要研究方向为电站节能、供热、灵活性等技术，。

Vibration mechanism of pipeline systems induced by butterfly valves and its suppression countemeasures
Ting WANG1 , Jinbao ZHANG2, Pengcheng ZHAI3, Tian XIE1, Yigang LI2, Yaowen WANG1, Qiwei MU1, Longwen YU3, Jianlin SHAO2, Guanwei LIU4
Affiliations
  • 1.Xi’an Thermal Power Research Institute Co., Ltd., Xi’an 710054, China
  • 2.Guoneng Sanhe Power Generation Co., Ltd., Langfang 065201, China
  • 3.Xi’an Xire Saving & Emissions Control Technology Co., Ltd., Xi’an 710054, China
  • 4.School of Energy and Power Engineering, Xi’an Jiaotong University, Xi’an 710049, China
出版时间: 2025-07-25 doi: 10.19666/j.rlfd.202410226
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摘要
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蝶阀在工业领域应用广泛，在某些工况，蝶阀内会产生较强的不稳定流动并引发管路系统振动。以某600 MW供热机组中低压连通管为研究对象，通过电厂实测与定常数值模拟相结合的方法揭示蝶阀内产生不稳定流动并导致连通管振动的机理。在此基础上，基于流型优化，设计了一种阀板加导流结构的新型蝶阀，并对原蝶阀和优化蝶阀进行振动最大工况的非定常数值模拟。结果表明，阀板加装导流结构后使大部分蒸汽主流沿低压缸进汽管中部流动，可有效减弱不稳定流动产生的激励力，抑制连通管振动。提出的新型蝶阀可应用于抑制存在蝶阀小开度工况管路系统的振动。

蝶阀  /  管路系统  /  振动机理  /  流型优化  /  振动抑制

Butterfly valves are widely used in industrial field, and under certain working conditions, strong unstable flow will occur in the butterfly valve and cause vibration in pipeline system. By taking the connecting pipe of the medium and low pressure cylinder of a 600 MW heating unit as the research object, the mechanism of unstable flow in the butterfly valve and the vibration of the connecting pipe was revealed through the combination of field measurement and steady numerical simulation. Then, based on the flow pattern optimization, a new type of butterfly valve with valve plate and diversion structure was designed, and the unsteady numerical simulation of the maximum vibration condition of the original butterfly valve and the optimized butterfly valve was carried out. The results show that, after adding the flow-guiding structure to the valve plate, most of the main steam flow moves along the middle of the steam inlet pipe of the low-pressure cylinder. This can effectively weaken the exciting force generated by unstable flow and suppress the vibration of the connecting pipe. The new butterfly valve proposed can be applied to suppress the vibration of the pipeline system with small opening of the butterfly valve.

butterfly valve  /  pipeline system  /  vibration mechanism  /  flow pattern optimization  /  vibration suppression
王汀, 彰金宝, 翟鹏程, 谢天, 李毅刚, 王耀文, 穆祺伟, 于龙文, 邵建林, 刘观伟. 蝶阀引发管路系统振动机理及抑制措施. 热力发电, 2025 , 54 (7) : 118 -126 . DOI: 10.19666/j.rlfd.202410226
Ting WANG, Jinbao ZHANG, Pengcheng ZHAI, Tian XIE, Yigang LI, Yaowen WANG, Qiwei MU, Longwen YU, Jianlin SHAO, Guanwei LIU. Vibration mechanism of pipeline systems induced by butterfly valves and its suppression countemeasures[J]. Thermal Power Generation, 2025 , 54 (7) : 118 -126 . DOI: 10.19666/j.rlfd.202410226
正文
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管路系统广泛应用于船舶、航空、汽车等领域，其振动和噪声可能会导致设备的失效与破坏，学者对此进行了大量的研究[1-5]。蝶阀因结构相对简单、重量轻、操作灵敏、安装空间相对较小被大量应用于石油化工、燃气输送、热力发电等领域，其流动与振动特性受到越来越多研究者的关注[6-8]。安装在管路系统中的蝶阀，在某些运行工况阀内会产生较强的不稳定流动，不稳定流动产生的激励力导致蝶阀产生振动，进而引发管路系统振动。因此，研究蝶阀引发管路系统振动的机理及其抑制方法具有十分重要的工程意义。
火电厂供热机组供热扩容及电调峰改造大量采用低压缸零出力技术，常出现蝶阀小开度时中低压连通管振动问题，导致连通管膨胀节裂纹、测量装置损坏、连通管泄漏等事故频繁发生，甚至发生过因膨胀节爆破导致机组被迫停机的事件，严重影响机组的安全运行和供热稳定性[9-13]。为了抑制中低压连通管振动，本文以某600 MW供热机组为研究对象，首先通过电厂实测与定常数值模拟相结合的方法揭示蝶阀引发连通管振动的机理；然后基于流型优的思想对阀板进行优化；最后通过对原蝶阀和优化后蝶阀在连通管振动最大工况的流场非定常数值模拟，比较优化前后的蒸汽激励力，说明抑制效果。
1　数值模拟方法
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1.1　模型建立
某600 MW供热机组中低压连通管及冷却蒸汽管路系统流道结构包含2个蝶阀、2个调节阀、 4个膨胀节和7个不同直径圆管相贯的三通结构。由于整个管路系统内的流动过程包含蝶阀、调节阀等复杂流动，物理边界对其影响非常显著。合理地剔除对流动影响小的结构，不仅可以准确反映流动的特性，还能提高网格质量、保证计算稳定性、节省计算资源。为此，本文不考虑膨胀节、法兰等对流道结构的影响，并将对流动影响较小且角度小于9°的模型“尖角”处变为小平面。最终建立的实际尺寸连通管及冷却蒸汽管路流动域三维模型和原始蝶阀结构见图1。需要说明的是，为了凸显连通管振动，将2个蝶阀设置成相同的开度；为了使计算模型出口流动均匀无回流，将管路系统出口在原有的基础上加长了6.5 m。
1.2　网格划分
汽轮机中低压连通管及冷却蒸汽管路系统内的流动复杂，其网格划分对计算结果的精度和计算效率有决定性影响。目前的网格划分方法主要有结构化和非结构化2种[14]，结构化网格只需存储各网格节点及其控制容积的几何信息，计算所需内存小、计算时间少[15]。
本文对计算区域采用分块网格划分方法，将整个计算区域分为13个块（以阀碟开度10°工况为例），具体如图2所示。
2个蝶阀划分为2个块（FLUID 11）、2个调节阀划分为2个块（FLUID 10）、进口管、供热管和部分与进口管相连的冷却管划分为1个块（FLUID 1）、连通管划分为1个块（FLUID 2）、连通管两侧的平衡孔后封口管各划分为2个块（FLUID 3、FLUID 4、FLUID 5、FLUID 6）、冷却管道划分为1个块（FLUID 9）、2个出口管划分为2个块（FLUID 7、FLUID 8）。在这13个块中，除蝶阀和调节阀采用非结构化网格外（图3），其余均采用结构化网格，总网格数为3 579万。
1.3　湍流模型选择
完成模型建立和网格划分后，进行流场数值模拟，还需要解决以下几个问题。
1）流动工质
本文选择Fluent软件实际气体模型中的水蒸气作为流动工质，该模型基于IAPWS-IF97水蒸气实际气体性质数据来计算水蒸气工质的物性，能更精确地模拟连通管内的蒸汽工质性质。
2）边界条件
对中压缸出口（模型进口）和低压缸进口（模型出口）采用进口总压和出口静压边界条件，对供热管出口采用流量出口边界条件。本文数值模拟5个工况的进、出口边界条件见表1。此外，由于电厂实际蒸汽管路均做了保温处理，所有固体壁面均采用绝热无滑移条件。
3）定常流场模拟湍流模型及壁面函数　目前求解N-S方程应用较广的方法有直接模拟、大涡模拟和雷诺平均3种，其中雷诺平均法更适合工程应用。西安交通大学毛靖儒研究团队曾采用标准k-ε、Realizable k-ε和SST k-ω 3种湍流模型对某调节阀典型工况进行了数值模拟。模拟结果表明，Realizable k-ε模型能更准确地模拟调节阀内流动特性，模拟所得的流量、速度场以及压力场结果与实验的误差最小[16]。因此，本文采用Realizable k-ε模型进行模拟。
对壁面函数的选择，由于Scalable壁面函数消除了进入黏性底层的内节点对模拟结果的影响，克服了标准壁面函数法的缺陷，因此本文选择Scalable壁面函数进行连通管内复杂流动的定常数值模拟。
4）非定常流场模拟方法　研究表明，大涡模拟（LES）能更好捕捉连通管内复杂流动的非定常特性，从而获得更精确的连通管流体激励力。因此，本文选择LES作为非定常流场模拟的湍流模型。西安交通大学毛靖儒研究团队曾对某调节阀采用LES进行了不同亚格子的非定常数值模拟，比较了同一工况2种亚格子模型阀出口最大马赫数截面监测点的压力脉动，发现Smagorinsky-Lilly亚格子模型（SL亚格子模型）与WALE亚格子模型计算所得的压力脉动差别不大，但SL亚格子模型计算所得的压力脉动幅度较大[17]。因此，最终选用LES通流模型及SL亚格子模型进行连通管内流动的非定常数值模拟。计算时间步10–4 s，每个时间步迭代计算10次。
2　结果与讨论
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2.1　蝶阀5个开度工况定常流场数值模拟
靠近中压缸排汽口的蝶阀为蝶阀A，远离中压缸排汽口的蝶阀为蝶阀B。对该600 MW机组进行了现场测试，蝶阀A和蝶阀B在不同开度时的振动测试结果见图4和图5。电厂实测结果表明，连通管振动主要发生在蝶阀5%~20%开度工况，振动最大时蝶阀开度为10°。
图6和图7给出了2个蝶阀来流管道中心截面，在开度5°、10°、15°、20°和40°这5个工况下，定常数值模拟所得的流场和压力分布。可以看出，2个蝶阀在5个工况下的流场差别不大。在蝶阀开度5°~20°工况，蝶阀前压力变化不大，通过蝶阀后压力才产生剧烈变化。
为了便于分析，图8给出了蝶阀A不同工况下的流场速度矢量图。从图8中可以看出，在蝶阀小开度工况时，蝶阀阀板向来流方向开启一侧流出的主流蒸汽会发生分离并产生空穴区，随着开度增大，该空穴区先增大后减小。蝶阀开度小于5°时，蒸汽主流基本贴附阀板流动，主流脉动不强，激励力和波动冲击力不大；而开度大于40°后，由于开度大，蒸汽主流在离开阀板后大部分沿管道中心流入低压缸，对阀板的脉动激励力和对连接管内壁的波动冲击力也较小；在蝶阀10°~20°开度工况，主流蒸汽时而贴附阀板、时而与阀板分离，形成较强的不稳定流动和较大的脉动激励力与波动冲击力，从而使连通管产生较大的振动。
图9给出了振动最大工况即蝶阀B开度10°时阀板开启侧的流道结构和速度矢量。可以看出，由于蝶阀流道结构的影响，在蝶阀阀板向来流方向开启的一侧（图9中左侧），从蝶阀流出的蒸汽主流会先离开阀板产生分离涡（图9中红线区域），然后又贴附阀板。在蒸汽主流与阀板分离和贴附的过程中，会对阀板产生脉动激励力，并对阀壳和蝶阀与低压缸进汽口连接管的内壁产生波动的冲击力，由于蒸汽主流流量大，该脉动激励力和冲击力也较大。
上述定常流场数值模拟的分析结果与电厂实测的振动较大区间吻合，即蝶阀开度在10°~20°时易产生流场不稳定和较大振动。这说明蝶阀引发连通管振动的机理是小开度下从蝶阀阀板向来流方向开启一侧流出的蒸汽主流会产生较强的不稳定流动，产生较大的激励力，引发管道系统振动。
2.2　基于流型优化的阀板结构优化
为了从根源上减弱蝶阀小开度工况不稳定流动对连通管的激励力，抑制连通管振动，基于流型优化的思想，对蝶阀阀板进行了结构优化。
为了描述方便，将阀板向来流方向开启的那一侧定义为背向来流侧，另一侧定义为朝向来流侧（图10）。阀板结构优化的目标为使蒸汽主流与阀板分离后不再重新贴附阀板，而是沿管道中心流入低压缸。为此，在阀板背向来流侧增加90°的导流结构，具体如图10所示。该导流结构可使蝶阀小开度工况阀板背向来流侧流出的流体往管道中心流动而不再贴附阀板。这样，不仅减小了贴附阀板不稳定主流对阀板的激励力，还减小了该主流对阀壳和其后连接管道内壁的激励力。
2.3　原始蝶阀开度10°工况非定常流场数值模拟
为了验证阀板优化结构对连通管振动的抑制作用，首先对使用原始蝶阀的连通管进行了电厂实测振动最大工况（蝶阀开度10°）连通管内非定常流场的数值模拟。
电厂实测结果表明，连通管振动主要为低频（10~15 Hz）振动。因此，每隔0.01 s保存1次非定常流场模拟结果，以及阀壳内壁面、阀板表面和蝶阀与低压缸连接管内壁面的压力数据。
为了进一步认识蝶阀不稳定流动产生的激励力，图11给出了阀壳内壁、阀板和蝶阀与低压缸连接管道内壁（蝶阀后）这3个位置X、Y、Z方向不平衡力随计算时间步的变化曲线。各坐标轴的方向见图1。
表2给出了不同位置3个方向的不平衡力最大峰峰值。由表2可以看出：阀板所受的不平衡力主要集中在Z方向，验证了主流分离与贴附阀板是在阀板处产生激励力的主因；阀壳内壁和2个低压缸进汽连接管所受的不平衡力则集中在X方向与Y方向，这是主流冲击蝶阀阀壳和蝶阀与低压缸进口连接管内壁的位置不停变化产生的。此外，在X方向与Y方向2个连接管内壁所受的不平衡力最大达11 400.0 N，最小为8 785.0 N，比阀板所受的最大不平衡力3 500.0 N和阀壳所受的最大不平衡力2 770.0 N大得多，这是连接管内壁受到主流大面积直接冲击的缘故。
2.4　优化蝶阀开度10°工况非定常流场数值模拟
2.4.1　流场和压力场
图12和图13给出了蝶阀优化前后开度10°工况蝶阀B在来流管道中心截面的速度矢量场和压力场。需要说明的是，图12、图13中的0 s指非定常计算开始保存时的流场，并不是计算时间步。
由图12、图13可以看出：阀板加导流结构优化后，从蝶阀阀板向来流方向开启那一侧流出的蒸汽主流不再贴附阀碟，大部分沿低压缸进汽管中部流动；且蒸汽主流对低压缸进汽管内壁的冲击也大大减弱，不仅冲击速度降低，冲击角度也减小。因此，阀板加导流结构优化了蝶阀内的流型，可有效减弱不稳定流动产生的激励力。
2.4.2　激励力
图14为优化后阀壳内壁、阀板和蝶阀与低压缸连接管道内壁（蝶阀后）这3个位置X、Y、Z方向不平衡力随计算时间步的变化曲线。表3给出了优化后不同位置3个方向不平衡力最大峰峰值。
为了更直观展现优化结构对连通管内不稳定流动激励力的抑制效果，表4给出了优化前后不同位置不平衡力最大峰峰值及其差值。
从表4可以看出，优化后不同位置所受的不稳定流动激励力最大峰峰值普遍降低。总体而言，阀板加导流结构优化使蒸汽主流对阀板和连接管的激励力均降低了11%以上。显然，激励力的降低会使连通管振动减小，从而有效抑制连通管振动。
3　结论
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本文以某600 MW供热机组中低压连通管为对象，研究蝶阀引发的管路系统振动机理及抑制方法。通过对蝶阀开度5°~40°共5个工况连通管内流场的数值模拟，揭示了蝶阀引发连通管振动的激励源为小开度工况下主流蒸汽与阀板发生分离、形成空穴区和脱落涡，产生时而贴附阀板、时而与阀板分离的强不稳定流动。因此，抑制蝶阀引发管路系统振动的根本在于抑制蝶阀小开度时的强不稳定流动。
基于流型优化的思想，提出一种阀板加导流结构的新型蝶阀，并进行原始蝶阀和优化蝶阀连通管振动最大工况（开度10°）的非定常流场数值模拟。结果表明，在激励力最大的连接管内壁处，连接管A优化后X和Y方向的不平衡力最大峰峰值降低了12.00%和11.80%；连接管B优化后X和Y方向的不平衡力最大峰峰值降低了15.40%和18.50%。
虽然本文的研究结果尚未应用于工程实际，但优化前后不同部位不平衡力最大峰峰值的比较结果说明阀板加导流结构优化有效减弱了蝶阀小开度时不稳定流动产生的激励力，对蝶阀引发的管路系统振动能起到良好的抑制效果，可应用于抑制存在蝶阀小开度工况管路系统的振动。
基金
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  • 中国华能集团有限公司总部科技项目(HNKJ23-H54)
文献
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2025年第54卷第7期
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doi: 10.19666/j.rlfd.202410226
  • 首发时间：2026-03-06
  • 出版时间：2025-07-25
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  • 修回日期：2024-12-17
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Science and Technology Project of China Huaneng Group Co., Ltd.(HNKJ23-H54)
中国华能集团有限公司总部科技项目(HNKJ23-H54)
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    1.西安热工研究院有限公司，陕西　西安　710054
    2.国能三河发电有限责任公司，河北　廊坊　065201
    3.西安西热节能技术有限公司，陕西　西安　710054
    4.西安交通大学能源与动力工程学院，陕西　西安　710049
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https://castjournals.cast.org.cn/joweb/rlfd/CN/10.19666/j.rlfd.202410226
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2种不同金属材料的力学参数
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Family		 属数
Number of
genus		 种数
Number of
species		 占总种数比例
Percentage of
total species (%)		 属
Genus		 种数
Number of
species		 占总种数比例
Percentage of total
species (%)
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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