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Article(id=1217836118184215331, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, articleNumber=null, orderNo=null, doi=10.19666/j.rlfd.202503062, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1742745600000, receivedDateStr=2025-03-24, revisedDate=null, revisedDateStr=null, acceptedDate=null, acceptedDateStr=null, onlineDate=1768284356876, onlineDateStr=2026-01-13, pubDate=1766592000000, pubDateStr=2025-12-25, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1768284356876, onlineIssueDateStr=2026-01-13, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1768284356876, creator=13701087609, updateTime=1768284356876, updator=13701087609, issue=Issue{id=1217836113499177684, tenantId=1146029695717560320, journalId=1210938733613449225, year='2025', volume='54', issue='12', pageStart='1', pageEnd='156', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1768284355759, creator=13701087609, updateTime=1768284424805, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1217836403174593046, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1217836403174593047, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=150, endPage=156, ext={EN=ArticleExt(id=1217836118444262194, articleId=1217836118184215331, tenantId=1146029695717560320, journalId=1210938733613449225, language=EN, title=Practical application and technical discussions of the first set of 1 000 MW domestic full-capacity feed pump unit, columnId=1211002405299294959, journalTitle=Thermal Power Generation, columnName=Thermal energy science research, runingTitle=null, highlight=null, articleAbstract=

The optimization design of the first domestically produced full-capacity feedwater pump used for No.9 unit of the Huaneng North Power Dalat Power Plant Phase V expansion project (1×1 000 MW) is introduced. The three-dimensional structural model of the feedwater pump is established by using ANSYS Workbench software, and the thermal stress analysis of the pump body and finite-element calculation of the impeller strength are conducted. Moreover, the trial operation of the turbine-driven feedwater pump unit and optimization suggestions are provided. The feedwater pump runs under various load conditions of the unit, ensuring that the feedwater flow and pump outlet pressure meet the operational requirements, with the temperature and vibration indicators of each bearing in the steam pump unit falling within the excellent range. Based on the performance assessment test data of the feedwater pump, the calculated efficiency is 84.32%, which exceeds the guaranteed efficiency value. The successful application of this domestically produced full-capacity steam feedwater pump unit in a 1 000 MW coal-fired unit can provide experience for planned or newly constructed units and has certain reference value.

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介绍了华能北方电力达拉特发电厂五期扩建工程（1×1 000 MW）9号机组采用的首台国产化全容量给水泵的优化设计，利用ANSYS Workbench软件建立给水泵三维结构模型，对给水泵筒体进行热应力分析、叶轮强度有限元计算，并给出了汽动给水泵（汽泵）组试运情况及优化建议。给水泵在机组各负荷工况下运行时，给水流量及泵出口压力能满足运行要求，汽泵组各轴承温度及振动指标达到优良范围。通过给水泵性能考核试验数据，计算给水泵效率为84.32%，高于效率保证值。该国产化全容量汽泵组在1 000 MW级燃煤机组的成功应用，可为计划或新建的机组提供经验。

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安宗武（1978），高级工程师，主要研究方向为大型火电机组启动调试技术及运行优化，。
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崔志勇（1976），高级工程师，主要研究方向为火电厂汽轮机安装、检修技术，。

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崔志勇（1976），高级工程师，主要研究方向为火电厂汽轮机安装、检修技术，。

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崔志勇（1976），高级工程师，主要研究方向为火电厂汽轮机安装、检修技术，。

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ArticleFig(id=1217836126790926532, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=EN, label=Fig.2, caption=Thermo-structural stress contour of the feedwater pump barrel, figureFileSmall=3duSEkvd/qZ7ZRW1cTAjhQ==, figureFileBig=QhQvj4BNICA7ksamHqyUzQ==, tableContent=null), ArticleFig(id=1217836126874812616, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=CN, label=图2, caption=给水泵筒体热-结构应力云图, figureFileSmall=3duSEkvd/qZ7ZRW1cTAjhQ==, figureFileBig=QhQvj4BNICA7ksamHqyUzQ==, tableContent=null), ArticleFig(id=1217836127076139214, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=EN, label=Fig.3, caption=Thermo-structural strain contour diagram of the feedwater pump barrel, figureFileSmall=ihgJO3A935gVf0rNFoOdvw==, figureFileBig=lxg1sD0TyYrkgaGVFGsrbw==, tableContent=null), ArticleFig(id=1217836127189385423, tenantId=1146029695717560320, 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tableContent=null), ArticleFig(id=1217836127952748785, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=EN, label=Tab.1, caption=

The main parameters of feedwater pumps at home and abroad

, figureFileSmall=null, figureFileBig=null, tableContent=
项目中国①德国日本英国
温度/℃192.0192.0192.0192.0
流量/(t·h–1)3 502.03 433.03 430.03 430.0
扬程/m4 002.03 680.03 690.03 690.0
效率/%87.7486.3086.8087.40
转速/(r·min–1)5 050.05 120.05 046.04 985.0
功率/kW37 982.034 792.034 725.034 487.0
芯包方式全抽芯全抽芯全抽芯全抽芯
), ArticleFig(id=1217836128065994999, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=CN, label=表1, caption=

国内外给水泵主要参数对比

, figureFileSmall=null, figureFileBig=null, tableContent=
项目中国①德国日本英国
温度/℃192.0192.0192.0192.0
流量/(t·h–1)3 502.03 433.03 430.03 430.0
扬程/m4 002.03 680.03 690.03 690.0
效率/%87.7486.3086.8087.40
转速/(r·min–1)5 050.05 120.05 046.04 985.0
功率/kW37 982.034 792.034 725.034 487.0
芯包方式全抽芯全抽芯全抽芯全抽芯
), ArticleFig(id=1217836128141492475, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=EN, label=Tab.2, caption=

Operation test data of recirculation mode of the turbine-driven feedwater pump unit

, figureFileSmall=null, figureFileBig=null, tableContent=
项目数值
汽泵转速/(r·min–1)1 0001 8002 800
汽泵入口压力/MPa0.370.450.65
汽泵出口压力/MPa1.306.5211.82
润滑油压力/MPa0.200.200.19
润滑油温度/℃41.041.041.5
汽泵前轴承振动X/Y/µm22.0/10.734.0/24.129.5/24.3
汽泵后轴承振动X/Y/μm21.5/16.431.3/23.621.9/15.5
汽泵前轴承温度/℃36.541.859.6
汽泵后轴承温度/℃36.442.556.6
密封水回水温度/℃25.6/24.725.8/25.026.5/25.7
), ArticleFig(id=1217836128246350081, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=CN, label=表2, caption=

汽泵组再循环方式试运数据

, figureFileSmall=null, figureFileBig=null, tableContent=
项目数值
汽泵转速/(r·min–1)1 0001 8002 800
汽泵入口压力/MPa0.370.450.65
汽泵出口压力/MPa1.306.5211.82
润滑油压力/MPa0.200.200.19
润滑油温度/℃41.041.041.5
汽泵前轴承振动X/Y/µm22.0/10.734.0/24.129.5/24.3
汽泵后轴承振动X/Y/μm21.5/16.431.3/23.621.9/15.5
汽泵前轴承温度/℃36.541.859.6
汽泵后轴承温度/℃36.442.556.6
密封水回水温度/℃25.6/24.725.8/25.026.5/25.7
), ArticleFig(id=1217836128317653251, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=EN, label=Tab.3, caption=

Main test results of the turbine-driven feedwater pump unit under different working conditions

, figureFileSmall=null, figureFileBig=null, tableContent=
项目VWO100%75%50%
主蒸汽压力/MPa24.36827.98123.36816.473
大气压力/kPa90.790.490.690.6
主给水泵入口压力/MPa2.9263.0402.4311.718
主给水泵入口温度/℃184.5183.6172.9157.7
主给水泵入口流量/(t·h–1)2 812.4372 794.2202 121.1781 352.947
主给水泵出口压力/MPa30.72733.59627.22018.811
主给水泵出口温度/℃189.8189.2177.3160.6
主给水泵出口流量/(t·h–1)2 774.9222 776.1382 103.6351 335.003
主给水泵扬程/m3 168.73 473.12 793.21 903.6
中间抽头压力/MPa13.48314.76212.0838.493
中间抽头温度/℃186.9182.7164.2162.9
中间抽头流量/(t·h–1)37.5118.0817.5417.94
中间抽头扬程/m1 218.81 351.61 099.3759.0
前置泵入口压力/MPa1.2521.2251.0030.754
前置泵入口温度/℃184.2183.2172.7157.6
前置泵入口流量/(t·h–1)2 812.0822 794.6502 122.2901 355.213
前置泵的扬程/m192.7208.7162.1107.2
转速/(r·min–1)4 5244 6644 0043 184
前置泵有效功率/kW1 476.11 588.7936.3395.2
给水泵有效功率/kW23 950.826 434.516 138.97 015.3
中间抽头有效功率/kW124.566.652.537.1
泵体对外散热系数1.001.001.001.00
给水泵轴功率/kW28 909.531 203.418 944.78 521.4
给水泵效率/%83.2884.3884.7681.67
修正到设计转速下流量/(t·h–1)2 986.262 878.002 544.742 041.24
修正到设计转速下扬程/m3 543.23 670.04 000.04 298.6
修正到设计转速下轴功率/kW34 607.934 095.232 710.729 265.2
), ArticleFig(id=1217836128430899463, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836118184215331, language=CN, label=表3, caption=

各工况下汽泵组主要试验结果

, figureFileSmall=null, figureFileBig=null, tableContent=
项目VWO100%75%50%
主蒸汽压力/MPa24.36827.98123.36816.473
大气压力/kPa90.790.490.690.6
主给水泵入口压力/MPa2.9263.0402.4311.718
主给水泵入口温度/℃184.5183.6172.9157.7
主给水泵入口流量/(t·h–1)2 812.4372 794.2202 121.1781 352.947
主给水泵出口压力/MPa30.72733.59627.22018.811
主给水泵出口温度/℃189.8189.2177.3160.6
主给水泵出口流量/(t·h–1)2 774.9222 776.1382 103.6351 335.003
主给水泵扬程/m3 168.73 473.12 793.21 903.6
中间抽头压力/MPa13.48314.76212.0838.493
中间抽头温度/℃186.9182.7164.2162.9
中间抽头流量/(t·h–1)37.5118.0817.5417.94
中间抽头扬程/m1 218.81 351.61 099.3759.0
前置泵入口压力/MPa1.2521.2251.0030.754
前置泵入口温度/℃184.2183.2172.7157.6
前置泵入口流量/(t·h–1)2 812.0822 794.6502 122.2901 355.213
前置泵的扬程/m192.7208.7162.1107.2
转速/(r·min–1)4 5244 6644 0043 184
前置泵有效功率/kW1 476.11 588.7936.3395.2
给水泵有效功率/kW23 950.826 434.516 138.97 015.3
中间抽头有效功率/kW124.566.652.537.1
泵体对外散热系数1.001.001.001.00
给水泵轴功率/kW28 909.531 203.418 944.78 521.4
给水泵效率/%83.2884.3884.7681.67
修正到设计转速下流量/(t·h–1)2 986.262 878.002 544.742 041.24
修正到设计转速下扬程/m3 543.23 670.04 000.04 298.6
修正到设计转速下轴功率/kW34 607.934 095.232 710.729 265.2
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1 000 MW机组首台国产化全容量给水泵组实际应用与技术分析
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崔志勇 1 , 尚卫军 2 , 安宗武 3 , 胡永海 4 , 江飞 1 , 姜宏伟 1 , 唐永利 1 , 王海英 1 , 王珊珊 4
热力发电 | 热能科学研究 2025,54(12): 150-156
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热力发电 | 热能科学研究 2025, 54(12): 150-156
1 000 MW机组首台国产化全容量给水泵组实际应用与技术分析
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崔志勇1 , 尚卫军2, 安宗武3 , 胡永海4, 江飞1, 姜宏伟1, 唐永利1, 王海英1, 王珊珊4
作者信息
  • 1.达拉特发电厂，内蒙古　鄂尔多斯　014300
  • 2.北方联合电力有限责任公司，内蒙古　呼和浩特　010020
  • 3.西安热工研究院有限公司，陕西　西安　710054
  • 4.上海能源装备有限公司，上海　201317

    • 崔志勇（1976），高级工程师，主要研究方向为火电厂汽轮机安装、检修技术，。

通讯作者:

安宗武（1978），高级工程师，主要研究方向为大型火电机组启动调试技术及运行优化，。
Practical application and technical discussions of the first set of 1 000 MW domestic full-capacity feed pump unit
Zhiyong CUI1 , Weijun SHANG2, Zongwu AN3 , Yonghai HU4, Fei JIANG1, Hongwei JIANG1, Yongli TANG1, Haiying WANG1, Shanshan WANG4
Affiliations
  • 1.Dalat Power Plant, Ordos 014300, China
  • 2.North United Power Co., Ltd., Hohhot 010020, China
  • 3.Xi’an Thermal Power Research Institute Co., Ltd., Xi’an 710054, China
  • 4.Shanghai Energy Equipment Co., Ltd., Shanghai 201317, China
出版时间: 2025-12-25 doi: 10.19666/j.rlfd.202503062
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摘要
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介绍了华能北方电力达拉特发电厂五期扩建工程（1×1 000 MW）9号机组采用的首台国产化全容量给水泵的优化设计，利用ANSYS Workbench软件建立给水泵三维结构模型，对给水泵筒体进行热应力分析、叶轮强度有限元计算，并给出了汽动给水泵（汽泵）组试运情况及优化建议。给水泵在机组各负荷工况下运行时，给水流量及泵出口压力能满足运行要求，汽泵组各轴承温度及振动指标达到优良范围。通过给水泵性能考核试验数据，计算给水泵效率为84.32%，高于效率保证值。该国产化全容量汽泵组在1 000 MW级燃煤机组的成功应用，可为计划或新建的机组提供经验。

给水泵  /  给水流量  /  轴承  /  国产化  /  可靠性

The optimization design of the first domestically produced full-capacity feedwater pump used for No.9 unit of the Huaneng North Power Dalat Power Plant Phase V expansion project (1×1 000 MW) is introduced. The three-dimensional structural model of the feedwater pump is established by using ANSYS Workbench software, and the thermal stress analysis of the pump body and finite-element calculation of the impeller strength are conducted. Moreover, the trial operation of the turbine-driven feedwater pump unit and optimization suggestions are provided. The feedwater pump runs under various load conditions of the unit, ensuring that the feedwater flow and pump outlet pressure meet the operational requirements, with the temperature and vibration indicators of each bearing in the steam pump unit falling within the excellent range. Based on the performance assessment test data of the feedwater pump, the calculated efficiency is 84.32%, which exceeds the guaranteed efficiency value. The successful application of this domestically produced full-capacity steam feedwater pump unit in a 1 000 MW coal-fired unit can provide experience for planned or newly constructed units and has certain reference value.

feedwater pump  /  feedwater flow  /  bearing  /  domestication  /  reliability
崔志勇, 尚卫军, 安宗武, 胡永海, 江飞, 姜宏伟, 唐永利, 王海英, 王珊珊. 1 000 MW机组首台国产化全容量给水泵组实际应用与技术分析. 热力发电, 2025 , 54 (12) : 150 -156 . DOI: 10.19666/j.rlfd.202503062
Zhiyong CUI, Weijun SHANG, Zongwu AN, Yonghai HU, Fei JIANG, Hongwei JIANG, Yongli TANG, Haiying WANG, Shanshan WANG. Practical application and technical discussions of the first set of 1 000 MW domestic full-capacity feed pump unit[J]. Thermal Power Generation, 2025 , 54 (12) : 150 -156 . DOI: 10.19666/j.rlfd.202503062
正文
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随着全球能源转型和国内经济高质量发展的不断深入，在国家“双碳”目标和《中国制造2025》政策的推动下，电力设备国产化率逐步提高，部分高端设备已达到国际领先水平。电力设备国产替代不仅有助于提高我国电力设备的自主创新能力，降低成本，还能有效提升我国电力行业的国际竞争力和抗风险能力，具有重要的意义[1-10]。
1　汽动给水泵应用现状
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给水泵作为锅炉给水的重要设备，其安全、可靠、稳定运行是保证机组正常运行的必要条件。为降低厂用电，我国大型火电超超临界机组一般采用2台容量50%或1台容量100%的汽动给水泵（汽泵）组，由小汽轮机驱动，同轴布置[5-7]。电动给水泵因厂用电率高使用率逐年下降，新建火电机组一般配置1台30%或40%容量的电动给水泵在机组启动阶段使用，汽泵运行后电动给水泵只作为备用。由于国内企业对大型高压水泵的核心技术自主研发能力与国外引进给水泵差距较大，在较长一段时期内国产化给水泵在大型超超临界火电机组中采用较少，大多数选用了德国、日本、英国等进口设备，引进设备成本高、供货周期长、运行和维护困难等问题突出。近年来，给水泵国产化技术经过攻坚克难，日益成熟，其主要在可靠性、稳定性、成本效益、密封工艺、叶轮腐蚀、给水泵效率、振动指标、售后服务等方面成绩显著，已达到或领先于国外引进技术水平。
统计近年来给水泵项目投标文件中有关给水泵厂家的主要设计参数，国内和国外给水泵主要参数对比见表1。
在相同工况下国产给水泵的设计效率达到87.74%，已达到国际给水泵的设计效率水平。当然，国产给水泵在核心材料和长期稳定性等方面仍需加大研发，才能取得用户信任，更好地推动国产化应用市场。
2　系统介绍
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华能北方达拉特发电厂9号机组为1 000 MW间接空冷超超临界机组，配置1台全容量给水泵组，前置泵和主给水泵均为上海能源装备有限公司自主研制的全国产化设备，主给水泵型号为FK5A49M型，筒体式可抽芯结构型式，包括主轴、筒体、泵壳、叶轮和导叶等部件。汽泵组布置方式为前置泵+变速箱+小汽轮机+主给水泵，前置泵和主给水泵均由小汽轮机同轴驱动，布置在汽轮机房8.6 m层处，前置泵入口设计双滤网，主给水泵入口设计单滤网，防止杂质和颗粒物进入泵体内。
汽泵组配置的驱动汽轮机为东方汽轮机有限公司生产的G40-1.0型小汽轮机（小机），型式为单缸、单轴、单流、冲动式、汽源外切换、凝汽式；该小汽轮机共设计3路汽源，调试用汽（起动汽源）为辅助蒸汽，正常运行为四段抽汽，低负荷补充汽源为再热冷段抽汽。小机后缸排汽向下进入小机凝汽器，经与循环水表面换热后凝结水集聚在热井，再通过小机凝结水泵送至主机凝汽器循环利用。图1为汽泵组的汽、水系统流程。
小机汽源切换设计方式为：当主汽轮机（主机）负荷降至40%且主蒸汽阀前压力低于0.50 MPa时，再热冷段供汽切换阀（PID调节）打开，四抽逆止阀关闭，此时汽源切换为再热冷段抽汽；当主机负荷高于40%时且主蒸汽阀前压力高于0.50 MPa时，再热冷段抽汽管道供汽切换阀调节关闭，四抽电动门及逆止阀开启，此时汽源切换为四段抽汽供汽。
3　给水泵结构安全性评定计算
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随着汽轮机单机容量和蒸汽参数提高，现代大容量锅炉给水泵具有压力高、容量大、水温高、转速高等特点，同时要防止在机组降负荷和给水泵最小流量工况下运行时不会产生汽蚀。采用前置泵以及给水泵采用抗汽蚀的材料，可很好地解决汽蚀问题。给水泵在设计阶段应准确核准汽蚀性能、材料的耐磨性、水力平衡、应力集中问题、叶轮强度和刚度，合理选择轴端密封型式及辅助配套设备等，才能保证给水泵的安全、稳定运行[11-12]。
3.1　给水泵筒体的热应力-结构校核
机组配置的FK5A49M型给水泵设计参数：温度为200 ℃，LP为入口端压力4.0 MPa；HP为出口端压力42.0 MPa；MP为抽头压力16.0 MPa；约束状态为筒体的4个支脚全固定，右端通过16个大螺栓与大端盖相连接。对给水泵筒体进行网格划分，应力集中区域局部加密，并进行网格无关性验证，确保网格设计的合理性。设空气自然对流系数为5×10–6 W/(m2·K)，导热系数为50 W/(m·K)，线膨胀系数15.5×10–6。先求出热应力分布，并施加到筒体结构分析上；设置好筒体力荷载、约束，利用ANSYS Workbench中的热-结构耦合模块得到筒体的应力、应变云图，结果如图2、图3所示。通过图2、图3应力云图分析，可以看出热结构耦合的最大应力为288.6 MPa，出口管与筒体相联贯处出现应力集中，这与水压试验分析时一致，但设计工况下筒体的安全系数得到提高（大于1.42），远小于材料20MnMo的屈服极限。最大应变也发生在出口端筒体处，最大应变约为0.25 mm，筒体的强度和刚度均满足结构设计要求。
3.2　给水泵叶轮强度有限元计算
基于1 000 MW等级超超临界火电机组全容量锅炉给水泵的叶轮为6级阵列布置，具有相同的应力分布特性，因此，选取其中一级分析计算。对给水泵叶轮进行网格划分，叶轮与盖板连接处局部加密，并进行网格无关性验证，确保网格设计的合理性。结果如图4、图5所示，从图4、图5可见：末级叶轮最大应力发生在叶片与前、后盖板的根处，此处有集中应力，最大应力值为217.0 MPa，小于材料的屈服极限，其安全系数为3.0；最大应变为0.05 mm，均发生在叶片入口处（图5红色区域）。叶轮设计强度和刚度均满足运行条件，安全和可靠性达到设计要求。
通过优化设计，建立给水泵整体三维结构模型，利用ANSYS Workbench中的热-结构耦合模块对给水泵筒体进行应力分析，对其中一级叶轮结构分析和计算，结果表明，给水泵筒体的强度和刚度，叶轮强度和刚度均满足设计要求，从设计和技术上保证该给水泵能满足机组安全、可靠运行的要求。
4　汽动给水泵组试运及效率计算
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4.1　汽泵组再循环方式试运
2024年4月14日，汽泵组及小汽轮机润滑油循环化验合格，在完成汽泵组润滑油系统、调节保安系统及汽泵小汽轮机单体试运工作后，于4月29日进行了汽泵组再循环方式的试运。汽泵组冲转时分别在1 000、1 800 r/min进行了低速和中速暖机。中速暖机完成，升速至2 800 r/min，检查前置泵入口压力为0.23 MPa，汽泵入口压力为0.65 MPa，汽泵出口压力为11.82 MPa，全面检查汽泵组及小汽轮机各参数均正常。汽泵组再循环方式试运数据见表2。
4.2　给水泵组性能考核试验
2024年11月19日至12月6日，9号机组在不同运行工况下对汽泵组进行性能考核试验[3]，汽泵组主要试验结果见表3，其中修正值为在设计额定转速4 804 r/min条件下。由表3可知，给水泵在THA100%工况下给水泵入口流量2 794.220 t/h，有效功率为26 434.5 kW，轴功率为31 203.4 kW，考虑泵体散热，取系数为1.0，计算THA试验工况下给水泵效率为84.38%。
由试验数据绘制给水泵的性能曲线。依据GB/T3216—2016《回转动力泵水力性能验收试验1级、2级和3级》2级标准，流量容差系数tQ取0.08，扬程容差系数tH取0.05，效率容差系数tη取0.05。容差系数（tQ、tH和tη）适用于保证点THA工况下QG、HG和ηG（保证点THA工况下，QG为2 827.3 t/h，HG为3 592.7 m，ηG为87.39%）。
由效率容差系数计算给水泵的效率保证值为83.02%，图6为汽泵保证扬程、流量和效率的评价。通过规定的工作点（QG, HG）和Q-H坐标轴原点的直线与测得的流量-扬程曲线的交点作一条垂直线与流量-效率曲线交于B点，B点处的效率值为84.32%，汽泵的效率高于保证值。由图6可见，汽泵的流量-扬程曲线与容差十字线相交，证明汽泵的流量和扬程均达到设计性能。
5　存在问题及优化建议
收起
该国产化汽泵组在试运过程中，给水泵转速、流量、出口压力及效率、泵组轴承振动、轴承温度等指标均达到设计值，满足机组运行要求。但仍需优化和不断改进，才能提升运行的灵活性，达到长期稳定运行的要求。
5.1　给水泵密封水回水温度限制问题
该给水泵轴端采用反螺旋密封型式，密封水设计为凝结水直接冷却，当汽轮机排汽背压变化时凝结水温度伴随着变化。机组设计背压为9.2 kPa时凝结水温度为44.6 ℃；背压为26.0 kPa时凝结水温度为66.2 ℃。给水泵厂家规定密封水回水温度运行中不能高于72.0 ℃，才能保证密封件材料不被高温碳化，从而影响使用寿命。该机组试运期间是在夏季工况，汽轮机排汽背压较高，凝结水温度最高达到67.0 ℃，此时给水泵密封水回水温度高于72.0 ℃，产生报警。机组通过适当降负荷降背压的方法，改变凝结水温度以满足给水泵密封水要求。
针对密封水回水温度高使给水泵不能可靠运行的问题，现场进行了优化改进。实施方案为：在给水泵密封水供水管道增加1台水-水换热器和1台增压泵，冷却水采用辅机冷却水、就近取水为原则。增设水-水换热器可解决夏季汽轮机排汽背压升高导致凝结水温度高无法满足给水泵密封水冷却要求的问题；增设1台增压泵可解决凝结水压力高造成能耗增大的问题，有了增压泵满足给水泵密封水压力要求的同时，凝结水可在较宽压力范围内调节，使凝结水变频调峰和节能调节不受制约。
通过优化改进，给水泵密封水温度得到明显降低，在凝结水温度达到65 ℃时，经过水-水换热器后的密封水温度为50 ℃左右，密封水回水温度为64 ℃，完全能满足给水泵可靠运行的要求。
5.2　汽泵组连续盘车问题
给水泵是由小汽轮机直接驱动的，盘车转速一般设计为100 r/min左右。热态启动和停泵后如果不盘车，泵组启动时在低转速暖机时间长，还有可能因小汽轮机转子出现热弯曲，在通过临界区时因轴承振动大导致给水泵组启动失败，对于配置单汽泵的机组则无法快速恢复机组启动运行。因此，在保证给水水质合格、盘车配置合理的情况下，给水泵组应进行连续盘车。
通过修改盘车电机变频器启动加速时间由60 s改为30 s，盘车启动后能快速的到达100 r/min，解决了给水泵芯包在低转速时容易出现抱死的可能，汽泵组实现了连续盘车。
5.3　材料及长期稳定性问题
当前，国产给水泵在大型火电机组中占有率较低，未来发展方向仍面临着挑战。超超临界机组对给水泵的耐高温、高压性能要求极高，需持续优化材料和结构设计，提升高参数适配性。国产全容量给水泵在1 000 MW机组的成功应用，实现了从依赖进口到自主研制的跨越，并在实际应用中验证了可靠性。将来需不断的汲取技术经验，优化设计，节能降耗，确保给水泵能长期安全稳定运行。
6　结语
收起
该国产化全容量给水泵通过建立三维结构模型、应用ANSYS Workbench软件进行给水泵筒体热应力分析、给水泵叶轮有限元计算等优化设计，保证了设备的安全和可靠性。
给水泵在机组各负荷工况下运行时，给水流量及泵出口压力能满足运行要求，汽泵组各轴承温度及振动指标达优良范围。通过给水泵性能考核试验，计算给水泵效率为84.32%，高于效率保证值。
国产大型汽泵已实现从依赖进口到自主研发的跨越，电力设备国产化替代是未来电力行业发展的必经之路，是保证国家能源安全、降低成本、提高电力产业国际竞争力的重要举措。然而，国产设备替代全面开展还面临着巨大的挑战，需不断的提升技术研发、标准化制定，提升水泵叶轮材料的耐腐蚀性和加工工艺，提升设备售后服务质量。现场设备安装、调试、运行维护等各环节均应把好质量关，逐步替代进口设备，推动国内产业的发展和技术进步。
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2025年第54卷第12期
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doi: 10.19666/j.rlfd.202503062
  • 接收时间：2025-03-24
  • 首发时间：2026-01-13
  • 出版时间：2025-12-25
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  • 收稿日期：2025-03-24
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    1.达拉特发电厂，内蒙古　鄂尔多斯　014300
    2.北方联合电力有限责任公司，内蒙古　呼和浩特　010020
    3.西安热工研究院有限公司，陕西　西安　710054
    4.上海能源装备有限公司，上海　201317

通讯作者:

安宗武（1978），高级工程师，主要研究方向为大型火电机组启动调试技术及运行优化，。
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