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Article(id=1236369222499103722, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236369220812984708, articleNumber=null, orderNo=null, doi=10.19666/j.rlfd.202403047, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1710432000000, receivedDateStr=2024-03-15, revisedDate=null, revisedDateStr=null, acceptedDate=null, acceptedDateStr=null, onlineDate=1772702993272, onlineDateStr=2026-03-05, pubDate=1732464000000, pubDateStr=2024-11-25, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1772702993272, onlineIssueDateStr=2026-03-05, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1772702993272, creator=13701087609, updateTime=1772702993272, updator=13701087609, issue=Issue{id=1236369220812984708, tenantId=1146029695717560320, journalId=1210938733613449225, year='2024', volume='53', issue='11', pageStart='1', pageEnd='168', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1772702992871, creator=13701087609, updateTime=1772703093306, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1236369642126627337, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236369220812984708, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1236369642126627338, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1236369220812984708, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=147, endPage=154, ext={EN=ArticleExt(id=1236369222746567661, articleId=1236369222499103722, tenantId=1146029695717560320, journalId=1210938733613449225, language=EN, title=Performance analysis of integrated steam injectors in cogeneration systems, columnId=1211002409397129992, journalTitle=Thermal Power Generation, columnName=Power generation technology forum, runingTitle=null, highlight=null, articleAbstract=

Based on a typical 600 MW coal-fired cogeneration unit, novel systems with integrated steam jet and external steam cooler are proposed. In novel system I, the waste heat from exhaust steam is recovered through a steam jet, in which reheat steam is chosen as the working fluid. In novel system II, an external steam cooler is used to reduce the superheat of the mixed steam and the heat load of the boiler. Based on EBSILON professional modeling, the system is analyzed considering the peak shaving performance and thermodynamic performance under the maximum heating condition (extracted steam for heating: 800 t/h) and variable conditions. Moreover, the effects of mixed steam pressure and heat exchanger end difference on the system performance are also investigated. The results show that, under the maximum heating condition, compared with those of the reference system, the heating capacities of the novel system I and II increase by 21.59 and 14.47 percentage points, and the power generation efficiencies are increase by 2.48 and 2.78 percentage points, respectively. With the heating load of 300 MW, the power load regulation ratios of the novel system I and II improve by 6.00 and 3.91 percentage points compared with the reference system, and the lower limits of generation reduce by 84.75 MW and 74.32 MW. The gross efficiency of the novel system I and II improve by 3.02 and 2.65 percentage points, respectively, when the mixing steam pressure is increased from 50 kPa to 85 kPa. With the upper temperature difference increasing from 1 ℃ to 9 ℃, the gross efficiencies of the novel system I and II decrease by 1.67 and 1.51 percentage points, respectively. The result can provide technical references for expanding heating capacity and deep peaking of coal-fired cogeneration systems.

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基于某典型超临界600 MW燃煤热电联产机组提出集成蒸汽喷射器和外置式蒸汽冷却器的新型系统。其中，新型系统I通过蒸汽喷射器利用再热蒸汽回收乏汽余热；新型系统II进一步集成外置式蒸汽冷却器降低混合蒸汽过热度并减少给水在锅炉的吸热量。基于EBSILON professional建模，对系统在最大供热工况（供热抽汽量800 t/h）和变工况进行调峰性能和热力学性能分析，并探讨混合蒸汽压力和换热器端差对系统性能的影响。结果表明：在最大供热工况下，新型系统I和新型系统II的供热量较参考系统分别提高21.59百分点和14.47百分点，发电效率提高2.48百分点和2.78百分点；在供热量为300 MW时，新型系统I和新型系统II的发电负荷调节率较参考系统提高了6.00百分点和3.91百分点，发电量下限降幅达84.75 MW和74.32 MW；混合蒸汽压力由50 kPa提高到85 kPa，新型系统I和新型系统II的总效率分别提高3.02百分点和2.65百分点；上端差由1 ℃提高到9 ℃，新型系统I和新型系统II的总效率分别降低1.67百分点和1.51百分点。研究结果可为燃煤热电联产机组扩大供热和深度调峰提供技术选项。

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赵世飞（1991），男，博士，讲师，主要研究方向为燃煤热电联产机组高效灵活运行技术，。
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夏大伟（1980），男，高级工程师，主要研究方向为网源协调技术，。

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夏大伟（1980），男，高级工程师，主要研究方向为网源协调技术，。

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夏大伟（1980），男，高级工程师，主要研究方向为网源协调技术，。

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orderNo=3, keyword=余热利用), Keyword(id=1236369227901366476, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, orderNo=4, keyword=深度调峰), Keyword(id=1236369228010418387, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, orderNo=5, keyword=热力学性能)], refs=[Reference(id=1236369231344890214, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, doi=null, pmid=null, pmcid=null, year=null, volume=null, issue=null, pageStart=null, pageEnd=null, url=null, language=null, rfNumber=［1］, rfOrder=0, authorNames=国家发展改革委, 国家能源局, journalName=null, refType=null, unstructuredReference=国家发展改革委, 国家能源局. 关于完善能源绿色低碳转型体制机制和政策措施的意见[EB/OL]. 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Main thermodynamic parameters under THA and maximum heating conditions

, figureFileSmall=null, figureFileBig=null, tableContent=
项目THA工况最大供热工况
主蒸汽流量/(t·h–1)1 696.741 696.74
主蒸汽压力/MPa24.2024.20
主蒸汽温度/℃566.00566.00
再热蒸汽流量/(t·h–1)1 396.021 359.70
再热蒸汽压力/MPa3.983.70
再热蒸汽温度/℃566.00566.00
供热抽汽流量/(t·h–1)800.00
供热抽汽压力/MPa0.40
供热抽汽温度/℃254.15
供热抽汽疏水温度/℃104.00
乏汽流量/(t·h–1)979.72284.79
乏汽损失/MW649.46251.67
供热量/MW0541.06
发电量/MW600.00461.97
蒸汽吸热量/MW1 252.161 259.14
背压/kPa4.904.90
), ArticleFig(id=1236369230141124922, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, label=表1, caption=

THA和最大供热工况下的主要热力学参数

, figureFileSmall=null, figureFileBig=null, tableContent=
项目THA工况最大供热工况
主蒸汽流量/(t·h–1)1 696.741 696.74
主蒸汽压力/MPa24.2024.20
主蒸汽温度/℃566.00566.00
再热蒸汽流量/(t·h–1)1 396.021 359.70
再热蒸汽压力/MPa3.983.70
再热蒸汽温度/℃566.00566.00
供热抽汽流量/(t·h–1)800.00
供热抽汽压力/MPa0.40
供热抽汽温度/℃254.15
供热抽汽疏水温度/℃104.00
乏汽流量/(t·h–1)979.72284.79
乏汽损失/MW649.46251.67
供热量/MW0541.06
发电量/MW600.00461.97
蒸汽吸热量/MW1 252.161 259.14
背压/kPa4.904.90
), ArticleFig(id=1236369230266954043, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=EN, label=Tab.2, caption=

Thermodynamic performance comparison of the heating processes

, figureFileSmall=null, figureFileBig=null, tableContent=
项目参考系统新型系统I新型系统II
λhot0.350.330.31
λcold0.240.240.24
ηex,Ⅰ/%70.0483.34
ηex,Ⅱ/%73.0072.91
ηex,gross/%67.2471.9176.37
), ArticleFig(id=1236369230376005951, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, label=表2, caption=

换热过程热力学性能对比

, figureFileSmall=null, figureFileBig=null, tableContent=
项目参考系统新型系统I新型系统II
λhot0.350.330.31
λcold0.240.240.24
ηex,Ⅰ/%70.0483.34
ηex,Ⅱ/%73.0072.91
ηex,gross/%67.2471.9176.37
), ArticleFig(id=1236369230472474946, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=EN, label=Tab.3, caption=

Thermodynamic performance comparison under maximum heating conditions

, figureFileSmall=null, figureFileBig=null, tableContent=
项目参考系统新型系统I新型系统II
蒸汽吸热量/MW1 259.141 288.781 240.16
第I级加热器换热量/MW274.46258.38
第II级加热器换热量/MW383.43360.98
供热量/MW541.06657.89619.36
发电量/MW461.97422.70417.96
给水温度/℃279.23273.16295.17
总效率/%74.0877.9877.79
发电效率/%59.8362.3162.61
发电标准煤耗率/(g·(kW·h)–1)205.25197.08196.12
), ArticleFig(id=1236369230598304070, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, label=表3, caption=

最大供热工况下热力学性能对比

, figureFileSmall=null, figureFileBig=null, tableContent=
项目参考系统新型系统I新型系统II
蒸汽吸热量/MW1 259.141 288.781 240.16
第I级加热器换热量/MW274.46258.38
第II级加热器换热量/MW383.43360.98
供热量/MW541.06657.89619.36
发电量/MW461.97422.70417.96
给水温度/℃279.23273.16295.17
总效率/%74.0877.9877.79
发电效率/%59.8362.3162.61
发电标准煤耗率/(g·(kW·h)–1)205.25197.08196.12
), ArticleFig(id=1236369230690578761, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=EN, label=Tab.4, caption=

Performance comparison of steam jets

, figureFileSmall=null, figureFileBig=null, tableContent=
项目新型系统I新型系统II
乏气回收比例/%26.3529.58
引射流体流量/(t·h–1)75.0484.24
工作流体压力/MPa3.032.94
工作流体温度/℃566.00282.77
工作流体流量/(t·h–1)256.01290.70
混合蒸汽压力/kPa6060
混合蒸汽流量/(t·h–1)331.05374.94
引射系数0.293 10.289 8
混合蒸汽供热占比/%41.7241.72
), ArticleFig(id=1236369230791242062, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1236369222499103722, language=CN, label=表4, caption=

蒸汽喷射器性能对比

, figureFileSmall=null, figureFileBig=null, tableContent=
项目新型系统I新型系统II
乏气回收比例/%26.3529.58
引射流体流量/(t·h–1)75.0484.24
工作流体压力/MPa3.032.94
工作流体温度/℃566.00282.77
工作流体流量/(t·h–1)256.01290.70
混合蒸汽压力/kPa6060
混合蒸汽流量/(t·h–1)331.05374.94
引射系数0.293 10.289 8
混合蒸汽供热占比/%41.7241.72
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热电联产系统集成蒸汽喷射器性能分析
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夏大伟 1 , 张少锋 1 , 李玲 1 , 张步庭 1 , 赵世飞 2
热力发电 | 发电技术论坛 2024,53(11): 147-154
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热力发电 | 发电技术论坛 2024, 53(11): 147-154
热电联产系统集成蒸汽喷射器性能分析
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夏大伟1 , 张少锋1, 李玲1, 张步庭1, 赵世飞2
作者信息
  • 1.国网河南省电力公司电力科学研究院，河南　郑州　450052
  • 2.华北水利水电大学能源与动力工程学院，河南　郑州　450045

    • 夏大伟（1980），男，高级工程师，主要研究方向为网源协调技术，。

通讯作者:

赵世飞（1991），男，博士，讲师，主要研究方向为燃煤热电联产机组高效灵活运行技术，。
Performance analysis of integrated steam injectors in cogeneration systems
Dawei XIA1 , Shaofeng ZHANG1, Ling LI1, Buting ZHANG1, Shifei ZHAO2
Affiliations
  • 1.State Grid Henan Electric Power Research Institute, Zhengzhou 450052, China
  • 2.College of Energy and Power Engineering, North China University of Water Resources and Electric Power, Zhengzhou 450045, China
出版时间: 2024-11-25 doi: 10.19666/j.rlfd.202403047
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摘要
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基于某典型超临界600 MW燃煤热电联产机组提出集成蒸汽喷射器和外置式蒸汽冷却器的新型系统。其中，新型系统I通过蒸汽喷射器利用再热蒸汽回收乏汽余热；新型系统II进一步集成外置式蒸汽冷却器降低混合蒸汽过热度并减少给水在锅炉的吸热量。基于EBSILON professional建模，对系统在最大供热工况（供热抽汽量800 t/h）和变工况进行调峰性能和热力学性能分析，并探讨混合蒸汽压力和换热器端差对系统性能的影响。结果表明：在最大供热工况下，新型系统I和新型系统II的供热量较参考系统分别提高21.59百分点和14.47百分点，发电效率提高2.48百分点和2.78百分点；在供热量为300 MW时，新型系统I和新型系统II的发电负荷调节率较参考系统提高了6.00百分点和3.91百分点，发电量下限降幅达84.75 MW和74.32 MW；混合蒸汽压力由50 kPa提高到85 kPa，新型系统I和新型系统II的总效率分别提高3.02百分点和2.65百分点；上端差由1 ℃提高到9 ℃，新型系统I和新型系统II的总效率分别降低1.67百分点和1.51百分点。研究结果可为燃煤热电联产机组扩大供热和深度调峰提供技术选项。

燃煤热电联产  /  蒸汽喷射器  /  余热利用  /  深度调峰  /  热力学性能

Based on a typical 600 MW coal-fired cogeneration unit, novel systems with integrated steam jet and external steam cooler are proposed. In novel system I, the waste heat from exhaust steam is recovered through a steam jet, in which reheat steam is chosen as the working fluid. In novel system II, an external steam cooler is used to reduce the superheat of the mixed steam and the heat load of the boiler. Based on EBSILON professional modeling, the system is analyzed considering the peak shaving performance and thermodynamic performance under the maximum heating condition (extracted steam for heating: 800 t/h) and variable conditions. Moreover, the effects of mixed steam pressure and heat exchanger end difference on the system performance are also investigated. The results show that, under the maximum heating condition, compared with those of the reference system, the heating capacities of the novel system I and II increase by 21.59 and 14.47 percentage points, and the power generation efficiencies are increase by 2.48 and 2.78 percentage points, respectively. With the heating load of 300 MW, the power load regulation ratios of the novel system I and II improve by 6.00 and 3.91 percentage points compared with the reference system, and the lower limits of generation reduce by 84.75 MW and 74.32 MW. The gross efficiency of the novel system I and II improve by 3.02 and 2.65 percentage points, respectively, when the mixing steam pressure is increased from 50 kPa to 85 kPa. With the upper temperature difference increasing from 1 ℃ to 9 ℃, the gross efficiencies of the novel system I and II decrease by 1.67 and 1.51 percentage points, respectively. The result can provide technical references for expanding heating capacity and deep peaking of coal-fired cogeneration systems.

coal-fired cogeneration  /  steam jet  /  waste heat recovery  /  deep peaking  /  thermodynamic performance
夏大伟, 张少锋, 李玲, 张步庭, 赵世飞. 热电联产系统集成蒸汽喷射器性能分析. 热力发电, 2024 , 53 (11) : 147 -154 . DOI: 10.19666/j.rlfd.202403047
Dawei XIA, Shaofeng ZHANG, Ling LI, Buting ZHANG, Shifei ZHAO. Performance analysis of integrated steam injectors in cogeneration systems[J]. Thermal Power Generation, 2024 , 53 (11) : 147 -154 . DOI: 10.19666/j.rlfd.202403047
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随着我国能源低碳转型的推进，随机性强的风电、光电等可再生能源大规模并网，电力系统面临严峻的灵活性短缺问题[1]为此，作为我国北方供热期供能主力的燃煤热电联产机组亟需提高发电负荷调节能力，实现深度调峰和热电解耦[2]。同时，热电联产机组也需要提高供热能力和发电效率，实现“三改联动”。然而，传统抽汽凝汽式热电联产热电负荷耦合性强。供热量的提高会显著降低其深度调峰能力[2]。因此，如何在提高灵活性的同时，具备较高的供热能力和发电效率成为热电联产机组低碳转型的关键。
近年来，诸多学者针对提高热电联产的灵活性和供热能力等问题进行相关研究。钱白云等[3]分析了4种不同热电解耦方案在在不同电负荷场景下的灵活性提升效果，指出低压缸零出力可使最大供热量提高56.31%的同时，电负荷率降低至44.29%。李明皓等[4]针对多机组提出了耦合电锅炉并提供全厂优化方案，实现深度调峰。杨凯旋等[5]提出抽汽-高背压-热泵耦合热电联产系统，通过多参数优化实现了灵活供能。曹丽华等[6-7]获得了热电联产机组储热罐容量最优值的确定方法和运行策略。吕泉等[8-9]对传统热电联产机组配置储热进行分析与建模，获得了其运行策略。陆树银等[10]指出集成吸收式热泵的热电联产机组在额定供热负荷下的最小功率负荷系数降低6.6%，机组调峰能力提高。杨绪青等[11]提出了一种压缩空气储能与吸收式热泵循环集成的热电联产系统，改善了系统的调节特性。
蒸汽喷射器作为一种回收电厂乏汽余热的技术手段，获得了诸多学者关注。Tan等人[12]对比分析了4种低温余热回收方式，指出在余热温度为100 ℃时，蒸汽喷射器比吸收式热泵㶲效率高2.37%。张钧泰等[13]提出了一种集成蒸汽喷射器的热电解耦系统，使最低电负荷率降低16%。刘荣堂等[14]提出集成蒸汽喷射器的热电协同系统，使机组的电负荷调节范围由45.99%～81.75%扩展为15.78%～100%。Zhang等人[15]指出将蒸汽喷射器与高背压机组集成可分别提高发电效率和供热量2.32%和4.21%。孙博昭等[16-17]对可调式蒸汽喷射器进行三维数值模拟和建模计算，指出集成喷射器的热电联产机组每年可减少发电煤耗0.83万t，CO2和SO2分别等量减排2.18万t和11.5 t。Liu等人[18]对比分析了多种蒸汽喷射器与热电联产机组的集成方案，最多可降低机组发电下限94.8 MW。
可见，以蒸汽喷射器作为余热回收的手段，集成方式较为灵活。以再热蒸汽作为工作流体会使混合蒸汽过热度较高。从热力学角度，这会影响系统热力学性能。然而，从灵活性的角度，该方案则能提高机组深度调峰能力，且可通过外置式蒸汽冷却器来改善系统性能。目前并未有相关研究。
鉴于此，本文基于蒸汽喷射器和外置式蒸汽冷却器与传统燃煤热电联产机组的集成，提出了2种新型热电联产系统，从热力学性能、调峰性能以及关键参数影响等角度进行分析，旨在提高传统热电联产系统的供热能力和深度调峰能力。
1　系统介绍
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1.1　传统燃煤热电联产系统
本文选取某典型超临界600 MW燃煤热电联产机组为参考系统，机组型号为N600-24.2/566/566，系统流程如图1所示。汽轮机型式为中间再热、单轴、凝汽式。回热系统为“三高四低一除氧”的布置方式。在供热期，部分中压缸的排汽被抽取作为热网水的热源，在热网加热器放热后，疏水进入除氧器。
本机组供热抽汽压力不低于0.4 MPa，热网设计供回水温度为110/60 ℃。考虑到低压缸叶片运行的安全性，低压缸乏汽流量不能低于最小冷却流量（通常为设计流量的30%）。此时对应的供热工况为最大供热工况[19]。表1给出了参考系统在汽机热耗验收（turbine heat acceptance，THA）工况和最大供热工况下的主要热力学参数。最大供热工况下低压缸乏汽量减少为THA工况下的29.07%。这部分乏汽损失无法进一步减少。热电联产机组的热电耦合特性也使得其在供热时负荷调节性能变差。
1.2　集成蒸汽喷射器的热电联产系统
本文提出集成蒸汽喷射器的热电联产系统（新型系统I）如图2所示。该系统以再热蒸汽作为工作流体，低压缸的乏汽为被引射流体，混合蒸汽为热网回水第I级加热器的热源。热网回水经第I级热网加热器加热后，由第II级热网加热器加热到供水温度。喷射器出口混合蒸汽压力的设计值为60 kPa。第I级热网加热器的上端差为5 ℃。
新型系统I可通过回收部分乏气余热降低乏汽损失，并提高机组供热量。同时，利用高品位的再热蒸汽作为工作蒸汽有利于降低系统在给定供热负荷下的发电量，提高系统的深度调峰性能。进一步考虑到再热蒸汽的温度较高，会使混合气体的过热度较高，从而不利于第I级热网加热器的高效换热，本文提出集成蒸汽喷射器和外置式蒸汽冷却器的热电联产系统（新型系统II）示意如图3所示。新型系统II利用外置式蒸汽冷却器来回收再热蒸汽的热量，降低第I级热网加热器内的换热温差，同时提高入炉给水的平均吸热温度。
2　系统建模和评价指标
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2.1　系统建模介绍
本文选用EBSILON Professional作为建模平台[20]，针对新型系统II搭建的模型如图4所示。主要假设有：1）锅炉的变工况运行模式为“定压-滑压-定压”，流量与压力的关系根据汽轮机热力特性书设定；2）在非设计工况运行时，汽轮机排汽压力、回热加热器的上下端差、泵的效率、管道压损等均为定值；3）锅炉和发电机效率分别设定为93%和99%；4）忽略汽轮机的机械损失和散热损失；5）变工况时，汽轮机压力和流量的关系遵循弗留格尔公式；6）蒸汽冷却器温升过高会使省煤器存在给水汽化风险，因此需要相应的温度控制。本文研究暂不考虑该温度控制。在上述假设下，软件模拟的结果与热力特性书中各工况的相对误差范围为–0.39%~0.24%。证明建模有较高的精度，可用于下文的计算分析。
2.2　评价指标
本文分别对蒸汽喷射器的性能、热网水加热过程的热力学性能、调峰性能以及系统整体热力学性能进行分析讨论。
蒸汽喷射器的引射系数μ可表示为[21]：
μ=mEmR
式中：mE和mR分别为被引射流体（乏汽）和工作流体（再热蒸汽）的质量流量，t/h。
换热过程可采用能质系数λ（energy quality coefficient）和换热过程㶲效率ηex来进行评价。其中，能质系数λ为换热过程中介质㶲变化量ΔE与能量变化量ΔQ的比值，表示为：
λ=ΔEΔQ
对于蒸汽，能质系数λs可近似表示为[22]：
λs=1−T0Ts
式中：T0和Ts分别为环境温度和蒸汽的饱和温度，K。
对于热网水，能质系数λw可表示为[23]：
λw=1−T0Tout−TinlnToutTin
式中：Tout和Tin分别为热网水的出口和进口温度，K。
换热过程㶲效率ηex可被表示为：
ηex=λwλs×100%
热电联产机组的调峰能力可用发电负荷调节率ω来表示：
ω=Pmax−PminPTHA×100%
式中：Pmax、Pmin和PTHA分别为机组在供热工况时的最大发电量、最小发电量和THA工况下的发电量，MW。
热电联产系统的总效率ηg可由下式获得：
ηg=Pg+QgQb×100%
式中：Pg为机组的发电量，MW；Qg和Qb分别为机组的供热量和锅炉消耗的燃煤热量，MW。
热电联产系统的发电效率ηe可表示为[24]：
ηe=PgQb−Qg/ηb×100%
式中：ηb为锅炉效率，取93%。
则相应的发电标准煤耗率b可表示为：
b=122.8ηe
3　结果与讨论
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3.1　最大供热工况热力学性能
图5给出了最大供热工况下3个系统热网水加热过程的温度-换热量（T-Q）关系。新型系统I和新型系统II在第I级加热器中的换热平均温差低于参考系统。但在第I级加热器中，新型系统I的蒸汽过热度为345.52 ℃，远高于新型系统II（95.41 ℃）。
表2给出了换热过程热力学性能对比。新型系统II的热端总能质系数λhot最低，为0.31，换热过程总㶲效率ηex,gross为76.37%，较参考系统和新型系统I分别高9.13百分点和4.46百分点。
表3给出了3个系统整体热力学性能对比。新型系统I和新型系统II的供热量较参考系统分别提升21.59%和14.47%，发电量则较参考系统分别降低39.27 MW和44.01 MW。由于集成外置式蒸汽冷却器，新型系统II的锅炉吸热量比参考系统和新型系统I分别减少14.98 MW和44.62 MW。新型系统I和新型系统II的总效率较原系统分别高3.90百分点和3.71百分点，发电效率分别高2.48百分点和2.78百分点。
表4给出了最大供热工况下2个新型系统的蒸汽喷射器性能对比。因为新型系统II中增加了外置式蒸汽冷却器，导致其工作蒸汽温度比新型系统I低，使得其引射系数降低0.003 3。由于第I级热网水加热器上端差一样，2个系统混合蒸汽在供热过程占比均为41.72%。在引射系数不变的情况下，新型系统II的工作流体和引射流体的流量均会增加。新型系统II的乏汽回收比例为29.58%，较新型系统I提高3.23百分点。
3.2　变工况热力学性能
图6给出了3个系统的热电负荷特性区间对比。由图6可知，当供热量为300 MW时，新型系统I和新型系统II的发电负荷调节率比参考系统分别提高6.00百分点和3.91百分点。当供热量由100 MW提高到500 MW，新型系统I的发电量下限较参考系统降幅由12.60 MW提高到了84.75 MW，新型系统II的发电量下限较参考系统降幅由9.79 MW提高到了74.32 MW。图7给出了供热量为300 MW时，3个系统热力学性能对比。
由图7可知，在3个系统都能满足热电需求时，参考系统的总效率最高，新型系统I的总效率最低。运行时优先考虑参考系统的运行方式，当其无法满足需要的较低发电量时，优先选择新型系统II，当新型系统II无法降至所需发电量时，再选择新型系统I。
图8给出了在最大供热工况下，负荷率（主蒸汽蒸发量）变化对3个系统的热力学性能影响。由图8可知，随着负荷率的下降，3个系统的最大供热能力和对应的发电量都随之下降。此外，当负荷率由100%降到30%时，参考系统、新型系统I和新型系统II的发电标准煤耗率分别提高了95.05、97.69、97.80 g/(kW·h)。
3.3　关键参数对系统热力学性能影响
图9给出了在最大供热工况下，喷射器混合蒸汽压力对热力学性能影响。由图9可知：当混合蒸汽压力由50 kPa提高到85 kPa时，新型系统的第I级加热器供热占比提高27.59%，新型系统I和新型系统II的引射系数分别降低0.022 0和0.023 8；新型系统I和新型系统II供热量增幅分别为95.79 MW和54.61 MW，发电量降幅分别为30.15 MW和31.88 MW。总效率分别提高3.02百分点和2.65百分点，发电效率分别提高2.36百分点和2.33百分点。
图10给出了在最大供热工况下，第I级加热器上端差对3个系统的热力学性能影响。由图10可知，随着第I级加热器上端差的提高，新型系统的最大供热能力下降，对应的发电量提高。此时，新型系统I和新型系统II的总效率和发电效率均下降。其中总效率分别降低1.67百分点和1.51百分点，发电效率分别降低1.24百分点和1.32百分点。
4　结论
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为提高热电联产机组供热能力和负荷调节能力，以某超临界600 MW燃煤热电联产机组为例，提出集成蒸汽喷射器和外置式蒸汽冷却器的新型系统，对机组在最大供热工况和变工况性能以及关键参数的影响进行分析，得到如下结论。
1）新型系统I和新型系统II较参考系统最大供热量提高，对应发电量下降，总效率和发电效率提高。在最大供热工况下，新型系统I和新型系统II供热量较参考系统分别提高21.59百分点和14.47百分点，发电量分别降低39.27 MW和44.01 MW。总效率较原系统分别高3.90百分点和3.71百分点，发电效率分别高2.48百分点和2.78百分点。
2）新型系统I和新型系统II较参考系统发电负荷调节能力提高，尤其是发电量下限降幅较大。当供热量由100 MW提高到500 MW时，新型系统I的发电量下限较参考系统降幅由12.60 MW提高到84.75 MW，新型系统II的发电量下限较参考系统降幅由9.79 MW提高到74.32 MW。
3）蒸汽喷射器混合蒸汽压力的提高会使新型系统乏汽回收量提高，第I级加热器上端差会使新型系统乏汽回收量降低。混合蒸汽压力由50 kPa提高到85 kPa，新型系统I和新型系统II的总效率分别提高3.02百分点和2.65百分点；上端差由1 ℃提高到9 ℃，新型系统I和II的总效率分别降低1.67百分点和1.51百分点。
基金
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  • 国家自然科学基金青年科学基金项目(52206012)
  • 国网河南省电力公司电力科学研究院(52170223000M)
文献
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2024年第53卷第11期
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doi: 10.19666/j.rlfd.202403047
  • 接收时间：2024-03-15
  • 首发时间：2026-03-05
  • 出版时间：2024-11-25
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  • 收稿日期：2024-03-15
基金
National Natural Science Foundation of China(52206012)
国家自然科学基金青年科学基金项目(52206012)
State Grid Henan Electric Power Research Institute(52170223000M)
国网河南省电力公司电力科学研究院(52170223000M)
作者信息
    1.国网河南省电力公司电力科学研究院，河南　郑州　450052
    2.华北水利水电大学能源与动力工程学院，河南　郑州　450045

通讯作者:

赵世飞（1991），男，博士，讲师，主要研究方向为燃煤热电联产机组高效灵活运行技术，。
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2种不同金属材料的力学参数
科
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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