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Article(id=1233732516671189319, tenantId=1146029695717560320, journalId=1149651085930835976, issueId=1233732515798774086, articleNumber=null, orderNo=null, doi=10.12284/hyxb2021085, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=research-article, receivedDate=1587052800000, receivedDateStr=2020-04-17, revisedDate=1591200000000, revisedDateStr=2020-06-04, acceptedDate=null, acceptedDateStr=null, onlineDate=1772074353615, onlineDateStr=2026-02-26, pubDate=1621872000000, pubDateStr=2021-05-25, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1772074353615, onlineIssueDateStr=2026-02-26, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1772074353615, creator=13701087609, updateTime=1772074353615, updator=13701087609, issue=Issue{id=1233732515798774086, tenantId=1146029695717560320, journalId=1149651085930835976, year='2021', volume='43', issue='5', pageStart='1', pageEnd='144', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1772074353408, creator=13701087609, updateTime=1772074353408, updator=13701087609, preIssue=null, nextIssue=null, ext=null, issueFiles=null}, startPage=120, endPage=126, ext={EN=ArticleExt(id=1233732516918653257, articleId=1233732516671189319, tenantId=1146029695717560320, journalId=1149651085930835976, language=EN, title=Thermodynamic analysis of a new ocean thermal energy conversion regenerative cycle, columnId=1194652705852465724, journalTitle=Haiyang Xuebao, columnName=Article, runingTitle=null, highlight=null, articleAbstract=

In view of the problems of small available temperature difference and low utilization efficiency of ocean thermal energy conversion (OTEC). A new thermodynamic cycle of OTEC using non-azeotropic mixed working fluid is proposed. Based on the laws of thermodynamics, the thermodynamic analysis of the proposed thermodynamic cycle is carried out. Evaporation pressure, mass fraction of working fluid, evaporation temperature and condensation temperature are selected as influencing variables to study the proposed thermodynamic cycle. The results show that when the working fluid mass fraction is selected as a variable, with the evaporation pressure increases the cycle thermal efficiency and the net output of system increase first and then decrease. The system thermal efficiency achieves a maximum value of 5.28% when the working fluid mass fraction is 0.91. The maximum value of 3.83 kW is obtained when the mass fraction of the working fluid is 0.96. When the evaporation pressure is selected as the variable, the cycle thermal efficiency and the net output of the system increase first and then decrease with the mass fraction of the working medium increases. The cycle thermal efficiency achieves a maximum value of 5.26% when the evaporating pressure is 0.595 MPa, and the net output work obtains a maximum value of 3.57 kW when the evaporating pressure is 0.58 MPa. Compared with Uehara cycle and Yoon cycle under the same operating conditions, the proposed cycle system has the highest thermal efficiency. The analysis results of the proposed thermal cycle system can provide a theoretical basis and reference for improving the utilization efficiency of OTEC.

, correspAuthors=Weimin Liu, authorNote=null, correspAuthorsNote=null, copyrightStatement=Copyright © 2021 Pratacultural Science. All rights reserved., 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, authorCompany=null, fund=null, authors=null, authorsList=Jingping Peng, Yunzheng Ge, Fengyun Chen, Lei Liu, Haoyu Wu, Weimin Liu), CN=ArticleExt(id=1233732519787557230, articleId=1233732516671189319, tenantId=1146029695717560320, journalId=1149651085930835976, language=CN, title=新型海洋温差能回热循环热力学分析, columnId=1149698756456657529, journalTitle=海洋学报, columnName=论文, runingTitle=null, highlight=null, articleAbstract=

针对海洋温差能可利用温差小，利用效率低的问题，本文提出了一种采用非共沸混合工质的新型海洋温差能回热循环，并基于热力学定律对提出的热力循环进行热力学分析。选取蒸发压力、工质的质量分数作为变量，对提出的热力循环进行热力学分析研究。研究结果表明：以工质质量分数为变量时，循环热效率和系统净输出随蒸发压力的增加先增大后减小，系统热效率在工质质量分数为0.91时取得最大值5.28%，净输出功在浓度为0.96时取得最大值3.83 kW。以蒸发压力为变量时，循环热效率和系统净输出随工质质量分数的增大先增大后减小，系统热效率在蒸发压力为0.595 MPa时取得最大值5.26%，净输出功在压力为0.58 MPa时取得最大值3.57 kW。在相同运行控制参数下与Uehara循环、Yoon循环进行对比，提出的循环系统热效率最佳。提出的热力循环系统分析结果可对提高海洋温差能利用效率提供理论依据和参考。

, correspAuthors=刘伟民, authorNote=null, correspAuthorsNote=
刘伟民，研究员，博士，主要从事海洋热能转换技术及综合利用方面研究。E-mail：
, copyrightStatement=版权所有©《海洋学报》编辑部 2021
彭景平，葛云征，陈凤云，等. 新型海洋温差能回热循环热力学分析[J]. 海洋学报，2021，43(5)：120–126Peng Jingping，Ge Yunzheng，Chen Fengyun, et al. Thermodynamic analysis of a new ocean thermal energy conversion regenerative cycle[J]. Haiyang Xuebao，2021, 43(5)：120–126
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彭景平（1987-），男，山东省临沂市人，主要从事海洋温差能开发利用方面研究。E-mail：

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彭景平（1987-），男，山东省临沂市人，主要从事海洋温差能开发利用方面研究。E-mail：

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Initial conditions for theoretical analysis of circulatory system

, figureFileSmall=null, figureFileBig=null, tableContent=
工况温海水温度T/℃冷海水温度T/℃工质质量分数w蒸发压力 p/MPa
1 26 5 0.90 0.55
2 26 5 0.90 0.56
3 26 5 0.90 0.57
4 26 5 0.90 0.58
5 26 5 0.90 0.59
6 26 5 0.90 0.595
7 26 5 0.90 0.60
8 26 5 0.90 0.604
9 26 5 0.89 0.60
10 26 5 0.90 0.60
11 26 5 0.905 0.60
12 26 5 0.91 0.60
13 26 5 0.915 0.60
14 26 5 0.92 0.60
15 26 5 0.93 0.60
16 26 5 0.94 0.60
17 26 5 0.95 0.60
18 26 5 0.96 0.60
19 26 5 0.97 0.60
20 26 5 0.98 0.60
), ArticleFig(id=1233807266965672367, tenantId=1146029695717560320, journalId=1149651085930835976, articleId=1233732516671189319, language=CN, label=表1, caption=

循环系统的理论分析初始条件组合

, figureFileSmall=null, figureFileBig=null, tableContent=
工况温海水温度T/℃冷海水温度T/℃工质质量分数w蒸发压力 p/MPa
1 26 5 0.90 0.55
2 26 5 0.90 0.56
3 26 5 0.90 0.57
4 26 5 0.90 0.58
5 26 5 0.90 0.59
6 26 5 0.90 0.595
7 26 5 0.90 0.60
8 26 5 0.90 0.604
9 26 5 0.89 0.60
10 26 5 0.90 0.60
11 26 5 0.905 0.60
12 26 5 0.91 0.60
13 26 5 0.915 0.60
14 26 5 0.92 0.60
15 26 5 0.93 0.60
16 26 5 0.94 0.60
17 26 5 0.95 0.60
18 26 5 0.96 0.60
19 26 5 0.97 0.60
20 26 5 0.98 0.60
), ArticleFig(id=1233807267049558448, tenantId=1146029695717560320, journalId=1149651085930835976, articleId=1233732516671189319, language=EN, label=Table 2, caption=

Parameters of the proposed cycle under the conditions described in reference [12]

, figureFileSmall=null, figureFileBig=null, tableContent=
节点温度
T/K		压力
p/MPa		氨质量
分数w		焓值h/kJ·kg−1熵值S/ kJ·kg−1K−1质量流量比/
kg·kg−1
1 299.20 0.85 0.90 856.69 3.40 1.00
2 299.20 0.85 0.99 1 641.8 5.91 0.43
3 286.33 0.67 0.99 1 610.3 5.91 0.01
4 276.48 0.48 0.99 1 570.2 5.91 0.99
5 281.46 0.48 0.90 767.31 3.20 1.00
6 279.15 0.48 0.90 258.21 1.38 1.00
7 279.15 0.48 0.90 258.21 1.38 1.00
8 279.21 0.85 0.90 258.76 1.38 1.00
9 282.17 0.85 0.90 272.61 1.43 1.00
10 284.33 0.85 0.90 282.75 1.46 1.00
11 291.75 0.85 0.90 317.79 1.58 1.00
12 299.20 0.85 0.83 275.96 1.54 0.57
13 286.33 0.85 0.83 215.00 1.33 0.57
14 281.21 0.85 0.83 190.90 1.24 0.57
), ArticleFig(id=1233807267162804660, tenantId=1146029695717560320, journalId=1149651085930835976, articleId=1233732516671189319, language=CN, label=表2, caption=

文献[12]所述工况下提出的循环各节点参数

, figureFileSmall=null, figureFileBig=null, tableContent=
节点温度
T/K		压力
p/MPa		氨质量
分数w		焓值h/kJ·kg−1熵值S/ kJ·kg−1K−1质量流量比/
kg·kg−1
1 299.20 0.85 0.90 856.69 3.40 1.00
2 299.20 0.85 0.99 1 641.8 5.91 0.43
3 286.33 0.67 0.99 1 610.3 5.91 0.01
4 276.48 0.48 0.99 1 570.2 5.91 0.99
5 281.46 0.48 0.90 767.31 3.20 1.00
6 279.15 0.48 0.90 258.21 1.38 1.00
7 279.15 0.48 0.90 258.21 1.38 1.00
8 279.21 0.85 0.90 258.76 1.38 1.00
9 282.17 0.85 0.90 272.61 1.43 1.00
10 284.33 0.85 0.90 282.75 1.46 1.00
11 291.75 0.85 0.90 317.79 1.58 1.00
12 299.20 0.85 0.83 275.96 1.54 0.57
13 286.33 0.85 0.83 215.00 1.33 0.57
14 281.21 0.85 0.83 190.90 1.24 0.57
), ArticleFig(id=1233807267259273652, tenantId=1146029695717560320, journalId=1149651085930835976, articleId=1233732516671189319, language=EN, label=Table 3, caption=

Comparison of parameters of Uehara cycle, Yoon cycle and proposed cycle under the conditions described in reference [17]

, figureFileSmall=null, figureFileBig=null, tableContent=
变量循环形式
Uehara循环Yoon循环新循环
冷凝器出口蒸气质量分数10.951
温海水进口温度/℃262626
冷海水进口温度/℃555
蒸发器出口端差/℃222
装机功率/kW202020
透平效率0.80.80.8
泵效率0.650.650.65
工质质量流量/kg·h−12 8102 8006 723
温海水质量流量/kg·h−1232 800230 500209 400
冷海水质量流量/kg·h−1118 100116 400104 700
工质侧压降/kPa101010
海水侧压降/kPa505050
工质种类H2O+NH3NH3H2O+NH3
工质浓度/kg·kg−10.95510.91
系统效率/%2.3792.4012.532
), ArticleFig(id=1233807267355742648, tenantId=1146029695717560320, journalId=1149651085930835976, articleId=1233732516671189319, language=CN, label=表3, caption=

文献[17]所述工况下Uehara循环、Yoon循环和新循环的参数比较

, figureFileSmall=null, figureFileBig=null, tableContent=
变量循环形式
Uehara循环Yoon循环新循环
冷凝器出口蒸气质量分数10.951
温海水进口温度/℃262626
冷海水进口温度/℃555
蒸发器出口端差/℃222
装机功率/kW202020
透平效率0.80.80.8
泵效率0.650.650.65
工质质量流量/kg·h−12 8102 8006 723
温海水质量流量/kg·h−1232 800230 500209 400
冷海水质量流量/kg·h−1118 100116 400104 700
工质侧压降/kPa101010
海水侧压降/kPa505050
工质种类H2O+NH3NH3H2O+NH3
工质浓度/kg·kg−10.95510.91
系统效率/%2.3792.4012.532
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新型海洋温差能回热循环热力学分析
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彭景平 1 , 葛云征 1 , 陈凤云 1 , 刘蕾 1 , 吴浩宇 1 , 刘伟民 1, *
海洋学报 | 论文 2021,43(5): 120-126
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海洋学报 | 论文 2021, 43(5): 120-126
新型海洋温差能回热循环热力学分析
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彭景平1 , 葛云征1, 陈凤云1, 刘蕾1, 吴浩宇1, 刘伟民1, *
作者信息
  • 1自然资源部第一海洋研究所 海洋工程环境研究中心，山东 青岛 266061

    • 彭景平（1987-），男，山东省临沂市人，主要从事海洋温差能开发利用方面研究。E-mail：

通讯作者:

刘伟民，研究员，博士，主要从事海洋热能转换技术及综合利用方面研究。E-mail：
Thermodynamic analysis of a new ocean thermal energy conversion regenerative cycle
Jingping Peng1 , Yunzheng Ge1, Fengyun Chen1, Lei Liu1, Haoyu Wu1, Weimin Liu1, *
Affiliations
  • 1Marine Engineering Environment Research Center, First Institute of Oceanography, Ministry of Natural Resources, Qingdao 266061, China
出版时间: 2021-05-25 doi: 10.12284/hyxb2021085
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摘要
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针对海洋温差能可利用温差小，利用效率低的问题，本文提出了一种采用非共沸混合工质的新型海洋温差能回热循环，并基于热力学定律对提出的热力循环进行热力学分析。选取蒸发压力、工质的质量分数作为变量，对提出的热力循环进行热力学分析研究。研究结果表明：以工质质量分数为变量时，循环热效率和系统净输出随蒸发压力的增加先增大后减小，系统热效率在工质质量分数为0.91时取得最大值5.28%，净输出功在浓度为0.96时取得最大值3.83 kW。以蒸发压力为变量时，循环热效率和系统净输出随工质质量分数的增大先增大后减小，系统热效率在蒸发压力为0.595 MPa时取得最大值5.26%，净输出功在压力为0.58 MPa时取得最大值3.57 kW。在相同运行控制参数下与Uehara循环、Yoon循环进行对比，提出的循环系统热效率最佳。提出的热力循环系统分析结果可对提高海洋温差能利用效率提供理论依据和参考。

海洋温差能  /  蒸发压力  /  循环热效率  /  工质质量分数  /  净输出功率

In view of the problems of small available temperature difference and low utilization efficiency of ocean thermal energy conversion (OTEC). A new thermodynamic cycle of OTEC using non-azeotropic mixed working fluid is proposed. Based on the laws of thermodynamics, the thermodynamic analysis of the proposed thermodynamic cycle is carried out. Evaporation pressure, mass fraction of working fluid, evaporation temperature and condensation temperature are selected as influencing variables to study the proposed thermodynamic cycle. The results show that when the working fluid mass fraction is selected as a variable, with the evaporation pressure increases the cycle thermal efficiency and the net output of system increase first and then decrease. The system thermal efficiency achieves a maximum value of 5.28% when the working fluid mass fraction is 0.91. The maximum value of 3.83 kW is obtained when the mass fraction of the working fluid is 0.96. When the evaporation pressure is selected as the variable, the cycle thermal efficiency and the net output of the system increase first and then decrease with the mass fraction of the working medium increases. The cycle thermal efficiency achieves a maximum value of 5.26% when the evaporating pressure is 0.595 MPa, and the net output work obtains a maximum value of 3.57 kW when the evaporating pressure is 0.58 MPa. Compared with Uehara cycle and Yoon cycle under the same operating conditions, the proposed cycle system has the highest thermal efficiency. The analysis results of the proposed thermal cycle system can provide a theoretical basis and reference for improving the utilization efficiency of OTEC.

ocean thermal energy conversion  /  evaporation pressure  /  cycle thermal efficiency  /  working fluid mass fraction  /  net output work
彭景平, 葛云征, 陈凤云, 刘蕾, 吴浩宇, 刘伟民. 新型海洋温差能回热循环热力学分析. 海洋学报, 2021 , 43 (5) : 120 -126 . DOI: 10.12284/hyxb2021085
Jingping Peng, Yunzheng Ge, Fengyun Chen, Lei Liu, Haoyu Wu, Weimin Liu. Thermodynamic analysis of a new ocean thermal energy conversion regenerative cycle[J]. Haiyang Xuebao, 2021 , 43 (5) : 120 -126 . DOI: 10.12284/hyxb2021085
正文
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1 引言
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海洋温差能转换的实质是将储存在海水中的太阳能转换成为电能[1-2]，海洋覆盖地球约71%的面积，是巨大太阳能接收器。海洋是地球上巨大的可再生能源载体，而温差能是诸多海洋能中储量最大的可再生能源[3]。随着常规化石能源的紧缺和造成的环境污染问题日益严重，而海洋温差能又具备受季节及昼夜的影响小、储量大和稳定性好的优势，海洋温差能开发利用倍受国际研究者的青睐[4]。但是由于表层海水与深层海水仅有约为15～25℃的温差，可利用理论循环热效率通常为3%～5%[5-6]。提高海洋温差能利用热效率成为国内外研究人员的研究重点和方向。
国内外学者对提升海洋温差能发电系统利用效率方面做了一些研究，包括工质选取和热力循环形式等方面。Chen等[7]对朗肯循环进行了理论和试验研究，分析了R717、R22、R125、R134a、R152a和R245fa6中工质在不同透平进口压力下的循环热效率，研究结果表明R717是海洋温差能最适合的工质。黄靖伦等[8]采用R245fa/R123非共沸混合工质对有机朗肯循环余热回收系统的热力性能进行了研究，分析了分别采用R245fa、R123单工质和R245fa/R123混合工质循环系统的热力性能，结果显示混合工质可提高系统的㶲效率。Aydin等[9]开展了采用太阳能再热提高朗肯循环效率的研究，研究结果表明在透平进口设置太阳能再热可以使循环效率从1.9%提高到3%。Kusuda等[10]对双级朗肯循环进行了研究，研究结果显示双级朗肯循环系统可以减小换热器内的不可逆损失，有利于提高循环系统的输出功。Kalina[11]在1984年提出了一种新的热力循环系统，该循环系统热效率是朗肯循环的1.6～1.9倍。Uehara等[12]提出了一种新型高效海洋温差能热力循环，采用氨−水非共沸混合工质，采用了两个透平，并采用了中间抽气回热的方法，系统循环热效率高于Kalina循环[13-14]。Yuan等[15-16]通过在循环系统中安装引射器对Uehara循环加以改进，采用氨水再热−引射吸收的方法提高循环效率，研究结果表明温差为24℃时，循环效率达到5.27%，循环热效率高于Uehara循环。Yoon等[17]提出了一种带有两级透平和回热器的单工质海洋热能转换热力循环，通过对透平效率、换热器压降、透平出口压力等参数分析系统性能，研究结果表明系统热效率略高于Uehara循环。
目前，有关蒸发压力、工质质量分数等因素对海洋温差能热力循环效率的研究较少，本文提出一种新的采用非共沸工质海洋温差能回热循环系统，选取蒸发压力、工质质量分数、蒸发冷凝温度参数对循环系统进行热力分析。
2 热力循环系统介绍
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本文提出的高效海洋温差能回热循环系统由一个主循环和两个热回收支路构成，选取R134a/R123混合物作为系统工质，其原理图和T-S-w图如图1、图2所示。循环系统由蒸发器、气液分离器、两级透平发电机、工质泵、回热器、吸收器和冷凝器组成。其工作原理为：蒸发器中表层热海水将混合工质加热成为气液两相混合溶液，气液两相混合工质在气液分离器中分离为气相和液相，气相工质蒸气进入透平做功，液相工质溶液进入热回收支路。工质蒸气在第一级透平做功后的乏气，有少部分抽出进入抽气热回收支路，剩余的乏气进入第二级透平做功。在吸收器中两条热回收支路的工质与第二级透平排出的乏气混合进入冷凝器，深层冷海水将混合工质冷却为液态后，由工质泵输送到回热支路回热器进行预热，然后进入蒸发器进入下一次循环。两条热回收支路通过回热器1、2、3回收利用分离器分离出的液态工质和双级透平中间抽气的热量，可有效提高循环系统的热效率。
3 仿真模型建立
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3.1 数值模型
在分析提出的循环热力过程中的各节点位置如图1所示。在数值计算过程中，为了在理论研究中可以明确循环热力过程中各基本热力参数关系，定量分析提出的热力循环系统，拟进行以下简化假设：
（1）循环系统中各分离、交汇处的蒸气压力相同；
（2）冷凝器出口的工质为饱和液体；
（3）分离器分离出的液体和气体均为饱和状态；
（4）两级透平内的气态工质和工质泵内的液态工质均为等熵过程；
（5）换热器的窄点端差选取2℃。
根据质量守恒和能量守恒方程，系统中主要设备的数值模型建立如下：
蒸发器和冷凝器的能量守恒方程可以表示为
${{蒸发器：}}{Q_{\rm{e}}} = {c_{\rm{w}}}{m_{\rm{w}}}\left( {{T_{{\rm{wi}}}} - {T_{{\rm{wo}}}}} \right) = {m_1}\left( {{h_1} - {h_{11}}} \right),$
${{冷凝器：}}{Q_{\rm{c}}} = {c_{\rm{c}}}{m_{\rm{c}}}\left( {{T_{{\rm{ci}}}} - {T_{{\rm{co}}}}} \right) = {m_5}\left( {{h_5} - {h_6}} \right),$
式中，${Q_{\rm{e}}}$为蒸发器换热量，单位：kW；${c_{\rm{w}}}$为温海水比热，单位：kJ/(kg·℃)；${m_{\rm{w}}}$为温海水质量流量，单位：kg/s；${T_{{\rm{wi}}}}$为蒸发器进口温海水温度， 单位：℃；${T_{{\rm{wo}}}}$为蒸发器出口温海水温度， 单位：℃；${m_1}$为蒸发器出口（1点）工质质量流量，单位：kg/s；${h_1}$为蒸发器出口（1点）工质焓值，单位：kJ/kg；${h_{11}}$为蒸发器进口（11点）工质焓值，单位：kJ/kg；${Q_{\rm{c}}}$为冷凝器换热量，单位：kW；${c_{\rm{c}}}$为冷海水比热，单位：kJ/(kg· ℃)；${m_{\rm{c}}}$为冷海水质量流量，单位：kg/s；${T_{{{{\rm{ci}}}}}}$为冷凝器进口温海水温度， 单位：℃；${T_{{\rm{co}}}}$为冷凝器出口冷海水温度， 单位：℃；${m_5}$为冷凝器出口（5点）工质质量流量，单位：kg/s；${h_5}$为冷凝器出口（5点）工质焓值，单位：kJ/kg；${h_6}$为冷凝器进口（6点）工质焓值，单位：kJ/kg。
系统中3个回热器的能量守恒方程可以表示为
${{回热器1：}}{m_8}\left( {{h_9} - {h_8}} \right) = {m_{13}}\left( {{h_{13}} - {h_{14}}} \right),$
${{回热器2：}}{m_9}\left( {{h_{10}} - {h_9}} \right) = {m_3}\left( {{h_3} - {h_{16}}} \right),$
${{回热器3：}}{m_{10}}\left( {{h_{11}} - {h_{10}}} \right) = {m_{12}}\left( {{h_{12}} - {h_{13}}} \right),$
式中，${m_8}$为回热器1进口（8点）混合工质溶液的质量流量，单位：kg/s；${h_8}$为回热器1进口（8点）混合工质溶液的焓值，单位：kJ/kg；${h_9}$为回热器1出口（9点）混合工质溶液的焓值，单位：kJ/kg；${m_{13}}$为回热器1进口（13点）低浓度工质溶液的质量流量，单位：kg/s；${h_{13}}$为回热器1进口（13点）低浓度工质溶液的焓值，单位：kJ/kg；${h_{14}}$为回热器1出口（14点）低浓度工质溶液的焓值，单位：kJ/kg；${m_9}$为回热器2进口（回热器1出口，9点）混合工质溶液的质量流量，单位：kg/s；${h_{10}}$为回热器2出口（10点）混合工质的焓值，单位：kJ/kg；${h_{16}}$为回热器2出口（16点）抽气工质的焓值，单位：kJ/kg；${m_{10}}$为回热器3进口（10点）混合工质溶液的质量流量，单位：kg/s；${h_{11}}$为回热器3出口（11点）混合工质溶液的焓值，单位：kJ/kg；${h_{12}}$为回热器3进口（12点）低浓度工质溶液的焓值，单位：kJ/kg。
气液分离器的质量守恒方程和能量守恒方程可表示为
${m_1} = {m_2} + {m_{12}},$
${m_1}{h_1} = {m_2}{h_2} + {m_{12}}{h_{12}},$
式中，${m_2}$为一级透平进口（2点）气相工质质量流量，单位：kg/s；${m_{12}}$为分离器液相出口（12点）工质质量流量， 单位：kg/s；${h_2}$为一级透平进口（2点）气相工质焓值，单位：kJ/kg；${h_{12}}$为分离器液相出口（12点）工质焓值， 单位：kJ/kg。
吸收器的能量守恒方程可表示为
${m_5}{h_5} = {m_4}{h_4} + {m_{15}}{h_{15}} + {m_{17}}{h_{17}},$
式中，${m_5}$为冷凝器进口混合工质的质量流量，单位：kg/s；${h_5}$为冷凝器进口混合工质的焓值，单位：kJ/kg；${m_4}$为二级透平出口高浓度R134a蒸气的质量流量，单位：kg/s；${h_4}$为二级透平出口高浓度R134a蒸气的焓值，单位：kJ/kg；${m_{15}}$为膨胀阀1出口低浓度R134a溶液的质量流量，kg/s；${h_{15}}$为膨胀阀1出口低浓度R134a溶液的焓值，单位：kJ/kg；${m_{17}}$为膨胀阀2出口低浓度R134a溶液的质量流量，单位：kg/s；${h_{17}}$为膨胀阀2出口低浓度R134a溶液的焓值，单位：kJ/kg。
双级透平：在提出的循环系统中采用的透平形式是双级透平，在一级透平出口处进行抽气，抽出进入抽气热回收支路。中间抽气点的压力按下式选取
${p_3} = \frac{{{p_2} + {p_4}}}{2},$
式中，${p_2}$为一级透平进口（2点）压力，单位：MPa；${p_3}$为透平中间（3点）抽气压力，单位：MPa；${p_4}$为二级透平出口（4点）压力，单位：MPa。
透平内工质等熵膨胀做功，透平的能量守恒方程可表示为
${{一级透平输出功：}}{W_{{\rm{t}}1}} = {m_2}\left( {{h_2} - {h_3}} \right),$
${{二级透平输出功：}}{W_{{\rm{t}}2}} = \left( {{m_2} - {m_3}} \right)\left( {{h_3} - {h_4}} \right),$
式中，${W_{{\rm{t}}1}}$为一级透平输出功，单位：kW；${h_3}$为透平中间（3点）抽气工质焓值，单位：kJ/kg；${W_{{\rm{t}}2}}$为二级透平输出功，单位：kW；${m_3}$为透平中间（3点）抽气工质质量流量，单位：kg/s；${h_4}$为二级透平出口（4点）工质焓值，单位：kJ/kg。
工质泵的能量守恒方程可表示为
${\eta _{{\rm{p.f}}}}{W_{{\rm{p.f}}}} = {m_7}\left( {{h_8} - {h_7}} \right),$
式中，${\eta _{{\rm{p.f}}}}$为工质泵的效率；${W_{{\rm{p.f}}}}$为工质泵的电机功率，单位：kW；${m_7}$为工质泵进口混合工质溶液的质量流量，单位：kg/s；${h_7}$为工质泵进口混合工质溶液的焓值，单位：kJ/kg；${h_8}$为工质泵出口混合工质溶液的焓值，单位：kJ/kg。
循环热效率和系统效率可以表示为
${\eta _{{\rm{cyc}}}} = \frac{{{W_{\rm{t}}}}}{{{Q_{\rm{e}}}}} = \frac{{{W_{{\rm{t}}1}} + {W_{{\rm{t}}2}}}}{{{Q_{\rm{e}}}}},$
${\eta _{{\rm{sys}}}} = \frac{{{W_{{\rm{net}}}}}}{{{Q_{\rm{e}}}}} = \frac{{{W_{\rm{t}}} - {W_{{\rm{p.f}}}} - {W_{{\rm{p.w}}}} - {W_{{\rm{p.c}}}}}}{{{Q_{\rm{e}}}}},$
式中，${\eta _{{\rm{cyc}}}}$为循环热效率；${W_{\rm{t}}}$为两级透平总输出功，单位：kW；${\eta _{{\rm{sys}}}}$为系统效率；${W_{{\rm{net}}}}$为系统净输出功，单位：kW；${W_{{\rm{p.w}}}}$为温海水泵电机功率，单位：kW；${W_{{\rm{p.c}}}}$为冷海水泵电机功率，单位：kW。
3.2 计算流程
依据可利用海洋温差能的海域实际海水温度情况，表层温海水温度选取26℃，深层冷海水温度选取5℃，新型海洋温差能回热循环系统的理论分析初始条件组合如表1所示。循环系统中各节点的状态参数及工质的热力学性质使用自主研发的热物性计算软件进行计算。依据质量守恒和能量守恒定律，循环系统计算流程如图3所示。
4 结果讨论
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在海洋温差能利用系统中影响系统循环热效率的因素主要有工质质量分数、蒸发压力、蒸发和冷凝温度。本文通过数值计算研究了工质质量分数和蒸发压力参数对循环热效率和系统净输出功的影响。在循环热效率的计算过程中采用单位工质进行计算，在系统净输出功率计算过程中采用装机容量为10 kW的模型进行量算。
4.1 工质质量分数对循环热效率和净输出功率的影响
在给定的温差能循环系统初始条件：表层温海水温度为26℃，冷海水温度为5℃，蒸发器和冷凝器窄点端差均为2℃，蒸发压力为0.6 MPa。循环热效率随着混合工质质量分数的增大先增大后减小，如图4所示。循环热效率在混合工质质量分数小于0.9时，循环热效率随工质质量分数的增大快速升高，在混合工质质量分数为0.9～0.93之间时，系统热效率变化幅度不大，并在混合工质质量分数为0.91时，系统热效率取得极大值5.28%，当混合工质质量分数超过0.93时，随着工质质量分数的增加，循环热效率迅速减小。出现上述变化规律的原因是：在蒸发温度不变的情况下，混合工质的气化率随着工质质量分数增加而增大，透平输出功率随之增大。同时，随着混合工质气化率的增加，蒸发器内的换热量增大。蒸发器内换热量的增大比透平输出功率增大的趋势更快，如图5所示。因而出现了循环热效率随混合工质质量分数的增大先增大后减小的变化规律。
随着混合工质质量分数的增大，系统净输出功率先增大后减小，在工质质量分数为0.96时取得极大值3.83 kW，如图4所示。在装机容量不变的情况下，蒸发器冷凝器内的换热量基本不变。随着混合工质气化率的增加，系统内混合工质的质量流量逐渐减小，随之减小的是工质泵的功率，系统的净输出功率增大。当工质质量分数继续增大，分离器内液相溶液过少导致液相热回收支路失去了回热功能，循环热效率减小迅速导致净输出功率减小。
4.2 蒸发压力对循环热效率和净输出功率的影响
在给定温差能循环系统初始条件，表层温海水温度为26℃，深层冷海水温度为5℃，混合工质质量分数为0.9。循环热效率随蒸发压力的增大先增大后减小，蒸发压力由0.55 MPa增加到0.595 MPa时，循环热效率从4.60%升高到5.26%，在蒸发进口压力继续增加到0.604 MPa时，循环热效率减小到5.00%，如图6所示。在蒸发温度和工质质量分数不变的情况下，随着蒸发压力的增加，混合工质的气化率减小导致透平输出功率减小。此时，随换热器内混合工质气化率减少，换热器内换热量减小，相比于蒸发器换热量透平输出功率的变化幅度更大，如图7所示。因此出现了循环热效率随蒸发压力的增大先增大后减小的变化规律。
系统净输出功率随着蒸发压力的增加先缓慢增大后快速减小，在蒸发压力为0.58 MPa时取得极大值3.57 kW，如图6所示。随着蒸发压力的升高蒸发器内工质气化率逐渐减小，单位工质的透平输出功率降低，在装机功率不变的情况下，工质质量流量随蒸发压力的升高而增加，工质泵耗功随之增大。在循环热效率的影响下，随着蒸发压力的升高海水泵的耗功先减小后增大。在海水泵耗功、透平输出功率和工质泵耗功耦合作用下，系统净输出功率随蒸发压力的增加呈现出先增大后减小的变化规律。
4.3 验证对比
通过在一定的运行工况下与Uehara循环和Yoon循环的计算结果对比，以验证文中提出的新型海洋温差能回热循环具有较高的循环热效率。文献[12]中运行工况为：工质采用氨的质量分数为0.9的氨水混合工质，蒸发压力为0.8 MPa，蒸发温度和冷凝温度分别为299.15 K和279.15 K。在上述工况下，Uehara循环和提出新型海洋温差能回热循环的循环热效率分别为5.3%和5.6%，新循环的热效率比Uehara循环高了5.66%，提出的新循环系统各节点计算参数见表2，节点编号见图1。在文献[17]所述的运行工况下，将提出的新型海洋温差能回热循环与Uehara循环、Yoon循环计算结果进行对比，如表3所示。新热力循环的系统效率为2.532%，高于Uehara循环和Yoon循环的2.379%和2.401%。
5 结论
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本文依据热力学定律，选取混合工质质量分数和蒸发压力性能参数对提出的新型海洋温差能回热循环进行热力分析研究。得到了提出的新热力循环系统循环热效率和净输出功率的变化规律，并与其他热力循环形式进行了对比，得到了如下结论。
（1）在给定的运行工况下，提出的新型海洋温差能回热循环系统净输出功率和热效率均随混合工质质量分数的增加先增大后减小，随蒸发压力的增加先增大后减小。
（2）新型海洋温差能回热循环的热效率最佳值点和净输出功率最大值点并不是同一个参数值点。以工质质量分数为变量时，循环热效率在工质质量分数为0.91时取得极值5.28%，净输出功率在工质质量分数为0.96时取得极值3.83 kW；以蒸发压力为变量时，工质质量分数为0.9时，循环热效率在蒸发压力为0.595 MPa时取得极值5.26%，净输出功率在蒸发压力为0.58 MPa时取得极值3.57 kW。
（3）在相同的温冷海水和工质质量分数等运行参数下，与Uehara循环和Yoon循环进行对比，提出的新型海洋温差能回热循环性能最佳。在文献[12]的运行参数下，提出的新循环热效率比Uehara循环高5.66%；在文献[17]的运行参数下，提出的新循环系统效率为2.532%高于Uehara循环的2.379%和Yoon循环的2.401%。
基金
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  • 国家自然科学基金（41976204，51709055）；中韩海洋科学共同研究中心项目（PI-2018-3）
文献
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参考文献 引证文献
排序方式：
1
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Ding Liang, Li Hui, Shi Xuezeng. Performance analysis and improvement of solar energy reheated CC-OTEC system[J]. Shipbuilding of China, 2019, 60(S1): 171−178.
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Matsuda Y, Yoshitake T, Sugi T, et al. Construction of a static model for power generation of OTEC plant using uehara cycle based on experimental data[J]. Journal of Marine Science and Engineering, 2018, 6(1): 18−31.
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2021年第43卷第5期
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文章信息
doi: 10.12284/hyxb2021085
  • 接收时间：2020-04-17
  • 首发时间：2026-02-26
  • 出版时间：2021-05-25
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  • 收稿日期：2020-04-17
  • 修回日期：2020-06-04
基金
国家自然科学基金（41976204，51709055）；中韩海洋科学共同研究中心项目（PI-2018-3）
作者信息
    1自然资源部第一海洋研究所 海洋工程环境研究中心，山东 青岛 266061

通讯作者:

刘伟民，研究员，博士，主要从事海洋热能转换技术及综合利用方面研究。E-mail：
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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
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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
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