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收稿日期:
2024-05-13
修回日期:
2024-06-26
出版日期:
2024-06-27
通讯作者:
崔颖晗
作者简介:
王迪(1989—),男,博士,副教授,wd1989125@163.com
基金资助:
Di WANG1(), Yinghan CUI1(
), Lingfang SUN1, Yunlong ZHOU2
Received:
2024-05-13
Revised:
2024-06-26
Online:
2024-06-27
Contact:
Yinghan CUI
摘要:
为了解决可再生能源的间歇性和不稳定性等问题,基于超临界压缩二氧化碳储能(supercritical compressed carbon dioxide energy storage,SC-CCES)系统,利用CO2基二元混合物作为循环工质,对系统进行热力学性能分析。研究不同混合工质在不同比例下的储能性能以及储能系统往返效率和储能密度的影响。结果表明:超临界CO2混合工质储能系统的往返效率随着混入氪气质量分数的增加而升高,且高于单一CO2工质的往返效率;随着混入异丁烷、R32、R134a、丙烷的质量分数的增加能够使储能密度逐渐增加。研究结果对未来建设CO2混合工质储能循环工程应用奠定理论基础。
中图分类号:
王迪, 崔颖晗, 孙灵芳, 周云龙. 超临界二氧化碳混合工质储能系统热力学分析[J]. 化工学报, DOI: 10.11949/0438-1157.20240521.
Di WANG, Yinghan CUI, Lingfang SUN, Yunlong ZHOU. Thermodynamic analysis of supercritical carbon dioxide mixed working fluid energy storage system[J]. CIESC Journal, DOI: 10.11949/0438-1157.20240521.
参数 | 仿真值 | 参考值 | 相对误差/% |
---|---|---|---|
主压缩机温度/K | 322.8 | 324 | 0.37 |
主压缩机压力/kPa | 13842 | 13840 | 0.01 |
再压缩机温度/K | 391.9 | 391 | 0.23 |
再压缩机压力/kPa | 13968 | 13731 | 1.73 |
透平温度/K | 747.8 | 750 | 0.29 |
透平压力/kPa | 7889 | 7890 | 0.01 |
低温回热器热端温度/K | 337.2 | 335 | 0.66 |
低温回热器热端压力/kPa | 7820 | 7760 | 0.77 |
低温回热器冷端温度/K | 391.3 | 389 | 0.59 |
低温回热器冷端压力/kPa | 13840 | 13730 | 0.8 |
高温回热器热端温度/K | 415 | 418 | 0.72 |
高温回热器热端压力/kPa | 7890 | 7820 | 0.9 |
高温回热器冷端温度/K | 695.7 | 698 | 0.33 |
高温回热器冷端压力/kPa | 13730 | 13610 | 0.88 |
表1 模型验证
Table 1 Verification of the model
参数 | 仿真值 | 参考值 | 相对误差/% |
---|---|---|---|
主压缩机温度/K | 322.8 | 324 | 0.37 |
主压缩机压力/kPa | 13842 | 13840 | 0.01 |
再压缩机温度/K | 391.9 | 391 | 0.23 |
再压缩机压力/kPa | 13968 | 13731 | 1.73 |
透平温度/K | 747.8 | 750 | 0.29 |
透平压力/kPa | 7889 | 7890 | 0.01 |
低温回热器热端温度/K | 337.2 | 335 | 0.66 |
低温回热器热端压力/kPa | 7820 | 7760 | 0.77 |
低温回热器冷端温度/K | 391.3 | 389 | 0.59 |
低温回热器冷端压力/kPa | 13840 | 13730 | 0.8 |
高温回热器热端温度/K | 415 | 418 | 0.72 |
高温回热器热端压力/kPa | 7890 | 7820 | 0.9 |
高温回热器冷端温度/K | 695.7 | 698 | 0.33 |
高温回热器冷端压力/kPa | 13730 | 13610 | 0.88 |
参数 | 数值 | 单位 |
---|---|---|
储能时间 | 660 | s |
释能时间 | 480 | s |
储能阶段混合工质流量 | 70 | kg/s |
释能阶段混合工质流量 | 80 | kg/s |
压缩机等熵效率 | 89 | % |
透平等熵效率 | 90 | % |
储冷罐内导热油体积 | 55 | m3 |
储热罐内导热油体积 | 0 | m3 |
环境温度 | 298.15 | K |
热源温度 | 838.15 | K |
表2 系统设计参数
Table 2 System design parameter
参数 | 数值 | 单位 |
---|---|---|
储能时间 | 660 | s |
释能时间 | 480 | s |
储能阶段混合工质流量 | 70 | kg/s |
释能阶段混合工质流量 | 80 | kg/s |
压缩机等熵效率 | 89 | % |
透平等熵效率 | 90 | % |
储冷罐内导热油体积 | 55 | m3 |
储热罐内导热油体积 | 0 | m3 |
环境温度 | 298.15 | K |
热源温度 | 838.15 | K |
图5 压缩机入口温度变化下混合工质质量分数为6%、10%的往返效率
Fig.5 The round-trip efficiency with the mass fraction of the mixed working medium is 6% and 10% under the change of compressor inlet temperature
图6 压缩机入口温度变化下混合工质质量分数为6%、10%的储能密度
Fig. 6 The energy storage density with the mass fraction of the mixed working medium is 6% and 10% under the change of compressor inlet temperature
图7 高压节流阀压降变化下混合工质质量分数为6%、10%的往返效率
Fig. 7 The round-trip efficiency of the mass fraction of the mixed working medium is 6% and 10% under the pressure drop change of the throttle valve
图8 高压节流阀压降变化下混合工质质量分数为6%、10%的储能密度
Fig. 8 The energy storage density with the mass fraction of the mixed working medium is 6% and 10% under the pressure drop change of the throttle valve
图9 热源流量变化下混合工质质量分数为6%、10%的往返效率
Fig. 9 The round-trip efficiency of the mass fraction of the mixed working medium is 6% and 10% under the change of heat source flow rate
图10 热源流量变化下混合工质质量分数为6%、10%的储能密度
Fig. 10 The energy storage density of the mass fraction of the mixed working medium is 6% and 10% under the change of heat source flow rate
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