基于CO2 混合工质的压缩储能系统性能

doi:10.19799/j.cnki.2095-4239.2024.1198

储能科学与技术 ›› 2025, Vol. 14 ›› Issue (6): 2391-2404.doi: 10.19799/j.cnki.2095-4239.2024.1198

基于CO₂ 混合工质的压缩储能系统性能

王斌¹(), 谭鋆²^,⁴, 李凤合³, 蔺新星¹, 关苏敏²^,⁴, 丁若晨¹, 苏文³()

^1.中国三峡集团科学技术研究院，北京 101100
^2.中国长江电力股份有限公司，湖北宜昌 443000
^3.中南大学能源科学与工程学院，湖南长沙 410083
^4.湖北省智慧水电技术创新中心，湖北武汉 430000

收稿日期:2024-12-17 修回日期:2025-02-07 出版日期:2025-06-28 发布日期:2025-06-27
通讯作者: 苏文 E-mail:wang_bin14@ctg.com.cn;suwenzn@csu.edu.cn
作者简介:王斌（1989—），男，硕士研究生，研究方向为可再生能源与清洁能源，E-mail：wang_bin14@ctg.com.cn；
基金资助:
中国长江电力股份有限公司科研项目(Z152402007)

Performance research of compression energy storage system with CO₂-based mixture

Bin WANG¹(), Jun TAN²^,⁴, Fenghe LI³, Xinxing LIN¹, Sumin GUAN²^,⁴, Ruochen DING¹, Wen SU³()

^1.China Three Gorges Corporation, Beijing 101100, China
^2.China Yangtze Power Co. Ltd. , Yichang 443000, Hubei, China
^3.School of Energy Science and Engineering, Central South University, Changsha 410083, Hunan, China
^4.Hubei Technology Innovation Center for Smart Hydropower, Wuhan 430000, Hubei, China

Received:2024-12-17 Revised:2025-02-07 Online:2025-06-28 Published:2025-06-27
Contact: Wen SU E-mail:wang_bin14@ctg.com.cn;suwenzn@csu.edu.cn

摘要/Abstract

摘要：

为了提高压缩储能系统的储能密度，同时解决CO₂难以冷凝的问题，本工作提出了一种基于CO₂混合工质的压缩储能系统，在高低压侧CO₂混合工质均以液相的形式存储。构建了系统在稳态工况下的热经济模型，探讨7种CO₂混合工质(CO₂/R32、CO₂/R41、CO₂/R22、CO₂/R125、CO₂/R143a、CO₂/R601和CO₂/R601a)的系统适应性，并优选出最佳的CO₂混合工质和组分配比，揭示关键运行参数对系统性能的影响。结果表明，随着CO₂质量分数的增加，系统的储能效率和㶲效率均有所提升，其中CO₂/R41、CO₂/R32和CO₂/R22的表现较优，且对CO₂质量分数的敏感性较低。在7种混合工质中，CO₂/R41(0.65/0.35)在设计工况下展现出最佳的热经济性，计算得到系统的储能效率和㶲效率分别为59.12%和53.11%；系统所需高低压储罐体积分别为5217.65 m³和2787.39 m³，得到储能密度为9.36 kWh/m³；系统投资成本为134.06×10⁶ 元，投资回收期为6.59 a。此外，对于压缩CO₂/R41(0.65/0.35)储能系统，随着高压储罐温度的增加，储能效率和㶲效率线性提升，投资成本呈现先降后升的趋势；而低压储罐温度的升高导致储能效率和㶲效率下降，投资成本和投资回收期上升。

关键词: CO₂混合工质, 压缩储能, 性能分析

Abstract:

To improve the energy storage density of compressed energy storage systems and address challenges in CO₂ condensation, this study proposes a liquid-phase CO₂-based compressed energy storage system, where CO₂ mixtures are stored in liquid form on both high- and low-pressure sides. A steady-state thermal-economic model was developed to assess the system adaptability of seven CO₂-based mixtures (CO₂/R32, CO₂/R41, CO₂/R22, CO₂/R125, CO₂/R143a, CO₂/R601, and CO₂/R601a). In addition, the optimal CO₂-based mixtures and mixing ratios were selected to reveal the impact of the key operating parameters on the system performance. The results demonstrate that with an increase in the CO₂ mass fraction, the round-trip efficiency (RTE) and exergy efficiency (ηex) of the system are improved. CO₂/R41, CO₂/R32, and CO₂/R22 exhibit superior performance and lower sensitivity to CO₂ mass fraction. Among the seven mixed working fluids, CO₂/R41 (0.65/0.35) demonstrated the best thermal-economic performance under design conditions, with RTE and ηex of 59.12% and 53.11%, respectively. The high- and low-pressure storage tanks require volumes of 5217.65 m³ and 2787.39 m³, respectively, achieving an energy storage density of 9.36 kWh/m³. The total capital cost (TCC) is 134.06×10⁶ CNY, with a payback period (PBP) of 6.59 years. For the compressed CO₂/R41 (0.65/0.35) energy storage system, increasing the high-pressure storage tank temperature linearly increases RTE and η_ex, whereas TCC initially decreases before increasing. Conversely, an increase in the temperature of the low-pressure storage tank decreased RTE and ηex while increasing both TCC and PBP.

Key words: CO₂-based mixture, compression energy storage, performance analysis

中图分类号:

TK 02

王斌, 谭鋆, 李凤合, 蔺新星, 关苏敏, 丁若晨, 苏文. 基于CO₂ 混合工质的压缩储能系统性能[J]. 储能科学与技术, 2025, 14(6): 2391-2404.

Bin WANG, Jun TAN, Fenghe LI, Xinxing LIN, Sumin GUAN, Ruochen DING, Wen SU. Performance research of compression energy storage system with CO₂-based mixture[J]. Energy Storage Science and Technology, 2025, 14(6): 2391-2404.

图/表 22

图1

表1

系统部件的能量平衡公式"

部件	公式
透平	$W t u r, i = m m i x, d i s h i n, i - h o u t, i t d i s = m m i x, d i s h i n, i - h o u t s, i η e s t d i s$
压缩机	$W c o m, i = m m i x, c h a r h o u t, i - h i n, i t c h a r = m m i x, c h a r h o u t s, i - h i n, i t c h a r η c s$
冷却器	$Q c o o l e r, i = m m i x, c h a r h i n, i - h o u t, i t c h a r = m w a t e r, i c p T i n, i - T o u t, i t c h a r$ $m i n T i n_m i x, C O 2, i - T o u t_w a t e r, i = P P T D$
加热器	$Q h e a t e r, i = m m i x, d i s h i n, i - h o u t, i t d i s = m w a t e r, i c p T i n, i - T o u t, i t d i s$ $m i n T i n - o u t_w a t e r, i - T i n - o u t_m i x, C O 2, i = P P T D$
蓄冷器	$Q c o l d, i = m m i x, c h a r h i n, i - h o u t, i t c h a r = m m i x, d i s h i n, i - h o u t, i t d i s$
散热器	$Q c o o l i n g = m m i x, d i s h i n, i - h o u t, i t d i s = m m i x, c h a r h i n, i - h o u t, i t c h a r$
节流阀	$h i n, i = h o u t, i$

表1

表2

系统部件的㶲损失方程"

部件	㶲损失方程
透平	$I t u r, i = m m i x, d i s e i n, i - e o u t, i t d i s - W t u r, i$
压缩机	$I c o m, i = m m i x, c h a r e i n, i - e o u t, i t c h a r + W c o m, i$
冷却器	$I c o o l e r, i = m m i x, c h a r e i n, i - e o u t, i t c h a r + m w a t e r, i e i n, i - e o u t, i t c h a r$
加热器	$I h e a t e r, i = m m i x, d i s e i n, i - e o u t, i t d i s + m w a t e r, i e i n, i - e o u t, i t d i s$
蓄冷器	$I c o l d, i = m m i x, c h a r e i n, i - e o u t, i t c h a r + m m i x, d i s e i n, i - e o u t, i t d i s$
散热器	$I c o o l i n g, i = m m i x, d i s e i n, c o o l i n g - e o u t, c o o l i n g t d i s = m m i x, c h a r e i n, c o o l i n g - e o u t, c o o l i n g t c h a r$
节流阀	$I T V, i = m m i x, c h a r e i n, i - e o u t, i t c h a r = m m i x, d i s e i n, i - e o u t, i t d i s$

表2

表3

成本计算公式[8]"

部件/项目	成本计算公式
透平	$C t u r b i n e = 479.34 m m i x, d i s 0.93 - η e s l o g P i n P o u t 1 + e 0.036 T i n - 54.4$
压缩机	$C c o m p r e s s o r = 71.1 0.92 - η c s m m i x, c h a r P o u t P i n l o g P o u t P i n$
换热器	$C h e a t e r = C c o o l e r = 2681 A 0.59$
混合工质储罐	$C S T = 1000 V$
储水罐	$C W T = 5941.7 V - 0.389$
场地开发成本	$C s i t e = 0.1 P E C$
设备安装成本	$C i n s t a l l = 0.2 P E C$
工程、管理和规划成本	$C e n g = 0.05 P E C + C s i t e + C i n s t a l l$
应急成本	$C c o n t i n g = 0.1 P E C + C s i t e + C i n s t a l l$

表3

表4

图2

表5

工况参数"

参数	设计值
额定功率P_ed/MW	15
储能时间t_char/h	8 (0：00—8：00)
释能时间t_dis/h	5 (18：00—23：00)
低压储罐温度T_low/℃	-40
高压储罐温度T_high/℃	35
压缩机出口温度/℃	130
压缩机等熵效率η_cs/%	85
汽轮机等熵效率η_es/%	85
发电机额定效率γ/%	98
储水罐压力P_water/kPa	300
换热器的窄点温差 $Δ T$ /℃	10
环境温度T₀/℃	25
峰值电价P_peak/(元/kWh)	1.25 (8：00—13：00; 18：00—23：00)
谷电价格P_valley/(元/kWh)	0.3 (23：00—8：00)
平价电力价格P_parity/(元/kWh)	0.74 (13：00—18：00)
运行年限n/a	20

表5

图3

图4

图5

图6

图7

图8

图9

图10

图11

表 6

表7

表8

图12

图13

图14

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工质	物理特性
工质	临界温度/℃	临界压力/MPa	沸点/℃	摩尔质量/(kg/kmol)
CO₂	31.10	7.38	-78.40	44.01
R32	78.10	5.78	-51.70	52.02
R41	107.10	4.90	-29.5	72.00
R22	96.15	4.99	-40.81	86.47
R125	66.05	3.592	-49.00	120
R143a	73.10	3.76	-47.00	94.20
R601	196.60	3.37	36.10	72.15
R601a	187.20	3.38	27.80	72.15

名称	㶲损失/kWh	比例/%
节流阀1	93.09	0.15
节流阀2	760.89	1.26
节流阀3	404.92	0.67
中温蓄冷器	5534.08	9.22
高温蓄冷器	1263.50	2.10
加热器1	3647.83	6.07
加热器2	2344.54	3.90
冷却器1	2587.55	4.31
冷却器2	1449.68	2.41
透平1	4246.77	7.07
透平2	10496.58	17.49
压缩机1	8047.76	13.41
压缩机2	19122.04	31.87

参数	数值
压缩耗电量/MWh	126.84
发电量/MWh	75.00
储能效率/%	59.12
㶲效率/%	53.11
储热水总质量/t	1946.93
CO₂/R41总质量/t	2746.18
高压储罐体积/m³	5217.65
低压储罐体积/m³	2787.39
储能密度/(kWh/m³)	9.36

名称	数值
透平成本/元	12.32×10⁶
压缩机成本/元	4.63×10⁶
换热器成本/元	12.39×10⁶
高压储罐成本/元	36.52×10⁶
低压储罐成本/元	19.51×10⁶
储水罐成本/元	0.06×10⁶
土地开发成本/元	8.97×10⁶
设备安装成本/元	17.93×10⁶
工程、管理和规划成本/元	5.83×10⁶
应急成本/元	11.66×10⁶
PEC/元	85.43×10⁶
TCC/元	129.82×10⁶
年现金流出值/元	13.89×10⁶
年现金流入值/元	34.22×10⁶
投资回收期/a	6.38

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基于CO₂ 混合工质的压缩储能系统性能

Performance research of compression energy storage system with CO₂-based mixture

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