先进绝热压缩空气储能系统储能阶段建模仿真和动态分析

doi:10.3976/j.issn.1002-4026.20230171

Abstract

Abstract:

Energy and environment problems are becoming increasingly prominent, renewable energy is developing rapidly, and its intermittency is one of the key problems restricting its development. Advanced adiabatic compressed air energy storage (AA-CAES) is an effective method to address the intermittency of renewable energy. In this study, a mathematical model for the energy storage stage of AA-CAES is established, and dynamic and sensitivity analysis of the conservation of energy, energy balance, and key parameters of each component are conducted. The results reveal that the proposed mathematical model follows the laws of conservation of energy and exergy balance; the exergy loss of the compressor is greater than that of the heat exchanger; energy and heat are mainly stored in heat transfer oil and high-pressure air, respectively; the deviation between compressor operating and design condition reduces the efficiency; the effect of the air flow rate and inlet temperature of the first-stage turbine on the operation time is greater than that of the storage temperature, adiabatic efficiency and stored air mass. This paper provides reference for adjusting parameters and optimizing energy storage system according to actual demand.

Key words: advanced adiabatic compressed air energy storage, energy analysis, exergy analysis, dynamic characteristics, modeling and simulation

CLC Number:

TK02

LI Shuangjiang, XIAO Feng, CHEN Wei, ZHANG Bin, ZHU Qing, WANG Zijie, WU yang. Modeling, simulation and dynamic analysis of the energy stage of advanced adiabatic compressed air energy storage system[J].Shandong Science, 2024, 37(5): 42-54.

Figures/Tables 16

Fig.1

Table 1

Fig.2

Fig.3

Table 2

Design parameters of the energy storage stage"

部件	设计参数	数值	部件	设计参数	数值
C1/C2/C3	质量流量 $q m, 0$ /(kg·s^-1)	40.05	HX3	空气质量流量 $q m, a i r, 0$ /(kg·s^-1)	40.05
	转速n₀/(r·min^-1)	9 600		导热油质量流量 $q m, o i l, 0$ /(kg·s^-1)	28.73
	压比ε₀	4.8		传热系数X₀/(J·K)	208.09
	绝热效率η₀	0.8		压力损失ΔP₀/Pa	2 000
HX1	空气质量流量 $q m, a i r, 0$ /(kg·s^-1)	40.05	AT
	导热油质量流量 $q m, o i l, 0$ /(kg·s^-1)	22.51
	传热系数X₀/(kJ·K^-1)	219.24		容积V/m³	9 313
	压力损失ΔP₀/Pa	2 000		初始压力P/MPa	3.2
HX2	空气质量流量 $q m, a i r, 0$ /(kg·s^-1)	40.05		储气压力P/MPa	10.0
	导热油质量流量 $q m, o i l, 0$ /(kg·s^-1)	26.87		入口阻力系数K/(kg·s^-1·Pa^-1)	10 000
	传热系数X₀/(kJ·K^-1)	199
	压力损失ΔP₀/Pa	2 000

Table 2

Fig.4

Table 3

Fig.5

Table 4

Fig.6

Fig.8

Fig.9

Fig.10

Fig.11

Fig.12

References 15

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符号	定义	单位	符号	定义	单位
w	功率	kW	n	转速	r/min
c_p	定压比热容	kJ·kg/K	Q	换热量	kW
κ	比热容比		Δ	参数差值
T	温度	K	u	比内能	kJ/kg
ε	压比		ρ	密度	kg/m³
η	效率		c	空气流速	m/s
h	焓	kJ/kg	V	体积	m³
P	压力	MPa	v	比体积	m³/kg
w	功率	kW	φ	阻力系数
q_m	质量流量	kg/s	s	比熵	kJ/( kg·K)
τ	时间	s或h	E_n	能量	MJ
G	折合流量	m·s·K^0.5	E_x	㶲	MJ

部件	能量	数值/MJ
C1	压缩机耗功,E_n,in,C1	7.918
C2	压缩机耗功,E_n,in,C2	7.922
C3	压缩机耗功,E_n,in,C3	8.070
HX1	导热油储热,E_n,out,HX1	-7.358
HX2	导热油储热,E_n,out,HX2	-8.275
HX3	导热油储热,E_n,out,HX3	-8.637
Air	空气焓差,E_n,in,air	0.361
压缩过程总能量	0

部件	能量	数值/MJ
C1	压缩机㶲输入,E_x,in,C1	7.918
	压缩机㶲损失,E_x,des,C1	-0.980
C2	压缩机㶲输入,E_x,in,C2	7.922
	压缩机㶲损失,E_x,des,C2	-0.963
C3	压缩机㶲输入,E_x,in,C3	8.070
	压缩机㶲损失,E_x,des,C3	-1.035
HX1	换热器㶲输出,E_x,out,HX1	-1.432
	换热器㶲损失,E_x,des,HX1	-0.501
HX2	换热器㶲输出,E_x,out,HX2	-1.539
	换热器㶲损失,E_x,des,HX2	-0.668
HX3	换热器㶲输出,E_x,out,HX3	-1.572
	换热器㶲损失,E_x,des,HX3	-0.681
Air	空气㶲输出,E_x,out,air	-14.537
压缩过程总㶲		0

Modeling, simulation and dynamic analysis of the energy stage of advanced adiabatic compressed air energy storage system

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