压缩空气储能系统双悬臂转子动平衡方法研究

doi:10.19799/j.cnki.2095-4239.2024.1238

储能科学与技术 ›› 2025, Vol. 14 ›› Issue (5): 1954-1968.doi: 10.19799/j.cnki.2095-4239.2024.1238

压缩空气储能系统双悬臂转子动平衡方法研究

毛豪杰¹^,²(), 张雪辉²^,³(), 焦瀚晖²^,³, 李和平¹(), 刘彦¹, 陈海生²^,³

^1.杭州电子科技大学能源研究所，浙江杭州 310018
^2.中国科学院工程热物理研究所，北京 100190
^3.中国科学院长时规模储能重点实验室，北京 100190

收稿日期:2024-12-26 修回日期:2025-01-25 出版日期:2025-05-28 发布日期:2025-05-21
通讯作者: 张雪辉,李和平 E-mail:maohaojie@hdu.edu.cn;zhangxuehui@iet.cn;peacelee@hdu.edu.cn
作者简介:毛豪杰（2000—），男，硕士研究生，研究方向为转子动力学，E-mail：maohaojie@hdu.edu.cn；
基金资助:
国家自然科学基金(52306285);山东能源研究院企业联合基金(SEI U202301);中国科学院国际合作局对外合作重点项目(117GJHZ2023009MI)

Study on dynamic balancing method of double cantilever rotor in compressed air energy storage system

Haojie MAO¹^,²(), Xuehui ZHANG²^,³(), Hanhui JIAO²^,³, Heping LI¹(), Yan LIU¹, Haisheng CHEN²^,³

^1.Institute for Energy Studies, Hangzhou Dianzi University, Hangzhou 310018, Zhejiang, China
^2.Institute of Engineering Thermophysics, Chinese Academy of Sciences, Beijing 100190, China
^3.Key Laboratory of Long-Duration and Large-Scale Energy Storage, Chinese Academy of Sciences, Beijing 100190, China

Received:2024-12-26 Revised:2025-01-25 Online:2025-05-28 Published:2025-05-21
Contact: Xuehui ZHANG, Heping LI E-mail:maohaojie@hdu.edu.cn;zhangxuehui@iet.cn;peacelee@hdu.edu.cn

摘要/Abstract

摘要：

压缩空气储能(CAES)系统具有规模大、效率高等特点，被认为是最具发展潜力的大规模储能技术之一。整体齿式压缩机作为CAES系统的核心装备之一，其双悬臂转子的稳定性越来越受到人们的重视。为解决转子两端悬挂叶轮不平衡量引起的转子振动报警，通常选用多平衡面现场动平衡，而多平面平衡操作复杂且启停次数多，为简化平衡过程、延长双悬臂转子使用寿命，本工作对CAES系统双悬臂转子不平衡特性及动平衡方法进行了研究。首先，基于有限元分析软件对压缩机双悬臂转子进行了建模分析，研究表明对于双悬臂转子的双端不平衡，可解耦为单端不平衡进行平衡，从而避免生产过程中复杂的动平衡过程。然后，通过现场一端叶轮进行现场动平衡实验，对比了不同试重对轴系动平衡效果的影响，实验结果表明添加试重产生的振动幅值与相位变化量越大，计算所得配重的平衡效果越好。最后，在另一端叶轮完全模拟现场实际情况对叶轮出厂原始不平衡量进行盲平，验证了本研究方法的有效性和普适性，平衡效率达到84.01%。

关键词: 压缩空气储能, 转子动力学分析, 双悬臂转子, 现场动平衡, 影响系数法

Abstract:

Compressed air energy storage (CAES) systems are recognized for their large-scale capacity and high efficiency, making them one of the most promising technologies for large-scale energy storage. Within a CAES system, the stability of the double-cantilever rotor in the integral gear compressor is a critical focus area. To address rotor vibration alarms caused by the unbalance of the suspended impellers at both ends of the rotor, the multibalance plane field dynamic balancing is usually employed. However, to simplify the balancing process and prolong the service life of double-cantilever rotors, this study investigates the unbalance characteristics and dynamic balancing methods of double-cantilever rotors in CAES systems. First, a model analysis of the double-cantilever rotor of the compressor was carried out using finite element analysis software. The research shows that unbalance at both ends of the double-cantilever rotor can be decoupled into single-end unbalances. This approach eliminates the need for complex dynamic balancing during production. Next, a field dynamic balancing experiment was performed, focusing on one end of the impeller. The study compared the effects of different test weights on the shafting's dynamic balance performance. Experimental results show that greater vibration amplitude and phase changes caused by the addition of test weights led to improved balance effects when determining counterweights. Finally, at the other end of the impeller, the original unbalance of the impeller was completely simulated based on real-world conditions. This validated the effectiveness and universality of the research method. The balance efficiency reached 84.01%.

Key words: compressed air energy storage, rotor dynamics analysis, cantilever rotor, field dynamic balancing, influence coefficient method

中图分类号:

TH 113

毛豪杰, 张雪辉, 焦瀚晖, 李和平, 刘彦, 陈海生. 压缩空气储能系统双悬臂转子动平衡方法研究[J]. 储能科学与技术, 2025, 14(5): 1954-1968.

Haojie MAO, Xuehui ZHANG, Hanhui JIAO, Heping LI, Yan LIU, Haisheng CHEN. Study on dynamic balancing method of double cantilever rotor in compressed air energy storage system[J]. Energy Storage Science and Technology, 2025, 14(5): 1954-1968.

图/表 37

图1

图2

图3

表1

双悬臂转子主要参数"

部件	参数	数值	部件	参数	数值
一级叶轮	质量/kg	2.003	齿轮段	长度/mm	125
	直径转动惯量/kg· $m m 2$	3611		齿数	25
	极转动惯量/kg· $m m 2$	6159		齿轮旋向	左
二级叶轮	质量/kg	1.753	总轴段	长度/mm	854.01
	直径转动惯量/kg· $m m 2$	2680		质量/kg	27.829
	极转动惯量/kg· $m m 2$	4602		振动报警值/ $μ m$	40
配重盘	质量/kg	0.2749		振动停机值/ $μ m$	50
	直径转动惯量/kg· $m m 2$	212.65		额定转速/(r/min)	32620
	极转动惯量/kg· $m m 2$	408.26

表1

图4

图5

表2

图6

图7

图8

图9

图10

图11

图12

图13

图14

图15

图16

图17

图18

表3

表4

图19

图20

图21

表5

图22

图23

图24

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图26

图27

图28

表6

0.9g/183°试重下各转速振动"

转子转速	传感器5振动	传感器6振动
6000 r/min	2.24 $μ m$ /-57.48°	1.83 $μ m$ /35.79°
8000 r/min	3.79 $μ m$ /-65.93°	3.89 $μ m$ /40.45°
10000 r/min	4.59 $μ m$ /-87.97°	7.69 $μ m$ /24.62°

表6

表7

图29

图30

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参数	数值
轴向长度/mm	60
轴直径/mm	60
半径间隙/mm	0.09
瓦块数	4
瓦块包角/(°)	72

变量	数值
实验1(不同试重质量)	0.72 g/-90°
实验1(不同试重质量)	0.91 g/-90°

实验2(不同试重角度)	0.72 g/-60°
	0.72 g/-90°
	0.72 g/-120°

实验号	试重	转子转速	传感器7计算配重	传感器8计算配重	实际加重
实验1	0.72 g/-90°	6000 r/min	4.21 g/230.83°	4.58 g/222.08°	4.7 g/234.35°
		8000 r/min	4.34 g/235.03°	4.47 g/231.79°
		10000 r/min	4.62 g/236.64°	5.16 g/244.54°

实验2	0.91 g/-90°	6000 r/min	4.51 g/234.94°	4.47 g/221.6°	4.56 g/230.45°
		8000 r/min	4.02 g/232.98°	3.97 g/222.1°
		10000 r/min	5.48 g/236.38°	4.44 g/226.2°

实验号	试重	转子转速	传感器7计算配重	传感器8计算配重	实际加重
实验3	0.72 g/-60°	6000 r/min	2.89 g/228.74°	3.23 g/224.49°	2.84 g/229.75°
		8000 r/min	2.48 g/232.47°	2.61 g/225.63°
		10000 r/min	3.09 g/235.17°	2.70 g/231.95°

实验4	0.72 g/-120°	6000 r/min	7.66 g/232.9°	6.94 g/216.08°	6.23 g/235.96°
		8000 r/min	6.6 g/234.5°	6.44 g/218.31°
		10000 r/min	4.81 g/265.67°	4.92 g/248.33°

转子转速	传感器5计算配重	传感器6计算配重
6000 r/min	1.47 g/258.69°	1.17 g/235.6°
8000 r/min	1.06 g/272.14°	1.05 g/242.5°
10000 r/min	0.78 g/280.46°	1.06 g/243.14°

压缩空气储能系统双悬臂转子动平衡方法研究

Study on dynamic balancing method of double cantilever rotor in compressed air energy storage system

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