| 子系统参数对双层隔振系统隔振特性的影响 |
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| 引用本文： | 陈俊,丁杰,闫兵,王永胜,董大伟,华春蓉.子系统参数对双层隔振系统隔振特性的影响[J].交通运输工程学报,2018,18(3):114-128. |
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| 作者姓名： | 陈俊 丁杰 闫兵 王永胜 董大伟 华春蓉 |
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| 作者单位： | 1.株洲中车时代电气股份有限公司, 湖南 株洲 4120002.西南交通大学 机械工程学院, 四川 成都 6100313.西南交通大学 牵引动力国家重点实验室, 四川 成都 610031 |
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| 基金项目： | 国家自然科学基金项目51405399 |
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| 摘 要： | 为了阐明子系统参数对双层隔振系统隔振特性的影响, 建立了针对带子系统的双层隔振系统的三自由度动力学模型; 推导了一、二级主系统与子系统振幅比的解析式; 分析了3种振幅比随子系统质量比、固有频率比和阻尼比的变化规律; 给出了子系统充当双层隔振系统吸振器时最优参数的解析解和数值精确解; 以中国首批内燃动车动力包为研究对象, 探讨了散热器子系统的刚度、阻尼和质量对动力包双层隔振系统隔振性能以及柴油发电机组和散热器本身振动烈度的影响规律; 得到了最优散热器隔振器刚度的动力包双层隔振系统样机, 并进行了振动试验。试验结果表明: 散热器隔振器刚度大于拐点处刚度1.5倍会严重恶化子系统的振动情况, 其阻尼损耗系数取0.24左右能有效抑制双层隔振系统力传递率和振动烈度比的峰值, 取较大的散热器质量能有效提高双层隔振系统的隔振性能, 减小机组和散热器本身的振动烈度; 经过设计后, 停机工况下二级隔振器最大动反力减小50%, 常规工况下二级隔振器的实测最大动反力为296N, 优于同类水平, 常规工况下机组与散热器实测振动烈度最大值分别为15.45、4.97mm·s-1, 水平优秀。可见, 取较大的子系统质量和阻尼, 并将其视为双层隔振系统的吸振器进行优化设计, 可使双层隔振系统在柴油机启停机工况和常规工况下都具备较优的动力学性能。
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| 关 键 词： | 车辆工程 子系统 双层隔振系统 隔振特性 动力包 吸振器 |
| 收稿时间： | 2017-11-25 |
Effect of subsystem parameters on vibration isolation characteristics of two-stage vibration isolation system |
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| CHEN Jun,DING Jie,YAN Bing,WANG Yong-sheng,DONG Da-wei,HUA Chun-rong.Effect of subsystem parameters on vibration isolation characteristics of two-stage vibration isolation system[J].Journal of Traffic and Transportation Engineering,2018,18(3):114-128. |
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| Authors: | CHEN Jun DING Jie YAN Bing WANG Yong-sheng DONG Da-wei HUA Chun-rong |
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| Affiliation: | 1.Zhuzhou CRRC Times Electric Co., Ltd., Zhuzhou 412000, Hunan, China2.School of Mechanical Engineering, Southwest Jiaotong University, Chengdu 610031, Sichuan, China3.Statek-Key Laboratory of Traction Power, Southwest Jiaotong University, Chengdu 610031, Sichuan, China |
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| Abstract: | To determine the effect of subsystem parameters on the vibration isolation characteristics of a two-stage vibration isolation system (TSVIS), a three degrees-of-freedom (3-DOF) dynamics model of TSVIS with a subsystem was established. The analytical expressions for the amplitude ratio of the first-and second-stage main system and the subsystem were derived. The variation rules of these three amplitude ratios with the mass, natural frequency, and damping ratio of the subsystem were analyzed. The exact analytical and numerical solutions of the optimum parameters for the subsystem as an absorber on TSVIS were presented. The first batch of diesel railcar power packs in China were selected as the research objects, and the influences ofstiffness, damping, and mass of the radiator on the vibration isolation performance of the power pack TSVIS and the vibration intensities of the diesel generator set and radiator were investigated. The prototype of the power pack TSVIS with the optimum stiffness of the radiator isolator was obtained. A vibration test was carried out. Test result shows that a radiator vibration isolator stiffness greater than 1.5 times the turning point stiffness can seriously deteriorate the radiator's vibrations. A damping loss factor of approximately 0.24 can effectively restrain the vibration intensity and force transmission ratio peak of the TSVIS. A larger mass of the radiator can effectively improve the vibration isolation performance of the TSVIS and reduce the vibration intensities of both the diesel unit and the radiator. The maximum dynamic reaction force, under the stalling condition of the second-stage vibration isolator, reduces by 50%. The maximum measured dynamic reaction force of the second-stage vibration isolator under normal condition is 296 N, which is better than the current value. The maximum measured vibration intensities of the diesel unit and radiator under normal condition are 15.45 and 4.97 mm·s-1, respectively, which represents an exceptionally satisfactory level. Therefore, by employing a larger mass and damping of the subsystem, and optimizing the TSVIS by regarding it as a vibration absorber, can improve the dynamic performances of the TSVIS under diesel engine starting, stalling and normal conditions.43 figs, 25 refs. |
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