Characteristics of Vibration and Sound Radiation for Railway Wheels Considering Wear and Unequal Thickness Web Plate
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摘要: 为了降低轨道车轮振动的声辐射,以双S型辐板车轮为研究对象,建立了反映磨耗及不等厚辐板的9种城市轨道车轮三维有限元模型,分别获得了车轮在各阶振动模态下的固有频率及结构振型,对比分析了不同车轮的声功率级响应曲线,从而得到车轮在不同磨耗条件及不等厚特征情况下的声辐射水平。研究结果表明:与初始现役车轮相比,辐板上部不等厚车轮在峰值声功率级上降低了13.82 dBA;随着踏面磨耗加深,车轮的噪声逐渐增大;辐板上部不等厚车轮在不同磨耗下的最大声功率级均小于初始现役车轮。Abstract: To reduce the sound radiation of rail wheel vibration, taking the dual S-type web wheels as the research object, 9 types 3D finite element models of urban rail wheels reflecting the wear and unequal thickness of the spokes have been established. Based on the finite element model, the natural frequencies and structural modes of the wheel in each vibration mode were obtained, and the sound power level response curves of different wheels were compared and analyzed to obtain sound radiation level of the wheels under different wear conditions and unequal thickness characteristics. The research results show that: compared with the initial active wheels, the peak sound power level of the wheels with unequal thickness on the upper part of the spoke plate is reduced by 13.82 dBA; as the tread wear deepens, the noise of the wheels increases gradually; the maximum sound power level of wheels with unequal thickness on the upper part of the spoke plate under different wear is less than that of the initial active wheels.
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Key words:
- wheel rail noise /
- urban rail wheel /
- sound radiation /
- abrasion /
- unequal thickness web plate
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表 1 不等厚辐板车轮轴向振动模态的固有频率
Table 1. The natural frequency distribution of wheel axial vibration modes
Hz 轴向模态
(m, n)初始
车轮上部
不等厚中部
不等厚下部
不等厚(0, 0) 319 335 378 444 (0, 1) 205 216 242 299 (0, 2) 403 425 431 424 (0, 3) 1080 1115 1101 1079 (0, 4) 1940 1991 1960 1935 (0, 5) 2897 2897 2919 2888 (0, 6) 3906 4007 3932 3892 (1, 0) 1735 1827 1700 1839 (1, 1) 1960 2174 1927 2010 (1, 2) 2443 2711 2384 2488 (1, 3) 3175 3459 3064 3238 (1, 4) 4101 4425 4077 4170 表 2 不等厚辐板车轮径向振动模态的固有频率
Table 2. The natural frequency distribution of wheel radial vibration modes
Hz 径向模态
(r, n)初始车轮 上部
不 等厚中部
不 等厚下部
不 等厚(r, 0) 2366 2617 2662 2474 (r, 1) 829 841 1061 1146 (r, 2) 1358 1358 1719 1630 (r, 3) 2075 2249 2502 2202 (r, 4) 2850 3146 3209 2881 (r, 5) 3683 4083 3960 3663 表 3 不等厚辐板车轮周向振动模态的固有频率
Table 3. The natural frequency distribution of wheel circumferential vibration modes
Hz 周向模态
(c, n)初始车轮 上部
不等厚中部
不等厚下部
不等厚(c, 0) 549 542 568 675 表 4 磨耗车轮轴向振动模态的固有频率
Table 4. The natural frequency distribution of wheel axial vibration modes
Hz 轴向模态(m, n) 初始车轮 轻微磨耗 严重磨耗 极限磨耗 (0, 0) 319 342 371 403 (0, 1) 205 223 246 272 (0, 2) 403 393 380 360 (0, 3) 1080 1053 1011 944 (0, 4) 1940 1897 1824 1706 (0, 5) 2897 2835 2729 2550 (0, 6) 3906 3822 3681 4350 (1, 0) 1735 1798 1859 1913 (1, 1) 1960 2025 2108 2188 (1, 2) 2443 2456 2467 2474 (1, 3) 3175 3137 3077 2976 (1, 4) 4101 4057 3981 3870 表 5 磨耗车轮径向振动模态的固有频率
Table 5. The natural frequency distribution of wheel radial vibration modes
Hz 径向模态(r, n) 初始车轮 轻微磨耗 严重磨耗 极限磨耗 (r, 0) 2366 2447 2563 2686 (r, 1) 829 881 957 1033 (r, 2) 1358 1423 1524 1621 (r, 3) 2075 2144 2261 2390 (r, 4) 2850 2888 2964 3026 (r, 5) 3683 3678 3675 3637 表 6 磨耗车轮周向振动模态的固有频率
Table 6. The natural frequency distribution of wheel circumferential vibration modes
Hz 周向模态(c, n) 初始车轮 轻微磨耗 严重磨耗 极限磨耗 (c, 0) 549 595 657 731 表 7 磨耗下上部不等厚车轮与初始车轮峰值声功率级
Table 7. Peak sound power levels of upper nonuniform thickness wheels and initial wheels under wear conditions
磨耗深度/mm 初始车轮/dBA 上部不等厚车轮/dBA 0 112.66 98.84 9.67 119.83 101.92 19.34 123.78 104.42 29.00 124.80 118.10 -
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