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Analysis of main influencing factors of vibration acceleration of porous electrode electrostatic precipitators
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摘要: 针对烧结机头烟气净化所使用的多孔电极电除尘器内部由二次扬尘效应所带来的颗粒物排放浓度不稳定的问题，优化振打装置结构及参数可提高除尘性能，保证多孔电极电除尘器高效稳定运行。通过物理实验和数值分析研究了振打锤、振打砧质量、锤臂长度以及悬挂方式对板表面切向振打加速度的影响。研究结果表明：随振打锤质量增加，板表面切向振打加速度平均值提升了50%；板表面切向振打加速度随着振打砧质量增加而减小，振打砧质量从4.4 kg增加到5.4 kg，板表面平均切向振打加速度降低10%，下降幅度较大，振打砧质量大于5.4 kg后，降低幅度显著减小；板表面平均切向振打加速度随振打锤臂长增大增长18.2%；单点偏心吊挂的板表面切向振打加速度大于最小振打加速度设计值180 g，相对均方根小于0.4。为满足工业烧结机头烟气除尘需求，采用单点偏心悬挂，使用质量为14.83 kg、锤臂长度为335 mm的振打锤，结合质量为4.4 kg振打砧的振打装置最优。该研究结果可为多孔电极电除尘器在烧结机头超低排放设计应用提供设计参考。Abstract: The problem of unstable particulate emission concentration in the porous electrode electrostatic precipitator （ESP） used for flue gas purification in the header of the sintering machine， is usually caused by the effect of secondary dust lifting. the optimization of the structure and parameters of the vibration device can improve the performance of the dust removal and ensure the high efficiency and stable operation of the porous electrode ESP. Through physical experiments and numerical analysis， the effects of vibration hammer， vibration anvil mass， hammer arm length and suspension method on the tangential vibration acceleration on the plate surface were investigated. The results showed that： with the increase of the vibrating hammer mass， the average tangential acceleration of the plate surface increased by 50%； the tangential acceleration of the plate surface decreased with the increase of the vibrating anvil mass； with an increase of the vibrating anvil mass from 4.4 kg to 5.4 kg， the average tangential acceleration of the plate surface reduced by 10%， and when the vibrating anvil mass exceeded 5.4 kg， the decrease extent reduced significantly； the average tangential acceleration of the plate surface increased with the length of the vibrating hammer arm. The average tangential vibration acceleration of the plate surface increased by 18.2% with the increase of the arm length of the hammer； the tangential vibration acceleration of the plate surface with single-point eccentric suspension was larger than the minimum design value of vibration acceleration of 180 g， and the relative root-mean-square was less than 0.4. In order to meet the requirements of the flue gas de-dusting of the header of the industrial sintering machine， it was optimal to adopt the vibration device with single-point eccentric suspension， a vibration hammer with the mass of 14.83 kg， the length of the arm of 335 mm， in combination with a vibration anvil with a mass of 4.4 kg. This study can provide a reference basis for the design and application of porous electrode ESPs in the ultra-low emission design of sinter headers.
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2 多孔板振打紧固连接下的监测点布置
2. Arrangements of monitoring points on the porous plate vibration device with tight connections
6 C型板解析解和数值解相对误差
6. Relative errors of analytical solutions and numerical solutions of C-plates
7 多孔板实测值与解析解相对误差
7. Relative errors between measured values and analytical solutions for porous plates
8 不同振打锤质量下板表面平均切向振打加速度
8. The average tangential vibration acceleration of plate surfaces under different vibration hammer massed
9 直柄圆形振打锤几何形状
9. The geometric shape of the circular vibrating hammer with straight handle
11 不同振打砧质量下的板表面平均切向振打加速度
11. Average tangential vibration acceleration of plate surfaces under different vibration anvil masses
12 不同振打锤臂长度下板表面平均切向振打加速度
12. Average tangential vibration acceleration of plate surfaces under different vibration hammer arm lengths
13 单点偏心悬挂振打结构及其监测点分布
13. A vibration structure with single-point eccentric suspension and its monitoring points
14 不同悬挂方式下的板表面平均切向振打加速度
14. Average tangential vibration acceleration of plate surfaces under different suspension modes
1 仪器参数
1. Instrument parameters
仪器设备名称 量程 准确度 YE6231G信号采集器 -10~10 Vp ±0.5% CA-YD-180压电式加速度计 -1000~1000 g ±0.1 g 
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2 C型板解析解与数值解对比
Table 2 Comparisons of analytical solutions and numerical solutions for C-plates g 测点序号 极板一 极板二 极板三 极板四 极板五 极板六 极板七 极板八 解析解 数值解 解析解 数值解 解析解 数值解 解析解 数值解 解析解 数值解 解析解 数值解 解析解 数值解 解析解 数值解 5 365 344 292 300 264 273 249 263 235 253 212 230 187 200 455 436 4 486 474 432 421 402 393 376 384 352 343 335 345 281 293 234 247 3 461 471 405 398 375 365 356 345 336 322 375 376 305 321 261 285 2 457 468 416 409 368 377 325 344 291 304 314 330 246 255 331 347 1 626 619 579 586 526 513 474 481 426 411 486 485 446 450 310 326
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3 多孔板实测值与数值解对比
Table 3 Comparisons of measured values and numerical solutions for porous plates g 测点序号 极板一 极板二 极板三 极板四 极板五 实测值 数值解 实测值 数值解 实测值 数值解 实测值 数值解 实测值 数值解 6 77 83 72 73 69 75 72 68 68 71 5 155 166 142 153 113 124 117 108 106 98 4 249 259 220 235 201 223 202 185 183 167 3 320 342 282 268 250 243 252 231 236 222 2 422 436 380 391 347 370 359 356 327 332 1 588 613 512 527 452 485 466 443 434 427
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4 偏心吊挂下的板表面切向振打加速度分布
4. Tangential vibration acceleration distribution of plate surfaces under eccentric suspension
测点序号 极板一 极板二 极板三 极板四 极板五 6 237 221 213 199 186 5 223 247 235 224 206 4 269 263 268 231 213 3 271 236 283 273 253 2 435 369 325 337 291 1 630 596 553 510 493
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