1、某台球团冷却风机异常振动原因分析及治理One billiard ball regiment cooling fan abnormal vibration cause analysis and governance摘要：介绍某钢铁厂 1 台球团冷却风机振动故障情况，分析了风机振动大的原因，简述了动平衡过程，并对动平衡过程中出现的异常情况进行了分析。指出试加重量较轻及滚动轴承故障容易导致影响系数分散度大，进而影响动平衡精度和效率。Abstract: the article introduces one billiard ball cooling fan vibration fault situat
2、ion for a certain steel works, analyzes the reasons of the fan vibration, dynamic balance process is briefly described, and the dynamic balance in the process of abnormal situation is analyzed. Try point out with lighter weight and rolling bearing fault is easy to cause influence coefficient dispers
3、ion, affect dynamic balancing precision and efficiency. 关键词：球团风机；动平衡；影响系数；滚动轴承Key words: pellets fan; Dynamic balance; Influence coefficient; Rolling bearing 中图分类号：TH432 文献标志码：BChinese library classification number: TH432 literature symbol code: B Abnormal Vibration Analysis and Troubleshooting of a
4、 Pelletizing Cooling Fanhttp:/ http:/ Vibration Analysis and Troubleshooting of a Pelletizing Cooling Fan Abstract: This paper introduces the vibration fault of 1# pelletizing cooling fan in a steel plant. The cause of serious vibration of the fan is analyzed. The fan dynamic balance process is give
5、n and the abnormal phenomenon during dynamic balance process is analyzed. Too small trial balance weight and rolling bearing fault can cause large dispersion of influence coefficients, and then influence balance accuacy and efficiency.Abstract: This paper introduces the vibration fault of 1 # pellet
6、izing cooling fan in a steel plant. The cause of serious vibration of the fan is analyzed. The fan dynamic balance process is given and the abnormal phenomenon during dynamic balance process is analyzed. The Too small trial balance weight and rolling bearing faults can cause large dispersion of infl
7、uence coefficients, and then influence the balance accuacy and efficiency. Key words: pelletizing fan; dynamic balance; influence coefficient; rolling bearingKey words: pelletizing fan; The dynamic balance; Influence coefficient; Rolling bearing 0 引言0 the introduction 球团矿的冷却是钢铁厂竖炉生产过程中的重要环节之一，主要http
8、:/ http:/ 。本文通过对某台球团冷却风机振动问题的测试分析，提出了风机动平衡试验时试加重质量及角度合理选择方法，对动平衡试验影响系数分散度大和风机滚动轴承振动信号频谱丰富等问题进行了分析并提出了处理意见，可为同型风机故障治理提供参考。Pellets of cooling is one of the important link of steel shaft furnace production process, the main cooling device for cooling fan, its safe operation has great influence to the p
9、rocess of production. Cooling fan is bad work environment, prone to various faults 1-2. This article through to a billiards ball of cooling fan vibration test and analysis, put forward the wind dynamic balance test, try increasing the quality and the Angle of reasonable selection method, the coeffic
10、ient of dispersion effect on dynamic balance test and fan rolling bearing vibration signal spectrum, this paper analyzed the problems of the rich and puts forward the processing opinion, can provide reference for same type fan fault management. 1 球团冷却风机振动现象分析One pellet cooling fan vibration phenomen
11、on analysis 某厂 2#球团冷却风机结构参数为：叶轮直径 1 260 mm，转子质量 400kg，转子两端间距 1 200mm，工作转速 2 980r/min。风机转子采用悬臂布置，由滚动轴承支撑，轴系结构见图 1。http:/ http:/ parameters of the plant 2 # pellet cooling fan for: impeller phi 1 260 mm in diameter, rotor quality is 400 kg, spacing of 1 200 mm on both ends of the rotor, work speed 980
12、 r/min. Fan rotor arranged cantilever, supported by rolling bearings, shaft system structure as shown in figure 1. 2011 年 3 月 5 日，该风机因叶片故障而被迫停机。更换备用叶轮开机后，振动变大。风机侧轴承垂直方向通频幅值最大达到90m，严重影响了风机的安全运行。为了深入分析风机振动原因，在风机转子两轴承上分别布置垂直、水平传感器，并在 2#轴承垂直方向布置键相传感器，测点布置见图 2。On March 5, 2011, and was forced to stop by
13、the failures of the blades of the fan. Replacement spare impeller after boot, vibration. Fan side bearing vertical frequency amplitude maximum of 90 microns, seriously affect the safe operation of the fan. For in-depth analysis of fan vibration reasons, decorate in the fan rotor, respectively on two
14、 bearing vertical and horizontal sensors, and decorate in the 2 # bearing vertical direction key http:/ http:/ measuring point layout as shown in figure 2. 图 3 给出了该冷却风机定速后的原始振动频谱图。可以看出，测点振动信号中除了含有较大幅度的工频分量外，还含有丰富的低频和高频分量。工作转速下运行半小时，各测点工频分量幅值和相位约有 5%20% 的波动。Figure 3 shows the cooling fan after the co
15、nstant speed of the original vibration spectrum. It can be seen that measuring point vibration signal in addition to contain power frequency components significantly, also contain rich low-frequency and high-frequency components. The working speed run half an hour, the power frequency component ampl
16、itude and phase of measuring points, about 5% 20% of volatility. http:/ http:/ 振动原因初步分析2 vibration reasons for preliminary analysis 从图 3 中可以看出，振动信号中频率成分很丰富，轴承振动烈度很大。滚动轴承由内圈、外圈、滚动体及保持架组成。滚动轴承运行一段时间后，容易出现内、外圈松动、轴承径向游隙过大等故障3-7 。此时，转子滚动轴承系统将会处于比较严重的非线性状态，系统动力响应比较复杂8 ，在转子不平衡力强迫激励作用下，有可能会因此而激发出二倍频、三倍频等频率分
17、量，导致频谱丰富。在这种情况下，可以首先通过动平衡方法降低转子上不平衡激励力。基频振动降下来后，其他频率分量有可能会随之而降下来。Can be seen from figure 3, the vibration signals in the frequency content is very rich, bearing vibration intensity is very large. Roller bearing inner ring, outer ring, rolling elements and cage. Rolling bearings run after period of t
18、ime, prone to inner and outer ring is loose, excessive bearing radial clearance on the failure 3. At this point, the rotor - bearing system will be in a state of serious nonlinear, dynamic response is complicated system 8, the rotor unbalance force under the forced vibration, may thus inspired twice
19、 or three times frequency and other frequency component, and lead to rich spectrum. In this case, you can firstly reduce unbalanced exciting force on the rotor dynamic balance method. The fundamental frequency vibration after down, other frequency components are likely to http:/ http:/ and come down
20、. 3 风机动平衡过程分析3 wind dynamic balance process analysis 3.1 试加重方案的合理确定3.1 try to accentuate the reasonable solution 虽然由动平衡理论可知，试加重的大小和角度可以任意选取，但为了提高动平衡效率，减少开机次数，首次试加重的合理选择非常重要。Although the dynamic balance theory shows that try to increase the size and Angle can be arbitrary selection, but in order to i
21、mprove the efficiency of dynamic balance, decrease The Times of boot for the first time, try increasing the reasonable choice is very important. 加重质量的选取与风机转速、加重半径等有关。没有经验时，可参照下式选取Increase the quality of select and fan speed, increasing radius and so on. There is no experience, can be reference to th
22、e type selection http:/ http:/ 为加重质量，kg；M 为风机转子质量，kg； 为风机角速度，rad/s； r 为加重半径，m；g 为重力加速度，m/s2。Type: m to increase quality, kg; M for the quality of fan rotor, kg; For fan angular velocity omega, rad/s; R to increase radius, m; G is acceleration of gravity, m/s2. 本台风机，振动最大值出现在 1#测点垂直，在叶轮的外圆加重。将已知数据代入式（
23、1） ，则试加重质量：This fan, the maximum value appeared in 1 # point vertical vibration, the impeller outer circle. The known data plug in type (1), try increasing the quality: m=(0.14009.8)/(22980/60)20.636.4gM = (0.1 x 400 x 9.8) / (2 PI (2980/60) 2 x 0.63 material 6.4 g 考虑到该加重量偏轻，实际试加时将加重量放大了 3 倍，即取试加重量为
24、 18g。Considering the partial light in weight, the actual trial overtime magnified by 3 times, will add weight 18 g means try add weight. 试加重角度直接影响到动平衡效率。试加重角度正确，加重后振动减小，可以为后续方案调整创造有利条件。http:/ http:/ increasing Angle directly affect the efficiency of dynamic equilibrium. Try increasing Angle is corre
25、ct, aggravating after vibration is reduced, can adjust the create favorable conditions for subsequent solutions. 由测振仪相位定义及转子动力学理论可知，采取如图 2 所示的传感器布置方式并考虑垂直振动时，不平衡力所在角度与键相标记之间的关系为1Defined by the vibration phase and rotor dynamics theory, take the sensor arrangement as shown in figure 2 and consider ve
26、rtical vibration, the unbalanced force is the relationship between the phase angles and key tags for 1 - （2）Phi alpha delta (2) 式中： 为不平衡力与键相标记之间夹角； 为振动相位； 为滞后角。动平衡配重位于不平衡力的反向，即：Type: phi for unbalanced force and the key phase Angle between tags; Alpha to vibration phase; The delta for lag Angle. Dyn
27、amic balancing counterweight is located on the reverse of unbalanced force, namely: 1+180-+180 （3）From 1 = + + 180 180 = alpha delta (3) 由此可见，滞后角 值直接影响加重角度。滞后角的选取与平衡转速距离临界转速的远近程度、支撑特性和转子结构形式等有关。http:/ http:/ 。对于悬臂布置的系统而言，参照同型风机，滞后角 可暂取 0。Thus, lag Angle values directly affect the compound Angle. The
28、 selection of lagging Angle and balance speed degree, support features and distances from the critical speed of the rotor structure and so on. For adopt rigid support system on both ends, when balancing speed is less than the critical speed, the delta 0 90 ; Near the critical speed, the delta 90 mat
29、erial; When balancing speed is greater than the critical speed, 90 “delta“ 180 9. For cantilever layout system, the reference to same type fan, lag Angle can temporarily take 0 . 以 1#测点垂直振动为准，求出的加重角度：1=210-0 +180=390即试加重角度取为 30。Will be subject to 1 # vertical vibration measuring point, and the incre
30、ase of Angle: phi 1 = 210 0 180 + = off for 30 390 or try increasing Angle. 3.2 动平衡过程分析3.2 analysis of dynamic balancing process 本台风机动平衡工作开展得不是很顺利，共进行了 4 次，见表1。现对其中的原因加以分析。This typhoon dynamic balance cant work very well, were conducted four http:/ http:/ as shown in table 1. Now on the reason analy
31、sis. 表 1 四次动平衡试验加重数据汇总 mDynamic balance test four times heavier data summary table 1 mu m 备注：以上加重方案均在风机工作转速下进行，每次加重时，前面的配重都保留。Note: the above compound solutions are, under the fan working speed every time aggravating, in front of the counterweight is retained. 影响系数是指在转子零度方向、1m 半径处加单位质量所引起的振动变化量。影响系数
32、取决于转子结构、转速、支撑系统刚度、阻尼等因素。上述参数不变时，影响系数应该基本保持不变10 。加重过程中，影响系数分散度较小是动平衡工作的前提条件。Influence coefficient refers to the direction of rotor is zero, at 1 m radius and vibration caused by unit mass variation. Influence coefficient http:/ http:/ on the rotor structure, the stiffness and damping factors such as
33、speed, supporting system. These parameters constant, the influence coefficient should remain the same basic 10. Aggravate in the process, influence coefficient smaller dispersion is a prerequisite for dynamic balance work. 表 2 给出该风机四次加重求出的影响系数。图 4 给出各测点加重的影响系数矢量图。Table 2 shows the four aggravating a
34、nd the influence coefficient of the fan. Figure 4 shows the influence of each measuring point increase coefficient vector diagram. 可以看出，4 次加重求出的影响系数分散度较大。1#测点水平影响系数相位差达到 190，接近相反。影响系数幅值相差 3 倍多。http:/ http:/ 110。2#测点水平影响系数幅值和相位都相差较大。影响系数幅值和相位的分散度大直接导致动平衡计算时的误差较大。As you can see, 4 times increase and t
35、he influence coefficient of dispersion is bigger. 1 # point level influence coefficient of phase difference of 190 , close to the opposite. Influence coefficient amplitudes vary more than 3 times. 2 # point vertical influence coefficient amplitude though the difference is not big, but nearly 110 Ang
36、le difference. 2 # point level influence coefficient of amplitude and phase are comparatively large difference. Big influence coefficient of amplitude and phase dispersion directly lead to dynamic balance calculation error is larger. 3.3 影响系数分散度大的原因分析3.3 influence coefficient of dispersion of root c
37、ause analysis 该风机两侧轴承采用滚动轴承。运行一段时间后，滚动轴承有可能出现内圈、外圈松动、轴承游隙过大等现象。实践表明：此时会出现振动波动或两次启停振动有一定程度差异。如果动平衡试加重量较轻，加重所引起的振动变化有可能被滚动轴承故障引起的不稳定振动所掩盖，这将会导致所计算出的影响系数误差大。以本台风机动平衡试验为例，第 1 次加重质量只有 18g，根据该影响系数http:/ http:/ 2 次加重方案实施后效果也不理想。第 3 次加重 42g 后振动幅值和相位变化幅度较大，加重影响明显，由此求出的影响系数比较准确，并使得第 4 次调整取得了较好效果。因此，为了取得合理的影响系
38、数，试加重质量不能太轻。特别是对于运行了一段时间，采用滚动轴承支撑的机组而言。On both sides of the bearing adopts rolling bearing of the fan. Run after a period of time, likely loose inner ring, outer ring, rolling bearings and bearing clearance is too large. Practice shows that appears vibration wave or two rev. Stop a certain degree. I
39、f the dynamic balancing test and lighter weight, increase caused by the vibration change is likely to be overshadowed by the unstable vibration of rolling bearing failure cause, it will lead to great error in the influence coefficient calculated by. Dynamic balance test to the typhoon as an example,
40、 the first increase quality only 18 g, according to the influence coefficient and the second scheme after aggravating effect is not ideal. After third time increase 42 g vibration amplitude and the phase change range is larger, aggravating effect obvious, thus find out the influence coefficient more
41、 accurate, and making his fourth adjustment has obtained the good effect. Therefore, in order to obtain reasonable influence coefficient, try increasing the quality not too light. Especially for running a period of time, using the rolling bearing support unit. 4 动平衡后的振动频谱分析http:/ http:/ after the dy
42、namic balance of vibration spectral analysis 动平衡前，各测点振动信号频谱丰富。图 5 给出第 4 次动平衡试验后的振动频谱图。比较图 3 可以看出，各测点振动均达到优秀水平。虽然频谱中仍有一些低频和高频分量，但其幅值已经大大降低。这一现象曾在我们处理过的多台机组上发生，说明风机轴承上的杂频分量确实是由于转子不平衡力激励所致。Dynamic balance, the measuring point vibration signal spectrum is rich. Figure 5 shows the vibration of dynamic ba
43、lance test 4 times spectrum figure. Comparison can be seen in figure 3, each measuring point vibration to achieve good level. Although there are still some of the spectrum of low frequency and high frequency components, but its amplitude has been greatly reduced. This phenomenon have on more units t
44、hat we processed, explains the fan bearings on the noise frequency component is really due to rotor unbalanced force motivation. 5 风机故障治理总结5 fan fault management http:/ http:/ 对于采用滚动轴承支撑的风机转子而言，滚动轴承内、外圈松动等故障容易导致振动波动，较轻的加重质量所引起振动变化有可能被滚动轴承故障所掩盖，由此导致计算出的加重影响系数误差大，并导致动平衡工作困难。试加重量应尽可能重些。1) for the fan t
45、he rotor adopts rolling bearing support, inner and outer ring rolling bearing looseness of fault vibration fluctuation, easy to cause the deterioration of the lighter quality caused by the vibration change is likely to be concealed by a rolling bearing fault, leading to calculate the aggravating eff
46、ect coefficient error is large, and causes the dynamic balance work difficult. Try to add as much as possible should be heavier in weight. 2） 该型风机叶轮上加重对两个轴承振动的影响近似同相。以近风机侧测点为例，振动高点与不平衡力之间的滞后角约2535。每 1kg 加重所引起的垂直和水平振动变化分别约为300m 和 540m。这些结论可为同型风机动平衡提供指导。2) the type air blower impeller on aggravating t
47、he impact on the two bearing vibration approximation in phase. Near the fan side station as an example, the vibration between the high and unbalanced force lag Angle about 25 to 35 . Each 1 kg increase vertical and horizontal vibration caused by the change of about 300 mu mu m and 540 m respectively. These conclusions can provide guidance for same typ
