Shock and Vibration
Volume 2017 (2017), Article ID 1367683, 10 pages
https://doi.org/10.1155/2017/1367683

Research Article

Influence of Wheel Eccentricity on Vertical Vibration of Suspended Monorail Vehicle: Experiment and Simulation

Kaikai Lv, Kaiyun Wang, Zhihui Chen, Chengbiao Cai, and Lirong Guo

State Key Laboratory of Traction Power, Southwest Jiaotong University, Chengdu 610031, China

Correspondence should be addressed to Kaiyun Wang; kywang@swjtu.edu.cn

Received 28 July 2017; Revised 8 November 2017; Accepted 3 December 2017; Published 20 December 2017

Academic Editor: Abdul Qadir Bhatti

Copyright © 2017 Kaikai Lv et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

Abstract.

This paper investigates the influence of wheel eccentricity on vertical vibration of suspended monorail vehicle based on experiment and simulation. Two sets of tests are conducted in the first Chinese suspended monorail, and the tested acceleration is analyzed and exhibited. A multibody dynamic model of the suspended monorail vehicle is established to simulate the vertical vibration of car body excited by wheel eccentricity. The results show that there are three factors which may cause an abnormal vibration considering the track and the vehicle system. The influence of wheel eccentricity on the car body vibration was firstly analyzed. Simulated acceleration of car body has a great accordance with test. The wheel eccentricity could excite the resonance of car body at the speed of 21 km/h, and the vertical acceleration would increase considerably. Decreasing the secondary stiffness can effectively reduce the vertical vibration caused by wheel eccentricity, especially at the resonant speed. In the secondary test, the peak of car body acceleration at speed of 20 km/h is not appearing when only renewing the wheels, and the acceleration is decreasing obviously at the domain frequency. It is further determined that the abnormal vibration is mainly caused by the wheel eccentricity.

1. Introduction

Nowadays, most Chinese cities are facing the pressure of traffic jam. As to solve the problem, a large number of short-distance transportation systems are built, such as subways, light rail transit, bus rapid transit (BRT), maglev transit, and straddle monorail [1]. And now, another new transportation is developed, suspended monorail. This new form of transportation is researched and developed, and the experimental stage has been finished. Several problems of vehicle and monorail track were found and solved at the experimental stage, such as the wheel eccentricity.

Wheel eccentricity is mainly caused by misalignment in the fixation of the wheel during manufacturing or maintenance and is a special classification of wheel out-of-roundness (OOR) [2]. The wheel OOR is a common phenomenon in railway vehicles, which could cause high-frequency forces between wheel and rail with the increasing of the running speed [3–5]. In addition, under the certain periodic excitation, the running comfort of the vehicle is severely threatened [6, 7]. A number of scholars have been devoted to investigate the mechanism and the influence of wheel OOR in railway. Jin et al. [8] investigated the mechanism of the polygonal wear of metro train wheels based on experiment and structure model test, and the average passing frequency of a polygonal wheel is approximately close to the first bending resonant frequency of the wheelset, which is the main reason of the polygonal wear. More than 2000 wheels of seven types of locomotives widely used in China have been measured [9], two types of fright traffic locomotives suffer serious polygonal wear problem, and the other types exhibited more or less wheel eccentricity. Johansson and Andersson [10, 11] analyzed and summarized the extensive wheel measurement campaign performed in Sweden, the wheel roughness and the rail roughness were also been compared, and a tool was developed for investigation of wheel tread polygonal wear. The mechanism of the wheel OOR was explained by a simple model proposed by Brommundt [12]. Badger et al. [13] studied the evident degradation of the grinding force, wheel wear, and vibration caused by the wheel eccentricity, and some recommendations are given for detecting and determining the wheel eccentricity. Wu et al. [14] studied the dynamic stresses of the wheel set axle based on a coupled vehicle/track dynamic model with the flexible wheelset; the results show that the resonance of wheel set axle could be excited by polygonal wear, which would increase the dynamic stress for the wheel set axle. The growth mechanism of wheel polygonal of railway vehicle and its damage for the track and components were overviewed in detail [2, 15, 16]. Although a great number of researches have been carried out by scholars all over the world, the OOR of the railway wheels has not been completely explained and solved [14].

For the first suspended monorail vehicle in China, an abnormal vertical vibration of car body was found in the experimental stage, which seriously affects the ride comfort. The objective of this paper is to validate the wheel eccentricity which is the root cause for this abnormal vibration of car body based on experiment and simulation. And the influence mechanism of the wheel eccentricity on the car body acceleration is also analyzed.

2. Investigation on the Vertical Vibration of Car Body by First Test

On the trial running stage of the first suspended monorail vehicle in China, the vertical vibration of the car body exhibited an abnormal phenomenon. The obvious feature of the vibration is that it shows a clear resonance characteristic, and the amplitude of vibration was particularly violent at the speed of about 20 km/h. The ride comfort is extremely influenced by the abnormal vibration, and the maximum speed of the vehicle is therefore limited. As to explore the root reason of this special vibration, the first test was conducted.

2.1. Description of the First Test

The test was conducted in the first suspended monorail line of China, aiming to find the main reason of the abnormal vibration. This test mainly measured the vertical acceleration of the car body, the acceleration sensors was mounted on the floor of car body, as shown in Figure 1(a), and Figure 1(b) shows the data acquisition.

(a)

(b)

Figure 1: Acceleration measurement of the car body: (a) sensor position and (b) data acquisition.

In this test, the velocity of the vehicle was set to 10~30 km/h and the interval was 5 km/h. Due to the fact that the cause of the abnormal vibration is not clear, the maximum speed of 30 km/h was mainly to ensure the running safety.

2.2. Results and Discussion of the First Test

Analyzing the measured data was the key means to find the cause of vibration. Firstly, the RMS of the acceleration was counted to represent the level of the vertical vibration, and its variation trend with speeds is illustrated in Figure 2. It can be seen that, at the speed of 20 km/h, the maximum amplitude of the acceleration for the car body increases considerably and reaches a peak of 1.62 m/s². The test results show a very uniformity with the travel experience.

Figure 2: Measured acceleration of car body at different velocity.

In order to further analyze the measured data, the frequency spectrum of the measured acceleration is shown in Figure 3. It can be clearly found that each acceleration has a certain domain frequency. With the increase of running speed, the domain frequency increased accordingly.

(a)

(b)

(c)

(d)

(e)

Figure 3: The frequency spectrum of the measured acceleration at different speeds: (a) 10 km/h, (b) 15 km/h, (c) 20 km/h, (d) 25 km/h, and (e) 30 km/h.

It is known that vibration is caused by the excitation, and excitation is mainly generated from the vehicle itself and the track. The relationship among domain frequency of measured acceleration, wavelength of the excitation, and the velocity is as follows:

where denotes the wavelength of excitation, is the running velocity, and is the domain frequency of vibration.

According to formula (1), the excited wavelength at each speed can be calculated, as listed in Table 1.

Table 1: Calculated wavelength of excitation.

Velocity (km/h)
10
15
20
25
30

Domain frequency (Hz)
1.73
2.58
3.48
4.27
5.08

Calculated wavelength (m)
1.61
1.61
1.60
1.63
1.64

The calculated wavelengths in Table 1 are 1.60~1.64 m, which can conclude that the main wavelength of the excitation is 1.60~1.64 m, and this is the main reason for the abnormal vibration.

2.3. The Possibilities for the Excitation

According to the measured car body acceleration, the existence of the excitation with 1.6~1.64 m wavelength is the cause for abnormal vibration. For this type of excitation, there have three possibilities considering the track and vehicle system.

(1) The Wheel Eccentricity. The radius of the wheel is 0.27 m, and the wheel circumference is 1.70 m. But it is noted that the wheel of suspended monorail vehicle is solid tire and the compressed deformation cannot be ignored during running, as shown in Figure 4. The axle load of the vehicle is 4, the static vertical force is about 20 kN, and the compressed deformation is about 6.7 mm. In this condition, the rolling radius decreased to 0.263 m, the rolling circumference decreased to about 1.65 m, and this is in great accordance with the domain wavelength of the excitation.

Figure 4: Schematic diagram of compressed wheel.

(2) The Inherent Characteristics of the Monorail Track. Figure 5(a) shows the monorail track, and in order to ensure the running safe, the reinforcing rib is used to promote the reliability of the running track. When the vehicle passes, the unevenness of the track stiffness will cause the vibration [17, 18], as shown in Figure 5(b). The designed interval of the rib is 1.6 m, which is also in great accordance with the domain wavelength of the excitation.

(a)

(b)

Figure 5: The monorail track: (a) the reinforcing rib and (b) the compressed deformation of track.

(3) The Track Irregularity. If the wavelength of irregularity is concentrated at about 1.6 m, the excited vibration of car body will show the measured characteristic.

As the above analysis, there are three factors which may cause the abnormal vibration considering the track and the vehicle system. To improve the ride comfort, the effective strategy for the three factors is introduced. For the reinforcing rib, it is the inherent characteristic of the track to ensure running safety. The influence of rib on the car body vibration is inevitable but could effectively reduce by matching the vehicle parameters. As to the track irregularity, grinding the track surface could smooth the track and improve the ride comfort. In general, the irregularity is random, so the abnormal vibration is not likely caused by the irregularity. For wheel eccentricity, controlling the errors of manufacture and installation could reduce its influence on the ride comfort significantly.

Modifying the reinforcing rib and track irregularity is difficult operation, especially on the line that has been built. But the detection and elimination of wheel eccentricity are easy. So, the influence of the wheel eccentricity on the vertical vibration of the car body is firstly analyzed.

3. Multibody Dynamic Simulation

In this section, numerical simulations are conducted to give an insight into the consequent influence of the wheel eccentricity on the vehicle vibration. Only the wheel eccentricity is considered in the simulation. The results are compared with the test date, which can provide the evidence for the causes of the abnormal vibration.

3.1. Dynamic Model of Suspended Monorail Vehicle

In order to analyze the influence of the wheel eccentricity on the car body vibration, a detailed simulation model has been established using the multibody dynamic software of SIMPACK, as illustrated in Figure 6. In this model, the vehicle was treated as a full rigid multibody dynamic model, and the flexibility of the monorail track is not considered. The monorail track is box-sectioned beams with bottom opening, as shown in Figure 5(a). The bogie is placed inside the box beams, which could avoid the influence of the weather. The car body is suspended under the bogie; thus it can be running in the sky.

Figure 6: The simulation models for suspended monorail vehicle.

The suspended monorail vehicle consists of two bogies, and each bogie is mainly made up of one frame, one bolster, four driving wheels, four guiding wheels, a hanging device, and suspension systems. The structure of the bogie can be clearly seen in Figure 7.

Figure 7: The simulation models of bogie.

The driving wheel (solid rubber tire) is running on the running track, acting as the primary suspension. Each driving wheel can be rotated around the bogie, independently. In the dynamic model, the tire model of Pacejka Magic Formula was referenced to calculate the interaction between the driving wheel and the track, and and are representing the vertical damping and stiffness of the driving tire.

Not like the self-steering performance of the railway vehicle, the guiding wheels are needed to provide the steering force when the suspended monorail vehicle passes curve. The guiding wheels are also solid rubber tire, and they are running along the guiding track. In order to ensure the curving passing performance of the vehicle, the guiding wheels have an initial compression to provide an initial lateral force. In the dynamic model, the linear force element was used to simulate the guiding force, and and are representing the damping and stiffness of the guiding wheel.

The connection between the car body and the bolster is the hanging device, and the points , , , and are four rotated joints, which can rotate around the -axis. There has one damper between the car body and the hanging device, which is used to reduce the lateral vibration of the car body, and represents its damping. The lateral stopper between car body and hanging device limits the large lateral rotation angle of the car body, and represents the stiffness of the stopper.

Two sets of spring-damper systems are installed between the bolster and the frame, where and are representing the damping and stiffness.

3.2. Eccentricity Model of Monorail Wheel

The wheel OOR is a very common phenomenon in the railway vehicle, and a lot of investigations have been done aiming at this uneven problem. As to the wheel OOR model, two main methods are used to describe the polygonal wear in the wear circumferential direction in railway, as shown in Figure 8.

(a)

(b)

Figure 8: Methods to describe the wheel OOR: (a) transforming into track irregularity and (b) the harmonic deviation.

The first method is transforming the wheel OOR into the track irregularity, and the wheel surface is kept constant. The second method is using the harmonic deviation of the wheel radius to describe the wheel OOR. The formulas of the harmonic deviation are given as follows [19]:

where denotes the amplitude of the polygonal wear, is the radius of the wheel, is the order of polygon wear, is the wheel rotation angle, and is the actual radius of the wheel from the central axis, which is related to .

In the monorail vehicle, the compressed deformation of tire cannot be ignored which is caused by vertical forces. Therefore, the second method was chosen to investigate the influence of the wheel eccentricity on the vertical vibration of monorail vehicle.

3.3. Dynamic Vibration of Car Body with Wheel Eccentricity at Different Speeds

In the simulation, only the excitation of wheel eccentricity is considered. All the driving wheels are equipped with wheel eccentricity and no phase difference exists. The vehicle was running on the tangent track. The main parameters of the suspended monorail vehicle used in the simulation are listed in Table 2.

Table 2: Main parameters of the vehicle.

Parameters
Value
Units

Axle load
4000
kg

Bogie distance
5900
mm

Driving wheel base
1500
mm

Guiding wheel base
2900
mm

Driving wheel radius
270
mm

Mass of car body
7500
kg

Mass of bogie
1000
kg

Vertical stiffness of driving wheel
3.0
MN/m

Vertical stiffness of guiding wheel
1.8
MN/m

Secondary stiffness -axis (one side)
1.0
MN/m

Secondary damper -axis (one side)
30
kN⋅s/m

lateral damper
30
kN⋅s/m

The effects of the wheel eccentricity and its amplitude on the vertical acceleration of car body are illustrated in Figure 9. It can be observed that, with the increase of the eccentricity amplitude, the vertical acceleration of car body is increasing correspondingly. But the variation trend of the vertical acceleration of car body with the speed is not influenced by the amplitude of the wheel eccentricity. In the speed range , the acceleration of car body is obviously increased with the speed rising. Nevertheless, when the speed is in the range of , the car body acceleration decreases gradually. With the continuous increasing in the velocity, the acceleration of car body induced by the wheel eccentricity rises gradually. There is a peak at the speed of 21 km/h, which means that the vertical vibration of the car body is more obvious, and this is fully coincided with the experiment.

Figure 9: Vertical acceleration of car body at different speeds.

To understand the effects of the wheel eccentricity on the vibration of the car body, the time history of the vertical acceleration of the car body at the speed of 21 km/h is shown in Figure 10. The amplitude of wheel eccentricity is set to 2 mm. For the case of wheel with eccentricity, the maximum vertical acceleration of car body is about 1.45 m/s². The period of the oscillation of the acceleration is about 0.279 s. According to the calculated results, the excitation frequency of wheel eccentricity for the car body acceleration at the speed of 21 km/h is 3.47 Hz approximately, which gets close to the resonant frequency of the car body vertical motion 3.39 Hz. Therefore, the wheel eccentricity attributes to the vertical resonance of car body at the speed of 21 km/h, so that the vertical vibration of car body is rising considerably.

Figure 10: Vertical acceleration of car body at the speed of 21 km/h.

Figure 11 shows the frequency spectrum of the vertical acceleration of car body at different speeds. It can be seen that there is a major frequency existing in the frequency domain, which is induced by the wheel eccentricity.

Figure 11: The frequency spectrum of the simulated acceleration at different speeds.

The comparison of simulated and experiment results in the dominant frequency of the car body acceleration which is showed in Table 3. It can be clear seen that the calculated domain frequency of car body acceleration with wheel eccentricity shows well accordance with the experiment. This comparison further verifies that the wheel eccentricity may cause the abnormal vibration of car body.

Table 3: Simulated dominant frequency of car body acceleration.

Velocity/(km/h)
10
15
20
25
30

Simulated/Hz
1.71
2.59
3.45
4.33
5.19

Experiment/Hz
1.73
2.58
3.48
4.27
5.08

3.4. Influence of the Secondary Suspension on the Vibration of Car Body with Wheel Eccentricity

The vibration induced by wheel eccentricity transfers to the car body, which will seriously affect the ride comfort. For the suspended monorail vehicle, the secondary suspension is the most important component to attenuate the car body vibration, so its effect on the car body acceleration is calculated in the excitation of wheel eccentricity, which is hoped to reduce the influence of wheel eccentricity on ride comfort. The cases of vertical acceleration of car body with different secondary stiffness and damping are compared, as shown in Figure 12. The amplitude of wheel eccentricity is also set to 2 mm in the simulation.

(a)

(b)

Figure 12: The effect of secondary suspension on the vibration of car body with wheel eccentricity: (a) stiffness and (b) damping.

Figure 12(a) indicates that, with the decrease of the secondary stiffness, the vertical acceleration of car body decrease significantly. When the stiffness decreased to 0.3 MN/m, the abnormal vibration is not appearing at low speed (<20 km/h). When the stiffness increased to 1.5 MN/m, the peak of vertical acceleration is appearing at the speed of 23 km/h, which is a little higher than the stiffness of 1.0 MN/m.

The comparison analysis for the effect of the secondary damping on the vertical acceleration of car body with wheel eccentricity is demonstrated in Figure 12(b). When the speed is lower than 25 km/h, increasing the secondary damping can effectively reduce the car body acceleration caused by the wheel eccentricity. However, when the speed is higher than 25 km/h, the index of car body acceleration is rising with the increasing of the secondary damping.

4. Investigation on the Vertical Vibration of Car Body by Second Test

From the above analysis, the calculated result with wheel eccentricity shows a great accordance with the experiment. But the reinforcing rib and the track irregularity were not considered in the simulation. In order to verify that the abnormal vibration was induced by the wheel eccentricity, the secondary test is conducted. New wheel without eccentricity was installed on the vehicle and the monorail track was as same as the first test, so as the sensor position and test methods.

Figure 13 gives the comparison of the two test results of car body vertical acceleration. It should be noted that the maximum speed in the second test is set to 60 km/h.

Figure 13: The comparison of the two test results.

It can be observed that the overall trend of the vertical acceleration of the car body increases as the vehicle velocity rising in the second test. Compared to the first test, the peak of car body acceleration at speed of 20 km/h is not appearing, which states that the vertical resonance of car body disappeared when renewing the wheel without eccentricity.

Figure 14 gives the comparison of the frequency spectrum of the two test results at different speeds. In the case of the second test, the car body acceleration is decreasing obviously at the domain frequency. Therefore, it can be deduced that the main reason of the abnormal vibration in the first test is wheel eccentricity.

(a)

(b)

(c)

(d)

(e)

Figure 14: The comparison of frequency spectrum: (a) 10 km/h, (b) 15 km/h, (c) 20 km/h, (d) 25 km/h, and (e) 30 km/h.

From the comparison of the two tests, the abnormal vertical vibration of car body was disappearing when only eliminate the wheel eccentricity. Because the track is the same in the two tests, it could confirm that the wheel eccentricity is the main reason of the abnormal vibration. Meanwhile, the domain frequency also can be seen at low frequency, this may mainly cause the irregularity and the reinforcing rib existing on the monorail track, and its influence and optimization will be carried out in the future work.

5. Conclusions

In this study, the influence of the wheel eccentricity on the vertical vibration of suspension monorail vehicle is investigated and validated, based on extensive experiments and simulation. The main conclusions can be drawn as follows:

(1)Based on the amplitude-frequency characteristic of the vertical acceleration in the first test, three possible reasons are proposed, which may cause the abnormal vibration of car body.(2)The simulated acceleration excited only by wheel eccentricity shows great accordance with the first tested results. The variation trend of the acceleration is not influenced by the amplitude of wheel eccentricity. The vertical vibration induced by the wheel eccentricity could excite the resonance of car body at the speed of 21 km/h.(3)Decreasing the secondary stiffness can significantly reduce the vertical vibration of the car body caused by wheel eccentricity, especially at the resonant speed. As to the secondary damping, increasing the secondary damping can effectively reduce the car body acceleration caused by the wheel eccentricity at low speed (<25 km/h). However, the index of car body acceleration is rising with the increasing of the secondary damping as the speed is higher.(4)In the case of the second test with new wheel, the peak of car body acceleration at speed of 21 km/h is not appearing, and the car body acceleration is decreasing obviously at the domain frequency. It is further determined that the abnormal vibration is mainly caused by the wheel eccentricity.

It should be noted that the flexibility of the monorail track is not considered in this study. However, in the real condition the track is not rigid; thus, it is necessary to take the effects of the track flexibility into account in future work. Meanwhile, the curve passing performance of vehicle with wheel eccentricity should be investigated in future work.

Conflicts of Interest

The authors declare that they have no conflicts of interest.

Acknowledgments

The authors wish to express their gratitude to State Key Laboratory of Traction Power for providing equipment and materials to this project and the China Sky Train Co., Ltd., for the cooperation and support. The authors are grateful for the financial support provided by the National Natural Science Key Foundation of China under Contract (Grant no. 51735012) and the Science and Technology Project of Sichuan Province (Grant no. 2017GZ0082).

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