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Numerical and Experimental Study on Vibration and Noise of Embedded Rail System

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1. Introduction

Around the world, because maintenance work on various ballast track systems has increased year by year, the maintenance cost, including labor and equipment costs, has also increased. Meanwhile, the ballast tracks required for the sleeper, ballasts and other materials are becomingly increasingly scarce. Therefore, research and development on railway systems around the world have trended towards non-ballast track system [1] [2] [3]. This study explores the embedded rail system of the light rail transit system (LRT), which is a non-ballast track system. While normal traffic cannot mingle with a general rail system, the embedded rail system merges a general lane with road traffic, so people are free to enter. LRT runs along its route without a fence or barrier. As a results, train-induced vibration and noise directly affect people and nearby buildings. However, there have been few studies on the vibration and noise of an embedded rail system in domestic.

In this paper, the three-dimensional finite element analysis is used to study the vibration and noise characteristics of embedded rail systems. Taking the Kaohsiung LRT as an example, vibration, and noise analyses of embedded rail systems are performed. The purpose of the study is to establish a set of effective simulation procedures and methodologies, and effectively apply them to practical engineering problems.

2. Numerical Simulation on Vibration and Noise of a Rail System

There are two stages in the vibration and noise analyses of rail systems. The first stage uses ANSYS to determine the dynamic response by moving a load on the rail system via the finite element method [4]. The second stage uses LMS Virtual.Lab to solve the equation for the sound pressure distribution of the external radiation field via the boundary element method [5]. To verify this simulation procedure, the feasibility of the acoustic vibration analysis technique is evaluated for the embedded rail of the Kaohsiung LRT system as an example, and the numerical simulation and measurement results are analyzed and discussed.

2.1. ANSYS Vibration Analysis Model

The embedded rail system consists of three elements: the steel rail, the encapsulation, and the concrete slab. The Kaohsiung LRT main line use a 54R2 (41GPU) track for the steel rail section, the encapsulation uses recycled waste tires, and the concrete track bed is a no-fasteners continuous support type [6] [7]. The overall cross-section is as shown in Figure 1.

The finite element model of the embedded rail system is established with ANSYS. The soil depth is 4 meters, the width is 10 meters, and the overall length of the track is 40 meters, as shown in Figure 2. The properties of the materials of the rail, encapsulation, and concrete are shown in Table 1, and the material parameters are inputted to ANSYS for dynamic moving load analysis.

The vehicle model is simplified as a double-row concentrated moving load. All concentrated loads are assumed to be 65 kN for train load analysis according

Figure 1. Cross-section of the Kaohsiung LRT (unit: mm).

Figure 2. Finite element model of the Kaohsiung LRT.

Table 1. Material properties of the Kaohsiung LRT.

to the original design. The boundary conditions are assumed to be at the soil boundary. Both the left and right sides of the model (X direction) and the bottom of the model (Y direction) are fixed. The deformation on both sides of the driving direction (Z direction) is assumed to be zero, which is considered to be the plane strain condition. The numerical model is modeled by solid elements in order to reduce analysis time, using the modal superposition method to solve the equations of motion.

2.2. LMS Virtual.Lab Sound Field Analysis Model

The sound field analysis uses LMS Virtual. Lab’s built-in transient boundary element with an air density of 1.255 kg/m^{3} and a sound velocity of 340 m/s. The node instantaneous displacement vibration response obtained from the ANSYS analysis is taken as the boundary condition of the sound field. All node displacements are applied to the nodes mapped by the sound field and the acoustic radiation is calculated. In order to understand the sound field response of a train passing through, the sound field is calculated at a point 1.2 m from the top of the rail, as shown in Figure 3.

3. Vibration and Noise Experiment of an LRT

In this study, two different types of embedded rail systems were selected. The general embedded track measurement points were located at the intersection of Kaisyuan 4th Road and Zhongshan 3rd Road. The upper part of the measurement location was the viaduct. The grass-embedded track measurement points were located near the intersection of Kaisyuan 4th Road and Ruinan Street. The two measuring points were close to the Kaohsiung mass rapid transit (MRT) system’s Kaisyuan station, which is the MRT red line R6 station.

The vibration measurement was carried out using the SPC-51 portable vibration monitoring system and the VSE-15D servo velocity-meter produced by Tokyo Sokushin Co., Ltd. The vibration was measured with measurement duration of 180 seconds for each recording and a sampling rate of 200 Hz. The gen eral embedded track measurement points were set at 1.28 m, 4.28 m, 6.98 m, 10.33 m, and 13.33 m from the rail center. Three single-axis servo velocity-meters (VSE-15D) were set at the same location to measure the X, Y, Z directions of the vibration speed. The X, Y, and Z directions are expressed as the perpendicular, parallel, and vertical driving directions to the ground, respectively. The measurement setup for the general embedded track is shown in Figure 4. The grass-embedded track measurement points were set at 1 m, 3 m, 6 m, 9 m, and 12 m from the rail center. The measurement setup for the grass-embedded track is shown in Figure 5.

Figure 3. LMS Virtual.Lab sound filed analysis model.

Figure 4. Measurement setup for the general embedded track.

Figure 5. Measurement setup for the grass-embedded track.

The noise measurement was performed using a low-profile surface pressure microphone (130A40, PCB Piezotronics, Inc., USA) and with an adaptable modular measurement system for physical signals (CRONOS PL-2, imc Meßsysteme GmbH, Germany). We referenced the selection of measurement points to the standard for noise control on land transport systems from Environmental Protection Administration [8]. The embedded track noise measurement setup consists of a microphone sensor (130A40) at a distance of 15 meters from the rail center and at a height of 1.2 meters from the ground. The microphone sensor faced the LRT, measuring the background noise and traffic noise when the train passes, as shown in Figure 4 and Figure 5.

4. Results of Numerical Simulation and Measurement

4.1. Analysis and Discussion of Vibration Results

Figure 6 shows a comparison of the numerical simulation results and measurement results for vibration of the general embedded track. It shows that the finite element model could effectively obtain the natural frequency (3.126 - 3.426 Hz) of the embedded rail system. In addition to determining the correctness of the dynamic analysis of the moving load, it can also be used as a reference for dynamic performance design of a rail system in order to avoid the structural damage caused by resonance.

Figure 7 shows a comparison between the displacement time histories of the general embedded track. It shows the simulation and measurement results with three displacement peaks when the train passed over the general embedded track with a speed of around 10 - 11 km/hr, inducing a displacement of approximately 0.3 mm.

4.2. Analysis and Discussion of Noise Results

The measurement and numerical simulation results for low-frequency noise of

Figure 6. Comparison of vibration results for the general embedded track: (a) numerical results, (b) and (c) measurement results.

Figure 7. Comparison of displacement time histories for the general embedded track.

the general embedded track are shown in Figure 8. The first three peaks of the noise spectrum simulation results lie at 22.461 Hz, 33.569 Hz, and 44.044 Hz respectively, while the peak of the local noise measurement spectrum lies between 33.2 to 33.5 Hz. This indicates that the LMS Virtual. Lab numerical simulation can effectively simulate low-frequency noise radiation as a train passes for reference in future noise reduction of embedded rail tracks.

5. Parametric Study on Vibration and Noise

This section considers the train speed, soil material, and encapsulation material

(a)(b)(c)

Figure 8. Comparison of noise results for the general embedded track: (a) numerical results; (b) and (c) measurement results

as the three basic parameters. The finite element model and numerical analysis procedure established in this paper are used in the parametric study in order to understand the sensitivity of each parameter to vibration and noise.

Figure 9 shows the maximum displacement and maximum sound pressure level of the embedded track at different train speeds (10, 25, and 40 km/hr). It shows that if the train speed increases, the maximum sound pressure level also increases, but the maximum displacement decreases. Figure 10 shows the maximum displacement and maximum sound pressure level of the embedded track at different soil elastic moduli (10, 25, and 40 MPa). It shows that if the soil elastic modulus increases, the maximum sound pressure level also increases, but the maximum displacement decreases. Figure 11 shows the maximum displacement and maximum sound pressure level of the embedded track at different encapsulation elastic moduli (0.6, 2.6, and 5 MPa). It shows that the maxi-

Figure 9. Parametric study on train speed.

Figure 10. Parametric study on soil elastic modulus.

Figure 11. Parametric study on encapsulation elastic modulus.

mum sound pressure level and maximum displacement are not sensitive to the elastic modulus of encapsulation.

6. Concluding Remarks

1) The comparison of the simulation and measurement results for the embedded rail system showed that: a) the finite element model could effectively determine the natural frequency of the embedded rail system and the correctness of the model and b) considering low-frequency noise only, the numerical simulation could effectively reflect the main frequency of low-frequency noise.

2) The parametric study on vibration and noise showed that: a) when the train speed increases, the maximum sound pressure level also increases, but the maximum displacement decreases; b) when the soil elastic modulus increases, the maximum sound pressure level also increases, but the maximum displacement decreases; and c) the maximum sound pressure level and maximum displacement are not sensitive to the elastic modulus of the encapsulation.

3) The vibration and noise frequency response from simulation and measurement results can be applied to dynamic performance design, vibration, and noise reduction for embedded rail systems.

Acknowledgements

This study was sponsored by CECI Engineering Consultants, Inc., Taiwan under project number CECI 105-05931.

Conflicts of Interest

The authors declare no conflicts of interest.

Cite this paper

*Journal of Applied Mathematics and Physics*,

**5**, 1629-1637. doi: 10.4236/jamp.2017.59135.

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