# Contact Loss beneath Track Slab Caused by Deteriorated Cement Emulsified Asphalt Mortar: Dynamic Characteristics of Vehicle-Slab Track System and Prototype Experiment

Authors: Dan Liu; Yu-feng Liu; Juan-juan Ren; Rong-shan Yang; Xue-yi Liu
Journal: Mathematical Problems in Engineering
 (2016)

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## Abstract

The contact loss beneath track slab caused by deteriorated cement emulsified asphalt mortar (CA mortar) has been one of the main diseases occurring in the CRTS- (China Railway Track System-) I Slab Track of high-speed railway in China. Based on the slab track design theory and the vehicle-track coupling vibration theory, a vehicle-track vertical coupling dynamic FEM model was established to analyze the influence of the contact loss length on the dynamic characteristics of vehicle and track subsystems at different train speeds. A prototype dynamic characteristic experimental test of CRTS-I Slab Track with CA mortar contact loss was conducted to verify the FEM model results. The train load was generated by the customized ZSS50 excitation car. The results showed that when the operation speed is less than 300 km/h, the contact loss with length smaller than 2.0 m barely affects the running smoothness ride safety of vehicle. The contact loss length effect on the dynamic characteristics of track subsystem is pronounced, especially on the track slab. Once the contact loss beneath the track slab occurs, the vibration displacement and the acceleration of the track slab increase rapidly, while it has little influence on the displacement and acceleration of the concrete roadbed.


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## Body

## 1. Introduction

Nonballasted track, which is smoother and more stable and requires lower maintenance, has been proven to be the best track structure type for high-speed railway [1, 2]. CRTS-I Slab Track, which is technically improved from Japanese Shinkansen Slab track, is one of the main nonballasted track types used in Chinese high-speed railways and has been widely applied on Chinese passenger dedicated lines (PDLs), whose total mileage has exceeded 2200 km.Due to the coupling action of train load, temperature load, and environmental conditions, the CRTS-I slab track inevitably generates various types of diseases. Cement emulsified asphalt mortar (CA mortar), which is one of the main components of CRTS-I slab track, plays an important role in maintaining the elasticity of structure and makes the maintenance more convenient [3–5]. During the construction process, the CA mortar of CRTS-I slab track is poured into the bag between track slab and concrete roadbed [6], which leads to the poor connections between CA mortar and track slab and between CA mortar and concrete roadbed. Therefore, the interface between track slab and CA mortar becomes a vulnerable position of CRTS-I Slab Track. Based on field investigations, the contact loss beneath track slabs caused by deteriorated CA mortar is the main common disease of CRTS-I Slab Track [7, 8]. It may change the path of force transfer, which will affect the mechanical behavior of structure [9]. Therefore, it is important to investigate the influence of contact loss beneath track slabs on the dynamic characteristic of slab track.Some researchers have studied the impact of CA mortar contact loss beneath track slabs on the dynamic characteristic of slab track. Shi [10] analyzed the effect of slab track defect on the dynamic performances of slab track. The results showed that the deterioration of CA mortar has great impact on the slab track, leading to the great increase of the acceleration of slab track. Xiang et al. [11] found that the contact loss caused by the deterioration of CA mortar would lead to the increase of the acceleration and displacement of track slabs. Li et al. [12] studied the influence of contact loss on the dynamic characteristics of the unit slab track on bridge. The results showed that the contact loss of CA mortar has significant influence on the vibration performance of the track. Previous researches have mainly focused on the FEM dynamic simulation, but experimental verification lacks. In this paper, a FEM model was applied to analyze the influence of contact loss beneath track slabs on the mechanical performance of slab track and the operation performance of vehicles with different train speeds, and an experimental testing of the dynamic characteristic of CRTS-I track slab with contact loss was conducted to verify the FEM results.


## 2. The Mechanism and Characteristics of Contact Loss

CRTS-I Slab Track (as shown in Figure1(a)) consists of unit prefabricated slabs measuring 4.95 m × 2.40 m × 0.19 m, CA mortar adjustment layer measuring 4.95 m × 2.4 m × 0.05 m, reinforced concrete roadbed measuring 5.0 m × 3.2 m × 0.3 m, cylindrical bollards, and resin filled around bollards. It has the same structure on the subgrade and bridge and in tunnel.Figure 1
CRTS-I Slab Track.
(a)
Schematic diagram of CRTS-I Slab Track (b)
Site picture of CRTS-I Slab Track with contact lossThe fresh CA mortar is consisting of cement, emulsified asphalt, sand, water, and admixtures (such as aluminum powder and superplasticizer) [13]. Unlike cement or asphalt, CA mortar has unique properties combining the strength of cement and the flexibility of asphalt [14]. The mechanical properties of CA mortar (such as strength, elasticity, and damping) play an important role in ride smoothness and ride safety.During the construction process, because the CA mortar is poured by means of its own gravity, its filling is likely to be uncompacted. It is one of the main causes of contact loss beneath track slabs. On the other hand, CA mortar is very sensitive with environmental conditions like water and temperature. The coupling effect of high frequency train load, temperature, and environmental conditions degrades the CA mortar strength and causes the deterioration of CA mortar performance. The contact loss beneath track slab caused by the deteriorated CA mortar may change the mechanical behavior of structure and affect the ride smoothness and safety.According to field researches, the contact loss beneath track slabs can occur at the corner, the end (as shown in Figure1(b)), and the middle. Based on the research conducted by Yang et al. [15], the structure with CA mortar damage located at the adjacent slab end is under the worst working condition. In this study, the lateral contact loss (with height of 5 mm and width of 2.4 m) beneath the end of track slab was taken into consideration.


## 3. Vehicle-Track Vertical Coupled Vibration FEM Model

### 3.1. Vehicle-Track Vertical Coupled Dynamic Model

Because of the complexity of structure and the coupling of vehicle-track system [16–18], it is very complicated and time-consuming to accurately describe the in-service conditions of vehicle subsystem and track subsystem. Therefore, the vehicle-track system needs to be simplified. In order to analyze the influence of contact loss beneath track slabs on the dynamic characteristics of vehicle and track subsystems, based on the vehicle-track coupling vibration theory, a 3D simplified vehicle-track vertical coupled vibration model was established by using LS-DYNA (see Figure 2).Figure 2
Vehicle-track vertical coupled vibration FEM model.
(a)
Side view (b)
3D model(1) This model included a vehicle subsystem and a track subsystem. The vehicle subsystem was considered as a multi-rigid-body system which consists of a car body, two bogies and four wheel-sets [19]. The wheel-set and bogie were connected by primary suspensions, and the bogie and car body were connected by secondary suspensions. Both primary suspensions and secondary suspensions were simplified as spring/damper systems. The main parameters for the vehicle subsystem are listed in Table 1.Table 1
Basic parameters of the vehicle subsystem.
Parameters Value Mass of car body 39600 kg Mass of wheelset 2500 kg Inertia of vertical motion of bogie 1.283 kg⋅m2 Damping of the primary suspension of vehicle 1.96× 104 N⋅s/m Damping of the secondary suspension of vehicle 4.0× 104 N⋅s/m Length between the truck pivot centers 17.5 m Mass of bogie 3500 kg Inertia of vertical motion for the car 1.94 kg⋅m2 Vertical stiffness of the primary suspension of vehicle 1.176× 106 N/m Vertical stiffness of the secondary suspension of vehicle 1.89× 106 N/m Wheel base for the bogie 2.5 m Radius of the wheel 0.43 m(2) The track subsystem was simplified as continuous elastic discrete support beam-shell FEM model [20, 21]. In the track subsystem, rail was supported by a series of discrete spring/damper elements which acted as fasteners [22]; track slab and concrete roadbed were both modeled as shell which was supported in a continuous manner; CA mortar under the track slab and soil roadbed were simplified as spring/damper elements. The CA mortar under the contact loss area was modeled as a series of nonlinear spring elements, whose stiffness can be calculated by (1)k=0x<htECAn·hTCAx≥ht,where k refers to the nonlinear spring stiffness;x refers to the compression value of CA mortar; ht refers to the contact loss height; ECA refers to the elastic modulus of CA mortar; hTCA refers to the height of CA mortar under contact loss area; n refers to the number of nonlinear spring elements. The main parameters for track subsystem are presented in Table 2.Table 2
Basic parameters of track subsystem.
Parameters Value Mass of rail per unit length 60 kg/m Young’s modulus of rail 2.06× 105 Mpa Poisson’s ratio of rail 0.3 Length of slab 4.95 m Width of slab 2.4 m Thickness of slab 0.19 m Young’s modulus of slab 3.6× 104 Mpa Poisson’s ratio of slab 0.2 Density of slab 2500 kg/m3 Thickness of CA mortar 0.05 m Young’s modulus of CA mortar 300 Mpa Vertical damping of CA mortar 3.46× 104 N⋅s/m Distance between fasteners 0.625 m Vertical stiffness of fastener 50 kN/mm Vertical damping of fastener 7.5× 104 N⋅s/m Length of concrete roadbed 125 m Width of concrete roadbed 3.2 m Thickness of concrete roadbed 0.3 m Young’s modulus of concrete roadbed 3.25× 104 Mpa Poisson’s ratio of concrete roadbed 0.2 Density of concrete roadbed 2500 kg/m3 Vertical stiffness of soil roadbed 120 Mpa/m Vertical damping of soil roadbed 1.0× 105 N⋅s/m(3) In the vertical coupling vibration model, there is a strong interaction between the rail and the wheel to combine the vehicle subsystem and track subsystem as one coupling system. This interaction has always been described with the Hertz Theory. The elastic deformations of the wheel and the rail form an ellipse contact area. The dimension of the contact ellipse depends on the normal force and the profiles of rail and wheel. In vehicle-track vertical dynamic coupling model, the wheel-rail contact was simplified as a Hertz spring. The relationship between the wheel-rail load (Pt) and the wheel-rail elastic compression (δ) can be expressed by(2)Pt=1G·δt2/3in which G is the constant of wheel-rail contact area, for the worn types of wheel treads, G=4.57R-0.149×10-8 (m/N2/3); for the conical types of wheel treads, G=3.86R-0.115×10-8 (m/N2/3), where R represents the radius of the wheel.


### 3.2. The Irregularity of Track

The irregularity of track, which was overlaid by the stochastic irregular waves with different wavelengths, phases, and amplitudes, is an extremely complicated random process related to the length of railway. In this paper, the irregularity of the Germany high-speed low disturbance was applied to excite the vibration of vehicle and slab track, it can be represented by the power spectral density (PSD) function:(3)SνΩ=AνΩC2Ω2+Ωr2Ω2+ΩC2,where SνΩ is the vertical power spectral density; Aν is the roughness constant (Aν=4.032×10-7 (m2·rad/m) [9]); ΩC and Ωr are the cutoff frequency (ΩC = 0.8246 (rad/m), Ωr = 0.0206 (rad/m) [9]); Ω is the spatial frequency of the irregularities.


## 3.1. Vehicle-Track Vertical Coupled Dynamic Model

Because of the complexity of structure and the coupling of vehicle-track system [16–18], it is very complicated and time-consuming to accurately describe the in-service conditions of vehicle subsystem and track subsystem. Therefore, the vehicle-track system needs to be simplified. In order to analyze the influence of contact loss beneath track slabs on the dynamic characteristics of vehicle and track subsystems, based on the vehicle-track coupling vibration theory, a 3D simplified vehicle-track vertical coupled vibration model was established by using LS-DYNA (see Figure 2).Figure 2
Vehicle-track vertical coupled vibration FEM model.
(a)
Side view (b)
3D model(1) This model included a vehicle subsystem and a track subsystem. The vehicle subsystem was considered as a multi-rigid-body system which consists of a car body, two bogies and four wheel-sets [19]. The wheel-set and bogie were connected by primary suspensions, and the bogie and car body were connected by secondary suspensions. Both primary suspensions and secondary suspensions were simplified as spring/damper systems. The main parameters for the vehicle subsystem are listed in Table 1.Table 1
Basic parameters of the vehicle subsystem.
Parameters Value Mass of car body 39600 kg Mass of wheelset 2500 kg Inertia of vertical motion of bogie 1.283 kg⋅m2 Damping of the primary suspension of vehicle 1.96× 104 N⋅s/m Damping of the secondary suspension of vehicle 4.0× 104 N⋅s/m Length between the truck pivot centers 17.5 m Mass of bogie 3500 kg Inertia of vertical motion for the car 1.94 kg⋅m2 Vertical stiffness of the primary suspension of vehicle 1.176× 106 N/m Vertical stiffness of the secondary suspension of vehicle 1.89× 106 N/m Wheel base for the bogie 2.5 m Radius of the wheel 0.43 m(2) The track subsystem was simplified as continuous elastic discrete support beam-shell FEM model [20, 21]. In the track subsystem, rail was supported by a series of discrete spring/damper elements which acted as fasteners [22]; track slab and concrete roadbed were both modeled as shell which was supported in a continuous manner; CA mortar under the track slab and soil roadbed were simplified as spring/damper elements. The CA mortar under the contact loss area was modeled as a series of nonlinear spring elements, whose stiffness can be calculated by (1)k=0x<htECAn·hTCAx≥ht,where k refers to the nonlinear spring stiffness;x refers to the compression value of CA mortar; ht refers to the contact loss height; ECA refers to the elastic modulus of CA mortar; hTCA refers to the height of CA mortar under contact loss area; n refers to the number of nonlinear spring elements. The main parameters for track subsystem are presented in Table 2.Table 2
Basic parameters of track subsystem.
Parameters Value Mass of rail per unit length 60 kg/m Young’s modulus of rail 2.06× 105 Mpa Poisson’s ratio of rail 0.3 Length of slab 4.95 m Width of slab 2.4 m Thickness of slab 0.19 m Young’s modulus of slab 3.6× 104 Mpa Poisson’s ratio of slab 0.2 Density of slab 2500 kg/m3 Thickness of CA mortar 0.05 m Young’s modulus of CA mortar 300 Mpa Vertical damping of CA mortar 3.46× 104 N⋅s/m Distance between fasteners 0.625 m Vertical stiffness of fastener 50 kN/mm Vertical damping of fastener 7.5× 104 N⋅s/m Length of concrete roadbed 125 m Width of concrete roadbed 3.2 m Thickness of concrete roadbed 0.3 m Young’s modulus of concrete roadbed 3.25× 104 Mpa Poisson’s ratio of concrete roadbed 0.2 Density of concrete roadbed 2500 kg/m3 Vertical stiffness of soil roadbed 120 Mpa/m Vertical damping of soil roadbed 1.0× 105 N⋅s/m(3) In the vertical coupling vibration model, there is a strong interaction between the rail and the wheel to combine the vehicle subsystem and track subsystem as one coupling system. This interaction has always been described with the Hertz Theory. The elastic deformations of the wheel and the rail form an ellipse contact area. The dimension of the contact ellipse depends on the normal force and the profiles of rail and wheel. In vehicle-track vertical dynamic coupling model, the wheel-rail contact was simplified as a Hertz spring. The relationship between the wheel-rail load (Pt) and the wheel-rail elastic compression (δ) can be expressed by(2)Pt=1G·δt2/3in which G is the constant of wheel-rail contact area, for the worn types of wheel treads, G=4.57R-0.149×10-8 (m/N2/3); for the conical types of wheel treads, G=3.86R-0.115×10-8 (m/N2/3), where R represents the radius of the wheel.


## 3.2. The Irregularity of Track

The irregularity of track, which was overlaid by the stochastic irregular waves with different wavelengths, phases, and amplitudes, is an extremely complicated random process related to the length of railway. In this paper, the irregularity of the Germany high-speed low disturbance was applied to excite the vibration of vehicle and slab track, it can be represented by the power spectral density (PSD) function:(3)SνΩ=AνΩC2Ω2+Ωr2Ω2+ΩC2,where SνΩ is the vertical power spectral density; Aν is the roughness constant (Aν=4.032×10-7 (m2·rad/m) [9]); ΩC and Ωr are the cutoff frequency (ΩC = 0.8246 (rad/m), Ωr = 0.0206 (rad/m) [9]); Ω is the spatial frequency of the irregularities.


## 4. Dynamic Response of Vehicle Subsystem

In order to figure out the influence of contact loss length on the dynamical characteristic of vehicle subsystem, a vehicle-track vertical coupled vibration FEM model was modeled using finite element package LS-DYNA. The length of contact loss varies from 0 m to 2 m, and 200 km/h, 250 km/h, and 300 km/h were selected as the train speeds.


### 4.1. Acceleration of Vehicle Subsystem

The acceleration of vehicle subsystem, which includes the car body acceleration, bogie acceleration and wheel-set acceleration, is the main dynamical index for evaluating the driving comfort, in which the car body acceleration is the most important factor. The car body acceleration, bogie acceleration, and wheel-set acceleration are shown in Figure3.Figure 3
Influence of contact loss length on vertical acceleration of vehicle subsystem.
(a)
Vertical car body acceleration (b)
Vertical bogie acceleration (c)
Vertical wheel-set accelerationFrom Figure3, it is clear that once the contact loss occurs, the vertical wheel-set acceleration increases with the increased contact loss length, and when it is more than 0.7 m, the vertical bogie acceleration increases significantly with the increased contact loss length, whereas the vertical car body acceleration has a small increase when the contact loss length exceeds 1.5 m. When the contact loss length increases from 0.0 m to 2.0 m, the wheel-set acceleration increases approximately 34.40% at 200 km/h of train speed, and the vertical bogie acceleration increases about 87.40% at 200 km/h of train speed. When the contact loss length increases from 0.0 m to 1.5 m, the car body acceleration only grows by 1.2%, which means that the contact loss shorter than 1.5 m has bare influence on the car body acceleration. When the contact loss length increases to 2.0 m, the car body acceleration increases about 13.4% to 0.35 m/s2, less than the running smoothness index of 2.5 m/s2 carried out by Zhai [23]. It can be concluded that due to the shock absorption of primary suspensions and second suspensions, when the train speed is no more than 300 km/h, the contact loss shorter than 2.0 m hardly affects the running smoothness of the vehicle.


### 4.2. Wheel-Rail Force

The wheel-rail force, which represents the interaction between the vehicle subsystem and track subsystem, is the main response to the track subsystem state and acts as the dynamic load to the track. The rate of wheel load reduction acting as one of the ride safety index can be calculated by the following equation:(4)δ=P¯-PminP¯in which δ represents the rate of wheel load reduction; P- is the average value of the wheel-rail force; Pmin is the minimum value of the wheel-rail force.The wheel-rail force curve in time domain at 300 km/h of train speed is shown in Figure4(a). It can be seen that when the train passes through the area with contact loss of 0.7 m in length, the wheel-rail force reaches the maximum value; compared with passing through the normal slab without contact loss, the maximum wheel-rail force increases significantly and the minimum wheel-rail force keeps constant. The relationships between the contact loss length and the maximum wheel-rail force at different train speeds are shown in Figure 4(b), and it can be found that, with the increased contact loss length, the maximum wheel-rail force increases gradually, especially for the contact loss length ranging from 0.5 m to 1.5 m. Comparing these curves in Figure 4(b), it is clear that the faster the train speed is, the greater the maximum wheel-rail force is.Figure 4
Influence of contact loss length on the wheel-rail force.
(a)
Time domain curve of Wheel-rail force (b)
Maximum wheel-rail force (c)
Rate of wheel load reductionFigure4(c) shows the influence of the contact loss length on the rate of wheel load reduction. It indicates that, for a 200 km/h train speed, when the contact loss length is less than 1.2 m, it hardly affects the rate of wheel load reduction, when the contact loss length increases to 2.0 m, the rate of wheel load reduction only grows by 7.7%, while for a 250 km/h train speed, when the contact loss length is less than 1.0 m, it barely has influence on the wheel load reduction rate, and when the contact loss length increases to 2.0 m, the rate of wheel load reduction rises about 14.5%. For a 300 km/h train speed, when the contact loss length is less than 0.7 m, the wheel load reduction barely changes with the increased contact loss length, and when the contact loss length increases to 2.0 m, the rate of wheel load increases about 39.0% to 0.5541. According to the research conducted by Zhai [23], in order to ensure the ride safety, the wheel load reduction rate of high-speed vehicle should not exceed 0.6. It can be concluded that for train speed no more than 300 km/h, the contact loss which is less than 2.0 m barely affects the ride safety.


## 4.1. Acceleration of Vehicle Subsystem

The acceleration of vehicle subsystem, which includes the car body acceleration, bogie acceleration and wheel-set acceleration, is the main dynamical index for evaluating the driving comfort, in which the car body acceleration is the most important factor. The car body acceleration, bogie acceleration, and wheel-set acceleration are shown in Figure3.Figure 3
Influence of contact loss length on vertical acceleration of vehicle subsystem.
(a)
Vertical car body acceleration (b)
Vertical bogie acceleration (c)
Vertical wheel-set accelerationFrom Figure3, it is clear that once the contact loss occurs, the vertical wheel-set acceleration increases with the increased contact loss length, and when it is more than 0.7 m, the vertical bogie acceleration increases significantly with the increased contact loss length, whereas the vertical car body acceleration has a small increase when the contact loss length exceeds 1.5 m. When the contact loss length increases from 0.0 m to 2.0 m, the wheel-set acceleration increases approximately 34.40% at 200 km/h of train speed, and the vertical bogie acceleration increases about 87.40% at 200 km/h of train speed. When the contact loss length increases from 0.0 m to 1.5 m, the car body acceleration only grows by 1.2%, which means that the contact loss shorter than 1.5 m has bare influence on the car body acceleration. When the contact loss length increases to 2.0 m, the car body acceleration increases about 13.4% to 0.35 m/s2, less than the running smoothness index of 2.5 m/s2 carried out by Zhai [23]. It can be concluded that due to the shock absorption of primary suspensions and second suspensions, when the train speed is no more than 300 km/h, the contact loss shorter than 2.0 m hardly affects the running smoothness of the vehicle.


## 4.2. Wheel-Rail Force

The wheel-rail force, which represents the interaction between the vehicle subsystem and track subsystem, is the main response to the track subsystem state and acts as the dynamic load to the track. The rate of wheel load reduction acting as one of the ride safety index can be calculated by the following equation:(4)δ=P¯-PminP¯in which δ represents the rate of wheel load reduction; P- is the average value of the wheel-rail force; Pmin is the minimum value of the wheel-rail force.The wheel-rail force curve in time domain at 300 km/h of train speed is shown in Figure4(a). It can be seen that when the train passes through the area with contact loss of 0.7 m in length, the wheel-rail force reaches the maximum value; compared with passing through the normal slab without contact loss, the maximum wheel-rail force increases significantly and the minimum wheel-rail force keeps constant. The relationships between the contact loss length and the maximum wheel-rail force at different train speeds are shown in Figure 4(b), and it can be found that, with the increased contact loss length, the maximum wheel-rail force increases gradually, especially for the contact loss length ranging from 0.5 m to 1.5 m. Comparing these curves in Figure 4(b), it is clear that the faster the train speed is, the greater the maximum wheel-rail force is.Figure 4
Influence of contact loss length on the wheel-rail force.
(a)
Time domain curve of Wheel-rail force (b)
Maximum wheel-rail force (c)
Rate of wheel load reductionFigure4(c) shows the influence of the contact loss length on the rate of wheel load reduction. It indicates that, for a 200 km/h train speed, when the contact loss length is less than 1.2 m, it hardly affects the rate of wheel load reduction, when the contact loss length increases to 2.0 m, the rate of wheel load reduction only grows by 7.7%, while for a 250 km/h train speed, when the contact loss length is less than 1.0 m, it barely has influence on the wheel load reduction rate, and when the contact loss length increases to 2.0 m, the rate of wheel load reduction rises about 14.5%. For a 300 km/h train speed, when the contact loss length is less than 0.7 m, the wheel load reduction barely changes with the increased contact loss length, and when the contact loss length increases to 2.0 m, the rate of wheel load increases about 39.0% to 0.5541. According to the research conducted by Zhai [23], in order to ensure the ride safety, the wheel load reduction rate of high-speed vehicle should not exceed 0.6. It can be concluded that for train speed no more than 300 km/h, the contact loss which is less than 2.0 m barely affects the ride safety.


## 5. Dynamic Response of Track Subsystem

Due to the excitation of rail irregularity, the train load will result in the vibration of track system. With the deterioration of track and the increased train speed, the vibration displacement of track system increases gradually. Once the vibration displacement is plethoric, it will cause the damage of track system which has an important impact on the ride smoothness and safety. In this case, the train has to slow down or stop. Therefore, the dynamic response of track system has important significance on ensuring the ride smoothness and safety.


### 5.1. Displacement of Rail

The vibration displacement of rail plays an important role in the rail irregularity, and the plethoric displacement of rail may affect the ride safety. Figure5(a) shows the relation between the length of contact loss and the vibration displacement of rail. The rail vibration displacement in the time domain is shown in Figure 5(b).Figure 5
Influence of contact loss length on the dynamic responses of rail.
(a)
Rail displacement (b)
Time-displacement curve of rail displacement (c)
Effects of the contact loss length on the rail accelerationFrom Figure5(a), it can be found that when the contact loss length is no more than 0.5 m, the increasing contact loss length has slight influence on the vibration displacement of rail. When the length of contact loss beneath the track slab exceeds 0.5 m, the displacement of rail has a significant upward trend. Compared with the normal slab without contact loss, when the contact loss length becomes 1.5 m, for a 200 km/h train speed, the displacement of rail increases about 75.3%; for a 250 km/h train speed, it increases about 79.32%; for a 300 km/h train speed, it grows about 83.78%, while for the track slabs with 2.0 m contact loss, when the train is running at the speed of 300 km/h, there is a slight decline in the increase rate of the rail displacement.Figure5(b) indicates that when the contact loss length increases to 1.5 m, the vibration amplitude of rail is greater than that without contact loss. For the normal slab without contact loss, after the train passed, the displacement of rail gradually reduces to the original value, while for the slab with contact loss of 1.5 m in length, after the train passed, there is a significant vibration of rail before being back to the original condition, which means that, with the increase of contact loss length, the dynamic effect on rail increases significantly.Figure5(c) shows the influence of contact loss length on the rail acceleration. From Figure 5(c), it can be seen that the contact loss which is shorter than 0.5 m has bare influence on the rail acceleration. Once the contact loss length exceeds 0.5 m, the rail acceleration increases progressively with the increase of the contact loss length, especially when the contact loss length is in the range of 0.5 m to 1.2 m. When the contact loss length increases to 2.0 m, for a 200 km/h and a 250 km/h train speed, the rail acceleration increases approximately 40%, and for a 300 km/h train speed, the train acceleration only increases about 7.6%.


### 5.2. Displacement and Acceleration of Track Slab

The influence of contact loss length on the track displacement is shown in Figure6(a). It indicates that the vibration displacement of track slab is strongly related to the contact loss length. The contact loss beneath the track slab leads to the rapid increase of slab displacement. When the contact loss length increases to 1.5 m, the displacement of track at a 300 km/h train speed is the greatest (2.358 mm), which is 9.32 times of that of the normal slab without contact loss, while the displacement of track at 200 km/h is the smallest (1.758 mm), which is 6.40 times of that of the normal slab without contact loss. This means that at a higher train speed, the contact loss which is in the range of 0.0 m to 1.5 m has more impact on the displacement of track. When the contact loss length reaches 2.0 m, the displacement of track at 250 km/h becomes the biggest, instead of at 300 km/h, and it reaches 3.418 mm and 12.99 times of that of the normal slab.Figure 6
Influence of contact loss length on the dynamic characteristic of track slab.
(a)
The displacement of track slab (b)
The acceleration of track slabFigure6(b) shows the relationship between the contact loss length and the track acceleration. It can be seen that when the contact loss length is less than 1.2 m, with the increased contact loss length, the track acceleration is likely to increase linearly. When the contact loss length increases to 1.2 m, at the train speed of 200 km/h, 250 km/h, and 300 km/h, the track accelerations increase to 54.82 m/s2, 59.06 m/s2, and 70.62 m/s2, which are almost 20 times of that of the normal slab. When the contact loss length is over 1.2 m, for a 200 km/h train speed, the acceleration of track almost keeps the same level, while for the train speed of 250 km/h and 300 km/h, the accelerations of track increase continuously, and when the length of contact loss reaches 2.0 m, the track accelerations reach 102.87 m/s2 and 116.83 m/s2, respectively.


### 5.3. Displacement and Acceleration of Concrete Roadbed

Figure7(a) represents the influence of contact loss length on the vibration displacement of concrete roadbed. It is clear that for the track with contact loss which is shorter than 1.2 m, the vibration displacement of concrete roadbed grows slightly with the increased contact loss length. When the contact loss length increases from 0.0 m to 1.2 m, for a 200 km/h train speed, the displacement of concrete roadbed grows by 2.09%; for a 250 km/h train speed and a 300 km/h train speed, the displacements increase about 3.18% and 4.43%, respectively, while for the contact loss length exceeding 1.2 m, the displacements of concrete roadbed are almost at the same value.Figure 7
Influence of contact loss length on the dynamic characteristic of concrete roadbed.
(a)
The displacement of concrete roadbed (b)
The acceleration of concrete roadbedFigure7(b) shows the influence of the contact loss length on the acceleration of concrete roadbed. It can be seen that when the length of contact loss beneath the track slab is less than 0.5 m, the acceleration of concrete roadbed reduces with the increased contact loss length. After that, there is an upward trend for the acceleration of concrete roadbed until the contact loss length reaches 1.2 m; then, it almost keeps the same level.From Figures7(a) and 7(b), it can be found that the concrete roadbed displacement is always in the range of 0.250 mm to 0.280 mm and the acceleration is always in the range of 0.2 m/s2 to 1.0 m/s2, and it can be concluded that the contact loss length has very small influence on the displacement and acceleration of the concrete roadbed.


## 5.1. Displacement of Rail

The vibration displacement of rail plays an important role in the rail irregularity, and the plethoric displacement of rail may affect the ride safety. Figure5(a) shows the relation between the length of contact loss and the vibration displacement of rail. The rail vibration displacement in the time domain is shown in Figure 5(b).Figure 5
Influence of contact loss length on the dynamic responses of rail.
(a)
Rail displacement (b)
Time-displacement curve of rail displacement (c)
Effects of the contact loss length on the rail accelerationFrom Figure5(a), it can be found that when the contact loss length is no more than 0.5 m, the increasing contact loss length has slight influence on the vibration displacement of rail. When the length of contact loss beneath the track slab exceeds 0.5 m, the displacement of rail has a significant upward trend. Compared with the normal slab without contact loss, when the contact loss length becomes 1.5 m, for a 200 km/h train speed, the displacement of rail increases about 75.3%; for a 250 km/h train speed, it increases about 79.32%; for a 300 km/h train speed, it grows about 83.78%, while for the track slabs with 2.0 m contact loss, when the train is running at the speed of 300 km/h, there is a slight decline in the increase rate of the rail displacement.Figure5(b) indicates that when the contact loss length increases to 1.5 m, the vibration amplitude of rail is greater than that without contact loss. For the normal slab without contact loss, after the train passed, the displacement of rail gradually reduces to the original value, while for the slab with contact loss of 1.5 m in length, after the train passed, there is a significant vibration of rail before being back to the original condition, which means that, with the increase of contact loss length, the dynamic effect on rail increases significantly.Figure5(c) shows the influence of contact loss length on the rail acceleration. From Figure 5(c), it can be seen that the contact loss which is shorter than 0.5 m has bare influence on the rail acceleration. Once the contact loss length exceeds 0.5 m, the rail acceleration increases progressively with the increase of the contact loss length, especially when the contact loss length is in the range of 0.5 m to 1.2 m. When the contact loss length increases to 2.0 m, for a 200 km/h and a 250 km/h train speed, the rail acceleration increases approximately 40%, and for a 300 km/h train speed, the train acceleration only increases about 7.6%.


## 5.2. Displacement and Acceleration of Track Slab

The influence of contact loss length on the track displacement is shown in Figure6(a). It indicates that the vibration displacement of track slab is strongly related to the contact loss length. The contact loss beneath the track slab leads to the rapid increase of slab displacement. When the contact loss length increases to 1.5 m, the displacement of track at a 300 km/h train speed is the greatest (2.358 mm), which is 9.32 times of that of the normal slab without contact loss, while the displacement of track at 200 km/h is the smallest (1.758 mm), which is 6.40 times of that of the normal slab without contact loss. This means that at a higher train speed, the contact loss which is in the range of 0.0 m to 1.5 m has more impact on the displacement of track. When the contact loss length reaches 2.0 m, the displacement of track at 250 km/h becomes the biggest, instead of at 300 km/h, and it reaches 3.418 mm and 12.99 times of that of the normal slab.Figure 6
Influence of contact loss length on the dynamic characteristic of track slab.
(a)
The displacement of track slab (b)
The acceleration of track slabFigure6(b) shows the relationship between the contact loss length and the track acceleration. It can be seen that when the contact loss length is less than 1.2 m, with the increased contact loss length, the track acceleration is likely to increase linearly. When the contact loss length increases to 1.2 m, at the train speed of 200 km/h, 250 km/h, and 300 km/h, the track accelerations increase to 54.82 m/s2, 59.06 m/s2, and 70.62 m/s2, which are almost 20 times of that of the normal slab. When the contact loss length is over 1.2 m, for a 200 km/h train speed, the acceleration of track almost keeps the same level, while for the train speed of 250 km/h and 300 km/h, the accelerations of track increase continuously, and when the length of contact loss reaches 2.0 m, the track accelerations reach 102.87 m/s2 and 116.83 m/s2, respectively.


## 5.3. Displacement and Acceleration of Concrete Roadbed

Figure7(a) represents the influence of contact loss length on the vibration displacement of concrete roadbed. It is clear that for the track with contact loss which is shorter than 1.2 m, the vibration displacement of concrete roadbed grows slightly with the increased contact loss length. When the contact loss length increases from 0.0 m to 1.2 m, for a 200 km/h train speed, the displacement of concrete roadbed grows by 2.09%; for a 250 km/h train speed and a 300 km/h train speed, the displacements increase about 3.18% and 4.43%, respectively, while for the contact loss length exceeding 1.2 m, the displacements of concrete roadbed are almost at the same value.Figure 7
Influence of contact loss length on the dynamic characteristic of concrete roadbed.
(a)
The displacement of concrete roadbed (b)
The acceleration of concrete roadbedFigure7(b) shows the influence of the contact loss length on the acceleration of concrete roadbed. It can be seen that when the length of contact loss beneath the track slab is less than 0.5 m, the acceleration of concrete roadbed reduces with the increased contact loss length. After that, there is an upward trend for the acceleration of concrete roadbed until the contact loss length reaches 1.2 m; then, it almost keeps the same level.From Figures7(a) and 7(b), it can be found that the concrete roadbed displacement is always in the range of 0.250 mm to 0.280 mm and the acceleration is always in the range of 0.2 m/s2 to 1.0 m/s2, and it can be concluded that the contact loss length has very small influence on the displacement and acceleration of the concrete roadbed.


## 6. Experimental Procedure

### 6.1. Model Preparation

There were two CRTS-I Slab Track models arranged in this test. Based on the construction process of CRTS-I Slab Track in Chinese passenger dedicated line, its prototype was constructed and used as the test model. The model preparation process is shown in Figure8. The track slab was prefabricated as a two-way prestressed concrete slab, the concrete roadbed and the cylindrical bollards were made with C40 reinforced concrete through field construction. The mechanical performance of CA mortar met the tentative requirements of the CA mortar for the CRTS-I Slab Track in passenger dedicated line.Figure 8
Production process of model.


### 6.2. Train Load

In this test, the train load was generated by the customized ZSS50 excitation car (as shown in Figure9) which consisted of a left experimental flat car and a right vibration car. There are two wheel-sets of experimental flat car; the front wheel-set was excitation wheel-set and the rear wheel-set was moving wheel; the length between the two wheel-sets is 3 m. The experimental flat simulates a bogie of high-speed vehicle. As shown in Figure 9, track slabs can be placed on the experimental flat car to make the static wheel load keeping at a certain level. There is a pair of eccentric blocks locked on the excitation car, and it was connected with the vibration motor placed on the vibration car. When the vibration motor is turning on, the rotating eccentric blocks can generate a sine vibration force to simulate the dynamic wheel load. The frequency and amplitude of dynamic wheel load vary with the different mass of eccentric blocks and rotated speed of eccentric motor. The excitation frequency can range from 10 Hz to 30 Hz; the ambient temperature for operating ranges from −45°C to 45°C.Figure 9
ZSS50 excitation car.


### 6.3. Dynamic Test

Two Slabs were provided for the dynamic test, and the CA mortar under the right end of Number 2 slab was excavated to simulate contact loss beneath the track slab (as shown in Figure10(b)). Based on the research conducted by Liu [24], the contact loss beneath the track slab which exceeds 1.538 m would lead to the plethoric pulling force of fasteners and the vertical rail displacement. This dynamic test focused on the influence of the contact loss length ranging from 0.0 m to 1.2 m on the dynamic characteristics of the slab track. During the test, the CRTS-I Slab Track was subjected to the repeated load generated by the ZSS50 excitation car; the vibration wheel-set was applied on the middle of Number 2 slab (the triangle areas shown in Figure 10(a)); the excitation frequency was 15 Hz. There were two track slabs placed on the experimental flat car to add the static wheel load to 55 kN; the dynamic wheel load ranged from 46 kN to 64 kN.Figure 10
The cement emulsified asphalt contact loss in the prototype experiment.
(a)
The contact loss position (b)
The excavated contact loss beneath the track slab


### 6.4. Test Results

#### 6.4.1. Wheel-Rail Force

During the test process, the wheel-rail force was tested using the shear difference method. Figure11 shows the maximum wheel-rail force change with the length of the contact loss beneath the track slab.Figure 11
Maximum wheel-rail force with different contact loss length.From Figure11, it is clear that with the increased contact loss length, the wheel-rail force increases significantly. For the excitation car on the normal slab track without the contact loss, the tested maximum wheel-rail force was 62.73 kN. When the contact loss of 0.3 m in length occurred, the tested maximum wheel-rail force rose about 2.4%, then for the contact loss length increased to 1.2 m, the tested maximum wheel-rail force rose about 11.7%.For a 300 km/h train speed, if the length of one vehicle is 22 m, the wheel passing frequency is 15 Hz [23]. So the experimental results should be compared with the results of the vehicle-track vertical vibration FEM model at a train speed of 300 km/h. Comparing Figures 11 and 4(b), it can be found that the maximum wheel-rail force of FEM model is much bigger than that of experimental test. The reason should include two sides. For one thing, the static wheel load of FEM model (68.25 kN) is bigger than that of experiment test. For another, the irregularity of FEM model significantly magnifies the dynamic response of wheel-rail force. Even though the maximum wheel-rail forces of FEM model and experimental test are not at the same level, it has the same upward trend with the increased contact loss length. The contact loss length would lead to the wheel-rail force increase, especially for the contact loss longer than 0.3 m.


#### 6.4.2. Accelerations of Rail and Track Slab

According to the analysis results of vehicle-track vertical vibration FEM model, it can be found that, compared with the dynamic characteristic of rail and concrete roadbed, the dynamic characteristic of track slab is more sensitive to the change of the contact loss length. During the test, the rail acceleration and the track acceleration were measured as is shown in Figure12.Figure 12
The tested results of the influence of contact loss length on the dynamic responses of track subsystem.
(a)
Tested acceleration of rail (b)
Tested acceleration of trackBecause of the bigger wheel-rail force and the excitation of irregularity in FEM model, the tested dynamic acceleration of rail and track slab is smaller than that of FEM model. From Figure12, it can be concluded that when the contact loss is longer than 0.3 m, the acceleration of rail has a significant increase with the increased contact loss length, and when the contact loss beneath the track slab occurs, the acceleration of track slab increases rapidly. When the contact loss length increases from 0.0 m to 1.2 m, compared with the normal track slab without contact loss, the tested rail acceleration rose 53.7% and the FEM rail acceleration rose about 5.98%, while the tested track slab acceleration increased by 11.35 times and the FEM acceleration increased by 20.71 times.It can be concluded that the dynamic characteristic of track slab is more sensitive to the contact loss; once the contact loss occurs, it would lead to a rapid increase of track acceleration, while the contact loss longer than 0.7 m would cause a significant increase of rail acceleration.


## 6.1. Model Preparation

There were two CRTS-I Slab Track models arranged in this test. Based on the construction process of CRTS-I Slab Track in Chinese passenger dedicated line, its prototype was constructed and used as the test model. The model preparation process is shown in Figure8. The track slab was prefabricated as a two-way prestressed concrete slab, the concrete roadbed and the cylindrical bollards were made with C40 reinforced concrete through field construction. The mechanical performance of CA mortar met the tentative requirements of the CA mortar for the CRTS-I Slab Track in passenger dedicated line.Figure 8
Production process of model.


## 6.2. Train Load

In this test, the train load was generated by the customized ZSS50 excitation car (as shown in Figure9) which consisted of a left experimental flat car and a right vibration car. There are two wheel-sets of experimental flat car; the front wheel-set was excitation wheel-set and the rear wheel-set was moving wheel; the length between the two wheel-sets is 3 m. The experimental flat simulates a bogie of high-speed vehicle. As shown in Figure 9, track slabs can be placed on the experimental flat car to make the static wheel load keeping at a certain level. There is a pair of eccentric blocks locked on the excitation car, and it was connected with the vibration motor placed on the vibration car. When the vibration motor is turning on, the rotating eccentric blocks can generate a sine vibration force to simulate the dynamic wheel load. The frequency and amplitude of dynamic wheel load vary with the different mass of eccentric blocks and rotated speed of eccentric motor. The excitation frequency can range from 10 Hz to 30 Hz; the ambient temperature for operating ranges from −45°C to 45°C.Figure 9
ZSS50 excitation car.


## 6.3. Dynamic Test

Two Slabs were provided for the dynamic test, and the CA mortar under the right end of Number 2 slab was excavated to simulate contact loss beneath the track slab (as shown in Figure10(b)). Based on the research conducted by Liu [24], the contact loss beneath the track slab which exceeds 1.538 m would lead to the plethoric pulling force of fasteners and the vertical rail displacement. This dynamic test focused on the influence of the contact loss length ranging from 0.0 m to 1.2 m on the dynamic characteristics of the slab track. During the test, the CRTS-I Slab Track was subjected to the repeated load generated by the ZSS50 excitation car; the vibration wheel-set was applied on the middle of Number 2 slab (the triangle areas shown in Figure 10(a)); the excitation frequency was 15 Hz. There were two track slabs placed on the experimental flat car to add the static wheel load to 55 kN; the dynamic wheel load ranged from 46 kN to 64 kN.Figure 10
The cement emulsified asphalt contact loss in the prototype experiment.
(a)
The contact loss position (b)
The excavated contact loss beneath the track slab


## 6.4. Test Results

### 6.4.1. Wheel-Rail Force

During the test process, the wheel-rail force was tested using the shear difference method. Figure11 shows the maximum wheel-rail force change with the length of the contact loss beneath the track slab.Figure 11
Maximum wheel-rail force with different contact loss length.From Figure11, it is clear that with the increased contact loss length, the wheel-rail force increases significantly. For the excitation car on the normal slab track without the contact loss, the tested maximum wheel-rail force was 62.73 kN. When the contact loss of 0.3 m in length occurred, the tested maximum wheel-rail force rose about 2.4%, then for the contact loss length increased to 1.2 m, the tested maximum wheel-rail force rose about 11.7%.For a 300 km/h train speed, if the length of one vehicle is 22 m, the wheel passing frequency is 15 Hz [23]. So the experimental results should be compared with the results of the vehicle-track vertical vibration FEM model at a train speed of 300 km/h. Comparing Figures 11 and 4(b), it can be found that the maximum wheel-rail force of FEM model is much bigger than that of experimental test. The reason should include two sides. For one thing, the static wheel load of FEM model (68.25 kN) is bigger than that of experiment test. For another, the irregularity of FEM model significantly magnifies the dynamic response of wheel-rail force. Even though the maximum wheel-rail forces of FEM model and experimental test are not at the same level, it has the same upward trend with the increased contact loss length. The contact loss length would lead to the wheel-rail force increase, especially for the contact loss longer than 0.3 m.


### 6.4.2. Accelerations of Rail and Track Slab

According to the analysis results of vehicle-track vertical vibration FEM model, it can be found that, compared with the dynamic characteristic of rail and concrete roadbed, the dynamic characteristic of track slab is more sensitive to the change of the contact loss length. During the test, the rail acceleration and the track acceleration were measured as is shown in Figure12.Figure 12
The tested results of the influence of contact loss length on the dynamic responses of track subsystem.
(a)
Tested acceleration of rail (b)
Tested acceleration of trackBecause of the bigger wheel-rail force and the excitation of irregularity in FEM model, the tested dynamic acceleration of rail and track slab is smaller than that of FEM model. From Figure12, it can be concluded that when the contact loss is longer than 0.3 m, the acceleration of rail has a significant increase with the increased contact loss length, and when the contact loss beneath the track slab occurs, the acceleration of track slab increases rapidly. When the contact loss length increases from 0.0 m to 1.2 m, compared with the normal track slab without contact loss, the tested rail acceleration rose 53.7% and the FEM rail acceleration rose about 5.98%, while the tested track slab acceleration increased by 11.35 times and the FEM acceleration increased by 20.71 times.It can be concluded that the dynamic characteristic of track slab is more sensitive to the contact loss; once the contact loss occurs, it would lead to a rapid increase of track acceleration, while the contact loss longer than 0.7 m would cause a significant increase of rail acceleration.


## 6.4.1. Wheel-Rail Force

During the test process, the wheel-rail force was tested using the shear difference method. Figure11 shows the maximum wheel-rail force change with the length of the contact loss beneath the track slab.Figure 11
Maximum wheel-rail force with different contact loss length.From Figure11, it is clear that with the increased contact loss length, the wheel-rail force increases significantly. For the excitation car on the normal slab track without the contact loss, the tested maximum wheel-rail force was 62.73 kN. When the contact loss of 0.3 m in length occurred, the tested maximum wheel-rail force rose about 2.4%, then for the contact loss length increased to 1.2 m, the tested maximum wheel-rail force rose about 11.7%.For a 300 km/h train speed, if the length of one vehicle is 22 m, the wheel passing frequency is 15 Hz [23]. So the experimental results should be compared with the results of the vehicle-track vertical vibration FEM model at a train speed of 300 km/h. Comparing Figures 11 and 4(b), it can be found that the maximum wheel-rail force of FEM model is much bigger than that of experimental test. The reason should include two sides. For one thing, the static wheel load of FEM model (68.25 kN) is bigger than that of experiment test. For another, the irregularity of FEM model significantly magnifies the dynamic response of wheel-rail force. Even though the maximum wheel-rail forces of FEM model and experimental test are not at the same level, it has the same upward trend with the increased contact loss length. The contact loss length would lead to the wheel-rail force increase, especially for the contact loss longer than 0.3 m.


## 6.4.2. Accelerations of Rail and Track Slab

According to the analysis results of vehicle-track vertical vibration FEM model, it can be found that, compared with the dynamic characteristic of rail and concrete roadbed, the dynamic characteristic of track slab is more sensitive to the change of the contact loss length. During the test, the rail acceleration and the track acceleration were measured as is shown in Figure12.Figure 12
The tested results of the influence of contact loss length on the dynamic responses of track subsystem.
(a)
Tested acceleration of rail (b)
Tested acceleration of trackBecause of the bigger wheel-rail force and the excitation of irregularity in FEM model, the tested dynamic acceleration of rail and track slab is smaller than that of FEM model. From Figure12, it can be concluded that when the contact loss is longer than 0.3 m, the acceleration of rail has a significant increase with the increased contact loss length, and when the contact loss beneath the track slab occurs, the acceleration of track slab increases rapidly. When the contact loss length increases from 0.0 m to 1.2 m, compared with the normal track slab without contact loss, the tested rail acceleration rose 53.7% and the FEM rail acceleration rose about 5.98%, while the tested track slab acceleration increased by 11.35 times and the FEM acceleration increased by 20.71 times.It can be concluded that the dynamic characteristic of track slab is more sensitive to the contact loss; once the contact loss occurs, it would lead to a rapid increase of track acceleration, while the contact loss longer than 0.7 m would cause a significant increase of rail acceleration.


## 7. Conclusions

In this study, the vehicle-track vertical coupling vibration FEM model was established to analyze the effects of the contact loss on the dynamic characteristic of the vehicle subsystem and the track subsystem at different train speeds. Then, the prototype experimental test was performed to verify the FEM model results. During the test, the customized ZSS50 excitation car was applied on the prototype of CRTS-I Slab Track with excavated CA mortar in different lengths which simulated the contact loss beneath the track slab. According to the analysis of the FEM model and the prototype experimental test, the following conclusions can be drawn:(1)
The vertical wheel-set acceleration is strongly dependent on the contact loss length, and the vertical bogie acceleration increases significantly once the contact loss length exceeds 0.7 m, whereas the vertical car body acceleration increases slightly when the contact loss length exceeds 1.5 m. Due to the shock absorption of primary suspensions and second suspensions, for a train speed no more than 300 km/h, the contact loss less than 2.0 m hardly affects the running smoothness of vehicle.(2)
With the increased contact loss length, the maximum wheel-rail force increases gradually, especially for the contact loss length in the range of 0.5 m to 1.5 m. There is a threshold value for the length of contact loss; once it is exceeded, the increase of the rate of wheel load reduction would occur. For the train speed of 200 km/h, 250 km/h, and 300 km/h, the threshold values are 1.2 m, 1.0 m, and 0.7 m, respectively. For the train speed less than 300 km/h, the contact loss shorter than 2.0 m barely leads to ride safety problem.(3)
For the track subsystem, the slab is the most sensitive component. Once the contact loss beneath the track slab occurs, the vibration displacement and the acceleration of track slab rise rapidly. When the length of contact loss beneath the track slab exceeds 0.5 m, there is a significant increase in the vibration amplitude and acceleration of rail. However, the contact loss length has little influence on the displacement and acceleration of the concrete roadbed.(4)
The results of prototype experimental test are in accordance with those of the vehicle-track vertical coupling vibration FEM model. Integrating the FEM model results and the experimental test results, the dynamic characteristics of the track subsystem are related to the contact loss length, especially for the track slab.



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*Source: 3073784-2016-11-21.xml*