Research Article  Open Access
Chao Chen, Mei Han, Yanhui Han, "A Numerical Model for Railroad Freight CartoCar End Impact", Discrete Dynamics in Nature and Society, vol. 2012, Article ID 927592, 11 pages, 2012. https://doi.org/10.1155/2012/927592
A Numerical Model for Railroad Freight CartoCar End Impact
Abstract
A numerical model based on LagrangeD'Alembert principle is proposed for cartocar end impact in this paper. In the numerical model, the friction forces are treated by using local linearization model when solving the differential equations. A computer program has been developed for the numerical model based on RungeKutta fourthorder method. The results are compared with the Multibody Dynamics/Kinematics software SIMPACK results and they are close. The ladings' relative displacement to struck car and the relative displacement between two ladings get larger as impact speed increases. There is no displacement between two ladings when the contact surfaces have the same friction coefficient.
1. Introduction
The freight damage incurred during railroad transportation is a serious economic and safety problem. The railroad freight car’s dynamic characteristic leads to most of the freight damage. The dynamics of railroad car and freight damage can be divided into two groups:(1)during the marshalling operation in train yard, the cartocar end impacts from coupling cause high car and lading acceleration;(2)the carbody vibrations come from track irregularities and some extra forces, such as the wind, and so forth.
Most of the damage is attributed to cartocar end impacts in the marshalling yard, so more focus is given on it when working out the load support and load securement method. Railroad freight car impact tests are always carried out for checking if the method can ensure transportation safety and no damage to the ladings. A railroad freight car impact test usually needs a lot of work to do; it needs much workforce, material resources, and financial support. Most of the time, carrying out an impact test will lead to disorder and breakoff transportation. Compared with impact test, numerical simulation is a more economical and faster method of investigating the effect on ladings when coupled.
Cartocar end impact is a special multibody dynamic problem between railroad freight cars. Investigation into the multibody dynamic has been carried out in the works [1–9]. Later, mathematical models are derived in [10] for studying the effect of impact on packaging. At the same time, numerical methods need to be developed for solving mathematical models. Euler tangent method, Newmark method, Wilson method, and RungeKutta fourthorder method are developed and widely applied in solving mathematical models [11–17]. RungeKutta fourthorder method means that the truncation error per step is . It is an important numerical method used extensively in engineering problems for solving firstorder differential equations.
Draft gear is the most important component of a freight car during impact. Its performance is investigated by mechanics dynamics software in [18–21]. The draft gear’s characteristic is analyzed under different impact speeds. The force versus draft gear travel of the Chinese MT2 under impact speed of 58 km/h is given by simulation and test.
In the paper, the secondorder differential equations of the cartocar end impact are converted to firstorder differential equations and solved by using RungeKutta 4th order method.
2. Draft Gear Interaction Process
Railroad cartocar end impacts usually occur in train yard, and most of the time the struck car is static when coupled with the striking car. The draft gear is an important component for reducing freight and car damage during cartocar end impacts.
MT2 friction draft gear is widely used in the class 70 t universal freight cars in China. This draft gear is composed by springs and friction mechanism; when it is compressed, part of kinetic energy is converted to friction energy and part of kinetic energy is converted to potential energy. MT2 draft gear has different force versus travel characteristic curves when loading and unloading. In Figure 1, the irreversible force versus draft gear travel characteristic curve is shown [22].
As shown in Figure 1, is draft gear travel and is speed difference between striking car and struck car. means draft gear loading process and means unloading process. Figure 1 shows that the resistant force in loading process is larger than unloading process. In the numerical calculation program, draft gear force versus travel characteristic curve is based on the test results, and the force is calculated by linear interpolation. MT2 draft gear force versus travel characteristic curves under impact speeds of 5 km/h, 6 km/h, 7 km/h, and 8 km/h are presented in the appendix.
3. CartoCar End Impact Dynamic Models
3.1. Railroad Freight Car Impact System
Railroad freight car impact test is using a striking car with a certain speed running to a static struck car and collides. The longitudinal status of the ladings and struck car is mainly observed during impact for checking the loading support and loading secure method. The method must ensure transportation safety and no lading damage.
The assumptions in models are(1)the wind acting on the striking car and struck car, and the rolling resistance between wheel and rail are neglected;(2)the carbody deformations during impact are neglected;(3)the carbody vertical bounce, yaw, pitch, and sway vibrations are neglected;(4)no lateral forces between ladings.
Sometimes more than one lading are loaded on freight car. There are longitudinal forces between ladings and car, between adjacent ladings. Figure 2 shows the railroad freight cartocar end impact dynamic system, where , represent mass and displacement, represents striking car, represents struck car, represent ladings, , are the stiffness and damping coefficients between ladings and car, , are the stiffness and damping coefficients between ladings and , is draft gear force, and is distance between two cars.
3.2. Longitudinal Dynamic Equations
The striking car, struck car and ladings in the impact dynamic system are treated as mass elements. According to the assumptions in Section 3.1, the external forces, constraint forces and inertial forces are an equivalent static system based on LagrangeD’Alembert principle. Then, universal longitudinal dynamic equations can be derived for each mass element.
External force acting on the striking car is the draft gear force. So the differential equation for striking car is where is gross weight of the striking car and is calculated by the following equation:
The acceleration and velocity initial values of the striking car are , ; the initial value of the draft gear force is .
The external forces acting on the struck car are the draft gear force and forces between ladings and car, where is the struck car tare weight and the acceleration and velocity initial values of struck car are , .
External forces acting on lading are the forces between lading and car, between adjacent ladings, where the acceleration and velocity initial values of lading are , .
4. DoubleStack Loading Impact Models
Doublestack loading method in gondola car is proposed as an example for analyzing longitudinal relation between ladings and car. It shows that the numerical method applied in railroad freight cartocar end impact simulation. In the model, the striking car and struck car are the same type and have the same draft gears.
4.1. Load Support and Load Securement Method and Force Analysis
Figure 3 shows the doublestack loading in a 70 t class gondola car. The securement method is using friction cushion to enlarge friction force.
The above struck car system includes three mass elements that are the struck car, 1st lading and 2nd lading. Forces acting on struck car are draft gear force and friction force from 1st lading; forces acting on the 1st lading are friction forces from struck car and the 2nd lading; force acting on the 2nd lading is friction force from 1st lading. The force analysis is illustrated in Figure 4.
4.2. Dynamic Equations of Motion
The universal longitudinal dynamic equations in Section 3.2 can be rewritten based on the force analysis
As striking car and struck car have the same draft gear type, so the travel of one draft gear is given as
The speed difference between striking car and struck car is given as
The model has two onedimensional friction elements: one is between 1st lading and carbody and the other is between 1st lading and 2nd lading. The onedimensional friction element’s friction force direction is dependent on the direction of the relative sliding velocity. Figure 5(a) shows that the direction of friction force changes abruptly as the direction of relative velocity changes. More calculation time is needed near the zeropoint, and even the differential equations cannot be integrated at zeropoint. The friction element is treated by using a local linearization model [23], which uses a parameter called switching speed. Figure 5(b) illustrates linear relationship between friction force and relative velocity, and the friction force is given as
(a)
(b)
4.3. Solution Methodology
For using RungeKutta fourthorder method, secondorder differential equations need to be rewritten in the form of firstorder differential equations. In general, to solve firstorder differential equation , RungeKutta fourthorder method is given as where is the step size.
Let in the striking car’s secondorder differential equation, then the reducedorder differential equations are given as
In the same way, the secondorder differential equations of other mass elements are given as,
4.4. Numerical Results and Discussion
The type of draft gear is MT2 in the dynamic models; the impact speeds are 5 km/h, 6 km/h, 7 km/h, and 8 km/h. The simulation is for studying relative displacement of 1st lading and 2nd lading, which are secured by the friction cushion. Case 1 only has friction cushion between 1st lading and car floor; Case 2 has friction cushion between 1st lading and car floor, and between two ladings; the friction cushion in Case 3 is the same as Case 1, but two ladings have different weight. The parameters in numerical model are given in Table 1.

A virtual model is built in Multibody Dynamics/Kinematics software SIMPACK which has the same parameters as Case 1 to validate the model and numerical method. It can be observed from Figure 6 that there is an excellent agreement between the results from RungeKutta fourthorder method and SIMPACK. The displacement between ladings and carbody and between 1st lading and 2nd lading increased with impact speeds.
Figure 7 shows the displacement between ladings and carbody under Case 2 versus different impact speeds. The displacement between ladings and carbody increased with impact speeds, but the displacement between 1st lading and 2nd lading is zero as two surfaces have the same friction coefficient.
In Case 3, the weight of 2nd lading is less than that in Case 1, so the gross weight of struck car reduced. The displacement between ladings and carbody versus impact speeds are illustrated in Figure 8. The displacements between ladings and carbody are increased compared with Case 1 under the same impact speed.
5. Conclusion
In this paper, railroad freight cartocar end impact system and the influence on ladings are considered. To derive differential equations of the system motion, forces acting in the system are analyzed and LagrangeD’Alembert principle is used. The obtained solution of the differential equations by RungeKutta fourthorder method is close to the results from SIMPACK. Based on numerical results from doublestack model, it is concluded that the higher the impact speed, the larger the ladings’ relative displacement to struck car. The lower weight the ladings, the larger the ladings’ relative displacement to struck car. There is no displacement between two ladings if they have the same friction coefficient between struck car and 1st lading and between 1st lading and 2nd lading.
Appendix
(a)
(b)
(c)
(d)
Acknowledgment
This paper is supported by “the Fundamental Research Funds for the Central Universities” (2011JBM246).
References
 W. Wang, Vehicle's ManMachine Interaction Safety and Driver Assistance, China Communications Press, Beijing, China, 2012. View at: Zentralblatt MATH
 H. J. Fletcher, L. Rongved, and E. Y. Yu, “Dynamics analysis of a twobody gravitationally oriented satellite,” Bell System Technical Journal, vol. 42, no. 5, pp. 2239–2266, 1963. View at: Google Scholar
 W. W. Hooker and G. Margulies, “The dynamical attitude equations for an $n$body satellite,” American Astronautical Society. Journal of the Astronautical Sciences, vol. 12, pp. 123–128, 1965. View at: Google Scholar
 W. W. Hooker, “A set of rdynamical attitude equations for an arbitrary nbody satellite having rotational degrees of freedom,” American Institute of Aeronautics and Astronautics Journal, vol. 8, no. 7, pp. 1205–1207, 1970. View at: Google Scholar  Zentralblatt MATH
 R. Schwertassek and R. E. Roberson, “A statespace dynamical representation for multibody mechanical systems part I: systems with tree configuration,” Acta Mechanica, vol. 50, no. 34, pp. 141–161, 1984. View at: Publisher Site  Google Scholar
 R. E. Roberson and R. Schwertassek, Dynamics of Multibody Systems, Springer, Berlin, Germany, 1988.
 W. Wang, X. Jiang, S. Xia, and Q. Cao, “Incident tree model and incident tree analysis method for quantified risk assessment: an indepth accident study in traffic operation,” Safety Science, vol. 48, no. 10, pp. 1248–1262, 2010. View at: Publisher Site  Google Scholar
 R. E. Roberson and W. Wittenburg, “A dynamical formalism for an arbitrary number of interconnected rigid bodies with reference to the problem of satellite attitude control,” in Proceedings of the 3rd International Federation of Automatic Control Congress (IFAC '66), London, UK, 1966. View at: Publisher Site  Google Scholar
 J. Wittenburg, Dynamics of Systems of Rigid Bodies, Teubner, Stuttgart, Germany, 1977.
 R. V. Dukkipati, Vehicle Dynamics, CRC Press, Boca Raton, Fla, USA, 2000.
 N. M. Newmark, “A method of computation for structural dynamics,” Journal of the Engineering Mechanical Division, vol. 85, no. 2, pp. 67–94, 1959. View at: Google Scholar
 E. L. Wilson, I. Farhoomand, and K. J. Bathe, “Nonlinear dynamic analysis of complex structure,” Earthquake Engineering and Structural Dynamics, vol. 1, no. 3, pp. 241–252, 1973. View at: Google Scholar
 K. J. Bath and E. L. Wilson, Numerical Methods in Finite Element Analysis, Prentice Hall, New York, NY, USA, 1976.
 E. Süli and D. F. Mayers, An Introduction to Numerical Analysis, Cambridge University Press, Cambridge, UK, 2003.
 J. Stoer and R. Bulirsch, Introduction to Numerical Analysis, Springer, New York, NY, USA, 3rd edition, 2002.
 G. DaHu and S. A. Meguid, “Stability of RungeKutta methods for delay differential systems with multiple delays,” IMA Journal of Numerical Analysis, vol. 19, no. 3, pp. 349–356, 1999. View at: Publisher Site  Google Scholar
 W. Zhiqiao, LStable Methods for Numerical Solution of Structural Dynamics Equations and Multibody Dynamics Equations, National University of Defense Technology, 2009.
 T. Guangrong, Study on System Dynamics of Heavy Haul Train, Southwest Jiaotong University, 2009.
 W. Chengguo, M. Dawei, W. Xuejun, and L. Lan, “Research on structures and performances of heavy haul buffer by numerical simulation,” Railway Locomotive & Car, vol. 29, no. 5, pp. 1–4, 2009. View at: Google Scholar
 H. Guoliang, L. Fengtao, W. Xuejun, and W. Chengguo, “Characteristics research in spring friction draft gear of heavy haul freight cars,” Lubrication Engineering, vol. 34, no. 7, pp. 69–73, 2009. View at: Google Scholar
 L. Ming, H. Guoliang, W. Xuejun, and W. Chengguo, “Simulation analysis and experiment research into two typical draft gear of heavy haul freight cars,” Coal Mine Machinery, vol. 30, no. 9, pp. 76–78, 2009. View at: Google Scholar
 H. Yunhua, L. Fu, and F. Maohai, “Research on the characteristics of vehicle buffers,” China Railway Science, vol. 26, no. 1, pp. 95–99, 2005. View at: Google Scholar
 D. Karnopp, “Computer simulation of stickslip friction in mechanical dynamic systems,” Journal of Dynamic Systems, Measurement and Control, Transactions of the ASME, vol. 107, no. 1, pp. 101–103, 1985. View at: Publisher Site  Google Scholar
Copyright
Copyright © 2012 Chao Chen 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.