MATEC Web of Conferences 157, 03006 (2018) https://doi.org/10.1051/matecconf/201815703006 MMS 2017
Calculated estimation of railway wheels equivalent conicity influence on critical speed of railway passenger car
Juraj Gerlici1,*, Rostyslav Domin2, Ganna Cherniak2, Tomáš Lack1 1University of Žilina, Faculty of Mechanical Engineering, Department of Transport and Handling Machines, 010 26 Žilina, Slovak Republic 2Volodymyr Dahl East Ukrainian National University, Department of Rail Transport, 93400 Sewerodonetsk, Ukraine
Abstract. The article presents the results of determining the equivalent conicity characterizing the geometric interaction of wheels and rails on 1520 mm track. The cases of interactions of rails and wheelsets, wheels of which have different profiles, are considered. The computer model of the motion speed of the passenger car is developed. According to the results of computer simulation, critical speeds for the bogie moving through the tracks of indented gauge are received. Based on the results of the simulation analysis, the significant dependence of the value of the equivalent conicity on the critical speed is confirmed. The necessity of considering the limit values of equivalent conicity in tests of high-speed rolling stock is emphasized. Keywords: railway wheels, equivalent conicity, critical speed, passenger vehicle
1 Introduction The increase of speed of passenger trains up to 160-200 km/h brings new technological level on the Ukrainian railways. Cars of high-speed trains must fully comply with international requirements, both in the level of comfort, and in terms of safety. In this regard, the task of ensuring the stability of motion of the high-speed rolling stock must be resolved as a matter of priority. According to the results of numerous researches, depending on the design and parameters of running gears the configuration of working surfaces of wheels and rails significantly affects the dynamic behavior of rail vehicles, in particular, critical speeds in respect of hunting oscillations [1, 4, 6]. The problem of optimal interaction of underframes and the track becomes of particular importance for high-speed rolling stock. According to regulatory documents operating on the railways of the European Union, field tests on the admission of the rolling stock to operation must be carried out under certain parameters of interaction between wheels and rails, including those which reflect the conditions of the worn out surfaces in contact [5, 13]. Such an approach was implemented to test the impact of natural wear of wheels and rails on the dynamic characteristics of the
* Corresponding author: [email protected] Reviewers: Alžbeta Sapietová, Josef Soukup
© The Authors, published by EDP Sciences. This is an open access article distributed under the terms of the Creative Commons Attribution License 4.0 (http://creativecommons.org/licenses/by/4.0/). MATEC Web of Conferences 157, 03006 (2018) https://doi.org/10.1051/matecconf/201815703006 MMS 2017
rolling stock. The results of the relevant research proved that for certain units of the rolling stock critical speeds in respect of hunting oscillation are considerably sensitive to contours of the threads of wheels [3]. However, up to this day regulatory documents on running dynamic tests of rolling stocks for 1520 mm tracks do not envisage tests on the impact of the depreciation of wheels on the dynamic behavior of the rolling stock, which does not allow qualitatively assess of its running characteristics in real operating conditions [2].
2 Characteristics of equivalent conicity According to numerous studies of oscillations and stability of motion of railway rolling stocks, geometric characteristics of the interaction of wheels and rails are the factors that determine the dynamic properties of the rolling stock [8, 11]. Therefore, in the study of conditions for safe and comfortable operation of the rolling stock intended for operation with high speeds, the impact of geometric characteristics of the interaction of wheels and rails should be estimated as a matter of priority. Among the parameters that characterize the geometric interaction of wheelsets and rails, the so-called “equivalent conicity” takes on the generalized role. Namely this parameter provides optimal estimation of the contact of the pair “wheel-rail” on straight sections of track and in curves of large radius. According to the known definitions, the equivalent conicity is equal to tangent tgγe of the cone angle γe of the wheelset with conical wheels, transverse movement of which has the same kinematic wavelength as this wheelset [12]. The equivalent conicity provides an opportunity to compare conditions of the contact of wheels and rails in different states based on the design and maintenance. The linearization approach is used. This approach involves the replacement of nonlinear dependence of the change of the radius of rolling circumference for linear one. The angular coefficient of linear dependence is the equivalent conicity. It is necessary to adhere to common rules in determining the equivalent conicity in order to able to compare the results obtained for various railways. For this purpose, the International Union of Railways implemented the principles of calculating the equivalent conicity defined by UIC 519 Leaflet [12]. Methods of calculating the equivalent conicity are as follows: analytical description of profiles of wheels and rails is given; Δr = f(y) characteristic is calculated for each lateral displacement y of the wheelset as the difference between right and left radius of rolling circumference of wheels Δr = rr - rl; the equivalent conicity tgγe for the lateral displacement y of the wheelset is determined using linear regression for the part of Δr = f(y) characteristic within 2y interval. The equivalent conicity should be calculated with the actual wheel profile of the tested vehicle and theoretical profile of the rail of the track with corresponding gauge. The lateral displacement of the wheelset is considered in the range of y = ± 3 mm. Acceptable values of the equivalent conicity, which should not be exceeded during the test of the rolling stock on the track, depend on the speed characteristics of rolling stocks and equal to [5]: 0.5 – at V ≤ 140 km/h; 0.4 –140 km/h < V ≤ 200 km/h; 0.35 – 200 km/h < V ≤ 230 km/h; 0.3 – 230 km/h < V ≤ 250 km/h; 0.25 – 250 km/h < V ≤ 280 km/h; 0.15 – 280 km/h < V ≤ 350 km/h. Values of the equivalent conicity for options of wheels profiles used on the Ukrainian railways are calculated in accordance with the said method, in particular, with GOST 9036 and DMetI, developed at the National Metallurgical Academy (Dnipro city) [7]. The wheel profile complying with GOST 9036 is considered in two states: initial (new or turned) and worn (Fig. 1).
2 MATEC Web of Conferences 157, 03006 (2018) https://doi.org/10.1051/matecconf/201815703006 MMS 2017 rolling stock. The results of the relevant research proved that for certain units of the rolling stock critical speeds in respect of hunting oscillation are considerably sensitive to contours of the threads of wheels [3]. However, up to this day regulatory documents on running dynamic tests of rolling stocks for 1520 mm tracks do not envisage tests on the impact of the depreciation of wheels on the dynamic behavior of the rolling stock, which does not allow qualitatively assess of its running characteristics in real operating conditions [2].
2 Characteristics of equivalent conicity
According to numerous studies of oscillations and stability of motion of railway rolling stocks, geometric characteristics of the interaction of wheels and rails are the factors that determine the dynamic properties of the rolling stock [8, 11]. Therefore, in the study of Fig. 1. Profiles of considered wheels (1 – new profile complying with GOST; 2 – profile with wear; 3 – DMetI profile) conditions for safe and comfortable operation of the rolling stock intended for operation with high speeds, the impact of geometric characteristics of the interaction of wheels and ccording to the recommendations of the rganization for ailways ooperation at the rails should be estimated as a matter of priority. maintenance of track on the sections of high speed operation minimum gauge tolerances Among the parameters that characterize the geometric interaction of wheelsets and rails, are and the ma imum ones are . hus the gauge for mm track the so-called “equivalent conicity” takes on the generalized role. Namely this parameter may e within – mm range. quivalent conicities at the change of gauge of the provides optimal estimation of the contact of the pair “wheel-rail” on straight sections of track with rails within the specified range in increments of mm are calculated for track and in curves of large radius. According to the known definitions, the equivalent given profiles of wheels. conicity is equal to tangent tgγe of the cone angle γe of the wheelset with conical wheels, he results of calculations showed that equivalent conicity tgγe for wheels with new transverse movement of which has the same kinematic wavelength as this wheelset [12]. standard profile of the running surface within the gauge changes from to mm is The equivalent conicity provides an opportunity to compare conditions of the contact of constant and equals to . . he equivalent conicity for wheels with worn running surface wheels and rails in different states based on the design and maintenance. The linearization changes from the value of . at mm track to the value of . at mm track. approach is used. This approach involves the replacement of nonlinear dependence of the hen the track gauge varies from mm to mm the value of tgγe varies from change of the radius of rolling circumference for linear one. The angular coefficient of . to . . hen the track gauge amounts to mm tgγe is equal to . and linear dependence is the equivalent conicity. when the track gauge increases from mm to mm the value of the equivalent It is necessary to adhere to common rules in determining the equivalent conicity in order to conicity changes from . 33 to . . able to compare the results obtained for various railways. For this purpose, the International or the wheel with the running surface complying with et profile the value of the Union of Railways implemented the principles of calculating the equivalent conicity equivalent conicity gradually changes from tgγe = . at mm track gauge to tgγe = defined by UIC 519 Leaflet [12]. . at mm track gauge which more than dou le the value of effective conicity in Methods of calculating the equivalent conicity are as follows: analytical description of case of wheels with the standard profile of running surfaces. profiles of wheels and rails is given; Δr = f(y) characteristic is calculated for each lateral ifferences etween the values of effective conicity for wheels with different profiles displacement y of the wheelset as the difference between right and left radius of rolling lead to a change in lengths of hunting waves Lhe of the wheelset. hus in the case of wheels circumference of wheels Δr = rr - rl; the equivalent conicity tgγe for the lateral displacement turned in accordance with 3 profile Lhe is equal to . m and independent of y of the wheelset is determined using linear regression for the part of Δr = f(y) the track gauge and in case of worn wheels the value of Lhe varies from . m at S = characteristic within 2y interval. mm to . at S = mm. n case of the use of et profile the length of the hunting The equivalent conicity should be calculated with the actual wheel profile of the tested wave of the wheelset slightly varies from . m to .3 m at the increase of track gauge vehicle and theoretical profile of the rail of the track with corresponding gauge. The lateral within – mm range. displacement of the wheelset is considered in the range of y = ± 3 mm. t should e noted that the reduction in the length of the hunting wave increases Acceptable values of the equivalent conicity, which should not be exceeded during the test frequencies of horizontal oscillations of the rolling stock. hus at = km h the of the rolling stock on the track, depend on the speed characteristics of rolling stocks and frequency of hunting oscillations of the wheelset with 3 profile wheels at equal to [5]: 0.5 – at V ≤ 140 km/h; 0.4 –140 km/h < V ≤ 200 km/h; 0.35 – 200 km/h < V ≤ mm track is . z whereas the frequency of hunting oscillations of the wheelset with 230 km/h; 0.3 – 230 km/h < V ≤ 250 km/h; 0.25 – 250 km/h < V ≤ 280 km/h; 0.15 – 280 worn wheels increases to .3 z. km/h < V ≤ 350 km/h. a le rings together the values of effective conicity tgγe and the length of the hunting Values of the equivalent conicity for options of wheels profiles used on the Ukrainian wave Lhe which are calculated for three configuration options of wheels running surfaces in railways are calculated in accordance with the said method, in particular, with GOST 9036 question at different track gauges. and DMetI, developed at the National Metallurgical Academy (Dnipro city) [7]. The wheel a le data showed that considered com inations of wheels profiles and rails differ profile complying with GOST 9036 is considered in two states: initial (new or turned) and significantly y the nature of interaction. ccording to the results of numerous studies worn (Fig. 1). configuration of working surfaces of wheels and rails can significantly affect the dynamic ehavior of rail vehicles in particular critical speeds in respect of hunting oscillations depending on the design and parameters of the running gears.
3 MATEC Web of Conferences 157, 03006 (2018) https://doi.org/10.1051/matecconf/201815703006 MMS 2017
Table 1.
Standard profile Track gauge, DMetI profile New Worn mm tgγe Lhe, m tgγe Lhe, m tgγe Lhe, m
3 Determination of critical speeds subsystems method [10]. Structurally “Passenger car” object is an integral system – “Wheelsets”; 2 – “Bogie”; 3 – “Passenger car”. The general model contains identical dissipative properties and force relations. The general system “Passenger car”
Fig. 2. – –
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for lateral displacements of heelsets ere made for each calculation option. t that the critical speed V as determined by the moment hen self oscillation regime stopped. Table 1. с
Standard profile Track gauge, DMetI profile New Worn mm tgγe Lhe, m tgγe Lhe, m tgγe Lhe, m
3 Determination of critical speeds
Fig. 3. raphic representation of the model of bogie ith oscillation dampers ig. sho s consolidated time based historical graphs for lateral displacements of all four heelsets ith heels in the initial ne state on 1 20 mm trac . s seen from the subsystems method [10]. Structurally “Passenger car” object is an integral system figure in this case self oscillations of heelsets die out for 12 seconds and at the given rate of motion speed drop this corresponds to the value of . m s i.e. Vс m s. The results of calculations in case of ne heels turned in accordance ith ST 03 profile – at other values of trac gauge ithin the range of 1 12 – 1 2 mm sho ed the insensitivity “Wheelsets”; 2 – “Bogie”; 3 – “Passenger car”. The general model contains identical of the critical speed in respect of hunting oscillations to trac gauge changes. dissipative properties and force relations. The general system “Passenger car”
Fig. 4. ori ontal lateral displacement of heelsets heel profile in accordance ith ST 03 . Fig. 2. ori ontal a is time [s] ertical a is heelset lateral displacement [m] raphs for displacement of heelsets ith orn heels at 1 20 mm trac are sho n in ig. . n this case critical speed is .3 m s. The comparison of this data and data from the ig. sho ed that parameters of motion stability of the car hen moving through the trac ith nominal gauge are severely affected by heels ear. t the same time there is the follo ing up ard trend in increases in critical speeds ith an increase at the trac gauge at – S 1 1 mm – Vс . m s; at S 1 1 mm – Vс 30. m s; at S 1 20 mm – Vс .3 – m s; at S 1 22 mm – Vс . m s; at S 1 2 mm – Vс .1 m s; at S 1 2 mm – Vс .3 m s.
5 MATEC Web of Conferences 157, 03006 (2018) https://doi.org/10.1051/matecconf/201815703006 MMS 2017
Fig. 5. – Vс – Vс
Fig. 6.
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Conclusion
References Fig. 5. o o 23 o o o o mm 98 – Vс o o mo o – Vс o 160 T o m o T o 22 o – T o o o – T o o o oo o m On the effectiveness of the work on the “wheel rail” o m o omo o o 3 o o m m I Fig. 6. o o m o o o o o o o m m o o m m o o o om o o o m o o m o T o o om o o o m o – – T – Sapietová, M. Sága, P. Novák, R. Bednár, J. Dižo, o o m o o m o o o m m o m o m
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