US3718040A - Method and apparatus for evaluating railroad track structure and car performance - Google Patents

Method and apparatus for evaluating railroad track structure and car performance Download PDF

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US3718040A
US3718040A US00178131A US3718040DA US3718040A US 3718040 A US3718040 A US 3718040A US 00178131 A US00178131 A US 00178131A US 3718040D A US3718040D A US 3718040DA US 3718040 A US3718040 A US 3718040A
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track
lateral
axle
forces
force
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W Freeman
L Peterson
J Wandrisco
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Quebec Cartier Mining Co
United States Steel Corp
Bessemer and Lake Erie Railroad Co
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/08—Railway vehicles
    • G01M17/10—Suspensions, axles or wheels
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/16—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring several components of force
    • G01L5/161—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring several components of force using variations in ohmic resistance
    • G01L5/1627—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring several components of force using variations in ohmic resistance of strain gauges
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/20—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring wheel side-thrust

Definitions

  • ABSTRACT Method and apparatus for determining dynamic lateral and vertical wheel-rail forces.
  • Axle bending sensors and axle load cells provide signals to a computer programmed to calculate lateral and vertical wheel-rail forces. These forces are used as the basis for comparing the effects of a variety of car truck design criteria and track conditions. Comparison of forces developed by the same equipment on different runs over the same trackage discloses track condition changes between runs.
  • FIG 4 1A A A A A A A A A L40 ⁇ V W vza'ov'v oqy W M 30,000 AXLE BEND/N6 MOMENT E11 0 V x W I 1 V? TOTAL AXLE LOAD (sou/v05) /8,000
  • railroad car trucks were equipped with axle bending sensors and axle load ceils for different truck configurations.
  • Test equipment including signal conditioning equipment, a tape recorder, an analog to digital converter, a computer and readout equipment was located on an equipment car and connected to the car truck undergoing test. Test runs were made over a section of track having a wide variety of curve radii for each type of truck configuration under study.
  • the computer was programmed to develop dynamic vertical and lateral forces througfliout the run and then to provide statistical comparison of the data of car behavior for different track inputs.
  • the data is then presented in form to evaluate such items as the desirability of making a vehicle suspension system more resilient, the desirability of reducing the unsprung weight of a car, altering car design characteristics which might influence natural periods of oscillation, reduction of static and dynamic axle loading, adjustment of track condition parameters to match operations and decreasing the frequency and level of lateral wheel-rail forces in curves.
  • the data is then used for altering track conditions and for car design criteria to minimize lateral wheel-rail forces and to achieve the objective of moving cars along the track centered on the rail with uniform loading on all wheels on curves and tangent track.
  • Another object is to provide apparatus for analyzing the dynamic and lateral forces between railroad wheels and rails.
  • a further object is to provide a method for determining the dynamic vertical and lateral forces between railroad wheels and rails.
  • a still further object is to provide a method of evaluating design criteria for railroad car trucks.
  • Still another object is to provide a method for evaluating railroad track conditions.
  • Yet another object is to provide a method for evaluating track maintenance and detecting track defects.
  • FIG. 1 is a schematic drawing of the testing apparatus of our invention.
  • FIG. 2. is a force diagram illustrating the force calculations of our method.
  • FIG. 3 is a partial side view of a truck showing a pad which will absorb part of the lateral energy transmitted to the wheel.
  • FIG. 4 is a partial computer produced graph for a type C truck, first axle, trailing truck, tangent track, welded rail at 35 miles per hour.
  • FIG. 5 is a partial computer produced graph for a type A truck, first axle, lead truck, 7 curve, jointed rail at 35 miles per hour.
  • FIG. 6 is a partial computer produced graph showing various forces for a type A truck, first axle, trailing truck, tangent track, welded rail at 35 miles per hour.
  • FIG. 7 is a partial computer produced graph showing various forces for a type B truck, first axle, trailing truck, tangent track, welded rail at 35 miles per hour.
  • FIG. 8 is a series of charts showing the cumulative frequency distribution of lateral wheel forces in thousands of pounds for three types of trucks as percent of time less than ordinate value.
  • FIG. 9 is a series of charts showing the cumulative frequency distribution of the lateral to vertical force ratio for three types of trucks on a 5 curve, welded rail, at 35 miles per hour as percent of time less than ordinate value.
  • FIG. 10 is a series of charts showing the cumulative frequency distribution of the lateral wheel force (A), dynamic vertical wheel force (B) and lateral to vertical force ratio (C) on the high rail side for a type A truck on a 5 curve at 35 miles per hour for welded rail and jointed rail as percent of time less than ordinate value.
  • FIG. 11 is a series of charts showing the cumulative frequency distribution of the net lateral force (A), dynamic axle rock (B) and dynamic axle loading (C) in thousands of pounds of type A, B, and C trucks on a curve, welded rail at 35 miles per hour as percent of time less than ordinate value.
  • FIG. 12 is a chart showing the net lateral force, at one standard deviation, lo, above the mean of the frequency distribution of the measured values for three trucks at different curvatures on jointed rails at 35 miles per hour.
  • FIG. 13 is a chart showing the total axle load, at one standard deviation, above the mean of the frequency distribution of the measured values for three type trucks of different curvatures on welded rails at 35 miles per hour.
  • FIG. 14 is a chart showing the load transfer across an axle at one standard deviation, 10', above the mean of the frequency distribution of the measured values on various degrees of track curvatures for different type trucks at different speeds for both jointed and welded rail.
  • FIGS. 15A and B are grossly exaggerated depictions of the forces on rails and wheels due to alternate axle loading and unloading.
  • FIG. 16 is a chart showing the maximum wheel lateral to vertical ratio at one standard deviation, 10-, above mean of the frequency distribution of the calculated values on different track curvatures at 35 miles per hour on jointed rails for two types of trucks.
  • FIG. 17 is a chart showing the maximum wheel lateral to vertical ratio at one standard deviation, 10', above mean of the frequency distribution of the calculated values on different track curvatures at 35 miles per hour on welded rails for three types of trucks.
  • FIG. 18 is a chart showing the average vertical truck load shifting in thousands of pounds to high and low rails on different curves for different trucks at and 35 miles per hour.
  • FIG. 19 is a partial computer produced graph showing various forces in thousands of pounds for a type A truck, second axle, lead truck, tangent track, jointed rail at 20 miles per hour correlated with rail joints.
  • FIG. 20 is a partial computer produced graph showing various forces in thousands of pounds for a type A truck, first axle, lead truck, tangent track, jointed rail at 35 miles per hour correlated with a turn out.
  • reference numeral 2 generally indicates the truck of a railroad car with side frames 4, wheels 6, and axles 8 to be tested.
  • 'll'wo conventional electrical resistance strain gauges 10 are mounted on each axle on a common axis parallel to the axis of rotation of the axle and spaced apart from the wheels as shown by distances d and e in FIG. 2.
  • Leads 12 from strain gauges 10 are connected to slip rings 14 through holes in the axle.
  • the slip rings 14 are connected through leads M to a car mounted signal amplifier and conditioner module 15.
  • Four conventional compression load cells using electrical resistance strain gauges 18 are located between side frames 4 and axles 8 and are connected through lines B to module 15.
  • Module 15 is connected to an analog signal recorder 16 and to a conventional analog to digital converter 20 which is in turn connected to a general purpose digital computer 22.
  • Computer 22 may include a conventional cathode ray tube display 24 and aconventional teleprinter 26.
  • a digital tape recorder 27 is connected to computer 22.
  • a track side reference location detector 28, such as a mile post detector, is connected to module 15.
  • Detector 28 may be either the metal detector type in which detecting the presence of a metal plate attached to a tie at the desired location provides a signal to the recorder 16, a mechanical trip type which has a track side arm at each desired location for tripping a car mounted switch to provide a signal to the recorder or light source and photocell receiver.
  • Recorder 16 is connected to converter 20.
  • Determination of the dynamic vertical and lateral force reactions at each wheel is a particularly critical part of the measurements. While the load cells 18 provide a measure of the vertical force transmitted from car to axle, it is not a measure of the forces transmitted from wheel to rail. In order to determine the vertical and lateral wheel-rail forces, calibrated strain gauges 10 are used at known locations and positions on the axle to measure instantaneous bending moments.
  • strain gauges 10 Continuous measuring of bending strains at any known point in the revolving axle 8 is made by strain gauges 10.
  • the strain gauge will provide a sine wave output as the location undergoes bending with axle rotation. This output is due to gauge position and is not a direct measurement of the maximum bending strain except at the extreme points twice each revolution. More than one strain gauge may be used at each location to improve the accuracy of the determination of bending moments.
  • L is the right lateral force
  • B is the right bearing force as measured by a load cell
  • V is the right vertical force
  • M is as previously described.
  • L is the right lateral force, L1
  • L is the left lateral force
  • L is the net lateral force which will have a sign indicating its direction.
  • the desired vertical and lateral forces are obtained by substituting the known dimensions and measured quantities for the appropriate terms.
  • a resultant computed value having a negative sign indicates that the force vector is in the opposite direction to that shown in FIG. 2.
  • a number of trucks are equipped with strain gauges and load cells, at least one truck for each type of truck for which the particular design and performance characteristics are to be compared.
  • the instrumented trucks are used on loaded or empty freight cars and the connections B and M of FIG. 1 are made by cable to a test car in which the remainder of the components of FIG. I are installed.
  • the test car may be conveniently located in a train consist of loaded and/or empty freight cars and the test car.
  • the test train is then run along a section of track at various speeds.
  • the section of track preferably includes an adequate variety of curvatures and other track conditions to insure the accumulation of sufficient representative data.
  • a IS-mile section of track which included 6 miles of tangent track, curves from l to 8 and grades up to 0.8 percent gave very satisfactory results.
  • Speeds should be relatively constant, such as a run at 20 miles per hour and a run at 35 miles per hour, with other runs over specific track sections at 25, 30, 40, and 45 miles per hour. instrumented trucks should be placed in both leading and trailing positions.
  • the strain gauges and load cells are calibrated statically before a run. During the run the data is continuously fed into the module 15.
  • the track side reference location detector 28 simultaneously records location signals for later synchronization. Module includes amplifiers for altering all the signals recorded to be compatible with the inputs to the analog to digital converter. The signals are then processed by the computer in specific ways for specific purposes.
  • the data shown hereafter includes measurements from three different types of railroad trucks designated as a type A car equipped with standard plain bearings, a type B car equipped with standard roller bearings and a type C car equipped with standard roller bearings and lateral energy absorbing pads.
  • FIG. 3 shows a lateral energy absorbing pad 30 placed between axle 8 and side frame 4. Four lateral pads are provided on each truck.
  • FIGS. 4 and 5 are computer produced graphs illustrating one method of displaying the data acquired on test runs and processed by the computer.
  • FIG. 4 is for a type C car, first axle, trailing truck on tangent track with welded rails at 35 miles per hour.
  • FIG. 5 is for a type A car, first axle, lead truck on a 7 curve with jointed rails at 35 miles per hour speed. The abscissae are shown marked in units, each 357 units represents one second as shown in FIG. 4A. The same scale is used in the remainder of FIG. 4 and FIGS. 5, 6, 7, l9 and 20. Only a small fragment of the total run is shown.
  • FIG. 4A shows the output of one of the strain gauges l0 expressed as a bending moment in foot pounds.
  • FIG. 4B shows the total axle load in pounds as determined from gauges 18 in FIG. 1.
  • the total axle load may be expressed as n' R' L' l) where RR is a measure of rock based on the right wheel and E and E, are deviations from static values.
  • FIG. 4E shows the dynamic lateral forces L and L where a positive value indicates an inward force applied to the wheel and a negative value indicates an outward force applied to the wheel.
  • FIG. 4F shows the dynamic net lateral force expressed as LN LR LL where L is the dynamic net lateral force based on the right wheel and L and L,, are the dynamic lateral forces.
  • FIG. 4G shows the ratio of the lateral to vertical forces for each wheel expressed as Ratio 1411/ V ⁇ ; for the right wheel, and
  • Rati0 L /V for the left wheel. The ratios are a measure of potential derailing tendencies.
  • FIG. 5 shows the same data as FIG. 4, but for a type A car, first axle, lead truck on a 7 curve, jointed rail at 35 miles per hour.
  • Table l shows the data of FIG. 4 separated into frequency distribution groups; averaged, and the value of first standard deviation from the mean determined by conventional statistical methods.
  • VERTICAL FORCE COMPARISONS Transmittal of the load vertically to the axle bearings and eventually to the wheel-rail contact area is a much more complex occurrence when a car is moving as compared to when a car is standing still.
  • the dynamic pattern of load transmittal as a car traverses a given section of track is determined chiefly by the suspension system of the truck, such as bolsters, springs, bearings, wedges or snubbers, and the magnitude may vary considerably depending upon the characteristics and clearance between these components.
  • FIG. 11B Dynamic load transfer from one side of an axle to the other is termed rock," equation 1 l, and has been long recognized as a potential cause for derailment.
  • Rock is associated with rail joint spacing and truck type and the relation with truck type is shown in FIG. 11B.
  • FIGS. 4D and 5D illustrate rock by the computer produced graph method.
  • FIG. 14 also shows the nature of rock for different type cars at different speeds for both jointed and welded rail, the type C car exhibits the highest capability for absorbing shocks.
  • Bounce equation 10 is the simultaneous and synchronous loading of all bearings of the trucks of a car.
  • Car bounce is shown in FIGS. 43 and 5B, and FIG. 13 shows the bounce comparison of the three type trucks, type C exhibits the smallest bounce tendency.
  • Table 2 shows a summary of vertical loadings and high frequency peak to peak shocks.
  • LATERAL FORCE COMPARISONS The type B truck, equipped with roller bearings, allows only a small amount of lateral movement between the side frames and axles. Such truck is commonly called a rigid truck as compared to the flexible plain bearing truck, type A, which has considerable more lateral movement tolerance, or the type C which has the lateral pads to facilitate lateral movement. The differences are shown in FIGS. 8, 11A, and 12. These comparisons may also be made for any particular change in dimension to optimize the lateral force effects.
  • the dynamic lateral force frequencies correlates with the distances (7 to 12 inches) between rail corrugations at the predominant train speed.
  • This type of analysis may also be used to determine the effectiveness of lateral energy absorbing pads by comparing different dimensions, different materials, and different compressibilities.
  • FIGS. 9 and 10C compare the ratio on two different types of track and on high and low side of curves.
  • FIG. 16 compares the ratio for types A and B trucks over jointed rail at 35 miles per hour over several curves
  • FIG. 17 is a similar comparison, but on welded rails.
  • the lateral to vertical ratio could be calculated using net lateral force on each axle, or total net truck lateral force as well as different vertical forces could be used to develop potential derailment tendencies.
  • FIGS. 9 and 10C compare the ratio on two different types of track and on high and low side of curves.
  • FIG. 16 compares the ratio for types A and B trucks over jointed rail at 35 miles per hour over several curves
  • FIG. 17 is a similar comparison, but on welded rails.
  • the lateral to vertical ratio could be calculated using net lateral force on each axle, or total net truck lateral force as well as different vertical forces could be used to develop potential derailment tendencies.
  • the type A and C trucks allow lateral movement of the axles relative to the side frame and truck bolsters have the capability of absorbing the minor lateral profile changes of the rail by a back and forth hunting movement of the wheel and axle units only, without the heavier mass of the car and lading.
  • This independent lateral freedom allows such trucks to accommodate to track inputs, such as lateral irregularities, curve alignment and gauge variations, without the higher mass reinforced pivoting and pitching action of more rigid designs.
  • the relative effect of pivoting action may be determined by comparing the charts of FIG. 8 and is further shown in FIG. 11A.
  • car truck design criteria that may be determined in a similar manner include the effectiveness of suspension systems and damping devices, optimal wheelbase, spacing between wheels on an axle, allowable lateral motion of truck components, clearances between truck components and wheel tread contours. This technique can also be used to determine that best compromise in two or more car truck design features. For example, referring to FIGS. 6 and 7, the type A car has a higher dynamic axle load than the type C car and therefore more truck wear and damage potential, but
  • TRACK CONDITIONS The rails, roadbed, and general track structure conditions act as stimuli for inducing various reactions in passing cars.
  • Track geometry such as alignment, vertical profile, lateral profile, gauge, cross-level rail joint conditions and ballast characteristics very noticeably affect car behavior.
  • Statically measured track dimensions do not necessarily yield on accurate index as to what a car will sense under moving or dynamic conditions because physical measurements of gauge, crosslevel, alignment and the like under no-load conditions do not necessarily reflect the acceptability of the track under operation conditions. This is particularly true of roadbed resiliency.
  • the methods already described for evaluating truck features are also used in evaluating track conditions by comparing truck reactions with different track inputs.
  • FIG. 13 clearly identifies the effect of track curvature on total axle load for the three type trucks.
  • FIGS. 14, 16, 17, and 18 also illustrate the effect of curves.
  • Table 3 shows a typical lateral force for different degrees of curvature for a type b truck, first axle, high rail, welded rail at 35 miles per hour.
  • FIG. illustrates comparisons concerning lateral forces, vertical forces and lateral to vertical ratios for a type A truck.
  • FIG. 18 shows one method of comparing equilibrium behavior based on average vertical truck load shifts between high and low rails on selected curves at constant speeds of 20 and 35 miles per hour.
  • FIG. 19 shows the location of the rail joints when car rock is plotted on a computer production graph.
  • FIG. 20 shows the location of a turnout on a computer produced graph display. It is also possible to distinguish between trailing and facing movements in turnouts.
  • Other track conditions that may be evaluated by this method include gauge-curve relationship and gauge control.
  • Track condition in relation to a standard may be established by using a test car equipped with a truck of known dynamic characteristics.
  • the computer may be programmed to detect any measured or calculated force or force relationship that deviate from an established standard.
  • TRACK MAINTENANCE As an aid to track maintenance track conditions may be monitored by using the same method.
  • a measuring car equipped with trucks having load cells, axle strain gauges and the necessary recording equipment is run over the section of track for which conditions are to be monitored.
  • a characteristic base is developed which may take the form, for example, of the information shown in FIG. 4 converted to a cumulative distribution.
  • the results of another test run performed at a suitable monitor test interval, for example monthly, is then compared with the base run and any significant deviation in the information from the base run, such as magnitudes, frequencies, or occurrences of forces or ratios can be detected.
  • the location of the deviation may be determined, or by use of the CRT display 24, the computer 22 may be programmed to display the deviation as it occurs.
  • This method could be used to monitor the condition of track joints, turnouts, ballast movement, ballast resiliency and localized track defects, such as shelled spots, engine burns, spalling of rail head and partial fracture of head. Where defects create their particular pattern on strip charts, the computer may be programmed to identify the defect.
  • Apparatus for evaluating railroad track structure and car performance comprising a railroad car truck including two side frames, an axle and a pair of wheels mounted on said axle, a pair of load cells mounted between said axle and each side frame for providing a first signal and a second signal responsive to the vertical load of each truck side frame on said axle, a pair of electrical resistance strain gauges mounted on said axle for providing a third signal and a fourth signal responsive to the bending moments in said axle as it rotates under load, and means connected to said load cells and said strain gauges for combining said signals and calculating the vertical and lateral wheelrail forces at each wheel.
  • Apparatus according to claim 1 in which said means for calculating includes a signal amplifier and conditioner module, an analog to digital converter connected to said module and a general purpose digital process computer connected to said converter.
  • Apparatus according to claim 3 which includes a trackside reference location detector connected to said module.
  • Apparatus according to claim 3 which includes a printer connected to said computer, a cathode ray tube display connected to said computer, a digital tape recorder connected to said computer, and an analog recorder connected to said module and said converter.
  • a method for evaluating railroad track structure and car performance comprising the steps of continuously determining axle bending moments of a truck axle under load at two locations on the axle between the wheels of said axle as the wheels roll over a desired section of track, continuously determining the bearing force each truck side frame exerts on the car axle under load as the wheels roll over said section of track, and calculating the vertical and lateral wheel-rail forces for each wheel from said axle bending moments and said bearing forces.
  • a method in which the bending moments are determined by strain gauges and the bearing forces are determined by load cells and which includes statically calibrating the strain gauges and load cells, measuring the distance between the axis of the axle and the surface of the tread of the wheel, measuring the distance between each load cell and the adjacent wheel, measuring the distance between each strain gauge and the adjacent wheel, measuring the distance between the wheel treads, and said calculating of vertical and lateral forces are performed by combining an output from each strain gauge, an output from each load cell and said measurements.
  • a method in which the step of calculating the vertical and lateral forces comprises for L, L V and V where L, is the lateral force on the left wheel, L is the lateral force on the right wheel, V is the vertical force on the left wheel, and V is the rtical force on the right wheel and in which equations M is the calibrated strain gauge output adjacent the left wheel, 171 is the calibrated strain gauge output adjacent the right wheel, F is the calibrated load cell output adjacent the left wheel, E is the calibrated load cell output adjacent the right wheel, a is the measured distance between the left wheel and the adjacent load cell, b is the measured distance between the right wheel and the adjacent load cell, c is the measured distance between the axis of the axle and the surface of the tread of the wheel, d is the measured distance between the left wheel and the adjacent strain gauge, e is the measured distance between the right wheel and the adjacent strain gauge, and f is the measured distance between the wheel treads.
  • a method according to claim 8 which includes the steps of converting the outputs of the strain gauges and load cells from analog to digital form and calculating force relationships and in which said calculations are made by a general purpose digital computer.
  • a method according to claim 9 which includes recording the outputs of the strain gauges and the load cells in digital form.
  • a method according to claim 10 which includes the steps of simultaneously recording with said outputs periodic trackside reference location indicator signals.
  • a method according to claim 9 which includes the steps of determining the vertical and lateral forces for all axles of a truck.
  • a method according to claim 9 which includes the steps of determining the lateral and vertical forces for all axles ofa car.
  • a method according to claim 8 which includes calculating the net lateral force on the two wheels of a single axle according to the equation where L is the lateral force on the right wheel, L is the lateral force on the left wheel, and L is the net lateral force which will have a positive sign if toward the right wheel and a negative sign if toward the left wheel.
  • a method according to claim 8 including calculating the total dynamic axle load E, according to the equation 5, ER, EL,
  • E is the deviation of the right load ce ll output from static value expressed as a force
  • B is the deviation of the left load cell output from static value expressed as a force
  • a method according to claim 8 including the steps of determining dynamic vertical forces V and V where V, is the deviation from static value of V and V,;' is the deviation from static value of V 17.
  • a method according to claim 8 including calculating the lateral to vertical force ratio, R, according to the equation where L and V are the calculated lateral and vertical forces.
  • a method according to claim 13 including calculating the transfer of vertical forces to and from leading and trailing axles.
  • a method according to claim 8 including determining the frequencies of occurrence of repetitive deviations from static values of lateral and vertical forces.
  • a method according to claim 9 in which said calculations are performed for increments of travel over said sections of track thereby providing a series of values for vertical forces, a series of values for lateral forces and a series of values for each force relationship and which includes placing each value of a series in a range group, determining the frequency of occurrence of values in said range group, determining the mean of values of said group and determining one standard statistical deviation from the mean of values of said group.
  • a method according to claim 9 in which said calculations are performed for increments of travel over said section of track thereby providing a series of lateral and vertical force values, and which includes measuring the transfer of vertical forces from one rail to the other rail on curved track.
  • a method according to claim 9 in which said calculations are performed for increments of travel over said section of track thereby providing a series of lateral and vertical force values and which includes grouping said values according to track curvature.
  • a method according to claim 9 which includes the steps of recording the values of the vertical forces, lateral forces, and force relationships for said section of track, determining a second set of vertical and lateral force values with the same rolling equipment, and comparing the recorded values with the second set of values.
  • a method according to claim 9 which includes the steps of establishing acceptable standards for values of said forces and force relationships for a test car, operating said test car on a second section of track, calculating said forces and force relationships for said test car for said second section of track and comparing said calculated values of said forces and force relationships for said second section of track with said standard values.

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Cited By (59)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3939331A (en) * 1971-12-24 1976-02-17 Franz Plasser Bahnbaumaschinen Industriegesellschaft M.B.H. Railroad track survey apparatus
US3974689A (en) * 1975-03-11 1976-08-17 United States Steel Corporation System for detecting faults along an electric overhead traveling crane runway
US4005601A (en) * 1975-08-29 1977-02-01 Amac, Inc. Apparatus for detecting rail discontinuities
US4251931A (en) * 1979-04-11 1981-02-24 The United States Of America As Represented By The Secretary Of The Navy Terrain vehicle simulator contour measuring and storage device
US4305300A (en) * 1980-04-28 1981-12-15 Mts Systems Corporation Railway car side frame test machine
EP0892258A1 (de) * 1997-07-15 1999-01-20 SLM Schweizerische Lokomotiv- und Maschinenfabrik AG Messanordnung für einen Radsatz eines Schienenfahrzeuges und Vorrichtung zum Anbringen einer derartigen Messanordnung an einem Radsatz
US5970438A (en) * 1998-04-07 1999-10-19 Sperry Rail Service Method and apparatus for testing rails for structural defects
US6189456B1 (en) * 1997-10-07 2001-02-20 Trn Business Trust High capacity axle for railway freight cars
US20040020065A1 (en) * 2002-03-18 2004-02-05 Carr Gary A. Inner bearing split axle assembly
US20050103100A1 (en) * 2003-10-27 2005-05-19 Sumitomo Rubber Industries, Ltd. System and method for determining tire force
US20060000290A1 (en) * 2002-12-31 2006-01-05 Otto Daniel P Gauge restraint measurement system
US7214893B2 (en) 2005-02-15 2007-05-08 Electric Arc Technologies, Llc Load cell system
US20070152107A1 (en) * 2005-12-23 2007-07-05 Afs-Keystone, Inc. Railroad train monitoring system
DE102006001540B3 (de) * 2006-01-12 2007-08-09 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Verfahren und einer Einrichtung zur Zustandsüberwachung von Radsätzen oder Drehgestellen eines Schienenfahrzeugs
US20070208841A1 (en) * 2006-03-01 2007-09-06 L-3 Communications Corporation Self-assembling wireless network, vehicle communications system, railroad wheel and bearing monitoring system and methods therefor
US20070255509A1 (en) * 2006-04-28 2007-11-01 Asf-Keystone, Inc. Sensor interface
US20080264765A1 (en) * 2006-05-23 2008-10-30 Dematic Corp. Skewed slat control system for article conveyor
WO2009109200A1 (en) * 2008-03-05 2009-09-11 Ab Skf Device for attachment to a rotating part of a railway axle
US20090301221A1 (en) * 2005-05-30 2009-12-10 Lars Andersson Method and a system for determining a plurality of load components on a wheel
US20100023190A1 (en) * 2006-03-20 2010-01-28 General Electric Company Trip optimizer method, system and computer software code for operating a railroad train to minimize wheel and track wear
GB2462305A (en) * 2008-08-01 2010-02-03 Haldex Brake Products Ltd Method and apparatus for monitoring a force on a vehicle
ITBS20090119A1 (it) * 2009-06-26 2010-12-27 Lucchini Rs Spa Dispositivo di rilevamento delle deformazioni meccaniche in continuo di una sala montata ferroviaria
AT503622B1 (de) * 2006-04-20 2011-11-15 Siemens Ag Verfahren zum bestimmen von zwischen einem schienenfahrzeug und einer schiene auftretenden kräften
CN102422140A (zh) * 2009-04-27 2012-04-18 Agg厂房及设备有限公司 用于转向架的检测方法以及检测和装配试验台
US8260574B1 (en) 2007-12-21 2012-09-04 Dematic Corp. Diagnostic device for material handling system and method of diagnosing
WO2013020974A1 (de) * 2011-08-09 2013-02-14 AUMUND Fördertechnik GmbH Verfahren zur erfassung der schienenlage und/oder der laufrollenbelastung bei schienengeführten schüttgut-fördermitteln sowie zur durchführung des verfahrens geeignete messlaufrolle
CN103063451A (zh) * 2012-12-26 2013-04-24 浙江大学 轨道交通列车整车移动荷载模拟加载方法及装置
CN103852269A (zh) * 2012-12-01 2014-06-11 南车青岛四方机车车辆股份有限公司 高速列车运行动力学参数检测方法
CN104105954A (zh) * 2011-12-06 2014-10-15 新日铁住金株式会社 车辆的异常检测方法和装置
CN104619571A (zh) * 2012-09-11 2015-05-13 川崎重工业株式会社 载荷测量方法及装置、具备载荷测量装置的铁道车辆以及载荷管理系统
CN105128881A (zh) * 2015-10-09 2015-12-09 唐山轨道客车有限责任公司 转向架锁轴故障监测方法、装置及系统
US9365223B2 (en) 2010-08-23 2016-06-14 Amsted Rail Company, Inc. System and method for monitoring railcar performance
US9415784B2 (en) * 2014-10-10 2016-08-16 Progress Rail Services Corporation System and method for detecting wheel condition
JP2016148552A (ja) * 2015-02-10 2016-08-18 公益財団法人鉄道総合技術研究所 鉄道車両の歪み測定システム及び歪み測定装置
DE202008018608U1 (de) 2008-03-05 2016-08-29 Ab Skf Vorrichtung zur Anbringung an ein rotierendes Teil einer Eisenbahnfahrzeugachse
US9669851B2 (en) 2012-11-21 2017-06-06 General Electric Company Route examination system and method
US9682716B2 (en) 2012-11-21 2017-06-20 General Electric Company Route examining system and method
US9689681B2 (en) 2014-08-12 2017-06-27 General Electric Company System and method for vehicle operation
US9702715B2 (en) 2012-10-17 2017-07-11 General Electric Company Distributed energy management system and method for a vehicle system
US9733625B2 (en) 2006-03-20 2017-08-15 General Electric Company Trip optimization system and method for a train
US9828010B2 (en) 2006-03-20 2017-11-28 General Electric Company System, method and computer software code for determining a mission plan for a powered system using signal aspect information
US9834237B2 (en) 2012-11-21 2017-12-05 General Electric Company Route examining system and method
US9849893B2 (en) * 2013-03-27 2017-12-26 Aktiebolaget Skf Hub unit
US9873441B1 (en) 2016-08-04 2018-01-23 Ensco, Inc. Rail vehicle based deployable gage restraint measurement system
US9908545B2 (en) * 2014-09-22 2018-03-06 General Electric Company Method and system for operating a vehicle system to reduce wheel and track wear
US9950722B2 (en) 2003-01-06 2018-04-24 General Electric Company System and method for vehicle control
CN108106832A (zh) * 2017-12-25 2018-06-01 湖南联诚轨道装备有限公司 低地板有轨电车防折弯系统检测装置及方法
US20180238771A1 (en) * 2015-10-19 2018-08-23 Schenck Process Europe Gmbh Apparatus and method for calibrating and/or adjusting measuring apparatuses for dynamic forces
US10137915B2 (en) 2013-12-24 2018-11-27 Amsted Rail Company, Inc. System and method for detecting operational anomalies in train consists and railcars
US10259477B2 (en) 2013-11-27 2019-04-16 Amsted Rail Company Train and rail yard management system
US10308265B2 (en) 2006-03-20 2019-06-04 Ge Global Sourcing Llc Vehicle control system and method
WO2019111128A1 (en) * 2017-12-04 2019-06-13 Faiveley Transport Italia S.P.A. A system for determining an angular speed of an axle of a railway vehicle and corresponding method
US10569792B2 (en) 2006-03-20 2020-02-25 General Electric Company Vehicle control system and method
CN110853474A (zh) * 2019-11-08 2020-02-28 北京交通大学 一种列车动力弹射试验平台的牵引与制动系统
US10745037B2 (en) * 2015-04-28 2020-08-18 China Academy Of Railway Sciences Fully continuous ground measurement method and system for wheel rail vertical force
US11180170B2 (en) 2018-01-24 2021-11-23 Amsted Rail Company, Inc. Discharge gate sensing method, system and assembly
US11312350B2 (en) 2018-07-12 2022-04-26 Amsted Rail Company, Inc. Brake monitoring systems for railcars
US11926351B2 (en) 2020-09-01 2024-03-12 Bnsf Railway Company Apparatus and method for wear detection of railroad vehicle wheels
US12371077B2 (en) 2018-01-24 2025-07-29 Amsted Rail Company, Inc. Sensing method, system and assembly for railway assets

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5412874A (en) * 1977-06-30 1979-01-30 Hino Motors Ltd Apparatus for measuring three component forces applied to front wheel shaft
JP5228599B2 (ja) * 2008-04-22 2013-07-03 新日鐵住金株式会社 横圧の測定方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3392451A (en) * 1966-06-28 1968-07-16 Cleveland Technical Ct Inc Dynamic railway track inspecting apparatus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3392451A (en) * 1966-06-28 1968-07-16 Cleveland Technical Ct Inc Dynamic railway track inspecting apparatus

Cited By (101)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3939331A (en) * 1971-12-24 1976-02-17 Franz Plasser Bahnbaumaschinen Industriegesellschaft M.B.H. Railroad track survey apparatus
US3974689A (en) * 1975-03-11 1976-08-17 United States Steel Corporation System for detecting faults along an electric overhead traveling crane runway
US4005601A (en) * 1975-08-29 1977-02-01 Amac, Inc. Apparatus for detecting rail discontinuities
US4251931A (en) * 1979-04-11 1981-02-24 The United States Of America As Represented By The Secretary Of The Navy Terrain vehicle simulator contour measuring and storage device
US4305300A (en) * 1980-04-28 1981-12-15 Mts Systems Corporation Railway car side frame test machine
EP0892258A1 (de) * 1997-07-15 1999-01-20 SLM Schweizerische Lokomotiv- und Maschinenfabrik AG Messanordnung für einen Radsatz eines Schienenfahrzeuges und Vorrichtung zum Anbringen einer derartigen Messanordnung an einem Radsatz
US6189456B1 (en) * 1997-10-07 2001-02-20 Trn Business Trust High capacity axle for railway freight cars
US5970438A (en) * 1998-04-07 1999-10-19 Sperry Rail Service Method and apparatus for testing rails for structural defects
US7254896B2 (en) * 2002-03-18 2007-08-14 Ensco, Inc. Inner bearing split axle assembly
US20040020065A1 (en) * 2002-03-18 2004-02-05 Carr Gary A. Inner bearing split axle assembly
US7311010B2 (en) * 2002-12-31 2007-12-25 Otto Daniel P Gauge restraint measurement system
US20060005638A1 (en) * 2002-12-31 2006-01-12 Otto Daniel P Gauge restraint measuring system
US7007561B1 (en) * 2002-12-31 2006-03-07 Holland L.P. Gauge restraint measurement system
US20060162470A1 (en) * 2002-12-31 2006-07-27 Otto Daniel P Gauge resistant measurement system
US7451632B1 (en) 2002-12-31 2008-11-18 Holland Company Lp Gauge restraint load calibration system
US7337682B2 (en) 2002-12-31 2008-03-04 Holland Lp Gauge restraint measuring system
US7270018B2 (en) 2002-12-31 2007-09-18 Otto Daniel P Gauge restraint measuring system
US20060000290A1 (en) * 2002-12-31 2006-01-05 Otto Daniel P Gauge restraint measurement system
US9950722B2 (en) 2003-01-06 2018-04-24 General Electric Company System and method for vehicle control
US20080011092A1 (en) * 2003-10-27 2008-01-17 Akihiro Miyoshi System and method for determining tire force
US20050103100A1 (en) * 2003-10-27 2005-05-19 Sumitomo Rubber Industries, Ltd. System and method for determining tire force
US7249498B2 (en) * 2003-10-27 2007-07-31 Sumitomo Rubber Industries, Ltd. System and method for determining tire force
US7506539B2 (en) 2003-10-27 2009-03-24 Sumitomo Rubber Industries, Ltd. System and method for determining tire force
US7214893B2 (en) 2005-02-15 2007-05-08 Electric Arc Technologies, Llc Load cell system
US7926362B2 (en) * 2005-05-30 2011-04-19 Interfleet Technology Ab Method and a system for determining a plurality of load components on a wheel
US20090301221A1 (en) * 2005-05-30 2009-12-10 Lars Andersson Method and a system for determining a plurality of load components on a wheel
US20070152107A1 (en) * 2005-12-23 2007-07-05 Afs-Keystone, Inc. Railroad train monitoring system
US7688218B2 (en) 2005-12-23 2010-03-30 Amsted Rail Company, Inc. Railroad train monitoring system
DE102006001540B3 (de) * 2006-01-12 2007-08-09 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Verfahren und einer Einrichtung zur Zustandsüberwachung von Radsätzen oder Drehgestellen eines Schienenfahrzeugs
US20070208841A1 (en) * 2006-03-01 2007-09-06 L-3 Communications Corporation Self-assembling wireless network, vehicle communications system, railroad wheel and bearing monitoring system and methods therefor
US7705743B2 (en) 2006-03-01 2010-04-27 L-3 Communications Corporation Self-assembling wireless network, vehicle communications system, railroad wheel and bearing monitoring system and methods therefor
US10308265B2 (en) 2006-03-20 2019-06-04 Ge Global Sourcing Llc Vehicle control system and method
US20100023190A1 (en) * 2006-03-20 2010-01-28 General Electric Company Trip optimizer method, system and computer software code for operating a railroad train to minimize wheel and track wear
US10569792B2 (en) 2006-03-20 2020-02-25 General Electric Company Vehicle control system and method
US9828010B2 (en) 2006-03-20 2017-11-28 General Electric Company System, method and computer software code for determining a mission plan for a powered system using signal aspect information
US9733625B2 (en) 2006-03-20 2017-08-15 General Electric Company Trip optimization system and method for a train
US9233696B2 (en) * 2006-03-20 2016-01-12 General Electric Company Trip optimizer method, system and computer software code for operating a railroad train to minimize wheel and track wear
AT503622B1 (de) * 2006-04-20 2011-11-15 Siemens Ag Verfahren zum bestimmen von zwischen einem schienenfahrzeug und einer schiene auftretenden kräften
US7698962B2 (en) 2006-04-28 2010-04-20 Amsted Rail Company, Inc. Flexible sensor interface for a railcar truck
WO2007127132A3 (en) * 2006-04-28 2008-10-23 Asf Keystone Inc Sensor interface
US20070255509A1 (en) * 2006-04-28 2007-11-01 Asf-Keystone, Inc. Sensor interface
US20080264765A1 (en) * 2006-05-23 2008-10-30 Dematic Corp. Skewed slat control system for article conveyor
US7641039B2 (en) 2006-05-23 2010-01-05 Dematic Corp. Skewed slat control system for article conveyor
US8260574B1 (en) 2007-12-21 2012-09-04 Dematic Corp. Diagnostic device for material handling system and method of diagnosing
EP2765402A1 (en) * 2008-03-05 2014-08-13 Ab Skf Device
WO2009109200A1 (en) * 2008-03-05 2009-09-11 Ab Skf Device for attachment to a rotating part of a railway axle
US20110146409A1 (en) * 2008-03-05 2011-06-23 Jens Graf Device for Attachment to a Rotating Part of a Railway Axle
US8757000B2 (en) 2008-03-05 2014-06-24 Aktiebolaget Skf Device for attachment to a rotating part of a railway axle
DE202008018608U1 (de) 2008-03-05 2016-08-29 Ab Skf Vorrichtung zur Anbringung an ein rotierendes Teil einer Eisenbahnfahrzeugachse
RU2472130C2 (ru) * 2008-03-05 2013-01-10 Аб Скф Устройство для крепления к вращающейся части вагонной оси
GB2462305B (en) * 2008-08-01 2013-05-15 Haldex Brake Products Ltd Method of monitoring a vehicle and apparatus therefor
AU2009275636B2 (en) * 2008-08-01 2013-07-18 Bpw Bergische Achsen Kommanditgesellschaft Method of monitoring a vehicle and apparatus therefor
GB2462305A (en) * 2008-08-01 2010-02-03 Haldex Brake Products Ltd Method and apparatus for monitoring a force on a vehicle
CN102422140B (zh) * 2009-04-27 2015-08-12 Agg厂房及设备有限公司 用于转向架的检测方法以及检测和装配试验台
CN102422140A (zh) * 2009-04-27 2012-04-18 Agg厂房及设备有限公司 用于转向架的检测方法以及检测和装配试验台
ITBS20090119A1 (it) * 2009-06-26 2010-12-27 Lucchini Rs Spa Dispositivo di rilevamento delle deformazioni meccaniche in continuo di una sala montata ferroviaria
US9981673B2 (en) 2010-08-23 2018-05-29 Amsted Rail Company, Inc. System and method for monitoring railcar performance
US9365223B2 (en) 2010-08-23 2016-06-14 Amsted Rail Company, Inc. System and method for monitoring railcar performance
WO2013020974A1 (de) * 2011-08-09 2013-02-14 AUMUND Fördertechnik GmbH Verfahren zur erfassung der schienenlage und/oder der laufrollenbelastung bei schienengeführten schüttgut-fördermitteln sowie zur durchführung des verfahrens geeignete messlaufrolle
CN104105954A (zh) * 2011-12-06 2014-10-15 新日铁住金株式会社 车辆的异常检测方法和装置
US9511783B2 (en) 2011-12-06 2016-12-06 Nippon Steel & Sumitomo Metal Corporation Method and apparatus for detecting abnormality of vehicle
EP2790002A4 (en) * 2011-12-06 2015-09-02 Nippon Steel & Sumitomo Metal Corp EXPERIENCE AND DEVICE FOR DETECTING ANOMALIES IN A VEHICLE
CN104619571A (zh) * 2012-09-11 2015-05-13 川崎重工业株式会社 载荷测量方法及装置、具备载荷测量装置的铁道车辆以及载荷管理系统
US9476802B2 (en) 2012-09-11 2016-10-25 Kawasaki Jukogyo Kabushiki Kaisha Load measurement method and apparatus, railcar provided with load measurement apparatus, and load management system
CN104619571B (zh) * 2012-09-11 2017-06-09 川崎重工业株式会社 载荷测量方法及装置、具备载荷测量装置的铁道车辆以及载荷管理系统
US9702715B2 (en) 2012-10-17 2017-07-11 General Electric Company Distributed energy management system and method for a vehicle system
US9669851B2 (en) 2012-11-21 2017-06-06 General Electric Company Route examination system and method
US9682716B2 (en) 2012-11-21 2017-06-20 General Electric Company Route examining system and method
US9834237B2 (en) 2012-11-21 2017-12-05 General Electric Company Route examining system and method
CN103852269B (zh) * 2012-12-01 2016-08-17 中车青岛四方机车车辆股份有限公司 高速列车运行动力学参数检测方法
CN103852269A (zh) * 2012-12-01 2014-06-11 南车青岛四方机车车辆股份有限公司 高速列车运行动力学参数检测方法
CN103063451A (zh) * 2012-12-26 2013-04-24 浙江大学 轨道交通列车整车移动荷载模拟加载方法及装置
US9849893B2 (en) * 2013-03-27 2017-12-26 Aktiebolaget Skf Hub unit
US10259477B2 (en) 2013-11-27 2019-04-16 Amsted Rail Company Train and rail yard management system
US10137915B2 (en) 2013-12-24 2018-11-27 Amsted Rail Company, Inc. System and method for detecting operational anomalies in train consists and railcars
US9689681B2 (en) 2014-08-12 2017-06-27 General Electric Company System and method for vehicle operation
US9908545B2 (en) * 2014-09-22 2018-03-06 General Electric Company Method and system for operating a vehicle system to reduce wheel and track wear
US9415784B2 (en) * 2014-10-10 2016-08-16 Progress Rail Services Corporation System and method for detecting wheel condition
JP2016148552A (ja) * 2015-02-10 2016-08-18 公益財団法人鉄道総合技術研究所 鉄道車両の歪み測定システム及び歪み測定装置
US10745037B2 (en) * 2015-04-28 2020-08-18 China Academy Of Railway Sciences Fully continuous ground measurement method and system for wheel rail vertical force
CN105128881A (zh) * 2015-10-09 2015-12-09 唐山轨道客车有限责任公司 转向架锁轴故障监测方法、装置及系统
US10921217B2 (en) * 2015-10-19 2021-02-16 Schenck Process Europe Gmbh Apparatus and method for calibrating and/or adjusting a force transducer or acceleration sensor of a measuring apparatus for dynamic forces
US20180238771A1 (en) * 2015-10-19 2018-08-23 Schenck Process Europe Gmbh Apparatus and method for calibrating and/or adjusting measuring apparatuses for dynamic forces
US9873441B1 (en) 2016-08-04 2018-01-23 Ensco, Inc. Rail vehicle based deployable gage restraint measurement system
CN111601739B (zh) * 2017-12-04 2022-09-16 法伊韦利传送器意大利有限公司 用于确定轨道车辆的轮轴的角速度的系统和相应方法
WO2019111128A1 (en) * 2017-12-04 2019-06-13 Faiveley Transport Italia S.P.A. A system for determining an angular speed of an axle of a railway vehicle and corresponding method
RU2766480C2 (ru) * 2017-12-04 2022-03-15 ФАИВЕЛЕЙ ТРАНСПОРТ ИТАЛИЯ С.п.А. Система и способ определения угловой скорости оси железнодорожного транспортного средства
CN111601739A (zh) * 2017-12-04 2020-08-28 法伊韦利传送器意大利有限公司 用于确定轨道车辆的轮轴的角速度的系统和相应方法
CN108106832B (zh) * 2017-12-25 2019-09-24 湖南联诚轨道装备有限公司 低地板有轨电车防折弯系统检测装置及方法
CN108106832A (zh) * 2017-12-25 2018-06-01 湖南联诚轨道装备有限公司 低地板有轨电车防折弯系统检测装置及方法
US11180170B2 (en) 2018-01-24 2021-11-23 Amsted Rail Company, Inc. Discharge gate sensing method, system and assembly
US12351218B2 (en) 2018-01-24 2025-07-08 Amsted Rail Company, Inc. Discharge gate sensing method, system and assembly
US12371077B2 (en) 2018-01-24 2025-07-29 Amsted Rail Company, Inc. Sensing method, system and assembly for railway assets
US11312350B2 (en) 2018-07-12 2022-04-26 Amsted Rail Company, Inc. Brake monitoring systems for railcars
AU2019300171B2 (en) * 2018-07-12 2022-09-29 Amsted Rail Company, Inc. Brake monitoring systems for railcars
US11993235B2 (en) 2018-07-12 2024-05-28 Amsted Rail Company, Inc. Brake monitoring systems for railcars
US12370995B2 (en) 2018-07-12 2025-07-29 Amsted Rail Company, Inc. Brake monitoring systems for railcars
CN110853474A (zh) * 2019-11-08 2020-02-28 北京交通大学 一种列车动力弹射试验平台的牵引与制动系统
US11926351B2 (en) 2020-09-01 2024-03-12 Bnsf Railway Company Apparatus and method for wear detection of railroad vehicle wheels
US11926352B2 (en) 2020-09-01 2024-03-12 Bnsf Railway Company Apparatus and method for wear detection of railroad vehicle wheels
US12441376B2 (en) 2020-09-01 2025-10-14 Bnsf Railway Company Apparatus and method for wear detection of railroad vehicle wheels

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