US3926123A - Track surfacing apparatus - Google Patents

Track surfacing apparatus Download PDF

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Publication number
US3926123A
US3926123A US404427A US40442773A US3926123A US 3926123 A US3926123 A US 3926123A US 404427 A US404427 A US 404427A US 40442773 A US40442773 A US 40442773A US 3926123 A US3926123 A US 3926123A
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Prior art keywords
track
vibration
imparting
pressure
surfacing
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US404427A
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English (en)
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Franz Plasser
Erna Plasser
Josef Theurer
Egon Schubert
Klaus Riessberger
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Franz Plasser Bahnbaumaschinen Industrie GmbH
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Individual
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Priority to US490394A priority Critical patent/US3919943A/en
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
    • E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
    • E01B27/13—Packing sleepers, with or without concurrent work on the track
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B29/00—Laying, rebuilding, or taking-up tracks; Tools or machines therefor
    • E01B29/04—Lifting or levelling of tracks

Definitions

  • the present invention relates to improvements in apparatus for surfacing a track consisting of rails fastened to ties resting on ballast.
  • ballast In track surfacing, it has been proposed to impart at least substantially horizontal vibration to a track in a section wherein the ballast is compacted, particularly under the track ties and while the track is positioned at a desired level. In the leveled track, the ballast serves to absorb the forces to which passing trains subject the track. In view of the resiliency and wear of the ballast,
  • the track level changes in the course of time. Therefore, the track must be leveled from time to time to achieve the desired grade, at which the track is fixed by tamping the supporting ballast under the ties.
  • Tie tamping forms an essential part of many known track leveling methods. In this operation, the ballast is compacted underneath the ties by pressure and vibration to the highest attainable degree to form as rigid a track support as possible.
  • none of the known tamping methods has succeeded in fixing the track at a desired level sufficiently to resist depression by passing trains for long. Immediately after tamping, the track settles rather rapidly and this downward movement slows down with time. This phenomenon results from the fact that the tamping relocates the ballast pieces in new positions in which they are subjected to the vertical, static and dynamic loads of passing trains, leading to their wear and settling. Since the ballast does not settle uniformaly along the track, many deviations from a straight level soon appear.
  • the track section to be corrected is subjected to vibrations and is raised to the desired level. Subsequently, the ballast is tamped under the ties to fix the track at the raised level. This method has not been commercially used.
  • the track surfacing of the invention discounts the usual settling of the newly tamped ballast under the loads of trains passing thereover.
  • the combination of the horizontal vibration and the downward pressure provides a ballast compaction which far surpasses the quality achieved with known track surfacing methods and equipment.
  • the ties are pressed into the ballast and this vertical downward movement of the track into the compacted ballast is taken into account in determining the desired track level.
  • the track surfacing actually simulates and discounts the subsequent train traffic so that the desired level will be maintained despite of it.
  • substantially horizontal vibration means a vibration with a marked horizontal component extending transversely of the track elongation.
  • the vibration may be produced in planes oblique to the horizontal plane as long as the resultant vibration has a marked horizontal component.
  • the vibration has the same or nearly the same frequency as the natural or characteristic frequency of vibrations of the track, measured in a transverse direction, the frequency being, for instance, in the range of 8 to 13 cycles per second.
  • the vibrating force may be relatively small since the vibrated track section will be in resonance.
  • the track surfacing of this invention is very flexible and sensitive because it opens the way to a variety of controls.
  • it is of particular advantage to determine the downward stroke required to press the track down to the desired level, i.e. the deviation of the track therefrom, to produce an error signal proportional to the deviation, and to control the frequency and/or the amplitude and/or the duration of the vibration and/or the force and/or the duration of the downward pressure in response to the error signal.
  • Controlling the force of the downward pressure on the track in response to the error signal has the best results, i.e. the track responds best to changes in the force of the pressure as far as track leveling is concerned.
  • changing the vibration frequency and/or amplitude also has advantages. Combining and- /or selecting the indicated controls enables the operator to adapt the operation to ballast beds of all types.
  • the pressure force has a static and dynamic component, the dynamic component being an oscillating force whose amplitude does not exceed twice the static component of the pressure force. In this way, the pulsating stress will press on the track without lifting the apparatus off the track.
  • the determinative opertional parameters such as pressure force, frequency and amplitude of vibration, and duration, may be controlled not only in response to an original error signal but also by a continuous error signal during the movement of the track to the desired level.
  • it may be useful to increase the pressure force as the track approaches the desired grade since the compaction of the ballast increases correspondingly so that the ballast yields less and less to the downward pressure. In this way, the duration of the downward pressure may be decreased and the efficiency of the operation proportionally increased.
  • the amplitude of vibration may be considerably reduced or the vibration may be totally stopped shortly before the track reaches the desired level so that the ballast pieces will not be unduly dislocated by vibrations at this level.
  • the track surfacing according to the present invention also tends to fix the track strongly in its lateral position. Therefore, it will be most useful to line the track ahead of the track surfacing or in the range thereof.
  • the arrangement and type of means for imparting a substantially vertical downward pressure on both rails of the track are of particular importance.
  • the preferred pressure means are hydraulic rams and, to make a continuous operation possible, the rams are supported on a mobile apparatus and preferably are mounted in vertical alignment with rail engaging wheels to exert the pressure on the track by means of the wheels.
  • the pressure force may reach the magnitude of the weight of the apparatus.
  • a plurality of hydraulic rams may be spaced in the direction of track elongation and may be subjected to different pressures. In this manner, no special controls are needed to obtain a stepped change in the pressure force exerted upon the same track point as the apparatus advances continuously along the track. It is also useful to arrange a plurality of pressure means in a direction transverse to the track since different pressures applied to such means can take into account any superelevation of the track or different track level errors at the two rails at the same track point.
  • a plurality of vibration imparting means may be spaced in the direction of track elongation so that the vibration amplitude may be changed simply by switching on or off additional vibrators.
  • FIG. 1 is a schematic side elevational view of an apparatus incorporating structures arranged and designed to carry out the method of this invention
  • FIG. 2 is a like view of such an apparatus incorporating modified structures of the indicated type
  • FIGS. 3 and 4 are schematic transverse sections of the apparatus of FIG. 2 along lines IlIIII and IVIV, respectively;
  • FIGS. 5 and 6 are side elevational and top plan views, respectively, of an embodiment of an auxiliary car carrying the pressure-applying and vibrator structures used in the invention
  • FIGS. 7 and 8 are transverse sections of the auxiliary car along lines VIIVII and VIIIVIII, respectively, of FIG. 6;
  • FIGS. 9 to 13 schematically illustrate various embodiments of structures for transmitting horizontal vibrations from the vibrations to the track
  • FIG. 14 schematically illustrates an embodiment of a structure for transmitting horizontal vibrations directly to the track ties
  • FIG. 15 is a circuit diagram of a control circuit for controlling the downwardly applied pressure in dependence on, or a function of, the position of the track;
  • FIGS. 16 and 17 are circuit diagrams of control circuits for controlling the frequency of the vibrations in dependence on, or a function of, the position of the track;
  • FIGS. 18 and 19 are circuit diagrams of control circuits for controlling the amplitude of the vibrations in dependence on, or a function of, the position of the track;
  • FIG. 20 is a circuit diagram of a control circuit for simultaneously controlling the downwardly applied pressure and the amplitude of the vibrations in dependence on, or a function of, the position of the track;
  • FIG. 21 schematically shows an embodiment of the invention in combination with a track leveling and tamping machine, in side elevation.
  • FIG. 1 shows a mobile apparatus with a machine frame 1 mounted on wheels 2 running on rails 6 which, together with ties to which the rails are affixed, form the track.
  • Track sensing elements 3 and 4 are vertically movably mounted in frame 1 at its front and rear ends, respectively, the lower ends of the track sensing elements engaging the track while their upper ends carry a reference line, for instance a tensioned wire 5.
  • the track sensing elements are bogies whose wheels run on the track rails and which carry poles on whose tops rollers are mounted over which the tensioned wires 5 are trained.
  • reference wires 5 serve as a reference for determining the desired track level.
  • a measuring device 7 is mounted on frame 1 to mea sure the vertical distance between each rail 6 and its associated reference wire 5.
  • the upper end of measuring device 7 carries a sensor for sensing the level of reference wire 5.
  • This sensor may be, for instance, a wire engaging element, such as a fork or a roller, connected with a potentiometer.
  • the potentiometer is adjusted mechanically by the reference wire or by servomechanical means whenever there is a change in the distance between a rail and its associated reference wire.
  • the amount of adjustment of the potentiometer is a measure of the change of distance, as is more fully described in us. Pat. No. 3,547,039, dated Dec. 15,1970.
  • measuring device 7 Thelower end of measuring device 7 is affixed to pressure'roll 8 which is pressed against the associated raily6, for instance by hydraulic ram 9 which exerts a vertically downward pressure on the roll.
  • pressure roll follows the rail and transmits any changes in the distance between the railand the associated reference wire, due to a faulty track level, to the measuring device to actuate the potentiometer in the indicated manner.
  • Double-beveled or flanged wheels 11 are mounted on the machine frame to grip associated rail 6 (see FIGS. 9 to 13) and to hold each rail for substantially horizontal movement therewith, wheels 11 being arranged in pairs, with one wheel in front and the other wheel in back of pressure roll 8, preferably equidistant therefrom.
  • a hydraulic motor 10 is associated with each wheel 11 to apply a downward pressure thereagainst to maintain the engagement between the wheels and their associated rails.
  • a vibrator means (not shown) is associated with wheels 1 1 and arranged to impart vibrations or oscillations in a substantially horizontal direction transverse of the track to the wheels. Since hydraulic motors l0 assure gripping engagement of wheels 11 with rails 6, the substantially horizontal vibrations or oscillations are imparted to the track, i.e. the two rails affixed to the ties.
  • the vibrations imparted to the track will have the same or about the same frequency as the natural or characteristic frequency of vibrations of the track, for instance 8 to 13 cycles per second.
  • a track lining unit 12 mounted immediately behind the rear vibratory wheels 11 is a track lining unit 12 of generally conventional type and, therefore, illustrated only schematically.
  • a track gripping rollers connected to a hydraulic motor for shifting the rollers laterally for lining the track.
  • double-beveled wheels defining a substantially V-shaped peripheral groove engaging the rails enables the wheels to be used with rail heads of different widths and this assures constant gripping of the track rails during the continuous advance of the apparatus over a long stretch of track. Since the tail-gripping wheels are pressed down against the rails, the horizontal vibrations cannot cause disengagement of the wheels from the rails.
  • FIG. 2 has the same structure as that of FIG. 1 described hereinabove.
  • Swivel trucks 2', 2 mounted machine frame 1 for mobility on the track rails, a pair of front and rear sensing elements 3 and 4 carrying the reference wire 5 for determining the level of the track.
  • a vertically adjustable auxiliary car 13 is arranged underneath machine frame 1 and is attached thereto by coupling rod 30.
  • the auxiliary car runs on wheels 14, 14 on the track rails.
  • a pair of hydraulic rams 15, 15 are mounted between frame 1 and frame 16 of the auxiliary car vertically aligned with a respective pair of wheels 14, 14 so that the wheels are pressed vertically downwardly against the track rails.
  • the car wheels 14, 14 operate in the same way as pressure rolls 8 to exert a downward pressure on the track.
  • a pair of double-beveled or flanged wheels 17 are joumaled on axle 18 intermediate the pressure wheels 14, 14, preferably equidistant therefrom, the axle being mounted on car frame 16 (see FIG. 4).
  • Vibrator means 19, such as rotating unbalanced weights, are mounted on axle 18, the main component of the vibrations caused by this means extending in a substantially horizontal plane. These vibrations are transmitted from the axle by wheels 17 to the track.
  • auxiliary car 13 carries a measuring device 7 associated with each wheel 14 for measuring the distance between the track and the reference line 5 at each wheel.
  • the downward pressure exerted upon the track by hydraulic motors 15 through wheels 14 may be controlled at different track points in dependence on the position of the track at these points.
  • a track lining unit 12 is mounted on frame 1 behind the arrangement for exert ing a downward pressure and a horizontal vibration upon the track.
  • FIGS. 5 to 8 show a specific embodiment of an auxiliary car, such as used in the embodiment of FIG. 2.
  • the car comprises essentially a frame 16 of rectangular or quadratic shape which carries a pair of axles 20 on whose ends wheels or pressure rolls 14 are joumaled.
  • Pivots 21 are mounted on car frame 16 vertically above axles 20, 20, the outer ends of the piston rods of hydraulic rams 15, 15 being affixed to the pivots while the opposite ends of the hydraulic ram cylinders are affixed to pivots 22 which are mounted on machine frame 1, each axle 20 and pivots 21, 22 lying in a vertical plane extending transversely of the track.
  • Hydraulic rams 15 not only exert a downward pressure on wheels 14 of the auxiliary car but also serve for the vertical adjustment of the car.
  • a pair of symmetrically arranged transverse braces 23, 23 reinforce and sub-divide car frame 16.
  • a boxshaped carrier 24 is mounted on the frame between the transverse braces by means of parallel links 25, 25 which enable the carrier to be vertically reciprocated in relation to frame 16.
  • a pair of unbalanced rotating weights 26, 26 is mounted on the carrier symmetrically in respect of the longitudinal axis of the track on each side thereof, the weights of each pair rotating in opposite directions, as indicated by the arrows in FIG. 8.
  • Bearing boxes 27 are mounted on each end of the carrier 24 and double-beveled wheels 28 are joumaled in the bearing boxes.
  • Fluid pressure motors 29 are linked between the carrier and machine frame 1 to exert downward pressure on wheels 28 as well as to enable the carrier to be vertically reciprocated by swinging links 25, 25 up and down.
  • the links 25 are sufficiently resilient in a transverse direction to permit carrier 24 to be swung slightly in a direction transverse to the track so that its horizontal vibratory forces are kept from auxiliary car frame 16.
  • Coupling rods 30 connect the auxiliary car to machine frame 1 to prevent the car from moving in forwardly or backwardly in the direction of track elongation when the hydraulic rams 15 exert a downward pressure on the track.
  • Each measuring device 7 includes a vertical pole 31 pivoted to the car frame 16 and moving vertically with it in response to the track position at the track point engaged by a respective wheel 14.
  • the arrangement of the means for transmitting the downward pressure and the vibrations to the track and thus to the ballast therebeneath is of special importance.
  • the mounting of these means on an auxiliary car, as shown in FIGS. 2 to 8, is particularly useful because this enables the vibrations to be kept away from the main frame of the mobile apparatus and any sensitive measuring instruments mounted thereon.
  • the auxiliary car being relatively small and light, can better follow the track and thus increases the accuracy of the measurements of the distance between the track and the reference line, which determine the accuracy of the leveling operation.
  • the lower end of hydraulic ram 15 is supported by a spring means 32, for instance a cup spring, on vibrator 33 which is mounted directly on frame 16 of the auxiliary car.
  • the interposition of the spring means has the advantage of keeping vibrations away from machine frame 1.
  • more than one vibrator may be arranged between the pressure means 15 and the car frame 16 so that only vibrations in a horizontal direction are transmitted to the frame. If the maximum vibratory force is chosen to equal the pressure force of ram 15, the track will be subjected to a pulsating stress between zero and twice the pressure of ram 15. In this manner, considerable pressure may be exerted upon the track without unduly increasing the weight of the machine.
  • the upper end of pole 31 of measuring device 7 is glidably guided in a bushing in frame 1 and carries potentiometer 72 which is adjusted by a fork 71 holding the reference wire 5, the potentiometer producing a control signal corresponding to the track position in a manner well known in track leveling operations.
  • FIG. 8 illustrates a hydraulic motor 29 associated with each bearing box 27 so that each wheel 28 is pressed against the rail head it grips.
  • Each bearing box carries a transverse block 34, the inner ends of blocks 34 being interconnected by connecting block 35 which is pivoted to the transverse block ends at 36. This arrangement makes it possible for the wheels 28 to adapt to changes in the track gage (see also FIG. 13).
  • FIGS. 9 to 14 show modifications of means for transmitting horizontal vibrations or oscillatory forces to the track, such means being adaptable to varying track gages and changing widths of the rail heads.
  • FIG. 9 The simplest vibration transmitting means is illustrated in FIG. 9 wherein two double-beveled wheels 41 are journaled on transverse axle 40 at a fixed distance from each other.
  • the V-shaped peripheral grooves of the wheels have a relatively small apex angle and the rail heads are received in these grooves with some play.
  • Vibrating means 42 is arranged to impart a horizontal oscillation to axle 40, this oscillation being transmitted by wheels 41 to rails 6.
  • the vibrating means comprises a pair of unbalances rotating in opposite directions so that the vertical vibrations are substantially eliminated and only the horizontal vibratory components remain. Since the rail heads are received in the wheel grooves with play, this arrangement will adapt to varying widths of the rails heads as well as small changes in the track gage.
  • two parallel transverse axles 40 are spaced from each other.
  • the opposite ends of the adjacent axles carry double-beveled wheels 41 gripping a respective one of heads of rails 6 while the other end of each axle carries a smooth roller 43 running on top of the rail heads.
  • the Wheels and rollers are mounted on the axles at a fixed spacing but since the axles are laterally movable independently of each other, this arrangement permits a much wider adaptation to varying track gages than the embodiment of FIG. 9.
  • the axles may, if desired, be journaled in a frame which is laterally movable. Such gage changes will not influence the transmission of vibrations from the axles to the track due to changes in the track gage.
  • vibrating means 42 are mounted on each axle 40 to impart horizontal vibrations thereto in a manner described in connection with FIG. 9 but care must be taken for the two vibrating means to rotate synchronously and in the same phase so that the same vibratory force is exerted upon both rails of the track. It would be possible, of course, to replace the two separate vibrating means by a single vibrator arranged to impart horizontal oscillations to both axles simultaneously.
  • FIG. 11 shows another modification of vibration transmitting means useful for the adjustment to variations in the track gage.
  • a single transverse axle 40' carries two double-beveled wheels 41, 41', wheel 41 being mounted on the axle against transverse movement in relation thereto when a hydraulic motor enables the wheel 41 to be transversely moved along the axle for changing the distance between the wheels and thus to adapt them to different track gages.
  • the hydraulic motor comprises a cylinder 44 whose end walls define aligned bores through which axle 40 passes in a fluid-tight manner, wheel 41 being carried by the cylinder.
  • the cylinder is glidably mounted on collar 45 of axle 40'.
  • the collar functions as a piston when pressure fluid is delivered to, or removed from, the cylinder chambers through conduits 46 and 47, the flow of the pressure fluid moving the cylinder laterally on the axle.
  • a stop device 48 is provided to hold the wheel 41' in an adjusted position.
  • This device consists essentially of a two-way solenoid valve which can be moved into a stop position which prevents delivery or removal of pressure fluid from the cylinder chambers so that there can be no relative movement between piston 45 and cylinder 44.
  • the double-beveled wheels 41 are journaled in the lower ends of carrier arms 50 which are pivotal intermediate their ends about fulcrum axes 51 extending substantially in the direction of the track to enable the carrier arms to be pivoted in a vertical plane transverse to the track.
  • the upper ends of the carrier arms are linked to doubleacting, pressure fluid operated adjustment device 52. By delivering and/or removing pressure fluid through conduits 53 and 54, the adjustment device will pivot tions in the track gage.
  • fulcrums 51 may be mounted on boxshaped carrier 24 of the auxiliary car 13 (see FIGS. to 8), if desired, it is preferred, as shown in FIG. 12, to couple the fulcrums by a rigid carrier 55 for vibrating means 42 while the upper ends of the carrier arms 50 are guided in slotted guides in the main machine frame. In this manner, the vibratory forces are transmitted to the double-beveled wheels along the main axis so that the carrier arms may oscillate together with the laterally adjustable carrier 55 without the adjustment device 52 being unduly subjected to vibrations.
  • FIG. 13 has two double-beveled wheels 41 mounted on the short arms of two-armed levers 56, 56 which are pivoted intermediate their ends to frame 16 of an auxiliary car, for pivoting in a vertical plane transverse to the track about fulcrums 57.
  • the ends of the other lever arms are linked together by connecting link 58 whose ends are pivoted to the other lever arm ends at 59, 59.
  • This arrangement makes it possible to adapt the wheels to varying track gages, wheels 41 assuming the position indicated in broken lines at the left of the figure when the track gage decreases while the wheels swing the other way when the track gage becomes larger.
  • Vibrating means 42 are mounted on. the car frame to impart horizontal oscillations to the wheels.
  • carrier an 60, 60 are spaced apart a distance corresponding roughly to the length of the ties and are pivotal in a vertical plane transverse to the track about fulcrums 61, 61.
  • Pressure fluid operated adjustment devices 62, 62 are linked to the upper ends of the carrier arms while the lower carrier arm ends have pressure plates 63, 63 which may be pressed against the tie ends by operation of the adjacent devices.
  • Fulcrums 61 are connected by rigid carrier 64 to which horizontal vibrations are imparted by vibrator 65 which, in the illustrated embodiment, has the form of a eccentric shaft. The entire vibrating arrangement may be vertically adjusted by means of hydraulic motors 66.
  • the apparatus comprises a reference system which includes a measuring device for ascertaining the difference between the actual and the desired track level, which is well known per se in the track leveling art, and operatively coupled thereto a control circuit responsive to the track level measurements for actuating the downward pressure and horizontal vibrating means in dependence on, or a function of, error signals produced by the measuring device at successive track points.
  • FIGS. 15 to 20 illustrate different embodiments of such controls enabling selected operating parameters for the track leveling operation, such as the downward pressure force, the frequency and/or amplitude of the horizontal vibrations, and the duration of the pressure and/or vibrations, to be controlled in dependence on an initial error signal, i.e. an initial measurement of the distance between the track and the reference line which indicates a deviation from the desired track level, or on continuous and successive error signals corresponding to successive track points traversed by the continuously advancing machine.
  • an initial error signal i.e. an initial measurement of the distance between the track and the reference line which indicates a deviation from the desired track level
  • continuous and successive error signals corresponding to successive track points traversed by the continuously advancing machine.
  • the circuit diagram of FIG. 15 shows a control enabling the downward pressure force exerted upon the track to be controlled in response to a continuous measurement of the difference between the actual and the desired track level.
  • This control circuit comprises a bridge circuit which includes potentiometer 72 (see FIG. 7) whose output signal is adjusted by fork 71 which holds reference wire 5 and, therefore, is moved in dependence on the wire position, i.e. its distance from the actual track level.
  • the output voltage of the potentiometer is proportional to the actual track level as compared to the desired level which is set by the reference wire.
  • the resultant output signal of bridge circuit 70 and a signal corresponding to the desired track level are compared in amplifier 73.
  • the resultant reference signal is amplified in the amplifier and forms the output signal of the amplifier, which is proportional to the difference between the actual and the desired track levels.
  • the amplified output signal is transmitted to solenoid valve 74 which is continuously adjustable to control and adjustment of the valve in response to the measured track level error.
  • Valve 74 is arranged in the hydraulic fluid flow circuit delivering hyraulic fluid to the downward pressure applying motors, for instance hydraulic motors 9 or 15 (FIGS. 1 and 2), to control the hydraulic fluid delivery, i.e. the pres sure, in proportion to the amplified control signal coming from bridge circuit 70 and amplifier 73.
  • the hydraulic fluid flow circuit comprises a hydraulic fluid sump whose fluid delivery line is connected to the input of constant speed pump 75.
  • the output of the pump leads to slide valve 76 which controls the fluid flow to rams 9 or 15 so that it stops fluid delivery entirely when the control signal is zero, i.e. the track has reached the desired level, while the fluid flow is varied by valve 74 in response to variations in the control signal.
  • a signal indicator 77 such as an amperemeter, is arranged in the electrical circuit between amplifier 73 and valve 74 so that the size of the control signal may be read by an operator who is thus enabled to see the extent of the required track repositioning.
  • FIGS. 16 and 17 illustrate control circuits which control the frequency of the horizontal vibrations imparted to the track in response to such control signals.
  • the structure and operation of circuit elements 70 to 73 are identical to those of FIG. 15, the embodiment of FIG. 16 also providing amperemeter 77.
  • the control signal is transmitted to valve 80 to control the amount of hydraulic fluid flowing through hydraulic fluid circuit 81.
  • the circuit 81 includes the constant speed pump which receives hydraulic fluid from hydraulic fluid sump 83 wherein the hydraulic fluid is held at atmospheric pressure, and also hydraulic motor or motors 82 which drives or drive the vibrating means for imparting horizontal oscillations to the track.
  • the output of motor or motors 82 is proportional to the hydraulic fluid throughput in circuit 81 controlled by valve80, i.e. proportional to the control signal, the changing motor output correspondingly varying the horizontal oscillations or vibrations. For instance, if the frequency of the vibrations was near the resonance point of the track at the beginning of the operations at a given difference between the actual and the desired track levels, it will be changed away from resonance as the track level approached the desired level.
  • the frequency of the vibrations is controlled only by electrical means.
  • the hydraulic fluid circuit 81 of FIG. 16 is replaced by electrical circuit 90.
  • Direct current drive motor 91 for the vibrating means is arranged in shunt in circuit 90.
  • the control signal is transmitted from amplifier 73 to drive motor 94 which moves sliding contact 93 of variable resistance 93 in circuit 90 so that the power supplied to field coil 92 of direct current motor 91 is changed in proportion to the control signal.
  • FIGS. 18, 19 and 20 show controls for changing the amplitude of the horizontal vibrations in response to the error signal by switching a selected number of vibrators on or off.
  • two separate control circuits I and II are provided for operating drive motors 100 and 101, respectively, for the vibrating means.
  • the two control circuits are closed, i.e. power is fed to the drive motors, by closing switches 102 and 103, respectively. Opening and closing of the switches is controlled by switch tripping relays 104 and 105, respectively which are operated mechanically directly by camming surface 106 affixed to the pole of measuring device 7. The distance between the camming surface 106 and reference wire 5 is constant.
  • Switch tripping relays 104, 105 are mounted on rolls 8 or 14 (see FIGS. 1 and 2) so that the position of the camming surface 106 in relation to relays 104, 105 will depend on the level of the track.
  • camming surface 106 will actuate only relay 105 (as shown in FIG. 18) so that only control circuit I is closed to operate the vibrating means drive motor 100.
  • the actual track level is particularly high so that increased force is desirable for pressing the track 106 is mounted on the pole of measuring device 7 and remains at a constant distance from the rail on which the pole for measuring device 7 rides.
  • Relays 104 are mounted on the frame of the apparatus or on pressure rolls 8 or 14 and will be sequentially tripped as the pole rises.
  • FIG. 20 shows a control circuit diagram for controllingthe stepwise actuation of additional vibrators for increasing the vibration amplitude as well as additional hydraulic rams for increasing the downward pressure on the track in proportion to the length of the correction stroke required to reposition the track at the desired level.
  • the control circuit elements 70 to 73 are again the same as those described in connection with FIGS. 15 to 17, providing a control signal at the output of amplifier 73 which is proportional to the track level error.
  • This error signal is transmitted to computer which classifies the signal into individual signal steps, the illustrated embodiment providing three signal steps, the three resultant output signals of computer 120 operating solenoid slide valves 121, 122 and 123 which control hydraulic drive motors 124, 125 and 126 sequentially, the valves and associated drive motors being arranged in three separate hydraulic fluid circuits.
  • the drive motors operate the vibrating means.
  • hydraulic rams 130, 131 and 132 for experting downward pressure on the track are also mounted in the respective hydraulic fluid circuits, the pressure in the latter motors being controlled by pressure reducing slide valves 127, 128 and 129, respectively. These valves are also controlled by the output signals from computer 120.
  • the output signal of amplifier 73 indicates a relatively small track level error, it will be classified only in one step of computer 120. Thus, only a single vibrating means drive motor and a signle downward pressure ram will be actuated. As the level error increases, producing an error signal at the output of amplifier 73 proportional thereto, the computer will sequentially actuate the additional vibrating means drive motors and downward pressure rams. A further differentiation in the force applied to the track may be achieved by using vibrators with different amplitudes and rams with different pressures. It would also be possible, of course, to operate the vibrating means and the downward pressure rams independently by computer 120.
  • apparatus makes it possible to do track maintenance work attuned most sensitively to various requirements and conditions encountered in compacting ballast underneath a track and positioning the track at a desired level.
  • it is possible to control not only the speed in which the desired track level is reached but also the nature of the ballast tamping. Since these factors depend at least one three parameters, i.e. the downward pressure force, the frequency and the amplitude of the horizontal vibrations to which the track is subjected, variations in these parameters may be variously controlled and coordinated to meet all requirements in a most sensitive manner.
  • a continuous track work operation it is possible to operate the parameters sequentially at any given track point. It is also possible to anticipate an observed track depression of excessive magnitude before this point is reached by lifting the track at this point particularly high.
  • the invention may be advantageously combined with a mobile track leveling and lining machine of otherwise conventional structure, the track tamping, leveling and lining means being mounted on the machine frame ahead of the means for vibrating the track horizontally and pressing it downwardly, in the working direction of the machine.
  • FIG. 21 An apparatus of this type is shown in F [G 21 wherein an elongated machine frame runs on the track on wheels 2, 2, tamping assembly 140 being mounted on an overhanging frame portion whose front holds track jack 141 for leveling and/or lining the track, the leveling being effected in relation to reference line
  • a mobile track working machine of this general type is shown, for instance, in US. Pat. No. 3,21 1,109, dated Oct, 12, 1965, but any other track leveling and/or lining machine may be used.
  • auxiliary car 13 with its gear according the the invention is mounted intermediate the machine wheels.
  • the track may be raised by jack 141, at which time it may also be lined by the jack, the ballast may be tamped underneath the ties by assembly 140, and the track is then pressed down to the desired track level while being horizontally vibrated at any selected track point according to the invention, the repositioning of the track simultaneously causing com paction of the ballast thereunder.
  • any suitable vibrating means may be used for imparting substantially horizontal vibrations or oscillations to the track, including rotating unbalanced weights, vibrating rams or eccenter shafts.
  • the only essential characteristic of the vibrating means is that it has a marked horizontal component for imparting a substantially horizontal vibration to the track. It is also essential that the means for transmitting the vibrations to the track is so arranged that the track will vibrate with substantially the same frequency and amplitude as the controlled vibration of the vibrating means.
  • track surfacing according to the present invention holds the track at the desired level for a very long period of time since it compacts the ballast to an extent equivalent to that usually accom plished only by long and extensive train traffic and the resultant pressures and vibrations to which the passing trains subject the ballast. Furthermore, such track surfacing also results in a considerable compaction of the ballast at the ends of the ties, which has a most advantageous effect on the lining of the track.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track including a vibration-producing means and means for transmitting the vibration produced by said means to the track, and means arranged in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under the track ties may be compacted simultaneously with positioning the track at the desired level.
  • the track surfacing apparatus of claim 1 further comprising an apparatus frame and an auxiliary car vertically adjustably mounted on the apparatus frame, the auxiliary car carrying the vibration and pressure imparting means.
  • the track surfacing apparatus of claim 1 further comprising ballast tamping and track lifting means mounted ahead of the vibration and pressure imparting means in the Working direction of the apparatus.
  • the track surfacing apparatus of claim 2 wherein the means for transmitting the vibration comprises double-flanged wheels engaging the track rails and imparting the vibration to the track rails.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track including a vibration-producing means and a pair of pressure plates vertically adjustably arranged for pressure engagement with the end of respective ones of the ties for transmitting the vibration produced by the vibration-producing means to the track, means for varying the distance between the pressure plates in the direction of elonga' tion of the ties to effectuate said'pressure engagement, and means arranged in association with the Vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under the track ties may be compacted simultaneously with positioning the track at the desired level.
  • the distance varying means includes a pair of guide levers carrying the pressure plates, the guide levers being operatively coupled to the vibration-producing means.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track including a vibration-producing means and a pair of double-beveled rotatable wheels each defining a substantially V- shaped peripheral groove receiving the rail heads of the respective rails for transmitting the vibration produced by the vibration-producing means to the track rails, and means arranged in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under the track ties may be compacted simultaneously with positioning the track at the desired level.
  • the track surfacing appartus of claim 8 further comprising two parallel transverse axles spaced from each other and laterally movable in respect of the track, the rotatable wheels being fixedly mounted on opposite ends of the adjacent axles for gripping a respective one of the rail heads in their peripheral grooves,.and smooth rollers running on top of the rail heads carried by the other axle ends.
  • the track surfacing apparatus of claim 8 further comprising a transverse axle for mounting the rotatable wheels at respective ends thereof, one of the wheels being mounted against transverse movement in relation to the axle, the other wheel being mounted for transverse movement in relation to the axle, and means for moving the other wheel to vary the distance between the wheels for adaptation to varying track gages.
  • the track surfacing apparatus of claim 8 further comprising a pair of guide levers carrying the rotatable wheels, and means for pivoting the guide levers in a plane transverse to the track about fulcrum axes extending substantially parallel to the track to vary the distance between the rotatable wheels.
  • the track surfacing apparatus of claim 13 further comprising a rigid carrier interconnecting the fulcrums of the guide levers intermediate their ends, the
  • vibration-producing means being carried by the carrier
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track including a vibration-producing means and means for transmitting the vibration produced by said means to the track, rail engaging wheels and hydraulic rams mounted in vertical alignment with the wheels on the apparatus in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under the track ties may be compacted simultaneously with positioning the track at the desired level.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track including a vibration-producing means and means for transmitting the vibration produced by said means to the track, and a plurality of hydraulic rams supported on the apparatus and spaced from each other in the direction of track elongation in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under the track ties may be compacted simultaneously with positioning the track at the desired level.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level, means for imparting a substantially horizontal vibration to the track, an apparatus frame, and an auxiliary car vertically adjustably mounted on the apparatus frame, means carried by the auxiliary car and arranged in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby ballast under the track ties may be compacted simultaneously with positioning the track at the desired level, said pressure imparting means including rail engaging wheels mounting the auxiliary car for movement along the track and hydraulic rams in vertical alignment with the wheels to exert the pressure on the track by means of the wheels, one end of the rams being supported on the apparatus frame while the other ends thereof are supported on the auxiliary car.
  • the track surfacing apparatus of claim 19 further comprising elongated rods coupling the auxiliary car to the apparatus frame, the respective arm ends being pivotally supported on the apparatus frame and the auxiliary car.
  • An apparatus for surfacing a track consisting of rails fastened to ties resting on ballast comprising means for determining any deviation of the track position from a desired level including means for producing an error signal proportional to the determined deviation, means for imparting a substantially horizontal vibration to the track, means arranged in association with the vibration imparting means for imparting a substantially vertical downward ballast compacting pressure on both rails of the track whereby the ballast under th track ties may be compacted simultaneously with positioning the track at the desired level, and
  • the means for determining the track position deviations includes a potentiometer adjustable in response to the deviations to produce the proportional error signals
  • the electrical control circuit means includes a bridge circuit comprising the potemtiometer and having an output, and a circuit element receiving the error signals from the bridge circuit output, comparing the error signal with a reference signal proportional to the desired track level, and producing an amplified control signal resulting from the comparison for actuating the vibration and downward pressure imparting means.
  • the track surfacing apparatus of 24, wherein the pressure imparting means comprises hydraulic ram means, a hydraulic fluid circuit delivering hydraulic 18 fluid to the ram means, and a solenoid pressure control valve in the fluid circuit, the valve being arranged in the control circuit means for actuation by the control signal.
  • vibration imparting means comprises vibration-producing means and hydraulic drive motor means for actuating the vibration-producing means, and further comprising a hydraulic fluid circuit delivering hydraulic fluid to the drive motor means, and a solenoid valve controlling the fluid throughput of the hydraulic circuit, the valve being arranged in the control circuit means for actuation by the control signal.
  • the vibration imparting means comprises a vibration-producing means and an electric drive motor means for actuating the vibration-producing means, and further comprising an electric circuit operating the drive motor means, the electric circuit being energized by the control signal.
  • the vibration and downward pressure imparting means includes a plurality of vibration-producing means and a plurality of pressure means, the electrical control circuit means being arranged to transmit the control signal in stages to selected ones of said vibration-producing and pressure means.
  • the track surfacing apparatus of claim 21, wherein the means for determining the track position deviations includes an element vertically moving with the track according to its level, a camming surface fixedly mounted on the element, and switch means in the electrical control circuit means arranged for se quential actuation by the camming surface in response to vertical track movement for transmitting the error signal to the selected vibration-producing and pressure means.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
US404427A 1972-10-13 1973-10-09 Track surfacing apparatus Expired - Lifetime US3926123A (en)

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AT881672A AT336663B (de) 1972-10-13 1972-10-13 Verfahren und maschine zur niveaukorrektur eines gleises mit schotterbettung

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CA (1) CA1004083A (sk)
CH (1) CH565898A5 (sk)
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US3973550A (en) * 1975-11-10 1976-08-10 Frank W. Murphy Manufacturer, Inc. Engine shut-down device
US4046079A (en) * 1975-01-31 1977-09-06 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track surfacing apparatus
US4046078A (en) * 1975-01-31 1977-09-06 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track surfacing apparatus
US4064807A (en) * 1975-08-18 1977-12-27 Franz Plasser Bahnbaumaschinen Industriegesellschaft M.B.H. Mobile apparatus for non-stop track leveling and ballast tamping
US4068596A (en) * 1975-08-25 1978-01-17 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Mobile ballast tamper
US4125075A (en) * 1977-03-18 1978-11-14 Canron, Inc. High speed production tamper compactor
US4430946A (en) * 1981-01-16 1984-02-14 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Mobile machine and method for compacting ballast
US4432284A (en) * 1980-07-31 1984-02-21 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Mobile ballast cleaning machine
US4760796A (en) * 1986-04-02 1988-08-02 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Ballast cleaning machine with compacting device
US5127333A (en) * 1990-02-06 1992-07-07 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track maintenance machine for compacting ballast
US5419259A (en) * 1993-03-17 1995-05-30 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Machine for compacting track ballast with variable gauge track stabilizer
WO2012094125A1 (en) 2011-01-07 2012-07-12 Harsco Corporation Vertical force stabilizer

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AT337241B (de) * 1975-03-05 1977-06-27 Plasser Bahnbaumasch Franz Fahrbare maschine zum verdichten und korrigieren des gleises
US4212076A (en) * 1976-09-24 1980-07-08 Giddings & Lewis, Inc. Digital computer structure providing arithmetic and boolean logic operations, the latter controlling the former
AT371171B (de) * 1981-01-28 1983-06-10 Plasser Bahnbaumasch Franz Gleisnivellierstopf- und richtmaschine mit stabilisationsaggregat
AT373648B (de) * 1982-02-09 1984-02-10 Plasser Bahnbaumasch Franz Verfahren zum einblasen von bettungsmaterial mittels einer gleiskorrekturmaschine
DE3212062C2 (de) * 1982-04-01 1984-04-19 Philips Patentverwaltung Gmbh, 2000 Hamburg Vorrichtung zum Nachstellen des Betätigungsstößels einer Betätigungseinrichtung
US5172637A (en) * 1991-02-01 1992-12-22 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track surfacing machine for the controlled lowering of the track
DE19833520A1 (de) * 1998-07-25 2000-01-27 Weiss Gmbh & Co Leonhard Verfahren zum Verlegen und/oder Richten einschließlich Stabilisieren eines Eisenbahn-Gleisrostes in einem Schotterbett
AT503437B1 (de) * 2006-08-10 2007-10-15 Plasser Bahnbaumasch Franz Verfahren zum unterstopfen und stabilisieren eines gleises
RU2464370C2 (ru) * 2010-07-15 2012-10-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Иркутский государственный университет путей сообщения" (ФГБОУ ВПО ИрГУПС) Система автоматического контроля качества уплотнения балластного слоя рельсового пути
CN103835194A (zh) * 2012-11-27 2014-06-04 拜耳材料科技(中国)有限公司 压力分配装置及使用其对铁轨施压以保持轨面标高的方法
US9441330B2 (en) 2013-02-25 2016-09-13 Harsco Corporation Device for generating vertical force with rotating mass
CN103738357B (zh) * 2014-01-15 2016-11-02 株洲时代电子技术有限公司 基于转向架安装的探伤装置
NO2902546T3 (sk) 2014-01-30 2018-03-24
WO2016023609A1 (de) * 2014-08-13 2016-02-18 Plasser & Theurer Export Von Bahnbaumaschinen Gesellschaft M.B.H. Maschine zur stabilisation eines gleises
CN105625116B (zh) * 2014-11-04 2017-06-13 中国铁建高新装备股份有限公司 正线道岔稳定车作业施工方法
CN105625115B (zh) * 2014-11-04 2017-04-05 中国铁建高新装备股份有限公司 正线道岔稳定车在道岔区的稳定作业控制方法
CN110116734A (zh) * 2019-05-07 2019-08-13 中国铁建重工集团股份有限公司 磁浮轨道作业车
CN112284602B (zh) * 2020-07-22 2022-03-08 兰州理工大学 一种高精度夹紧力测量装置
CN113738126B (zh) * 2021-08-03 2022-08-12 安徽军瑶新型材料有限公司 一种装配式建筑用防倾斜水平装置及其实施方法
AT18204U1 (de) * 2022-11-22 2024-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stabilisationsaggregat, Schienenfahrzeug und Verfahren zum Stabilisieren eines Gleises

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046079A (en) * 1975-01-31 1977-09-06 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track surfacing apparatus
US4046078A (en) * 1975-01-31 1977-09-06 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track surfacing apparatus
US4064807A (en) * 1975-08-18 1977-12-27 Franz Plasser Bahnbaumaschinen Industriegesellschaft M.B.H. Mobile apparatus for non-stop track leveling and ballast tamping
US4068596A (en) * 1975-08-25 1978-01-17 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Mobile ballast tamper
US3973550A (en) * 1975-11-10 1976-08-10 Frank W. Murphy Manufacturer, Inc. Engine shut-down device
US4125075A (en) * 1977-03-18 1978-11-14 Canron, Inc. High speed production tamper compactor
US4432284A (en) * 1980-07-31 1984-02-21 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Mobile ballast cleaning machine
US4430946A (en) * 1981-01-16 1984-02-14 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Mobile machine and method for compacting ballast
US4760796A (en) * 1986-04-02 1988-08-02 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Ballast cleaning machine with compacting device
US5127333A (en) * 1990-02-06 1992-07-07 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Track maintenance machine for compacting ballast
US5419259A (en) * 1993-03-17 1995-05-30 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. Machine for compacting track ballast with variable gauge track stabilizer
AU673577B2 (en) * 1993-03-17 1996-11-14 Franz Plasser Bahnbaumaschinen-Industriegesellschaft M.B.H. A machine for consolidating the ballast bed of a track
WO2012094125A1 (en) 2011-01-07 2012-07-12 Harsco Corporation Vertical force stabilizer
US20120174816A1 (en) * 2011-01-07 2012-07-12 Harsco Corporation Vertical force stabilizer
US8505459B2 (en) * 2011-01-07 2013-08-13 Harsco Corporation Vertical force stabilizer

Also Published As

Publication number Publication date
JPS582281B2 (ja) 1983-01-14
AU6044873A (en) 1975-03-20
US3919943A (en) 1975-11-18
GB1454172A (en) 1976-10-27
ZA737512B (en) 1974-09-25
SU645605A3 (ru) 1979-01-30
CA1004083A (en) 1977-01-25
SU893140A3 (ru) 1981-12-23
ATA881672A (de) 1976-09-15
JPS4972812A (sk) 1974-07-13
DE2330102C2 (de) 1982-12-02
AT336663B (de) 1977-05-25
DE2330102A1 (de) 1974-04-25
FR2202980B1 (sk) 1980-08-08
FR2202980A1 (sk) 1974-05-10
CH565898A5 (sk) 1975-08-29

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