EP3481998A1 - Appareil et procédé de bourrage de ballast - Google Patents

Appareil et procédé de bourrage de ballast

Info

Publication number
EP3481998A1
EP3481998A1 EP16908294.8A EP16908294A EP3481998A1 EP 3481998 A1 EP3481998 A1 EP 3481998A1 EP 16908294 A EP16908294 A EP 16908294A EP 3481998 A1 EP3481998 A1 EP 3481998A1
Authority
EP
European Patent Office
Prior art keywords
tamping
hydraulic actuator
linear hydraulic
actuator
operatively coupled
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP16908294.8A
Other languages
German (de)
English (en)
Inventor
Damiano PADOVANI
Monika Ivantysynova
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Harsco Technologies LLC
Original Assignee
Harsco Technologies LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Harsco Technologies LLC filed Critical Harsco Technologies LLC
Publication of EP3481998A1 publication Critical patent/EP3481998A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • E01B27/16—Sleeper-tamping machines

Definitions

  • Embodiments disclosed herein related to an apparatus and method for tamping ballast.
  • Rails are generally constructed of a pair of elongated, substantially parallel rails, which are coupled to a plurality of laterally extending ties via metal tie plates and spikes and/or spring clip fasteners.
  • the rails and ties are disposed on a ballast bed formed of hard particulate material, such as gravel.
  • ballast adjacent to and/or under the ties is "tamped,” or compressed, to ensure that the ties, and therefore the rails, do not shift. This tamping process ensures that the rails and ties are sufficiently aligned, stable, and/or durable.
  • a rail vehicle for carrying out tamping operations is generally referred to as a
  • tamper and includes work heads for carrying out tamping operations.
  • work heads typically include a workhead frame, a sub frame, hydraulic actuators linking the sub frame to the tamping arms, a number of tamping tools (often referred to as tynes), attached to the tamping arms and terminating in paddles.
  • the tamping tools are adapted to move towards one another in a pincer-like motion in order to compress the ballast adjacent to and underlying the ties.
  • Vibration of the tamping tools further compresses the ballast.
  • multiple vibration devices may be employed in order to provide tools for tamping inside and outside the rails as well as forward and aft of the ties. Such tamping operations may be carried out at each tie via a tamper vehicle, which advances along the rails.
  • the present disclosure relates to an energy efficient hydraulic drive associated with tamping units where the vibration of the tamping tools is adjustable in terms of both amplitude and frequency.
  • a hydraulic drive may be installed on the tamping unit to provide a drive for each of the tamping tools.
  • Such tamping units may be equipped with a mobile frame (e.g., a subframe) extendable in the vertical and transverse directions, tamping arms pivoting about the sub frame, linear hydraulic actuators that drive each tamping arm and tamping tools for compressing ballast.
  • the position of the tamping tools may be sensed by displacement sensors associated with the linear hydraulic actuators.
  • the vibration of the tamping tools as well as the motion of the tamping tools may be controlled based on the displacement sensor signal. Accordingly, the motion of each linear hydraulic actuator may be controlled by an associated variable- displacement servo-pump.
  • Each linear hydraulic actuator may include one or multiple internal chambers
  • each linear hydraulic actuator includes two chambers
  • the flow rate going into a first chamber of a linear hydraulic actuator and the flow rate coming out a second chamber of each linear hydraulic actuator may both flow through the associated variable-displacement servo-pump.
  • the vibration of each tamping tool may be adjusted in terms of both amplitude and frequency by varying the displacement of the variable-displacement servo-pump, thus enabling an energy-efficient functioning of the system. Accordingly, hydraulic valves may no longer be needed to be positioned between linear hydraulic actuators and variable-displacement servo-pumps, thereby removing the losses due to flow throttling.
  • an apparatus may comprise: a rigid frame; a variable-displacement servo-pump operatively coupled to the frame; a double rod linear hydraulic actuator operatively coupled to the sub frame at a proximal end of the double rod linear hydraulic actuator and comprising: at least one internal cavity for receiving hydraulic fluid from the variable-displacement servo-pump via a hydraulic hose; and an actuator rod passing through a first internal cavity and a second internal cavity of the double rod linear hydraulic actuator; a tamping arm operatively coupled to a distal end of the double rod linear hydraulic actuator and a tamping tool coupled to the tamping arm.
  • the double rod linear hydraulic actuator is configured to translate in a longitudinal direction along the actuator rod in response to the at least one internal cavity of the double rod linear hydraulic actuator receiving hydraulic fluid, thereby causing movement of at least one of the tamping tools.
  • the apparatus may further comprise: a vibrator operatively coupled to the frame, wherein vibrations of the vibrator cause the tamping tool to vibrate when performing ballast tamping operations.
  • the double rod linear hydraulic actuator comprises at least one of a displacement sensor, a pressure transducer, and a position sensor for collecting sensor data associated with the double rod linear hydraulic actuator.
  • the apparatus may further comprise: an intelligent microcontroller for controlling displacement of hydraulic fluid between the variable- displacement servo-pump and the at least one cavity of the double rod linear hydraulic actuator in response to receiving sensor data associated with the double rod linear hydraulic actuator from at least one of the displacement sensor, the pressure transducer, and the position sensor.
  • the apparatus may further comprise: another linear actuator defining a lower end operatively coupled to the sub frame and an upper end operatively coupled to a workhead frame operatively coupled to the vehicle frame for raising and lowering the apparatus in relation to the tamper vehicle frame.
  • This linear actuator may be a single rod linear actuator.
  • an apparatus may comprise: a rigid frame; a variable-displacement servo-pump operatively coupled to the frame; a linear hydraulic actuator system operatively coupled to the frame at a proximal end of the linear hydraulic actuator system and comprising: a first single rod linear hydraulic actuator and a second single rod linear hydraulic actuator operatively coupled to each other via one or more pins and oriented in opposite directions on a common plane, wherein each of the first single rod linear hydraulic actuator and the second single rod linear hydraulic actuator comprise: at least one internal cavity for receiving hydraulic fluid from the variable-displacement servo-pump via a hydraulic hose; and an actuator rod passing through only one cavity of the at least one internal cavity; and a tamping arm operatively coupled to a distal end of the linear hydraulic actuator system and a tamping tool coupled to the tamping arm.
  • the first single rod linear hydraulic actuator in response to at least one internal cavity of the first single rod linear hydraulic actuator and the second single rod linear hydraulic actuator receiving hydraulic fluid, the first single rod linear hydraulic actuator is configured to extend along the actuator rod of the first single linear hydraulic actuator in a first longitudinal direction and the second single rod linear hydraulic actuator is configured to extend along the actuator rod of the second single linear hydraulic actuator in a second longitudinal direction opposite the first longitudinal direction, thereby causing movement of the tamping arm and therefore the movement of the tamping arm.
  • the apparatus may further comprise: a vibrator operatively coupled to the frame, wherein vibrations of the vibrator cause the tamping tool to vibrate when performing ballast tamping operations.
  • At least one of the first linear hydraulic actuator and the second linear hydraulic actuator comprises at least one of a displacement sensor, a pressure transducer, and a position sensor for collecting sensor data associated with at least one of the first linear hydraulic actuator and the second linear hydraulic actuator.
  • the apparatus may further comprise: an intelligent microcontroller for controlling displacement of hydraulic fluid between the variable- displacement servo-pump and the at least one cavity of the linear hydraulic actuator in response to receiving sensor data associated with the linear hydraulic actuator from at least one of the displacement sensor, the pressure transducer, and the position sensor.
  • the apparatus may further comprise: another linear actuator defining a lower end operatively coupled to the sub frame and an upper end operatively coupled to a workhead frame operatively coupled to the vehicle frame for raising and lowering the apparatus in relation to the tamper vehicle frame.
  • This linear actuator may be a single rod linear actuator.
  • a method may be provided. The method may comprise: advancing a tamping vehicle along railroad tracks to a first predetermined location; lowering, relative to the tamping vehicle, a frame of a tamping apparatus by extending a first linear hydraulic actuator defining a lower end operatively coupled to the sub frame and an upper end operatively coupled to the workhead frame operatively coupled to the vehicle frame; tamping, using the tamping apparatus, ballast positioned underneath one or more rail ties of the railroad tracks; raising, relative to the tamping vehicle frame by retracting the first linear hydraulic actuator; and advancing the tamping vehicle along the railroad tracks to a second predetermined location.
  • lowering the frame further comprises: lowering a tamping tool into the ballast for performing at least one tamping operation wherein an upper end of the tamping tool is operatively coupled to the tamping arm and the tamping arm is operatively coupled to a distal end of a second linear hydraulic actuator, and wherein a proximal end of the second linear hydraulic actuator is operatively coupled to the sub frame.
  • tamping the ballast comprises: measuring, using at least one of a displacement sensor, a pressure transducer, and a position sensor associated with the second linear hydraulic actuator, at least one of a fluid property and a position of an actuator rod comprised in the second linear hydraulic actuator; receiving, at a microcontroller, sensor data associated with the second linear hydraulic actuator from at least one of the displacement sensor, the pressure transducer, and the position sensor; determining, using the microcontroller, an amount of hydraulic fluid to be displaced within at least one cavity of the second linear hydraulic actuator; and displacing, using a variable-displacement servo-pump, the determined amount of hydraulic fluid to at least one cavity of the second linear hydraulic actuator, thereby causing the second linear hydraulic actuator to extend or retract in a longitudinal direction along the actuator rod, wherein causing the second linear hydraulic actuator to extend or retract in a longitudinal direction along the actuator rod causes the tamping tool to move.
  • FIGURE 1 illustrates an exemplary rail tamper, in accordance with some embodiments of the disclosure
  • FIGURE 2 illustrates an exemplary tamping unit, in accordance with some embodiments of the disclosure
  • FIGURE 3 illustrates an exemplary schematic of a hydraulic system that utilizes a dual-chambered "double rod” linear hydraulic actuator, in accordance with some embodiments of the disclosure
  • FIGURE 4 illustrates an exemplary actuator system that utilizes two dual- chambered "single rod” linear hydraulic actuators, in accordance with some embodiments of the disclosure
  • FIGURE 5 A illustrates an exemplary schematic of an actuator system that utilizes two dual -chambered "single rod” linear hydraulic actuators to perform an extension movement, in accordance with some embodiments of the disclosure.
  • FIGURE 5B illustrates an exemplary schematic of an actuator system that utilizes two dual-chambered "single rod” hydraulic actuators to perform a retraction movement, in accordance with some embodiments of the disclosure.
  • the apparatus and method for moving and vibrating tamping tools may be employed in a tamping machine rail vehicle 100, as illustrated in FIGURE 1.
  • the tamping vehicle 100 may include a frame assembly 102, a propulsion device 104, a tamping unit 106 and a cabin 108.
  • Frame assembly 102 may include a plurality of rigid frame members and a plurality of wheels 110 that are configured to travel on a pair of rails 112.
  • the tamping vehicle 100 may travel across the pair of rails 112, which is disposed over a series of rail ties 114 operatively coupled and/or secured to the rails 112.
  • the rails 112 and series of ties 114 may be disposed over a bed of ballast 115 (e.g., crushed stones, rocks, gravel, and/or the like).
  • the propulsion device 104 of the tamping vehicle 100 may be configured and/or utilized to move tamping vehicle 100 in one or more directions along the pair of rails 112.
  • the tamping unit 106 may be configured to tamp ballast between rail ties 114 to reshape the ballast. This reshaping of the ballast may improve the alignment, stability, and/or durability of the rails 112 and/or rail ties 114.
  • the tamping unit 106 may include multiple workheads. In the side view of
  • FIGURE 1 one workhead can be viewed while another workhead may also be included at an opposite side corresponding with the other rail. Any number of workheads (e.g., 2, 4, etc.) may be included in the tamping unit 106.
  • the tamping unit 106 may include tamping arms 116, which are operatively coupled to tamping tools 126 that may be lowered into the ballast between rail ties 114. Movement of the tamping arms 116, and therefore the tamping tools 126, may be controlled by one or more actuators 118 operatively coupled to a sub frame 124 as further described below.
  • the tamping tools 126 may be actuated (e.g., be caused to move) by one or more hydraulic actuators 118 that squeeze the tamping tools 126 around the rail ties 114 when inserted into the ballast beneath the rail ties to thereby compact and/or otherwise reshape the ballast material.
  • the tamping unit 106 may further include a variable-displacement servo-pump
  • the servo-pump 122 may be placed at a variety of positions on the rail vehicle 100.
  • the amount and/or flow rate of hydraulic fluid being sent to each chamber of the hydraulic actuators 118 may cause the tamping arms 116 and therefore the tamping tools 126 to translate, pivot, and/or otherwise move in a variety of directions.
  • the tamping unit 106 may be operatively coupled to the frame assembly 102 via a workhead frame 120, the sub frame 124 and an actuator operatively coupled between the workhead frame 120 and the sub frame 124.
  • the actuator preferably a hydraulic actuator
  • the actuator may be operable to lower the tamping unit 106 such that the tamping tools 126 may be inserted into the ballast between adjacent rail ties 114 where squeezing and vibration actions may be performed to tamp (e.g., compress, reshape, etc.) the underlying ballast.
  • the tamping vehicle 100 may advance along the rails
  • a linear hydraulic actuator may then be actuated in response to hydraulic fluid being sent to and/or from each chamber of the actuator to thereby lower the tamping unit 106 (e.g., the tamping tools 126 into the ballast).
  • the tamping tools 126 may be enabled to carry out the tamping operations of the ballast as desired, where movement of the tamping tools may be controlled by one or more actuators 118 in response to hydraulic fluid being sent to and/or from each chamber of the actuator.
  • the actuators 118 may cause vibration and thus causing the associated tamping tools 126 to vibrate during operation.
  • the flow of hydraulic fluid being sent to and/or from each chamber of the actuator(s) 118 used to control movement of the tamping unit 106 and/or the tamping tools 126 may be controlled by the variable-displacement servo-pump 122 and/or a hydraulic circuit included in the variable-displacement servo-pump.
  • the actuator that lowered the tamping unit may be actuated to raise (and in some cases stow) the tamping tools 126 and/or the tamping unit 106 as a whole for travel to a second rail tie 114.
  • the tamping vehicle 100 may also include a tracking device 125 that measures general linear movement of the rail vehicle 100 along the rail track 112. In this manner, the tracking device 125 may enable the tamping vehicle 100 to accurately position itself, the tamping unit 106, and/or the tamping tools 126 in relation to a rail tie 114. Additionally, cabin 108 of the tamping vehicle 100 may be structured such that it remains stationary relative to the frame assembly 102 as the rail vehicle 100 moves along the rails 112.
  • FIGURE 2 illustrates the tamping unit 106 in more detail.
  • the tamping unit 106 may include a sub frame 124, which may be extended in the vertical direction (e.g., raised and/or lowered) by an actuator during tamping operations.
  • the sub frame 124 of the tamping unit 106 may be operatively coupled to the frame assembly 102 (shown in FIGURE 1 but not shown in FIGURE 2) of the tamping vehicle 100 by one or more vertical bars (not pictured) extending downward from the workhead frame assembly 120.
  • an actuator may cause the sub frame 124 of the tamping unit 106 to translate in a vertical direction (e.g., raise and/or lower) along the vertical bars.
  • the sub frame 124 may include one or more apertures (not pictured) through which the vertical bars may pass when the tamping unit 106 is raised and/or lowered (e.g., translated vertically) along the longitudinal direction of the vertical bars.
  • the tamping unit 106 may include tamping tools 126.
  • Each tamping tool 126 may include a tamping pad at its lower end that is to be inserted into the ballast (e.g., lowered into the gravel bed beneath the rails 112 and/or the rail ties 114) during operation.
  • the tamping tools 126 may be mounted on the tamping arms 116 for pivoting about pivot joints 127 (shown in FIGURE 2 and in FIGURE 3) having pivot axes extending in a longitudinal direction of the rail ties 114 (e.g., orthogonal to the longitudinal direction of the rails 112) when being actuated by actuators 118.
  • the actuators 118 may be mechanically connected and/or otherwise operably coupled to each tamping arm 116 of the tamping unit 106 for moving the tamping tools 126 (e.g., pivoting the tamping arms about the pivot joints 127), in response to flow of hydraulic fluid in the chambers of the actuators coupled to the tamping arms.
  • the position of each tamping tool 126 may be sensed by a displacement sensor 128 associated with each actuator 118 and/or each chamber of each actuator.
  • Each displacement sensor 128 may measure, monitor, and/or otherwise determine an amount of fluid (e.g., hydraulic fluid) held in each chamber of an actuator 118.
  • Each displacement sensor 128 may also measure, monitor, and/or otherwise determine one or more fluid properties (e.g., pressure, volume, temperature, and/or the like) of a fluid being held inside of each chamber of an actuator 118.
  • each displacement sensor 128 may include an electronic sensor, a transmitter, a transceiver, a wireless communication unit, a wired communication unit, and/or the like for capturing, transmitting, and/or receiving sensor data (e.g., measured values and/or properties of hydraulic fluid in each chamber of an actuator 118).
  • Sensor data may be transmitted and/or received between displacement sensors 128 and a communication unit associated with the variable-displacement servo-pump 122 for controlling one or more flows of fluid (e.g., hydraulic fluid) to and/or from one or more chambers of actuators 118.
  • fluid e.g., hydraulic fluid
  • Each of the displacement sensor 128 and the variable-displacement servo-pump 122 may include electrical circuits, computing processor hardware, and/or the like for making intelligent determinations of how fluid is to be dispersed among different elements of the apparatus described herein.
  • each actuator 1 18 may determine the motion of the tamping tools 126. For example, when an actuator 118 extends outwardly in a direction along its longitudinal axis, the tamping arm and therefore the associated tamping tool 126 may pivot about a pivot joint 127. This pivoting action of the tamping arm 116 may cause the tamping tool 126 to move in a direction opposite of the direction in which the actuator 118 extends.
  • the tamping arm 116 and therefore the associated tamping tool 126 may pivot about the pivot joint 127 to thus cause the tamping tool 126 to move in a direction opposite of the direction in which the actuator retracts.
  • each actuator 118 may include one or more internal chambers (e.g., cavities) into which fluid (e.g., hydraulic fluid) is displaced.
  • the displacement of fluid in each chamber of an actuator 118 may cause the actuator 118 to actuate (e.g., retract and/or extend in a linear direction and also vibrate).
  • the amount and/or flow of fluid displaced in each chamber of the actuator 118 may be determined and/or monitored by a displacement sensor 128 and/or controlled by the variable-displacement servo-pump 122.
  • each chamber of the actuators 118 may be connected to a hydraulic circuit of the variable-displacement servo-pump 122 by means of hydraulic hoses 130.
  • FIGURE 3 shows a simplified schematic of a hydraulic system 132 used to power a dual-chambered "double rod” linear hydraulic actuator 118 in a closed-circuit configuration.
  • the schematic may depict a hydraulic circuit included in and/or associated with the variable- displacement servo-pump 122 that is utilized to disperse hydraulic fluid among various elements of the hydraulic system 132.
  • a dual -chambered double rod linear hydraulic actuator 118 may be operatively coupled to the sub frame 124.
  • the actuator 118 may also be hydraulically coupled with an associated variable-displacement servo-pump 122 via hydraulic hoses 130.
  • each chamber of the actuator 118 may be connected to one port of the associated variable-displacement servo-pump 122 by means of two hydraulic hoses 130.
  • each chamber of the actuator 118 may be connected to a low-pressure source 134 through both check valves 136 and relief valves 138.
  • a dedicated charge pump 140 may feed the low-pressure source 134.
  • the double rod actuator 118 of FIGURE 3 may be actuated when more hydraulic fluid is displaced within a first chamber of the double rod actuator 118 than a second chamber of the double rod actuator 118. Displacing more hydraulic fluid within the first chamber of the double rod actuator 118 increases the pressure within the first chamber of the double rod actuator 118, which thus causes the double rod actuator 118 to translate (e.g., move, slide, and/or the like) along the actuator rod 119 disposed within both the interior of the first and second chambers of the double rod actuator 118 in a first direction.
  • Each actuator 118 included in the tamping unit 106 may be driven by a dedicated variable-displacement servo-pump 122 or multiple variable-displacement servo-pumps 122. Alternatively, multiple actuators 118 may be driven by a common variable-displacement servo- pump 122. Each variable-displacement servo-pump 122 may be powered by a combustion engine 142 of the tamping unit 106. Each variable-displacement servo-pump 122 may also include an external drain 144 connected to a hydraulic tank of the tamping unit 106 for discharging hydraulic fluid as desired.
  • the check valves 136 may serve the purpose of
  • hydraulic fluid may be recycled and/or reused as it is collected in the hydraulic tank of the tamping unit 106.
  • the hydraulic system 132 may include an electronic control system that includes electronic sensors for measuring and/or monitoring hydraulic pressure in each chamber (e.g., a pressure transducer 146) and/or a position of an actuator rod 119 inside each chamber of an actuator 118 (e.g., a position sensor 148).
  • an angular sensor (not pictured) may be coupled to a pivot joint 127 so as to measure an angle of a tamping tool 126.
  • each of the pressure transducer 146 and/or the position sensor 148 may also include the displacement sensor 128 as described above, and/or vice versa.
  • Sensor signals and/or sensor data collected by the sensors 128, 146, 148 may be electrically transmitted to a digital microcontroller 150, where a desired hydraulic fluid displacement setting for each variable-displacement servo-pump 122 may be calculated.
  • the microcontroller 150 may execute a feedback control algorithm and send a command signal to an electrohydraulic valve included in a pump adjustment system 152, which may regulate fluid displacement of the variable-displacement servo-pump 122 to control the flow rate of hydraulic fluid flowing into and/or out of the variable-displacement servo-pump 122 in a suitable manner.
  • a goal of the hydraulic system 132 may be to create a motion of the actuator 118 characterized by a vibration adjustable in terms of both amplitude and frequency. Since the tamping arm 116 and therefore the tamping tool 126 is mechanically coupled to the actuator 118, vibration of the actuator may result in vibration of the tamping tool 126. This vibration of the tamping tool 126 may be controlled by adjusting a swashplate angle of the variable-displacement servo-pump 122 based on a measured position of a linear actuator rod 119 inside each chamber of the actuator 118.
  • the position of the linear actuator rod 119 inside each chamber of the actuator 118 may be measured using the position sensor 148 and/or displacement sensor 128. Both frequency and amplitude of the vibration of the tamping tool 126 may be adjusted to any value between zero and the upper limit of the system using the microcontroller 150.
  • monitoring the pressure in each chamber of the actuator 118 e.g., each chamber being in which hydraulic fluid is displaced by the variable-displacement servo- pump 122
  • the pressure sensor 146 may provide increased safety of operation by enabling the microcontroller 150 to limit a maximum squeezing force being applied to the ballast by the tamping tool 126 during operation (i.e., when tamping the ballast 115).
  • a critical pressure e.g., a pressure value that exceeds a predetermined threshold pressure value
  • a specific control algorithm executed by the microcontroller 150 may cause the variable-displacement servo-pump 122 to destroke (e.g., stop operation, reduce and/or limit fluid flow rate, and/or the like) and thereby limit the maximum squeezing pressure being applied to the ballast 115 by the tamping tool 126.
  • Another advantage of the hydraulic system 132 as described herein is the ability to achieve a desired amount (e.g., amplitude and/or frequency) of vibration of the tamping tool 126 without introducing any throttle loss between the variable-displacement servo-pump 122 and the actuator 118.
  • the hydraulic system 132 may not require any hydraulic valve to be positioned between the actuator 118 and the variable-displacement servo-pump 122 of the hydraulic system 132.
  • a direct hydraulic coupling e.g., the hydraulic hose 130
  • This capability of more easily adjusting vibration of the tamping tool 126 without utilizing hydraulic valves between the actuator 118 and the variable-displacement servo-pump 122 may provide a significant improvement to the field of art in terms of overall efficiency and fuel savings of the hydraulic system 132.
  • hydraulic valves Prior to the present disclosure, hydraulic valves have been necessarily positioned between actuators and the displacement pumps in hydraulic systems to adjust vibrations of tamping pads, thereby introducing unwanted metering losses between the displacement pumps and the actuators.
  • An alternative to utilizing a double rod actuator 118 as described with reference to FIGURE 3 that achieves the same end result of increased efficiency and fuel savings may include utilizing actuator system 154 as shown in FIGURE 4 instead of a double rod actuator 118.
  • the actuator system 154 may include two dual-chamber "single rod” actuators 118 (e.g., a first single rod actuator 118a and a second single rod actuator 118b) coupled together via pins 156 as shown in FIGURE 4.
  • the actuator system 154 may couple to the sub frame 124 of the tamping unit 106 via a first mounting port 158.
  • the actuator system 154 may couple to a tamping arm 116 via a second mounting port 160.
  • Each of the single rod actuators 118a, 118b may be driven by a variable-displacement servo-pump 122, which may be coupled to each single rod actuator 118a, 118b via a hydraulic hose 130.
  • the actuator system 154 of FIGURE 4 may be utilized to control movement of the associated tamping tool 126 (via the tamping arm 116) in response to hydraulic fluid flowing into and/or out of a chamber of each single rod actuator 118a, 118b of the actuator system 154.
  • the actuator system 154 may utilize two single rod actuators 118a, 118b to actuate and move the associated tamping arm 116 instead of one double rod actuator 1 18, a first single rod actuator 118a of the actuator system 154 may be responsible for causing the associated tamping tool 126 to move in a first direction, while a both single rod actuators 118a and 118b of the actuator system 154 may be responsible for causing the associated tamping tool 126 to move in a second direction that is opposite the first direction.
  • a first single rod actuator 118a may be actuated when more hydraulic fluid is displaced within a first chamber of the first single rod actuator 118a than a second chamber of the first single rod actuator 118a. Displacing more hydraulic fluid within the first chamber of the first single rod actuator 118a increases the pressure within the first chamber of the first single rod actuator 118a, which thereby causes the first single rod actuator 118a to extend (e.g., translate, move, slide, and/or the like) along the actuator rod 119 disposed within the interior of the second chamber of the first single rod actuator 118a in a first direction.
  • FIGURE 4 that utilizes two single rod actuators 118 may require the variable-displacement servo-pump 122 to coordinate hydraulic fluid flow between both single rod actuators 118 of the actuator system 154.
  • Areas of high and low pressure (p High and p Low) and direction of flow rate (Q) are illustrated in FIGURE 5A and FIGURE 5B. Accordingly, fluid may be displaced in and/or withdrawn from a first chamber of the second single rod actuator 118b to utilize, offset, and/or overcome the exerted force in the second direction.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)

Abstract

La présente invention concerne de manière générale un véhicule de bourrage de ballast de voie ferrée et des procédés d'utilisation associés, le véhicule comprenant : un châssis rigide ; une servo-pompe à déplacement variable accouplée de manière fonctionnelle au véhicule ; au moins un actionneur hydraulique linéaire, accouplé de manière fonctionnelle au châssis à une extrémité proximale du ou des actionneur(s) hydraulique(s) linéaire(s) et comprenant : au moins une cavité interne destinée à recevoir le fluide hydraulique provenant de la servopompe à déplacement variable par l'intermédiaire d'un tuyau hydraulique ; et une tige d'actionnement traversant une première cavité interne et une seconde cavité interne du ou des actionneur(s) hydraulique(s) linéaire(s) ; et un outil de bourrage, accouplé de manière fonctionnelle à une extrémité distale du ou des actionneur(s) hydraulique(s) linéaire(s). Un tampon de bourrage associé à l'outil de bourrage peut être abaissé dans du ballast sous-jacent à une voie ferrée, et entre des traverses de voie ferrée, pour mettre en oeuvre des opérations de bourrage de ballast.
EP16908294.8A 2016-07-05 2016-07-05 Appareil et procédé de bourrage de ballast Withdrawn EP3481998A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/US2016/040965 WO2018009173A1 (fr) 2016-07-05 2016-07-05 Appareil et procédé de bourrage de ballast

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EP3481998A1 true EP3481998A1 (fr) 2019-05-15

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CA (1) CA3029171A1 (fr)
WO (1) WO2018009173A1 (fr)

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AT522652A1 (de) * 2019-05-23 2020-12-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren und Vorrichtung zum Steuern/Regeln eines rotatorischen Antriebs eines Arbeitsaggregates einer Gleisbaumaschine
CN112160196A (zh) * 2020-10-21 2021-01-01 中国铁建高新装备股份有限公司 捣固装置及捣固车

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AT500972B1 (de) * 2004-10-29 2006-05-15 Plasser Bahnbaumasch Franz Verfahren zum unterstopfen von schwellen

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