EP3239398B1 - Unité de bourrage pour une bourreuse - Google Patents

Unité de bourrage pour une bourreuse Download PDF

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Publication number
EP3239398B1
EP3239398B1 EP17161805.1A EP17161805A EP3239398B1 EP 3239398 B1 EP3239398 B1 EP 3239398B1 EP 17161805 A EP17161805 A EP 17161805A EP 3239398 B1 EP3239398 B1 EP 3239398B1
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EP
European Patent Office
Prior art keywords
tamping
tamping unit
cylinder
vibration
hydraulic cylinder
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EP17161805.1A
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German (de)
English (en)
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EP3239398A1 (fr
Inventor
Bernhard Lichtberger
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HP3 Real GmbH
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HP3 Real GmbH
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • 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
    • E01B27/17—Sleeper-tamping machines combined with means for lifting, levelling or slewing 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
    • E01B2203/00—Devices for working the railway-superstructure
    • E01B2203/12—Tamping devices

Definitions

  • the invention relates to a tamping unit for a tamping machine, arranged on a, in a Stopfaggregatrahmen height adjustable guided, carrier arranged as rocker Stopftechnikmaschinefaren whose immersion in a ballast certain lower tufting ends with a vibratory drive in opposite directions drivable and hydraulically to each other beitellbar each of the tamping tools of a Stopftechnikmaschinefares is associated with a hydraulic cylinder, wherein the hydraulic cylinders form both the Beistellantrieb and the vibration drive of the tamping and Hydraulikzylinderan horrventile are provided for actuating the hydraulic cylinder, which are servo or proportional valves and which are preferably arranged directly on the hydraulic cylinder.
  • an adjustable opening width cylinder or opening width distance sensor may be provided for continuous opening width adjustment.
  • Tamping units penetrate with gravel tools the gravel of a track bed in the area between two sleepers (intermediate compartment), in the area of the support of the threshold in the ballast under the rail and compact the ballast by a dynamic vibration of the tamping between the opposable tamping pegs that can be provided to each other. Tamping units can plug one, two or more sleepers in one work cycle ( DE 24 24 829 A . EP 1 653 003 A2 ). According to the teaching of EP 1 653 003 A2 the effective as a linear drive Beistellantriebe are designed such that these not only a linear Beistellterrorism, but at the same time in one of the AT 339,358 , of the EP 0 331 956 or the US Pat. No.
  • the movements of a tamping unit include the vertical immersion of the tamping pick in the ballast, the Beistellieri in which the tamping ends are closed to each other and the superimposed dynamic oscillation which causes the actual compaction of the ballast grains.
  • Other known solutions use linear excitation via hydraulic cylinders. Two hydraulic cylinders are mechanically coupled in series. The one hydraulic cylinder performs the Beistell Gay, the other the vibratory movement. The size of the resulting vibration is determined mechanically and by the hydraulic excitation. The size of the amplitude can not be adjusted freely.
  • Optimal stop frequencies for compression are known to be between 25-40 Hz, with penetration of the tamping in normal ballast with Higher frequencies is easier, since only a lower immersion shock occurs and thus the stress on the bearings of the tamping unit can be reduced. This is no longer the case for irregular heavily contaminated hard gravel beds.
  • frequency and amplitude advantageous.
  • the tamping units in use today have a very high and costly maintenance. Typically, the units are at least partially overhauled and maintained every season. After 1-2 overhauls, the units must be replaced by new ones.
  • the amplitude decreases due to the elasticity of the hydraulic hoses and thus the compression effect decreases. From various studies it is known that decreasing Stopfamplituden or a decreasing compression frequency affect the compression and also reduce the penetration into the ballast.
  • the invention is therefore the object of tamping units of the type described with simple means such that the stability of the vibration drive by the use of only one Hydraulikbeistellzylinders is significantly increased, but at the same time on the use of highly stressed displacement sensors in the cylinder and an indirect complicated control can be dispensed with the associated disadvantages.
  • the invention achieves the stated object in that at least one means for determining the oil flow, in particular an oil flow sensor, is provided in the hydraulic cylinder oil supply circuit and that the control of the hydraulic cylinder is dependent on the oil flow data oil flow dependent so that a given Beistellweg the stuffing tools is achieved.
  • Each of the stuffing tools of a Stopftechnikmaschinepares is associated with a hydraulic cylinder, wherein the hydraulic cylinder form the Beistellantrieb as well as the vibration drive of Stopfpickel and the control of the proportional or servo valve takes place directly via the electrical valve input. At this control input, the signals are now electrically specified so that the desired flow through the Beistellzylinder arise.
  • the means for determining the oil flow allow the controllability of the hydraulic cylinder (positions).
  • the flow in the Hydraulikzylinderan tenueran may be measured, for example by an evaluation of the measured position of the valve piston in the valve.
  • a stopper auxiliary cylinder which is hydraulically biased.
  • the two cylinder pressures are measured by means of pressure sensors.
  • the vibration is switched off and the hydraulic cylinders are opened.
  • the unit moves together until a mechanical stop on the auxiliary cylinder on the piston side strikes the stopper auxiliary cylinder previously set by the operator.
  • the pressure in the auxiliary cylinder increases at short notice. This increase in pressure is detected and evaluated by the controller and stopped the Beistellieri.
  • shock valves which are pivoted in, for example, via compressed air cylinders as mechanical stops.
  • the hydraulic cylinder piston rod is then retracted until the mechanical stop is reached.
  • one has no continuously adjustable opening width but only two opening widths. This corresponds to the most commonly used tamping units today which still have shock valves. If distance sensors are used to control the opening width, then these can also be used to measure the auxiliary travel.
  • a single common hydraulic cylinder is used for the Beistellterrorism and the vibratory movement of at least one stuffing pickle (possibly also of several synchronously driven stuffing pickles of several pairs of stuffing needles).
  • Hydraulic cylinder control valves in particular servo or proportional valves, which are arranged directly on the hydraulic cylinder, are recommended for actuating the hydraulic cylinders.
  • the hydraulic lines should be as short as possible, so that the elasticity, the storage effect (damping) of the hydraulic hoses under the impact load, is kept low.
  • Typical requirements are amplitudes of 3-6 mm at the tamping ends at a maximum frequency of 50 Hz. Compression amplitudes close to the upper limit are better, for example, for loose gravel (after track cleaning and track renewal or new track construction).
  • the control / regulation specifies the oscillation, the oscillation amplitude and the oscillation frequency, depending on the height and the supplementary position of the tufting ends.
  • the linear addition movement corresponds to a constant oil flow with pressure on the A side of the valve.
  • the nominal flow rate is predetermined by an electrical signal course. For this purpose, for the linear Beistellterrorism required as above corresponding to the Beistellieri superimposed on the sign changing vibration oil flow. The amplitude of the AC voltage for the oil flow then corresponds to the vibration amplitude and the frequency of the AC voltage of the stop frequency.
  • the main advantage of the invention is the simple construction.
  • the Stopfaggregatö Maschinensweite ie the distance between the tufting ends, infinitely adjustable and is any free preselection of the stop frequency, such as immersion of the pimples at 50 Hz for a low insertion shock and a compression at 35 Hz in working position to reduce wear and noise , easily possible.
  • Continuous adjustment of the stuffing amplitude and its signal shape allows an optimal adaptation to the respective superstructure conditions. If a control loop is provided, an automatic readjustment of the plug movement takes place in the event of resistance changes by the control loop, thus ensuring that the desired plug amplitudes and frequencies are maintained.
  • the Beistell Gay is controlled and / or regulated by the controller / regulation.
  • the control / regulation it is advisable for the control / regulation to readjust the oscillation, the oscillation amplitude and the oscillation frequency accordingly, depending on the comparison of the desired flow to the actual flow, in particular with a flow meter, the oil flow , With the help of the pressure sensors, the achieved compacting force can be measured. If the maximum possible degree of compression is reached, the optimal time is to stop the plug. Otherwise, the compacted support will be reduced in area by drainage of compacted ballast.
  • the compacting work is proportional to the ballast bed hardness.
  • the compaction of the ballast bed can be calculated.
  • the measuring signals are numerically integrated as indicated.
  • each cylinder is assigned a hydraulic cylinder control valve.
  • a hydraulic cylinder control valve For a Einschwollenstopfmaschine therefore eight, for a two-shaft tamping machine already sixteen and for a Dreischwellenstopfmaschine thirty-two cylinders with the associated Hydraulikzylinderan horrventilen are required. In addition to the associated costs, the number of valves used naturally also increases the susceptibility to errors.
  • the stuffing tools 4, 5, 6, 17 are designed as two-armed lever. One arm of the respective stuffing tool 6 is formed by a tamping pick 17 and on this engages a hydraulic cylinder 5, the other end is mounted on a support 23. About pressure sensors 11, the cylinder pressures are measured.
  • the cylinder 5 is electrically actuated via a servo valve or a proportional valve 12.
  • a servo valve or a proportional valve 12 In the hydraulic cylinder oil supply circuit, there is an oil flow sensor 14. The pressure is generated via a hydraulic pump 15. The oil is sucked by the pump 15 from the hydraulic tank 16 via the oil flow sensor 14 to the control valve 12. Depending on the control of the valve 12, either the A connection or the B connection is supplied with pressure.
  • the auxiliary movement takes place when the A-side is pressurized, the opening movement when the B-side is pressurized.
  • the ballast 19 is compressed by the tamping 17 below the threshold 18.
  • the compacting movement 20 of the pickle 17 consists of a continuous closing movement 22 and a superimposed oscillatory movement 21.
  • a hydraulically preloaded position cylinder 8 with integrated displacement sensor 24 can be continuously adjusted by the operator to the desired opening width D. be set.
  • booting into working position now closes the side cylinder 5 until the mechanical stop 7 on the stop 9 occurs.
  • the resistance generates a pressure peak in the auxiliary cylinder 5 which is measured via the pressure sensor 11.
  • the electronics 25 detects this pressure peak and automatically switches off the further movement of the auxiliary cylinder 5. With this device, any desired opening width D can be set by the operator.
  • the Beistellterrorism the Beistellzylinders 3 can be seen by 22.
  • a non-contact laser distance meter 10 or another position sensor are used, which measures the distance of the mechanical stop 7.
  • the auxiliary cylinder 5 is also switched off. In the upper working position the vibration is always switched off.
  • 29 schematically indicates the position of the tamping unit 3 in the upper working rest position. The height ⁇ h is called the stop depth.
  • Figure 30 schematically illustrates a pivotable mechanical stop, often referred to as a flapper. Swiveled in, it delivers the normal opening angle as used for single sleepers. However, if there are double sleepers (with a rail joint) then the shock flaps 37 are swung out and the stuffing arms are opened further.
  • Fig. 3 schematically shows a side cylinder with the cylinder tube surface A z and the piston surface A k .
  • the auxiliary cylinder oscillates with the amplitude A.
  • Fig. 4 schematically shows a side cylinder which adjoins the Beistell Malawi v B moves. When working, the oscillation overlaps with the amplitude A and the continuous addition movement v B.
  • Fig. 6 shows the control characteristic of a control valve. Applied vertically is the flow. Horizontal the control signal in%. Positive flow 2, PA means pushing out of the piston rod and thus compression, negative flow 1, PB means flow reversal and retraction of the piston rod.
  • the diagram it can be seen that the operating point at Q is In and around this operating point, the oil flows for the vibration move. In the case shown, the setpoint with the additional frequency f would fluctuate between approx. -20% and 80%. The resulting flows would be Q min with negative modulation and Q max with positive modulation.
  • the setpoint input in% is carried out electrically eg by a current loop of 0-20mA. 0mA (-100%) would have full negative modulation, at 10mA (0%) no flow would set and at 20mA (100%) full positive modulation.
  • Fig. 7 schematically shows a control / regulating device 25.
  • the pressure sensors 11, the flow sensor 14 and the position sensors 10, 24 are connected.
  • the operator can enter the amplitude A, the frequency f and the additional speed v B via the touch display 26 or a keyboard 28.
  • the control valve 12 is activated.
  • the arithmetic unit can perform a desired-actual comparison 27 of the desired flow rate with the measured actual flow rate and adjust it so that the desired compression amplitude and the desired auxiliary speed result.
  • two hydraulic cylinders 4, 5 are connected to a common Hydraulikzylinderan Kunststoffventil 12, wherein between the Hydraulikzylinderan Kunststoffventil 12 and the hydraulic cylinders 4, 5, a flow divider 31 is provided. Between the flow divider 31 and the hydraulic cylinders 4, 5 each an oil flow sensor 14 is arranged. However, it could also be provided only an oil flow sensor upstream of the flow divider 31.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (14)

  1. Unité de bourrage (3) pour une bourreuse avec des paires d'outils de bourrage, conçues comme levier oscillant, placées sur un support (23), guidé de manière réglable en hauteur dans un châssis d'unité de bourrage, dont certaines extrémités de pics de bourrage (17) inférieures peuvent être entraînées en sens contraire pour l'immersion dans un lit de ballast (19) avec un entraînement par vibration (4, 5) et peuvent être fournies l'une à l'autre de manière hydraulique, un vérin hydraulique (5) étant associé à chacun des outils de bourrage (6) d'une paire d'outils de bourrage, les vérins hydrauliques (4, 5) formant la commande de rapprochement comme également l'entraînement par vibration des outils de bourrage (6) et pour l'actionnement des vérins hydrauliques (4, 5), des vannes pilotes de vérin hydraulique (12) étant prévues, qui sont des soupapes proportionnelles ou d'asservissement et qui sont disposées de préférence directement sur le vérin hydraulique (4, 5), caractérisée en ce que dans le circuit d'alimentation du liquide du vérin hydraulique, au moins un moyen est prévu pour la détermination du débit d'huile, en particulier un capteur de débit d'huile (14), et en ce que la commande des vérins hydrauliques (4, 5) s'effectue en fonction des données de débit d'huile, suivant le débit d'huile, de telle sorte qu'un trajet de rapprochement prédéfini des outils de bourrage peut être obtenu.
  2. Unité de bourrage selon la revendication 1, caractérisée en ce qu'un vérin de butée (8) à précontrainte hydraulique avec butée (9) et des capteurs de pression (11) sont montés au niveau du support d'unité de bourrage pour le mesurage de pression des pressions de vérin.
  3. Unité de bourrage selon les revendications 1 et 2, caractérisée en ce qu'est intégré un capteur de déplacement (24) dans le vérin de butée (8) à précontrainte hydraulique.
  4. Unité de bourrage selon l'une des revendications 1 à 3, caractérisée en ce qu'un capteur de déplacement (24) est monté conçu en tant que lasermètre (10), qui mesure la largeur d'ouverture (D) du vérin de rapprochement (4, 5)(*).
  5. Unité de bourrage selon l'une des revendications 1 à 3, caractérisée en ce qu'un capteur de déplacement (24) est monté conçu en tant que détecteur de distance à ultrasons qui mesure la largeur d'ouverture (D) du vérin de rapprochement (4, 5)(*).
  6. Unité de bourrage selon l'une des revendications 1 à 3, caractérisée en ce qu'un capteur de déplacement (24) est monté conçu en tant que système de mesure à câble, qui mesure la largeur d'ouverture (D) du vérin de rapprochement (4, 5)(*).
  7. Unité de bourrage selon l'une des revendications 1 à 6, caractérisée en ce qu'une butée (30) fixe peut être basculée vers l'intérieur et vers l'extérieur, qui prédétermine deux largeurs d'ouverture (D) du vérin de rapprochement (4, 5)(*).
  8. Unité de bourrage selon l'une des revendications 1 à 7, caractérisée en ce qu'un dispositif de commande/régulation (25) prédétermine la vibration (21), l'amplitude de vibration (A) et la fréquence de vibration (f) en fonction du débit mesuré, en particulier avec un capteur de débit (14).
  9. Unité de bourrage selon la revendication 8, caractérisée en ce que la position du vérin hydraulique peut être prédéterminée par le dispositif de commande/régulation (25), en fonction du débit (14, Qsoll).
  10. Unité de bourrage selon l'une des revendications 1 à 9, caractérisée en ce qu'une vibration (21) est superposée à un mouvement de rapprochement (VB) linéaire du vérin hydraulique (4, 5).
  11. Unité de bourrage selon l'une des revendications 8 à 10, caractérisée en ce que le dispositif de commande/régulation (25) prédétermine la vibration (21), l'amplitude de vibration (A) et la fréquence de vibration (f), en fonction de la hauteur (Δh) du pic de bourrage (17).
  12. Unité de bourrage selon l'une des revendications 8 à 10, caractérisée en ce que le dispositif de commande/régulation (25) prédétermine la vibration (21), l'amplitude de vibration (A) et la fréquence de vibration (f), en fonction de la chute de pression par arête de commande (Δp), du volume nominal (QN) et de la chute de pression nominale (ΔPN) de la vanne de commande.
  13. Unité de bourrage selon l'une des revendications 4 à 12, caractérisée en ce que le détecteur de distance (10) mesure le trajet de rapprochement (20).
  14. Unité de bourrage selon l'une des revendications 1 à 13, caractérisée en ce qu'au moins deux vérins hydrauliques (4, 5) sont raccordés au niveau d'une vanne pilote de vérin hydraulique (12) commune, un répartiteur de débit (31) étant prévu entre la vanne pilote de vérin hydraulique (12) et les vérins hydrauliques (4, 5).
    (*) N.d.T : traduction littérale du terme allemand peu fréquent « Beistellzylinder » en l'absence de contexte plus précis. A vérifier.
EP17161805.1A 2016-04-29 2017-03-20 Unité de bourrage pour une bourreuse Active EP3239398B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA50384/2016A AT518072B1 (de) 2016-04-29 2016-04-29 Stopfaggregat für eine Gleisstopfmaschine

Publications (2)

Publication Number Publication Date
EP3239398A1 EP3239398A1 (fr) 2017-11-01
EP3239398B1 true EP3239398B1 (fr) 2019-10-30

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AT (1) AT518072B1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT519738B1 (de) 2017-07-04 2018-10-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren und Vorrichtung zum Verdichten eines Gleisschotterbetts
AT520698B1 (de) * 2017-12-07 2020-09-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren und System zur Belastungsüberwachung eines Stopfaggregates
AT520791B1 (de) * 2017-12-21 2020-08-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren zum Betreiben eines Stopfaggregats einer Gleisbaumaschine sowie Stopfvorrichtung zur Gleisbettverdichtung und Gleisbaumaschine
AT520771B1 (de) * 2017-12-28 2020-08-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren zum Betreiben eines Stopfaggregats einer Gleisbaumaschine sowie Stopfvorrichtung zur Gleisbettverdichtung und Gleisbaumaschine
AT16726U1 (de) * 2018-09-13 2020-07-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren und Vorrichtung zum Unterstopfen von Schwellen eines Gleises
AT521765B1 (de) * 2018-09-18 2021-06-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat und Verfahren zum Unterstopfen von Schwellen eines Gleises
AT521850A1 (de) * 2018-10-24 2020-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Gleisbaumaschine und Verfahren zum Unterstopfen von Schwellen eines Gleises
AT521798B1 (de) * 2018-10-24 2021-04-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Verfahren und Vorrichtung zum Verdichten eines Schotterbettes
AT526293A1 (de) * 2022-07-05 2024-01-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat und Verfahren zum Unterstopfen von Schwellen eines Gleises

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AT339358B (de) 1974-05-09 1977-10-10 Plasser Bahnbaumasch Franz Antriebs- und steuereinrichtung fur vibrier- und verstellbare werkzeuge einer gleisbearbeitungsmaschine, insbesondere fahrbare gleisstopfmaschine
DE2424829A1 (de) 1974-05-22 1976-01-08 Deutsche Bundesbahn Verfahren zur erhoehung von arbeitsgeschwindigkeit und arbeitsgenauigkeit von gleisstopfmaschinen
US4068595A (en) 1975-11-17 1978-01-17 Graystone Corporation Track tamper
AT369455B (de) 1981-02-02 1983-01-10 Plasser Bahnbaumasch Franz Nivellier-gleisstopfmaschine mit automatischer stopfdruckregelung
IT1219091B (it) 1988-03-09 1990-04-24 So Re Ma Operatrici Ferroviari Macchina rincalzatrice perfezionata particolarmente per la rigenerazione di massicciate ferroviarie
AT500972B1 (de) 2004-10-29 2006-05-15 Plasser Bahnbaumasch Franz Verfahren zum unterstopfen von schwellen
AT513973B1 (de) * 2013-02-22 2014-09-15 System7 Railsupport Gmbh Stopfaggregat für eine Gleisstopfmaschine

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EP3239398A1 (fr) 2017-11-01
AT518072A4 (de) 2017-07-15
AT518072B1 (de) 2017-07-15

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