EP3545134B1 - Tamping unit for tamping sleepers of a track - Google Patents

Tamping unit for tamping sleepers of a track Download PDF

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Publication number
EP3545134B1
EP3545134B1 EP17793570.7A EP17793570A EP3545134B1 EP 3545134 B1 EP3545134 B1 EP 3545134B1 EP 17793570 A EP17793570 A EP 17793570A EP 3545134 B1 EP3545134 B1 EP 3545134B1
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EP
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Prior art keywords
tamping
squeezing
unit
cylinders
pressure chamber
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German (de)
French (fr)
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EP3545134A1 (en
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Thomas Philipp
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Plasser und Theurer Export Von Bahnbaumaschinen GmbH
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Plasser und Theurer Export Von Bahnbaumaschinen GmbH
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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
    • 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
    • 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 tamping under sleepers of a track, comprising opposing tamping tools which are each connected to an auxiliary cylinder for generating a auxiliary movement, an eccentric drive being provided for generating a vibratory movement.
  • Tamping units for tamping under sleepers of a track are already known several times, for example through AT 350 097 B .
  • a rotatable eccentric shaft serves as a vibration exciter, to which the auxiliary drives are linked to transmit the vibrations to the tamping tools.
  • the advantage of the vibration drive with an eccentric lies in the energy balance of the overall system. Only as much energy is supplied as is taken off at the tamping tine, or what is lost through friction in the system.
  • the energy storage at the eccentric takes place in a flywheel or flywheel, which absorbs energy when the tamping ax is braked and returns it to the dynamic system when the tamping ax is accelerated (kinetic energy).
  • the GB 797 044 A shows a tamping unit according to the preamble of claim 1.
  • the invention is based on the object of an improvement over the prior art for a tamping unit of the type mentioned Specify technique.
  • the object of the invention is in particular to create a compact design for tamping units.
  • the invention provides that a first auxiliary cylinder is mechanically connected to the eccentric drive and that a first pressure chamber of the first auxiliary cylinder is hydraulically connected to a second pressure chamber of a second auxiliary cylinder via a connecting line in order to transfer a pressure change generated in the first pressure chamber by means of an eccentric drive to the second Transfer pressure chamber.
  • the main advantage here is the energy balance of the overall system, because the storage effect of the eccentric drive is used. This combines the advantages of the eccentric drive with the advantage of a compact design because an auxiliary cylinder can be arranged independently of the eccentric drive.
  • An advantageous further development of the invention provides that there is an approximately identical force transmission ratio from the respective auxiliary cylinder to the associated tamping tool and that the two auxiliary cylinders are driven in opposite directions.
  • each mass has a counter mass that moves in opposite directions.
  • the static mass balance achieved in this way minimizes vibrations and noise emissions. This creates a more pleasant working environment for the worker, as well as low-noise use of the tamping unit in residential areas.
  • both auxiliary cylinders are aligned approximately horizontally, if the tamping tool assigned to the first auxiliary cylinder has a first mass moment of inertia with respect to a pivot axis, if the tamping tool assigned to the second auxiliary cylinder has a second mass moment of inertia with respect to a pivot axis and if both mass moments of inertia are coordinated with one another. In this way a dynamic mass balancing is ensured, whereby the over a Unit suspension on a tamping machine transmitting vibration is minimized.
  • a further advantageous embodiment of the invention is given by the fact that the tamping unit is composed of several individual unit modules to form a multi-sleeper unit. Due to the compactness of the individual aggregate modules, they can be combined cost-effectively to multi-sleeper aggregates. This has a positive effect on both production and maintenance of the individual modules.
  • each unit module is advantageously designed to be identical in construction with its own eccentric drive.
  • first auxiliary cylinders are mechanically connected to a common eccentric drive and if each first auxiliary cylinder is hydraulically connected to a second auxiliary cylinder.
  • a particularly advantageous embodiment provides that the connecting line is connected to a hydraulic system via a pressure screen.
  • the adjustment force and vibration of the adjustment cylinders are set via this pressure panel.
  • Another useful development is achieved in that an amplitude of an eccentric shaft is distributed uniformly between the two auxiliary cylinders. Instead of controlling one additional cylinder with two individual eccentrics, an eccentric shaft that is twice as large can be used for both additional cylinders.
  • FIG. 1 Simplified tamping unit 1 for tamping under a ballast bed 2 below sleepers 3 of a track 4 has pairs of two opposite tamping tools 14, 17 pivotable about a respective pivot axis 5. Specifically, as the respective tamping tool 14, 17, a tamping pick 6 with a pick arm 8 is mounted on a tool carrier 7 and is connected to an auxiliary cylinder 9, 15.
  • a first auxiliary cylinder 9 is connected at a cylinder-side end 10 to a vibration drive designed as an eccentric drive 11 with a rotating eccentric shaft 12, and at a piston-side end 13 to a first tamping tool 14.
  • a second auxiliary cylinder 15 is rotatably mounted on a rotation axis 16 on the tool carrier 7 and is connected with its piston-side end 13 to a second tamping tool 17.
  • the first auxiliary cylinder 9 has a first pressure chamber 18 and a third pressure chamber 19.
  • the second auxiliary cylinder 15 has a second pressure chamber 20 and a fourth pressure chamber 21.
  • the first pressure chamber 18 of the first auxiliary cylinder 9 is hydraulically connected to the second pressure chamber 20 of the second auxiliary cylinder 15 via a first connecting line 22 in order to transmit part of the vibration generated by the eccentric drive 11 to the second auxiliary cylinder 15.
  • the first and second auxiliary cylinders 9, 15 are connected to a constant pressure supply 23 of a hydraulic system.
  • the first connecting line 22 is connected to the constant pressure supply 23 and a tank 25 via a servo valve or a proportional valve 24.
  • a standby pressure in the first pressure chamber 18 of the first auxiliary cylinder 9 and in the second pressure chamber 20 of the second auxiliary cylinder 15 is thus regulated.
  • the auxiliary pressure is superimposed by a pressure generated by means of the eccentric drive oscillating pressure.
  • This oscillating pressure is divided between the two auxiliary cylinders 9, 15 via the first connecting line 22.
  • Hydraulic fluid oscillates back and forth between the first pressure chamber 18 and the second pressure chamber 20, which also causes a piston rod 29 of the second auxiliary cylinder 15 to vibrate.
  • An outflow in the direction of the proportional valve 24 is prevented via a first pressure screen 26.
  • the third pressure chamber 19 of the first auxiliary cylinder 9 is hydraulically connected to the fourth pressure chamber 21 of the second auxiliary cylinder 15 via a second connecting line 27. Volume compensation takes place via this second connecting line 27, which is necessary due to the increase in volume in the first and second pressure chambers 18, 20 during a provision process and the superimposed oscillation of the hydraulic fluid.
  • the second connecting line 27 is also connected to the constant pressure supply 23 and has a second pressure orifice 28 for pressure regulation. If the piston rods 29 of the auxiliary cylinders 9, 15 are pressed outwards during an ordering process and the stuffing tools 6 are provided, a volume reduction inevitably occurs in the third pressure chamber 19 and in the fourth pressure chamber 21 and the hydraulic fluid is discharged via the second pressure orifice 28.
  • Fig. 2 shows a further embodiment of the tamping unit 1 for tamping two sleepers 3 of the track 4 at the same time.
  • a first unit module 30 and a second unit module 31 are combined to form a two-sleeper tamping unit.
  • the tamping tools 14, 17 can be offset from one another in a transverse track direction in order to avoid a mutual collision.
  • radii r 1 , r 2 of an upper pivot lever and a lower pivot lever of the first tamping tool 14 and radii r 3 , r 4 of an upper pivot lever and a lower pivot lever of the second tamping tool 17 are defined with respect to the respective pivot axis 5.
  • a first mass moment of inertia l1 of the first tamping tool 14 about the assigned pivot axis 5 and a second mass moment of inertia l2 of the second tamping tool 17 about the assigned pivot axis 5 must be observed for a dynamic balance of a single unit module 30, 31 of the tamping unit 1.
  • Fig. 3 shows a course of the connecting lines 22, 27 in a combined tamping unit 1 from Fig. 2 .
  • a first hydraulic connection line 22 which is connected on the cylinder side to the first auxiliary cylinders 9 and the second auxiliary cylinders 15.
  • the second connecting line 27 connects the first auxiliary cylinders 9 to the second auxiliary cylinders 15 on the respective piston side.
  • Both first auxiliary cylinders 9 are either connected to a common eccentric drive 11 ( Fig. 4 ) or to its own eccentric drive 11 ( Fig. 2 ) connected.

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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)

Description

Gebiet der TechnikField of technology

Die Erfindung betrifft ein Stopfaggregat zum Unterstopfen von Schwellen eines Gleises, umfassend gegenüberliegende Stopfwerkzeuge, welche jeweils mit einem Beistellzylinder zur Erzeugung einer Beistellbewegung verbunden sind, wobei ein Exzenterantrieb zur Erzeugung einer Vibrationsbewegung vorgesehen ist.The invention relates to a tamping unit for tamping under sleepers of a track, comprising opposing tamping tools which are each connected to an auxiliary cylinder for generating a auxiliary movement, an eccentric drive being provided for generating a vibratory movement.

Stand der TechnikState of the art

Stopfaggregate zum Unterstopfen von Schwellen eines Gleises sind bereits mehrfach bekannt, wie z.B. durch AT 350 097 B . Als Vibrationserreger dient eine rotierbare Exzenterwelle, an der die Beistellantriebe zur Übertragung der Schwingungen auf die Stopfwerkzeuge angelenkt sind. Der Vorteil beim Vibrationsantrieb mit einem Exzenter liegt in der Energiebilanz des Gesamtsystems. Es wird nur so viel Energie zugeführt, wie am Stopfpickel abgenommen wird, bzw. was durch Reibung im System verloren geht. Die Energiespeicherung am Exzenter erfolgt in einer Schwungscheibe bzw. Schwungmasse, die beim Abbremsen des Stopfpickels Energie aufnimmt und beim Beschleunigen des Stopfpickels wieder in das dynamische System zurückgibt (Kinetische Energie).Tamping units for tamping under sleepers of a track are already known several times, for example through AT 350 097 B . A rotatable eccentric shaft serves as a vibration exciter, to which the auxiliary drives are linked to transmit the vibrations to the tamping tools. The advantage of the vibration drive with an eccentric lies in the energy balance of the overall system. Only as much energy is supplied as is taken off at the tamping tine, or what is lost through friction in the system. The energy storage at the eccentric takes place in a flywheel or flywheel, which absorbs energy when the tamping ax is braked and returns it to the dynamic system when the tamping ax is accelerated (kinetic energy).

Bei einem beispielsweise aus der EP 1 653 003 A2 bekannten hydraulischen Vibrationsantrieb wird ein großer Anteil der hydraulischen Energie für die Erzeugung der Vibrationen benötigt. Dieser Nachteil gegenüber einem Vibrationsantrieb mit Exzenter überlagert die möglichen Vorteile wie eine einfachere Ansteuerung oder eine kompaktere Bauweise.For example, from the EP 1 653 003 A2 known hydraulic vibration drive, a large proportion of the hydraulic energy is required to generate the vibrations. This disadvantage compared to a vibration drive with an eccentric superimposes the possible advantages such as a simpler control or a more compact design.

Die GB 797 044 A zeigt ein Stopfaggregat gemäß dem Oberbegriff des Anspruchs 1.The GB 797 044 A shows a tamping unit according to the preamble of claim 1.

Zusammenfassung der ErfindungSummary of the invention

Der Erfindung liegt die Aufgabe zugrunde, für ein Stopfaggregat der eingangs genannten Art eine Verbesserung gegenüber dem Stand der Technik anzugeben. Die Aufgabe der Erfindung besteht insbesondere darin, eine kompakte Bauweise für Stopfaggregate zu schaffen.The invention is based on the object of an improvement over the prior art for a tamping unit of the type mentioned Specify technique. The object of the invention is in particular to create a compact design for tamping units.

Erfindungsgemäß wird diese Aufgabe durch ein Stopfaggregat gemäß Anspruch 1 gelöst. Abhängige Ansprüche betreffen vorteilhafte Ausgestaltungen der Erfindung.According to the invention, this object is achieved by a tamping unit according to claim 1. The dependent claims relate to advantageous embodiments of the invention.

Die Erfindung sieht vor, dass ein erster Beistellzylinder mit dem Exzenterantrieb mechanisch verbunden ist und dass eine erste Druckkammer des ersten Beistellzylinders mit einer zweiten Druckkammer eines zweiten Beistellzylinders über eine Verbindungsleitung hydraulisch verbunden ist, um eine in der ersten Druckkammer mittels Exzenterantrieb erzeugte Druckänderung auf die zweite Druckkammer zu übertragen.The invention provides that a first auxiliary cylinder is mechanically connected to the eccentric drive and that a first pressure chamber of the first auxiliary cylinder is hydraulically connected to a second pressure chamber of a second auxiliary cylinder via a connecting line in order to transfer a pressure change generated in the first pressure chamber by means of an eccentric drive to the second Transfer pressure chamber.

Der wesentliche Vorteil besteht hier in der Energiebilanz des Gesamtsystems, weil die Speicherwirkung des Exzenterantriebs genutzt wird. Damit verbinden sich die Vorteile des Exzenterantriebs mit dem Vorteil einer kompakten Bauweise, weil ein Beistellzylinder unabhängig vom Exzenterantrieb anordenbar ist.The main advantage here is the energy balance of the overall system, because the storage effect of the eccentric drive is used. This combines the advantages of the eccentric drive with the advantage of a compact design because an auxiliary cylinder can be arranged independently of the eccentric drive.

Eine vorteilhafte Weiterbildung der Erfindung sieht vor, dass ein annähernd gleiches Kraftübertragungsverhältnis vom jeweiligen Beistellzylinder auf das zugeordnete Stopfwerkzeug gegeben ist und dass die beiden Beistellzylinder gegengleich angesteuert sind. Auf diese Weise hat jede Masse eine Gegenmasse, die sich entgegengesetzt bewegt. Der damit erreichte statische Massenausgleich minimiert Vibrationen und Schallemissionen. Dadurch entstehen ein angenehmeres Arbeitsumfeld für den Arbeiter, sowie ein geräuscharmer Einsatz des Stopfaggregates in Wohngebieten.An advantageous further development of the invention provides that there is an approximately identical force transmission ratio from the respective auxiliary cylinder to the associated tamping tool and that the two auxiliary cylinders are driven in opposite directions. In this way each mass has a counter mass that moves in opposite directions. The static mass balance achieved in this way minimizes vibrations and noise emissions. This creates a more pleasant working environment for the worker, as well as low-noise use of the tamping unit in residential areas.

Günstig ist es zudem, wenn beide Beistellzylinder annähernd horizontal ausgerichtet sind, wenn das dem ersten Beistellzylinder zugeordnete Stopfwerkzeug bezüglich einer Schwenkachse ein erstes Massenträgheitsmoment aufweist, wenn das dem zweiten Beistellzylinder zugeordnete Stopfwerkzeug bezüglich einer Schwenkachse ein zweites Massenträgheitsmoment aufweist und wenn beide Massenträgheitsmomente aufeinander abgestimmt sind. Auf diese Weise ist ein dynamischer Massenausgleich sichergestellt, wodurch die sich über eine Aggregataufhängung auf eine Stopfmaschine übertragende Vibration minimiert ist.It is also advantageous if both auxiliary cylinders are aligned approximately horizontally, if the tamping tool assigned to the first auxiliary cylinder has a first mass moment of inertia with respect to a pivot axis, if the tamping tool assigned to the second auxiliary cylinder has a second mass moment of inertia with respect to a pivot axis and if both mass moments of inertia are coordinated with one another. In this way a dynamic mass balancing is ensured, whereby the over a Unit suspension on a tamping machine transmitting vibration is minimized.

Eine weitere vorteilhafte Ausbildung der Erfindung ist dadurch gegeben, dass das Stopfaggregat aus mehreren einzelnen Aggregat-Modulen zu einem Mehrschwellen-Aggregat zusammengesetzt ist. Durch die Kompaktheit der einzelnen Aggregat-Module können diese kostengünstig zu Mehrschwellen-Aggregaten kombiniert werden. Dies schlägt sich sowohl in der Produktion als auch in der Wartung der einzelnen Module positiv nieder. Dabei ist jedes Aggregat-Modul voreilhafterweise baugleich mit einem eigenen Exzenterantrieb ausgeführt.A further advantageous embodiment of the invention is given by the fact that the tamping unit is composed of several individual unit modules to form a multi-sleeper unit. Due to the compactness of the individual aggregate modules, they can be combined cost-effectively to multi-sleeper aggregates. This has a positive effect on both production and maintenance of the individual modules. In this case, each unit module is advantageously designed to be identical in construction with its own eccentric drive.

Bei zwei nebeneinander angeordneten Aggregat-Modulen kann es auch sinnvoll sein, wenn zwei erste Beistellzylinder mit einem gemeinsamen Exzenterantrieb mechanisch verbunden sind und wenn jeder erste Beistellzylinder mit einem zweiten Beistellzylinder hydraulisch verbunden ist.In the case of two assembly modules arranged next to one another, it can also be useful if two first auxiliary cylinders are mechanically connected to a common eccentric drive and if each first auxiliary cylinder is hydraulically connected to a second auxiliary cylinder.

Eine besonders vorteilhafte Ausbildung sieht vor, dass die Verbindungsleitung über eine Druckblende an ein Hydrauliksystem angeschlossen ist. Über diese Druckblende wird die Beistellkraft und Vibration der Beistellzylinder eingestellt.A particularly advantageous embodiment provides that the connecting line is connected to a hydraulic system via a pressure screen. The adjustment force and vibration of the adjustment cylinders are set via this pressure panel.

Eine weitere sinnvolle Weiterbildung ist dadurch verwirklicht, dass sich eine Amplitude einer Exzenterwelle gleichförmig auf die beiden Beistellzylinder aufteilt. Anstatt mit zwei einzelnen Exzentern jeweils einen Beistellzylinder anzusteuern, kann eine doppelt so groß ausgeführte Exzenterwelle für beide Beistellzylinder verwendet werden.Another useful development is achieved in that an amplitude of an eccentric shaft is distributed uniformly between the two auxiliary cylinders. Instead of controlling one additional cylinder with two individual eccentrics, an eccentric shaft that is twice as large can be used for both additional cylinders.

Weitere Vorteile der Erfindung ergeben sich aus der Zeichnungsbeschreibung.Further advantages of the invention emerge from the description of the drawings.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die Erfindung wird nachfolgend in beispielhafter Weise unter Bezugnahme auf die beigefügten Figuren erläutert. Es zeigen:

  • Fig. 1 ein vereinfacht dargestelltes Stopfaggregat,
  • Fig. 2 eine Stopfaggregat in Modulbauweise,
  • Fig. 3 einen Verlauf der hydraulischen Verbindungsleitungen und
  • Fig. 4 ein Stopfaggregat in Modulbauweise mit gemeinsamen Exzenterantrieb.
The invention is explained below by way of example with reference to the accompanying figures. Show it:
  • Fig. 1 a simplified tamping unit,
  • Fig. 2 a tamping unit in modular design,
  • Fig. 3 a course of the hydraulic connecting lines and
  • Fig. 4 a tamping unit in modular design with a common eccentric drive.

Beschreibung der AusführungsformenDescription of the embodiments

Ein in Fig. 1 vereinfacht dargestelltes Stopfaggregat 1 zum Unterstopfen einer Schotterbettung 2 unterhalb von Schwellen 3 eines Gleises 4 weist Paare von zwei gegenüberliegenden, um eine jeweilige Schwenkachse 5 schwenkbare Stopfwerkzeugen 14, 17 auf. Konkret ist als jeweiliges Stopfwerkzeug 14, 17 ein Stopfpickel 6 mit einem Pickelarm 8 auf einem Werkzeugträger 7 gelagert und mit einem Beistellzylinder 9, 15 verbunden.An in Fig. 1 Simplified tamping unit 1 for tamping under a ballast bed 2 below sleepers 3 of a track 4 has pairs of two opposite tamping tools 14, 17 pivotable about a respective pivot axis 5. Specifically, as the respective tamping tool 14, 17, a tamping pick 6 with a pick arm 8 is mounted on a tool carrier 7 and is connected to an auxiliary cylinder 9, 15.

Ein erster Beistellzylinder 9 ist an einem zylinderseitigen Ende 10 mit einem als Exzenterantrieb 11 mit einer rotierenden Exzenterwelle 12 ausgeführten Schwingungsantrieb und an einem kolbenseitigen Ende 13 mit einem ersten Stopfwerkzeug 14 verbunden. Ein zweiter Beistellzylinder 15 ist auf einer Drehachse 16 drehbar auf dem Werkzeugträger 7 gelagert und mit seinem kolbenseitigen Ende 13 mit einem zweiten Stopfwerkzeug 17 verbunden.A first auxiliary cylinder 9 is connected at a cylinder-side end 10 to a vibration drive designed as an eccentric drive 11 with a rotating eccentric shaft 12, and at a piston-side end 13 to a first tamping tool 14. A second auxiliary cylinder 15 is rotatably mounted on a rotation axis 16 on the tool carrier 7 and is connected with its piston-side end 13 to a second tamping tool 17.

Der erste Beistellzylinder 9 weist eine erste Druckkammer 18 und eine dritte Druckkammer 19 auf. Der zweite Beistellzylinder 15 weist eine zweite Druckkammer 20 und eine vierte Druckkammer 21 auf. Die erste Druckkammer 18 des ersten Beistellzylinders 9 ist mit der zweiten Druckkammer 20 des zweiten Beistellzylinders 15 über eine erste Verbindungsleitung 22 hydraulisch verbunden, um einen Teil der mittels des Exzenterantriebs 11 erzeugten Schwingung auf den zweiten Beistellzylinder 15 zu übertragen.The first auxiliary cylinder 9 has a first pressure chamber 18 and a third pressure chamber 19. The second auxiliary cylinder 15 has a second pressure chamber 20 and a fourth pressure chamber 21. The first pressure chamber 18 of the first auxiliary cylinder 9 is hydraulically connected to the second pressure chamber 20 of the second auxiliary cylinder 15 via a first connecting line 22 in order to transmit part of the vibration generated by the eccentric drive 11 to the second auxiliary cylinder 15.

Angeschlossen sind der erste und der zweite Beistellzylinder 9, 15 an eine Konstantdruckversorgung 23 eines Hydrauliksystem. Über ein Servoventil oder ein Proportionalventil 24 ist die erste Verbindungsleitung 22 mit der Konstantdruckversorgung 23 und einem Tank 25 verbunden. Damit wird ein Beistelldruck in der ersten Druckkammer 18 des ersten Beistellzylinders 9 und in der zweiten Druckkammer 20 des zweiten Beistellzylinders 15 geregelt.The first and second auxiliary cylinders 9, 15 are connected to a constant pressure supply 23 of a hydraulic system. The first connecting line 22 is connected to the constant pressure supply 23 and a tank 25 via a servo valve or a proportional valve 24. A standby pressure in the first pressure chamber 18 of the first auxiliary cylinder 9 and in the second pressure chamber 20 of the second auxiliary cylinder 15 is thus regulated.

In der ersten Druckkammer 18 des ersten Beistellzylinders 9 wird der Beistelldruck überlagert von einem mittels des Exzenterantriebs erzeugten oszillierenden Druck. Über die erste Verbindungsleitung 22 teilt sich dieser oszillierende Druck auf die beiden Beistellzylinder 9, 15 auf. Dabei oszilliert Hydraulikflüssigkeit zwischen der ersten Druckkammer 18 und der zweiten Druckkammer 20 hin und her, wodurch auch eine Kolbenstange 29 des zweiten Beistellzylinders 15 in Vibration versetzt wird. Über eine erste Druckblende 26 wird ein Abfluss in Richtung Proportionalventil 24 verhindert.In the first pressure chamber 18 of the first auxiliary cylinder 9, the auxiliary pressure is superimposed by a pressure generated by means of the eccentric drive oscillating pressure. This oscillating pressure is divided between the two auxiliary cylinders 9, 15 via the first connecting line 22. Hydraulic fluid oscillates back and forth between the first pressure chamber 18 and the second pressure chamber 20, which also causes a piston rod 29 of the second auxiliary cylinder 15 to vibrate. An outflow in the direction of the proportional valve 24 is prevented via a first pressure screen 26.

Die dritte Druckkammer 19 des ersten Beistellzylinders 9 ist über eine zweite Verbindungsleitung 27 mit der vierten Druckkammer 21 des zweiten Beistellzylinders 15 hydraulisch verbunden. Über diese zweite Verbindungsleitung 27 erfolgt ein Volumenausgleich, der durch die Volumenzunahme in der ersten und zweiten Druckkammer 18, 20 während eines Beistellvorgangs sowie der überlagerten Oszillation der Hydraulikflüssigkeit notwendig ist.The third pressure chamber 19 of the first auxiliary cylinder 9 is hydraulically connected to the fourth pressure chamber 21 of the second auxiliary cylinder 15 via a second connecting line 27. Volume compensation takes place via this second connecting line 27, which is necessary due to the increase in volume in the first and second pressure chambers 18, 20 during a provision process and the superimposed oscillation of the hydraulic fluid.

Die zweite Verbindungsleitung 27 ist ebenfalls mit der Konstantdruckversorgung 23 verbunden und weist eine zweite Druckblende 28 zur Druckregulierung auf. Wenn die Kolbenstangen 29 der Beistellzylinder 9, 15 während eines Bestellvorgangs nach außen gedrückt und die Stopfwerkzeuge 6 beigestellt werden, entsteht in der dritten Druckkammer 19 und in der vierten Druckkammer 21 zwangsweise eine Volumenverkleinerung und die Hydraulikflüssigkeit wird über die zweite Druckblende 28 abgeleitet.The second connecting line 27 is also connected to the constant pressure supply 23 and has a second pressure orifice 28 for pressure regulation. If the piston rods 29 of the auxiliary cylinders 9, 15 are pressed outwards during an ordering process and the stuffing tools 6 are provided, a volume reduction inevitably occurs in the third pressure chamber 19 and in the fourth pressure chamber 21 and the hydraulic fluid is discharged via the second pressure orifice 28.

Durch die aufeinander abgestimmte Dimensionierung der beiden Beistellzylinder 9, 15 wird eine gleich große Beistellkraft sowie eine gleichförmige und symmetrische Vibration der Stopfwerkzeuge 6 erzeugt. Die aus der rotierenden Exzenterwelle 12 resultierende Amplitude des Exzenterantriebs 11 ist dabei doppelt so hoch ausgeführt wie bei herkömmlichen Exzenteraggregaten, da sich diese Gesamtamplitude auf beide Beistellzylinder 9, 15 aufteilt.Due to the mutually coordinated dimensions of the two auxiliary cylinders 9, 15, an equally large auxiliary force and uniform and symmetrical vibration of the tamping tools 6 are generated. The amplitude of the eccentric drive 11 resulting from the rotating eccentric shaft 12 is twice as high as in the case of conventional eccentric assemblies, since this total amplitude is divided between the two auxiliary cylinders 9, 15.

Fig. 2 zeigt eine weitere Ausführungsvariante des Stopfaggregats 1 zum gleichzeitigen Unterstopfen von zwei Schwellen 3 des Gleises 4. Dazu werden ein erstes Aggregat-Modul 30 und ein zweites Aggregat-Modul 31 zu einem Zweischwellen-Stopfaggregat kombiniert. Die Stopfwerkzeuge 14, 17 können dabei in einer Gleisquerrichtung zueinander versetzt werden um eine gegenseitige Kollision zu vermeiden. Fig. 2 shows a further embodiment of the tamping unit 1 for tamping two sleepers 3 of the track 4 at the same time. For this purpose, a first unit module 30 and a second unit module 31 are combined to form a two-sleeper tamping unit. The tamping tools 14, 17 can be offset from one another in a transverse track direction in order to avoid a mutual collision.

Anhand Fig. 2 wird eine bevorzugte Dimensionierung des erfindungsgemäßen Stopfaggregats erläutert. ,Dazu sind bezüglich der jeweiligen Schwenkachse 5 Radien r1, r2 eines oberen Schwenkhebels und eines unteren Schwenkhebels des ersten Stopfwerkzeugs 14 und Radien r3, r4 eines oberen Schwenkhebels und eines unteren Schwenkhebels des zweiten Stopfwerkzeugs 17 definiert.Based Fig. 2 a preferred dimensioning of the tamping unit according to the invention is explained. For this purpose, radii r 1 , r 2 of an upper pivot lever and a lower pivot lever of the first tamping tool 14 and radii r 3 , r 4 of an upper pivot lever and a lower pivot lever of the second tamping tool 17 are defined with respect to the respective pivot axis 5.

Für eine statische Ausgeglichenheit sollen diese Radien r1, r2, r3, r4 in folgendem Verhältnis zueinander stehen: r 1 / r 2 = r 3 / r 4

Figure imgb0001
Dann wirken bei gleich dimensionierten Beistellzylindern 9, 15 gleiche Beistellkräfte auf die zu verdichtende Schotterbettung 2.For a static balance, these radii r 1 , r 2 , r 3 , r 4 should be in the following ratio: r 1 / r 2 = r 3 / r 4th
Figure imgb0001
 Then, with the auxiliary cylinders 9, 15 of the same size, the same auxiliary forces act on the ballast bed 2 to be compacted.

Für eine dynamische Ausgeglichenheit eines einzelnen Aggregat-Moduls 30, 31 des Stopfaggregates 1 sind ein erstes Massenträgheitsmoment l1 des ersten Stopfwerkzeuges 14 um die zugeordnet Schwenkachse 5 und ein zweites Massenträgheitsmoment l2 des zweiten Stopfwerkzeuges 17 um die zugeordnete Schwenkachse 5 zu beachten.A first mass moment of inertia l1 of the first tamping tool 14 about the assigned pivot axis 5 and a second mass moment of inertia l2 of the second tamping tool 17 about the assigned pivot axis 5 must be observed for a dynamic balance of a single unit module 30, 31 of the tamping unit 1.

Für ein dynamisches Gleichgewicht zwischen den beiden Stopfwerkzeugen 6 muss folgende Bedingung eigehalten werden: r 1 / l 2 = r 3 / l 4

Figure imgb0002
Durch die annähernd horizontale Anordnung der Beistellzylinder 9, 15 gleichen sich damit alle Trägheitskräfte aus.For a dynamic equilibrium between the two tamping tools 6, the following condition must be met: r 1 / l 2 = r 3 / l 4th
Figure imgb0002
 Due to the almost horizontal arrangement of the auxiliary cylinders 9, 15, all inertial forces are thus balanced.

Fig. 3 zeigt einen Verlauf der Verbindungsleitungen 22, 27 bei einem kombinierten Stopfaggregat 1 aus Fig. 2. Hierzu gibt es wie in Fig. 1 eine erste hydraulische Verbindungsleitung 22, die jeweils zylinderseitig mit den ersten Beistellzylindern 9 und den zweiten Beistellzylindern 15 verbunden ist. Die zweite Verbindungsleitung 27 verbindet jeweils kolbenseitig die ersten Beistellzylinder 9 mit den zweiten Beistellzylindern 15. Fig. 3 shows a course of the connecting lines 22, 27 in a combined tamping unit 1 from Fig. 2 . As in Fig. 1 a first hydraulic connection line 22, which is connected on the cylinder side to the first auxiliary cylinders 9 and the second auxiliary cylinders 15. The second connecting line 27 connects the first auxiliary cylinders 9 to the second auxiliary cylinders 15 on the respective piston side.

Beide erste Beistellzylinder 9 sind dabei entweder an einen gemeinsamen Exzenterantrieb 11 (Fig.4) oder jeweils an einen eigenen Exzenterantrieb 11 (Fig.2) angeschlossen.Both first auxiliary cylinders 9 are either connected to a common eccentric drive 11 ( Fig. 4 ) or to its own eccentric drive 11 ( Fig. 2 ) connected.

Claims (7)

  1. A tamping unit (1) for tamping sleepers (3) of a track (4), comprising oppositely positioned tamping tools (14, 17) which are connected in each case to a squeezing cylinder (9, 15) for generating a squeezing motion, wherein an eccentric drive (11) is provided for generating a vibratory motion, characterized in that a first (9) of the squeezing cylinders (9, 15) is connected mechanically to the eccentric drive (11), and that a first pressure chamber (18) of the first squeezing cylinder (9) is connected hydraulically via a connecting line (22, 27) to a second pressure chamber (20) of a second (15) of the squeezing cylinders (9, 15) in order to transmit a pressure change, generated in the first pressure chamber (18) by means of the eccentric drive (11), to the second pressure chamber (20).
  2. A tamping unit (1) according to claim 1, characterized in that an approximately equal relationship of force transmission from the respective squeezing cylinder to the associated tamping tool (6) exists, and that the two squeezing cylinders are controlled in a diametrically opposed manner.
  3. A tamping unit (1) according to claim 1 or 2, characterized in that both squeezing cylinders (9, 15) are oriented approximately horizontally, that the tamping tool associated with the first squeezing cylinder (9) has a first mass moment of inertia with respect to a pivot axis, that the tamping tool associated with the second squeezing cylinder has a second mass moment of inertia with respect to a pivot axis, and that both mass moments of inertia are coordinated with one another.
  4. A tamping unit (1) according to one of claims 1 or 3, characterized in that the tamping unit (1) is composed of several individual unit modules (30, 31) to form a multi-sleeper unit.
  5. A tamping unit (1) according to claim 4, characterized in that two first squeezing cylinders (9) of unit modules (30, 31) arranged side by side are connected mechanically to a common eccentric drive (11), and that each first squeezing cylinder (9) is connected hydraulically to a second squeezing cylinder (15).
  6. A tamping unit (1) according to one of claims 1 or 3, characterized in that the connecting line (22, 27) is connected via a pressure diaphragm (26, 28) to a hydraulic system.
  7. A tamping unit (1) according to one of claims 1 or 4, characterized in that an amplitude of an eccentric shaft (12) is split evenly between the both squeezing cylinders (9, 15).
EP17793570.7A 2016-11-25 2017-10-30 Tamping unit for tamping sleepers of a track Active EP3545134B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA533/2016A AT519219B1 (en) 2016-11-25 2016-11-25 Stopfaggregat for clogging thresholds of a track
PCT/EP2017/001266 WO2018095558A1 (en) 2016-11-25 2017-10-30 Tamping unit for tamping sleepers of a track

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EP3545134B1 true EP3545134B1 (en) 2020-09-16

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US (1) US11053644B2 (en)
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CN (1) CN109983179B (en)
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AT518195B1 (en) * 2016-01-26 2017-11-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Method for compacting the ballast bed of a track and tamping unit
AT519219B1 (en) * 2016-11-25 2018-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat for clogging thresholds of a track
CN112160199A (en) * 2020-10-21 2021-01-01 中国铁建高新装备股份有限公司 Tamping device and tamping vehicle
CN113695215B (en) * 2021-09-20 2022-11-11 江西理工大学 Amplitude adjusting device and method

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CN109983179B (en) 2021-05-04
AT519219B1 (en) 2018-05-15
AT519219A4 (en) 2018-05-15
US20190271119A1 (en) 2019-09-05
WO2018095558A1 (en) 2018-05-31
ES2827829T3 (en) 2021-05-24
EA038406B1 (en) 2021-08-24
US11053644B2 (en) 2021-07-06
EP3545134A1 (en) 2019-10-02
CN109983179A (en) 2019-07-05
EA201900149A1 (en) 2019-10-31

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