EP3377699B1 - Tamping unit and method for tamping a track - Google Patents
Tamping unit and method for tamping a track Download PDFInfo
- Publication number
- EP3377699B1 EP3377699B1 EP16788021.0A EP16788021A EP3377699B1 EP 3377699 B1 EP3377699 B1 EP 3377699B1 EP 16788021 A EP16788021 A EP 16788021A EP 3377699 B1 EP3377699 B1 EP 3377699B1
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- EP
- European Patent Office
- Prior art keywords
- shaft
- tamping
- eccentric
- tamping unit
- vibration
- Prior art date
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- 238000000034 method Methods 0.000 title claims description 17
- 230000033001 locomotion Effects 0.000 claims description 26
- 230000005540 biological transmission Effects 0.000 claims description 14
- 238000007654 immersion Methods 0.000 claims description 3
- 230000008569 process Effects 0.000 description 6
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 206010000496 acne Diseases 0.000 description 1
- 238000005056 compaction Methods 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011946 reduction process Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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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
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- B06B1/162—Making use of masses with adjustable amount of eccentricity
-
- 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
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- B06B1/162—Making use of masses with adjustable amount of eccentricity
- B06B1/164—Making use of masses with adjustable amount of eccentricity the amount of eccentricity being automatically variable as a function of the running condition, e.g. speed, direction
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
- B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
- B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
- B07B1/42—Drive mechanisms, regulating or controlling devices, or balancing devices, specially adapted for screens
- B07B1/44—Balancing devices
-
- 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
- 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
- E01B27/20—Compacting the material of the track-carrying ballastway, e.g. by vibrating the track, by surface vibrators
-
- 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
-
- 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
- E01B2203/127—Tamping devices vibrating the track surface
Definitions
- the invention relates to a tamping unit for tamping a track, with tamping picks which can be immersed in a ballast bed and which can be set into vibration by means of a vibration drive, the vibration drive comprising a housing in which a shaft with an eccentric is arranged so as to be rotatable about a shaft axis and on which Eccentric a transmission element for transmitting a vibration movement is mounted.
- the invention relates to a method for tamping a track by means of the tamping unit, the vibration movement generated being transmitted to a pick arm via an auxiliary cylinder.
- the vibration drive Due to the high loads to which a tamping unit is exposed, the vibration drive must meet special requirements. When immersing the tamping pick in a ballast bed of a track and then compacting the ballast below a threshold, load changes occur that stress the vibration drive. In particular when tamping a non-renewed ballast bed, which is often completely encrusted, high opposing forces act on the tamping pick set in motion by means of a vibration drive. Even in such difficult operating conditions, the vibration drive must maintain the required vibration of the tamping picks with an approximately constant vibration amplitude in order to ensure a constant tamping quality.
- a hydraulic linear drive enables simple adjustment of the vibration parameters through to a rapid sequence of switch-on and switch-off processes. The latter is more difficult to implement in a known vibration drive with an eccentric axis due to the inertia of the masses in rotation.
- the invention has for its object to provide an improvement over the prior art for a vibration drive of the type mentioned. Another task is to specify a corresponding method for stuffing a track.
- the eccentric is rotationally and radially displaceably connected to the shaft, the position of the eccentric relative to the shaft being adjustable in the radial direction by means of an adjusting device.
- a torque is transmitted by means of the shaft to the eccentric designed as a separate component.
- the effect on the transmission element is determined by an adjustable center distance between an eccentric axis and the shaft axis.
- the amplitude of the vibration movement which can be transmitted by means of the transmission element is infinitely adjustable. While maintaining the advantages of an eccentric drive, the possibility is created to adjust vibration parameters during operation.
- a changed distance between the eccentric axis and the shaft axis not only leads to a changed vibration amplitude, but with constant torque also to a changed impact force, which is applied by means of the vibration drive.
- the transmission element is designed as a connecting rod for transmitting an oscillating vibration movement.
- the connecting rod can then be connected to a linearly guided piston, by means of which the vibration can be transferred to several components.
- the shaft has two opposite, mutually parallel flats on a lateral surface, by means of which the eccentric is guided radially.
- the flattened areas form a positive connection together with correspondingly designed counter surfaces of the eccentric, in order to reliably transmit a torque.
- the adjusting device comprises at least one hydraulic cylinder with a piston, wherein an adjusting force can be exerted on the eccentric by means of the piston. This means that an often already existing hydraulic system can be used to adjust the eccentric relative to the shaft.
- the hydraulic cylinder is advantageously arranged in the shaft. This cylinder is connected to a hydraulic line in the shaft, so that the adjustment device is compact and weight-saving.
- the hydraulic cylinder is advantageously controlled by means of a pilot-operated check valve. This ensures that the cylinder remains fixed in its position after an adjustment process even if high opposing forces act on the eccentric.
- the adjusting device comprises a further cylinder with a piston for fixing and / or for resetting the eccentric.
- the eccentric is thus clamped in position between two pistons, which provides a particularly robust fixation.
- the second piston is also advantageously controlled by means of a pilot-operated check valve.
- the vibration drive of the tamping unit can be automatically adapted to changed conditions during operation.
- the vibration drive comprises a sensor for detecting an instantaneous center distance between the shaft axis and an eccentric axis. In this way it can be checked whether a specified center distance has actually been set or is maintained during operation. Faults can thus be recognized immediately.
- the vibration drive comprises a sensor for detecting an angular position and / or angular velocity of the shaft. This creates the possibility to determine an actual rotational speed of the shaft at any time and, for example, to give the vibration drive a preferred start or end position.
- several vibratory drives can be operated synchronized in this way.
- a simple drive variant provides that the shaft is connected to a variable hydraulic motor.
- a simple adjustment of a vibration frequency is possible by changing the speed of the shaft.
- the shaft is coupled to a flywheel.
- the flywheel serves as a buffer to compensate for these energy fluctuations.
- the vibration movement generated is transmitted to the respective tamping pick via an auxiliary cylinder and a pick arm, the vibration movement being changed by adjusting the eccentric in relation to the shaft in the radial direction by means of the adjusting device. Specifically, the vibration amplitude is adjusted during operation.
- a tamping cycle is formed from a plurality of phases running in succession and that, by means of a control and / or regulation, at least in one phase a different axis distance between the shaft axis and an eccentric axis is set in relation to another phase.
- Individual phases of the tamping cycle include, for example, lowering the tamping unit, providing the tamping pick, raising the tamping unit and repositioning the tamping unit. Due to the adjustability, the vibration drive is optimally used for the respective phase.
- an axis distance equal to zero is set at least in one phase of the stuffing cycle in order to suspend the vibration for a desired duration regardless of the speed of the shaft. This is particularly useful during repositioning of the tamping unit between two tamping processes to reduce noise and reduce the power consumption of the vibration drive.
- the shaft is driven at different speeds during a stuffing cycle.
- the vibration frequency can be adapted to different requirements during a stuffing cycle. For example, a higher rotational speed is specified during an immersion process because the immersion resistance of a ballast bed is reduced with a higher vibration frequency.
- the illustrated tamping unit 1 comprises an adjustable vibratory drive 2 in order to set two opposing tamping pick 3 or tamping pick groups in vibration.
- Each tamping pick 3 is attached to a pick arm 4.
- the respective pick arm 4 is pivotally articulated on a lowerable tamping tool carrier 5 and connected to a piston rod of an associated auxiliary cylinder 6.
- the vibration drive 2, to which each pick arm 4 is connected via the associated auxiliary cylinder 6, is also fastened to the tamping tool carrier 5. A generated vibration is thus transmitted via the respective add-on cylinder 6 to the respective pick arm 4 and the tamping pick 3 attached to it.
- the vibration drive comprises a shaft 7, which is mounted in a housing 8 with sealed bushings. At least one further sealed bushing is provided for a transmission element 9 to which the auxiliary cylinders 6 of the tamping unit 1 are connected.
- the shaft 7 is advantageously mounted in the housing 8 by means of roller bearings. The components of the vibration drive 2 cause an oscillating vibration movement 10 during operation.
- the shaft 7 rotates about a shaft axis 11 and is rotationally connected to an eccentric 12.
- the Figures 3-6 show that an axis distance 15 can be set between an eccentric axis 13 and the shaft axis 11 by means of an adjusting device 14. If the center distance 15 is greater than zero, a rotational movement 16 of the shaft 7 and the eccentric 12 is transmitted into the vibratory movement 10 by means of the transmission element 9.
- the transmission element 9 is designed as a connecting rod, which is articulated with a linearly guided piston element 17 connected is. A pin 18 is provided for connecting the piston element 17 to the transmission element 9.
- Those components which are to be subjected to the vibration movement 10 can be connected to the piston element 17.
- the respective auxiliary cylinder is mounted directly on the eccentric with a suitable connection and itself functions as a transmission element 9 Fig. 2
- Oil-lubricated roller bearing 19 shown between the transmission element 9 and the eccentric 12 is in the Figures 3-6 not shown for the sake of clarity.
- the adjusting device 14 advantageously comprises a hydraulic cylinder 20 which is arranged in the shaft 7 and presses a piston 21 against an inner surface of the eccentric 12 seated on the shaft 7.
- the eccentric 12 can be adjusted relative to the shaft 7 by means of this pressure force.
- a further element of the adjusting device 14 generates a counterforce on an opposite inner surface of the eccentric 12. This is, for example, by means of a spring or - as in Fig. 3 shown - applied by means of a further piston 22 of a further cylinder 23.
- a mechanical adjustment device (not shown) can be used. This includes, for example, spindles or crankshafts guided in the shaft 7 in order to adjust the position of the eccentric 12 relative to the shaft 7.
- FIG. 4 show a simplified representation of two end positions of the adjustable eccentric 12.
- the center distance 15 between shaft axis 11 and eccentric axis 13 is zero.
- the rotational movement 16 of the shaft 7 and the eccentric 12 do not lead to any vibration movement here. This setting of the eccentric position thus serves to expose the vibration.
- a maximum center distance 15 between the shaft axis 11 and the eccentric axis 13 is set.
- the transmission element 9 designed as a connecting rod then transmits an oscillating vibration movement 10 with a vibration amplitude that corresponds to the maximum center distance 15.
- any value between zero and a maximum value can be set for the center distance 15.
- a reduced center distance 15 not only leads to a lower vibration amplitude, but also to a higher impact force of the vibration drive 2. This is advantageous for the operation of the tamping unit 1 in order to adapt the effect of the respective vibrating tamping pick 3 to a ballast bed if necessary ,
- the eccentric 12 is not seated on the shaft 7, but is connected to the shaft 7 in a rotationally locking and radially adjustable manner via the adjusting device 14.
- the free ends of the pistons 21, 22 are pushed into a respective longitudinal groove on an inner surface of the eccentric 12 and fixed in the longitudinal direction by means of fastening means 24.
- the pistons 21, 22 serve on the one hand for adjustment in the radial direction and on the other hand as elements of a rotationally locking connection between shaft 7 and eccentric 12.
- shaft 7 Shown shaft 7 according to the variant in Fig. 2 has two flats 25, by means of which the eccentric 12 is guided radially.
- two hydraulic cylinders 20, 23 are arranged in the shaft 7 as elements of the adjusting device 14.
- the pistons 21, 22 press against inner surfaces of the eccentric 12, as a result of which it is displaced radially to the shaft axis 11.
- the inner surfaces of the eccentric 12 slide along the flats 25 of the shaft 7.
- Each cylinder 20, 23 is connected to a respective pilot-operated check valve 26 via hydraulic lines arranged in the shaft 7.
- the check valves 26 are also advantageously arranged within the shaft 7 in order to ensure very short connecting lines between the pilot-operated check valves 26 and the cylinders 20, 23. This will respond quickly Adjustment device 14 allows. In addition, the compressible amount of fluid is minimized, so that the compressibility of a hydraulic fluid used is negligible.
- the use of two cylinders 20, 23 controlled by means of pilot-operated check valves 26 ensures that the eccentric 12 is securely fixed in its set position relative to the shaft 7.
- Supply lines and control lines of the adjusting device 14 are guided, for example, to the outside on an end face 27 of the shaft 7. These rotating lines are connected to a hydraulic system by means of a known rotary feedthrough.
- the vibration movement 10 can be adapted to individual phases of a stuffing cycle with the method according to the invention.
- the tamping tool carrier 5 is first lowered.
- the tamping picks 3 are immersed in a ballast bed of a track.
- the tamping ax 3 vibrate with a vibration frequency of up to 60 Hertz and in the vibration drive 2 the maximum center distance 15 between the shaft axis 11 and the eccentric axis 13 is set. The greatest possible vibration amplitude thus results at the free end of the respective tamping pick 3.
- the ballast is compacted below a threshold.
- the tamping picks 3 lying opposite in the track direction move towards one another with an additional movement, in that each additional cylinder 6 exerts a torque on the associated pimple arm 4.
- the additional movement is superimposed on the vibration movement 10 generated by the vibration drive 2.
- the vibration frequency is set to 35 Hertz in this phase.
- the impact force of the tamping pick 3 can be increased in this phase if necessary by slightly reducing the center distance 15 between the shaft axis 11 and the eccentric axis 13. Such a measure may be useful for a heavily encrusted ballast bed. Doing so the center distance 15 is only reduced to such an extent that the resulting reduction in the vibration amplitude remains negligible.
- the shaft 7 is additionally coupled to a flywheel in order to keep the angular velocity of the rotating masses constant over a period of oscillation, independently of a rotary drive.
- the power consumption of the vibration drive 2 according to the invention is thus significantly lower than that of a linear vibration drive, which generates a vibration, for example by means of a hydraulic cylinder.
- the tamping picks 3 are pulled out of the ballast bed by lifting the tamping tool carrier 5.
- the order cylinders 6 are also reset in this phase of the tamping cycle, the vibration is suspended until the tamping pick 3 has penetrated again by setting the center distance 15 between the shaft axis 11 and the eccentric axis 13 to zero.
- the vibration amplitude is reduced to zero, the vibration frequency remaining constant during this reduction process.
- the shaft 7 would have to be braked in order to suspend the vibration.
- the vibration drive 2 would inevitably run through low frequency ranges. Components of a tamping machine comprising tamping unit 1 or elements of the track section usually have low natural frequencies, so that undesirable resonances would occur.
- a cyclical braking and acceleration of the rotating masses would significantly increase the power consumption of the vibration drive 2.
- the adjusting device 14 is controlled by means of a control and / or a regulation.
- Various sensors can be attached to the tamping unit 1 in order to record vibration parameters such as frequency and amplitude in real time and to report them to the control system.
- a sensor for detecting the instantaneous center distance 15 between the shaft axis 11 and the eccentric axis 13 can be provided. A particularly precise setting of the center distance 15 can thus be achieved.
- the shaft 7 is driven by means of a hydraulic motor which uses the hydraulic system present in the tamping machine. This provides a sufficiently high torque and the speed is infinitely adjustable.
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- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Machines For Laying And Maintaining Railways (AREA)
- Road Paving Machines (AREA)
Description
Die Erfindung betrifft ein Stopfaggregat zum Stopfen eines Gleises, mit in ein Schotterbett eintauchbaren Stopfpickeln, die mittels eines Vibrationsantriebs in Vibration versetzbar sind, wobei der Vibrationsantrieb ein Gehäuse umfasst, in dem eine Welle mit einem Exzenter um eine Wellenachse drehbar angeordnet ist und wobei auf dem Exzenter ein Übertragungselement zur Übertragung einer Vibrationsbewegung gelagert ist. Zudem betrifft die Erfindung ein Verfahren zum Stopfen eines Gleises mittels des Stopfaggregats, wobei die erzeugte Vibrationsbewegung über einen Beistellzylinder auf einen Pickelarm übertragen wird.The invention relates to a tamping unit for tamping a track, with tamping picks which can be immersed in a ballast bed and which can be set into vibration by means of a vibration drive, the vibration drive comprising a housing in which a shaft with an eccentric is arranged so as to be rotatable about a shaft axis and on which Eccentric a transmission element for transmitting a vibration movement is mounted. In addition, the invention relates to a method for tamping a track by means of the tamping unit, the vibration movement generated being transmitted to a pick arm via an auxiliary cylinder.
Aufgrund der hohen Belastungen, denen ein Stopfaggregat ausgesetzt ist, muss der Vibrationsantrieb besondere Anforderungen erfüllen. Beim Eintauchen des Stopfpickels in ein Schotterbett eines Gleises und beim anschließenden Verdichten des Schotters unterhalb einer Schwelle treten laufend Lastwechsel auf, die den Vibrationsantrieb beanspruchen. Insbesondere bei der Stopfung eines nicht erneuerten Schotterbetts, das oftmals vollständig verkrustet ist, wirken auf den mittels Vibrationsantrieb in Schwingung versetzten Stopfpickel hohe Gegenkräfte. Auch bei derart schwierigen Einsatzbedingungen muss der Vibrationsantrieb die erforderliche Vibration der Stopfpickel mit einer annähernd konstanten Vibrationsamplitude aufrechterhalten, um eine gleichbleibende Stopfqualität sicherzustellen.Due to the high loads to which a tamping unit is exposed, the vibration drive must meet special requirements. When immersing the tamping pick in a ballast bed of a track and then compacting the ballast below a threshold, load changes occur that stress the vibration drive. In particular when tamping a non-renewed ballast bed, which is often completely encrusted, high opposing forces act on the tamping pick set in motion by means of a vibration drive. Even in such difficult operating conditions, the vibration drive must maintain the required vibration of the tamping picks with an approximately constant vibration amplitude in order to ensure a constant tamping quality.
Für den Einsatz in Stopfaggregaten hat sich deshalb ein aus der Patentschrift
Bei einer aus der
Der Erfindung liegt die Aufgabe zugrunde, für einen Vibrationsantrieb der eingangs genannten Art eine Verbesserung gegenüber dem Stand der Technik zu schaffen. Eine weitere Aufgabe besteht darin, ein entsprechendes Verfahren zum Stopfen eines Gleises anzugeben.The invention has for its object to provide an improvement over the prior art for a vibration drive of the type mentioned. Another task is to specify a corresponding method for stuffing a track.
Erfindungsgemäß werden diese Aufgaben gelöst durch einen Stopfaggregat gemäß Anspruch 1 und ein Verfahren gemäß Anspruch 12. Weiterbildungen finden sich in abhängigen Ansprüchen.According to the invention, these objects are achieved by a tamping unit according to
Dabei ist der Exzenter rotationsschlüssig und radial verschiebbar mit der Welle verbunden, wobei die Lage des Exzenters gegenüber der Welle in radialer Richtung mittels einer Verstelleinrichtung einstellbar ist. Im Betrieb wird mittels der Welle auf den als eigener Bauteil ausgebildeten Exzenter ein Drehmoment übertragen. Die Wirkung auf das Übertragungselement bestimmt dabei ein einstellbarer Achsabstand zwischen einer Exzenterachse und der Wellenachse. Konkret ist die Amplitude der mittels des Übertragungselements übertragbaren Vibrationsbewegung stufenlos einstellbar. Unter Beibehaltung der Vorteile eines Exzenterantriebs wird somit die Möglichkeit geschaffen, Vibrationsparameter während des Betriebs anzupassen. Ein veränderter Abstand zwischen Exzenterachse und Wellenachse führt dabei nicht nur zu einer veränderten Vibrationsamplitude, sondern bei gleichbleibendem Drehmoment auch zu einer veränderten Schlagkraft, die mittels des Vibrationsantriebs aufgebracht wird.The eccentric is rotationally and radially displaceably connected to the shaft, the position of the eccentric relative to the shaft being adjustable in the radial direction by means of an adjusting device. In operation, a torque is transmitted by means of the shaft to the eccentric designed as a separate component. The effect on the transmission element is determined by an adjustable center distance between an eccentric axis and the shaft axis. Specifically, the amplitude of the vibration movement which can be transmitted by means of the transmission element is infinitely adjustable. While maintaining the advantages of an eccentric drive, the possibility is created to adjust vibration parameters during operation. A changed distance between the eccentric axis and the shaft axis not only leads to a changed vibration amplitude, but with constant torque also to a changed impact force, which is applied by means of the vibration drive.
Eine vorteilhafte Weiterbildung der Erfindung sieht vor, dass das Übertragungselement als Pleuel zur Übertragung einer oszillierenden Vibrationsbewegung ausgebildet ist. Das Pleuel ist dann mit einem linear geführten Kolben verbindbar, mittels dem die Vibration auf mehrere Bauteile übertragbar ist.An advantageous development of the invention provides that the transmission element is designed as a connecting rod for transmitting an oscillating vibration movement. The connecting rod can then be connected to a linearly guided piston, by means of which the vibration can be transferred to several components.
In einer einfachen Ausprägung weist die Welle an einer Mantelfläche zwei gegenüberliegende, zueinander parallele Abflachungen auf, mittels derer der Exzenter radial geführt ist. In Rotationsrichtung bilden die Abflachungen gemeinsam mit entsprechend ausgeführten Gegenflächen des Exzenters eine formschlüssige Verbindung, um ein Drehmoment sicher zu übertragen.In a simple form, the shaft has two opposite, mutually parallel flats on a lateral surface, by means of which the eccentric is guided radially. In the direction of rotation, the flattened areas form a positive connection together with correspondingly designed counter surfaces of the eccentric, in order to reliably transmit a torque.
Weiters ist es vorteilhaft, wenn die Verstelleinrichtung zumindest einen hydraulischen Zylinder mit einem Kolben umfasst, wobei mittels des Kolbens eine Verstellkraft auf den Exzenter ausübbar ist. Damit ist ein oftmals bereits vorhandenes hydraulisches System nutzbar, um eine Verstellung des Exzenters gegenüber der Welle vorzunehmen.Furthermore, it is advantageous if the adjusting device comprises at least one hydraulic cylinder with a piston, wherein an adjusting force can be exerted on the eccentric by means of the piston. This means that an often already existing hydraulic system can be used to adjust the eccentric relative to the shaft.
Dabei ist günstigerweise der hydraulische Zylinder in der Welle angeordnet. Angeschlossen ist dieser Zylinder an eine in der Welle geführte hydraulische Leitung, sodass eine kompakte und gewichtsparende Ausführung der Verstelleinrichtung vorliegt.The hydraulic cylinder is advantageously arranged in the shaft. This cylinder is connected to a hydraulic line in the shaft, so that the adjustment device is compact and weight-saving.
Vorteilhafterweise ist der hydraulischen Zylinders mittels eines vorgesteuerten Rückschlagventils angesteuert. Damit ist sichergestellt, dass der Zylinder nach einem Verstellvorgang auch dann in seiner Position fixiert bleibt, wenn hohe Gegenkräfte auf den Exzenter einwirken.The hydraulic cylinder is advantageously controlled by means of a pilot-operated check valve. This ensures that the cylinder remains fixed in its position after an adjustment process even if high opposing forces act on the eccentric.
Eine Weiterbildung der Erfindung sieht vor, dass die Verstelleinrichtung einen weiteren Zylinder mit einem Kolben zur Fixierung und/oder zur Rückstellung des Exzenters umfasst. Der Exzenter ist somit in seiner Position zwischen zwei Kolben eingeklemmt, wodurch eine besonders robuste Fixierung gegeben ist. Auch der zweite Kolben ist dabei günstigerweise mittels eines vorgesteuerten Rückschlagventils angesteuert.A further development of the invention provides that the adjusting device comprises a further cylinder with a piston for fixing and / or for resetting the eccentric. The eccentric is thus clamped in position between two pistons, which provides a particularly robust fixation. The second piston is also advantageously controlled by means of a pilot-operated check valve.
Eine Verbesserung der Einsatzmöglichkeiten des Stopfaggregats ist gegeben, wenn die Verstelleinrichtung an eine Steuerung und/oder eine Regelung angeschlossen ist. Auf diese Weise ist der Vibrationsantrieb des Stopfaggregats während des Betriebs automatisch an geänderte Bedingungen anpassbar.There is an improvement in the possible uses of the tamping unit if the adjustment device is connected to a control and / or a Control is connected. In this way, the vibration drive of the tamping unit can be automatically adapted to changed conditions during operation.
Zum Generieren einer Rückmeldung nach einem Verstellvorgang ist es von Vorteil, wenn der Vibrationsantrieb einen Sensor zur Erfassung eines momentanen Achsabstands zwischen der Wellenachse und einer Exzenterachse umfasst. Auf diese Weise ist überprüfbar, ob ein vorgegebener Achsabstand auch tatsächlich eingestellt wurde bzw. im Betrieb aufrecht erhalten bleibt. Störungen sind somit sofort erkennbar.To generate a feedback after an adjustment process, it is advantageous if the vibration drive comprises a sensor for detecting an instantaneous center distance between the shaft axis and an eccentric axis. In this way it can be checked whether a specified center distance has actually been set or is maintained during operation. Faults can thus be recognized immediately.
Zudem ist es vorteilhaft, wenn der Vibrationsantrieb einen Sensor zur Erfassung einer Winkelstellung und/oder Winkelgeschwindigkeit der Welle umfasst. Damit ist die Möglichkeit geschaffen, jederzeit eine Ist-Drehzahl der Welle festzustellen und beispielsweise dem Vibrationsantrieb eine bevorzugte Anfangs- oder Endstellung vorzugeben. Zudem können auf diese Weise mehrere Vibrationsantriebe synchronisiert betrieben werden.It is also advantageous if the vibration drive comprises a sensor for detecting an angular position and / or angular velocity of the shaft. This creates the possibility to determine an actual rotational speed of the shaft at any time and, for example, to give the vibration drive a preferred start or end position. In addition, several vibratory drives can be operated synchronized in this way.
Eine einfache Antriebsvariante sieht vor, dass die Welle an einen variablen Hydraulikmotor angeschlossen ist. Neben der vorteilhaften Nutzung eines oftmals bereits vorhandenen Hydrauliksystems ist damit eine einfache Anpassung einer Vibrationsfrequenz möglich, indem die Drehzahl der Welle verändert wird.A simple drive variant provides that the shaft is connected to a variable hydraulic motor. In addition to the advantageous use of a hydraulic system that is often already present, a simple adjustment of a vibration frequency is possible by changing the speed of the shaft.
Zur Reduzierung einer Leistungsaufnahme des Vibrationsantriebs ist es von Vorteil, wenn die Welle mit einem Schwungrad gekoppelt ist. Während eines Vibrationszyklus wird nämlich laufend durch verzögerte und beschleunigte Massen Energie abgegeben bzw. aufgenommen. Das Schwungrad dient als Zwischenspeicher, um diese Energieschwankungen auszugleichen.To reduce the power consumption of the vibration drive, it is advantageous if the shaft is coupled to a flywheel. During a vibration cycle, energy is continuously released or absorbed by delayed and accelerated masses. The flywheel serves as a buffer to compensate for these energy fluctuations.
Bei einem erfindungsgemäßen Verfahren zum Stopfen eines Gleises mittels eines oben beschriebenen Stopfaggregats wird die erzeugte Vibrationsbewegung über einen Beistellzylinder und einen Pickelarm auf den jeweiligen Stopfpickel übertragen, wobei die Vibrationsbewegung verändert wird, indem mittels der Verstelleinrichtung der Exzenter gegenüber der Welle in radialer Richtung verstellt wird. Konkret erfolgt eine Anpassung der Vibrationsamplitude während des Betriebs.In a method according to the invention for tamping a track by means of a tamping unit described above, the vibration movement generated is transmitted to the respective tamping pick via an auxiliary cylinder and a pick arm, the vibration movement being changed by adjusting the eccentric in relation to the shaft in the radial direction by means of the adjusting device. Specifically, the vibration amplitude is adjusted during operation.
Vorteilhaft weitergebildet wird das Verfahren in der Weise, dass ein Stopfzyklus aus mehreren hintereinander ablaufenden Phasen gebildet wird und dass mittels einer Steuerung und/oder Regelung zumindest in einer Phase ein gegenüber einer anderen Phase unterschiedlicher Achsabstand zwischen Wellenachse und einer Exzenterachse eingestellt wird. Einzelne Phasen des Stopfzyklus bilden beispielweise ein Absenken des Stopfaggregats, ein Beistellen der Stopfpickel, ein Anheben des Stopfaggregats sowie ein Neupositionieren des Stopfaggregats. Durch die Verstellbarkeit wird der Vibrationsantrieb für die jeweilige Phase optimal eingesetzt.The method is advantageously further developed in such a way that a tamping cycle is formed from a plurality of phases running in succession and that, by means of a control and / or regulation, at least in one phase a different axis distance between the shaft axis and an eccentric axis is set in relation to another phase. Individual phases of the tamping cycle include, for example, lowering the tamping unit, providing the tamping pick, raising the tamping unit and repositioning the tamping unit. Due to the adjustability, the vibration drive is optimally used for the respective phase.
Dabei ist es von Vorteil, wenn zumindest in einer Phase des Stopfzyklus ein Achsabstand gleich Null eingestellt wird, um die Vibration unabhängig von der Drehzahl der Welle für eine gewünschte Dauer auszusetzen. Sinnvoll ist das insbesondere während einer Neupositionierung des Stopfaggregats zwischen zwei Stopfvorgängen zur Lärmreduktion und zur Verminderung der Leistungsaufnahme des Vibrationsantriebs.It is advantageous if an axis distance equal to zero is set at least in one phase of the stuffing cycle in order to suspend the vibration for a desired duration regardless of the speed of the shaft. This is particularly useful during repositioning of the tamping unit between two tamping processes to reduce noise and reduce the power consumption of the vibration drive.
Zusätzlich ist es vorteilhaft, wenn während eines Stopfzyklus die Welle mit unterschiedlichen Drehzahlen angetrieben wird. Auf diese Weise ist die Vibrationsfrequenz an unterschiedliche Anforderungen während eines Stopfzyklus anpassbar. Während eines Eintauchvorgangs wird beispielsweise eine höhere Drehzahl vorgegeben, weil sich mit höherer Vibrationsfrequenz der Eintauchwiderstand eines Schotterbetts reduziert.In addition, it is advantageous if the shaft is driven at different speeds during a stuffing cycle. In this way, the vibration frequency can be adapted to different requirements during a stuffing cycle. For example, a higher rotational speed is specified during an immersion process because the immersion resistance of a ballast bed is reduced with a higher vibration frequency.
Die Erfindung wird nachfolgend in beispielhafter Weise unter Bezugnahme auf die beigefügten Figuren erläutert. Es zeigen in schematischer Darstellung:The invention is explained below by way of example with reference to the accompanying figures. In a schematic representation:
- Fig. 1Fig. 1
- Stopfaggregat mit zwei PickelarmenTamping unit with two pick arms
- Fig. 2Fig. 2
-
Vibrationsantrieb des Stopfaggregats gemäß
Fig. 1 Vibration drive of the tamping unit according toFig. 1 - Fig. 3Fig. 3
- Schnittansicht des Vibrationsantriebs im AufrissSectional view of the vibration drive in elevation
- Fig. 4Fig. 4
- Schnittansicht mit Exzenter in Null-StellungSectional view with eccentric in zero position
- Fig. 5Fig. 5
- Schnittansicht mit Exzenter mit maximalem AchsabstandSectional view with eccentric with maximum center distance
- Fig. 6Fig. 6
- Ausführung mit alternativer VerstelleinrichtungVersion with alternative adjustment device
- Fig. 7Fig. 7
-
Schrägansicht der Welle gemäß
Fig. 2 Oblique view of the shaft according toFig. 2
Das in
Wie in
Die
An das Kolbenelement 17 sind jene Bauteile anschließbar, die mit der Vibrationsbewegung 10 beaufschlagt werden sollen. In einer einfacheren Variante ist der jeweilige Beistellzylinder direkt mit einem geeigneten Anschluss direkt am Exzenter gelagert und fungiert selbst als Übertragungselement 9. Das in
Die Verstelleinrichtung 14 umfasst günstigerweise einen hydraulischen Zylinder 20, der in der Welle 7 angeordnet ist und einen Kolben 21 gegen eine Innenfläche des auf der Welle 7 aufsitzenden Exzenters 12 drückt. Mittels dieser Druckkraft ist der Exzenter 12 gegenüber der Welle 7 verstellbar. Um den Exzenter 12 in seiner jeweiligen Lage zu fixieren bzw. zurückzustellen, erzeugt ein weiteres Element der Verstelleinrichtung 14 auf einer gegenüberliegenden Innenfläche des Exzenters 12 eine Gegenkraft. Diese wird beispielsweise mittels einer Feder oder - wie in
Anstelle einer hydraulischen Verstelleinrichtung 14 ist eine nicht dargestellte mechanische Verstelleinrichtung einsetzbar. Diese umfasst beispielsweise in der Welle 7 geführte Spindeln oder Kurbelwellen, um die Lage des Exzenters 12 gegenüber der Welle 7 zu verstellen.Instead of a
Die
In
Durch entsprechende Ansteuerung der Verstelleinrichtung 14 ist für den Achsabstand 15 jeder Wert zwischen Null und einem Maximalwert einstellbar. Dabei führt bei gleichbleibendem Drehmoment ein reduzierter Achsabstand 15 nicht nur zu einer geringeren Vibrationsamplitude, sondern auch zu einer höheren Schlagkraft des Vibrationsantriebs 2. Das ist für den Betrieb des Stopfaggregats 1 vorteilhaft, um im Bedarfsfall die Wirkung des jeweiligen vibrierenden Stopfpickels 3 auf ein Schotterbett anzupassen.By appropriate control of the adjusting
Bei einer alternativen Verstelleinrichtung 14 gemäß
Die in
Über in der Welle 7 angeordnete hydraulische Leitungen ist jeder Zylinder 20, 23 an ein jeweiliges vorgesteuertes Rückschlagventil 26 angeschlossen. Günstigerweise sind die Rückschlagventile 26 ebenfalls innerhalb der Welle 7 angeordnet, um sehr kurze Verbindungsleitungen zwischen den vorgesteuerten Rückschlagventilen 26 und den Zylindern 20, 23 sicherzustellen. Dadurch wird ein rasches Ansprechen der Verstelleinrichtung 14 ermöglicht. Zudem ist die komprimierbare Flüssigkeitsmenge minimiert, sodass die Kompressibilität einer verwendeten Hydraulikflüssigkeit vernachlässigbar ist. Die Verwendung zweier mittels vorgesteuerter Rückschlagventile 26 angesteuerter Zylinder 20, 23 bewirkt eine sichere Fixierung des Exzenters 12 in seiner eingestellten Lage gegenüber der Welle 7.Each
Versorgungsleitungen und Steuerleitungen der Verstelleinrichtung 14 sind beispielsweise an einer Stirnseite 27 der Welle 7 nach außen geführt. Ein Anschluss dieser rotierenden Leitungen an ein Hydrauliksystem erfolgt mittels einer bekannten Drehdurchführung.Supply lines and control lines of the adjusting
Mit dem erfindungsgemäßen Verfahren ist die Vibrationsbewegung 10 an einzelne Phasen eines Stopfzyklus anpassbar. Am Beginn des Stopfzyklus wird zunächst der Stopfwerkzeugträger 5 abgesenkt. Während dieser Phase tauchen die Stopfpickel 3 in ein Schotterbett eines Gleises ein. Dabei vibrieren die Stopfpickel 3 mit einer Vibrationsfrequenz von bis zu 60 Hertz und im Vibrationsantrieb 2 ist der maximale Achsabstand 15 zwischen Wellenachse 11 und Exzenterachse 13 eingestellt. Am freien Ende des jeweiligen Stopfpickels 3 ergibt sich damit die größtmögliche Vibrationsamplitude.The
In einer nächsten Phase erfolgt die Verdichtung des Schotters unterhalb einer Schwelle. Die in Gleisrichtung gegenüberliegenden Stopfpickel 3 bewegen sich mit einer Beistellbewegung aufeinander zu, indem jeder Beistellzylinder 6 auf den zugeordneten Pickelarm 4 ein Drehmoment ausübt. Dabei ist der Beistellbewegung weiterhin die mittels des Vibrationsantriebs 2 erzeugte Vibrationsbewegung 10 überlagert. Durch eine Anpassung der Drehzahl der Welle 7 ist in dieser Phase die Vibrationsfrequenz auf 35 Hertz eingestellt.In the next phase, the ballast is compacted below a threshold. The tamping picks 3 lying opposite in the track direction move towards one another with an additional movement, in that each
Wird die Welle 7 bereits mit einem maximalen Drehmoment angetrieben, kann in dieser Phase bei Bedarf durch geringfügige Reduktion des Achsabstands 15 zwischen Wellenachse 11 und Exzenterachse 13 die Schlagkraft der Stopfpickel 3 erhöht werden. Eine solche Maßnahme ist gegebenenfalls bei einem stark verkrusteten Schotterbett sinnvoll. Dabei wird der Achsabstand 15 nur so weit reduziert, dass die sich ergebende Verringerung der Vibrationsamplitude vernachlässigbar bleibt.If the
Während einer Schwingungsperiode werden die in Vibration befindlichen Massen der Beistellzylinder 6, der Pickelarme 4 und der Stopfpickel 3 zunächst in einer Richtung beschleunigt und abgebremst und anschließend in der Gegenrichtung beschleunigt und abgebremst. Diese Vibrationsbewegungen führen deshalb laufend zu einer Abgabe und einer Aufnahme von kinetischer Energie. Ein Großteil dieser fluktuierenden Energie wird in den durchgängig in Schwung befindlichen Rotationsmassen der Welle 7 und des Exzenters 12 zwischengespeichert.During an oscillation period, the masses of the
Günstigerweise ist die Welle 7 zusätzlich mit einem Schwungrad gekoppelt, um die Winkelgeschwindigkeit der rotierenden Massen unabhängig von einem Rotationsantrieb über eine Schwingungsperiode hinweg konstant zu halten. Die Leistungsaufnahme des erfindungsgemäßen Vibrationsantriebs 2 ist somit deutlich geringer als die eines linearen Vibrationsantriebs, der eine Vibration beispielsweise mittels eines Hydraulikzylinders erzeugt.Advantageously, the
Sobald der Verdichtungsvorgang beendet ist, werden die Stopfpickel 3 durch Anheben des Stopfwerkzeugträgers 5 aus dem Schotterbett gezogen. Dabei erfolgt auch eine Rückstellung der Bestellzylinder 6. In dieser Phase des Stopfzyklus wird die Vibration bis zum neuerlichen Eindringen der Stopfpickel 3 ausgesetzt, indem der Achsabstand 15 zwischen Wellenachse 11 und Exzenterachse 13 auf null gestellt wird.As soon as the compaction process has ended, the tamping picks 3 are pulled out of the ballast bed by lifting the
Konkret wird die Vibrationsamplitude bis auf null reduziert, wobei während dieses Reduktionsvorgangs die Vibrationsfrequenz konstant bleibt. Ohne die erfindungsgemäße Exzenterverstellung müsste die Welle 7 abgebremst werden, um die Vibration auszusetzen. Dabei würde der Vibrationsantrieb 2 zwangsläufig niedrige Frequenzbereiche durchlaufen. Bauteile einer das Stopfaggregat 1 umfassenden Stopfmaschine oder Elemente der Gleisstrecke weisen zumeist niedrigen Eigenfrequenzen auf, sodass es zu unerwünschten Resonanzen käme. Zudem würde ein zyklisches Abbremsen und Beschleunigen der rotierenden Massen die Leistungsaufnahme des Vibrationsantriebs 2 deutlich erhöhen.Specifically, the vibration amplitude is reduced to zero, the vibration frequency remaining constant during this reduction process. Without the eccentric adjustment according to the invention, the
Zur automatischen Durchführung der in den einzelnen Phasen eines Stopfzyklus vorgenommenen Änderungen der Exzenterlage wird die Verstelleinrichtung 14 mittels einer Steuerung und/oder einer Regelung angesteuert. Am Stopfaggregat 1 können diverse Sensoren angebracht sein, um in Echtzeit Vibrationsparameter wie Frequenz und Amplitude zu erfassen und an die Steuerung bzw. Regelung zu melden. Insbesondere kann ein Sensor zur Erfassung des momentanen Achsabstands 15 zwischen Wellenachse 11 und Exzenterachse 13 vorgesehen sein. Damit ist eine besonders präzise Einstellung des Achsabstands 15 realisierbar.For the automatic implementation of the changes in the eccentric position made in the individual phases of a stuffing cycle, the adjusting
Angetrieben wird die Welle 7 mittels eines Hydraulikmotors, der das in der Stopfmaschine vorhandene Hydrauliksystem nutzt. Damit ist ein ausreichend hohes Drehmoment vorhanden und die Drehzahl ist stufenlos einstellbar.The
Claims (15)
- A tamping unit (1) for tamping a track, having tamping tines (3) which are designed for immersion into a ballast bed and can be set in vibrations by means of a vibration drive (2), wherein the vibration drive (2) comprises a housing (8) in which a shaft (7) including an eccentric (12) is arranged for rotation about a shaft axis (11) and wherein a transmission element (9) for transmitting a vibratory motion (10) is mounted on the eccentric (12), characterized in that the eccentric (12) is connected to the shaft (7) in a rotation-locked and radially displaceable manner, and that the position of the eccentric (12) relative to the shaft (7) is adjustable in radial direction by means of an adjustment device (14).
- A tamping unit (1) according to claim 1, characterized in that the transmission element (9) is designed as a connecting rod for transmission of an oscillating vibratory motion (10).
- A tamping unit (1) according to claim 1 or 2, characterized in that the shaft (7) has, at a shell surface, two oppositely positioned parallel flat portions (25) by means of which the eccentric (12) is guided radially.
- A tamping unit (1) according to one of claims 1 to 3, characterized in that the adjustment device (14) comprises at least one hydraulic cylinder (20) with a piston (21), and that an adjustment force can be exerted upon the eccentric (12) by means of the piston (21).
- A tamping unit (1) according to claim 4, characterized in that the hydraulic cylinder (20) is arranged in the shaft (7).
- A tamping unit (1) according to claim 4 or 5, characterized in that the hydraulic cylinder (20) is controlled by means of a pre-controlled check valve (26).
- A tamping unit (1) according to one of claims 4 to 6, characterized in that the adjustment device (14) comprises a further cylinder (23) having a piston (22) for fixing and/or returning the eccentric (12).
- A tamping unit (1) according to one of claims 1 to 7, characterized in that the adjustment device (14) is connected to a control and/or a governing device.
- A tamping unit (1) according to one of claims 1 to 8, characterized in that the vibration drive (2) has a sensor for detecting a momentary axis distance (15) between the shaft axis (11) and an eccentric axis (13).
- A tamping unit (1) according to one of claims 1 to 9, characterized in that the vibration drive (2) comprises a sensor for detecting an angle position and/or angular velocity of the shaft (7).
- A tamping unit (1) according to one of claims 1 to 10, characterized in that the shaft (7) is connected to a variable hydraulic motor.
- A method of tamping a track by means of a tamping unit (1) according to one of claims 1 to 11, wherein the generated vibratory motion (10) is transmitted via a squeezing drive (6) to a tine arm (4), characterized in that the vibratory motion (10) is changed in that the eccentric (12) is adjusted relative to the shaft (7) in radial direction by means of the adjustment device (14).
- A method according to claim 12, characterized in that a tamping cycle is formed of several phases taking place one after the other, and that during at least one phase, by means of a control and/or governing device, an axis distance (15) between the shaft axis (11) and an eccentric axis (13) is set which is different versus another phase.
- A method according to clam 13, characterized in that, during at least one phase of the tamping cycle, an axis distance (15) equalling zero is set.
- A method according to one of claims 12 to 14, characterized in that during a tamping cycle, the shaft (7) is powered with different speeds of rotation.
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PL16788021T PL3377699T3 (en) | 2015-11-20 | 2016-10-21 | Tamping unit and method for tamping a track |
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ATA749/2015A AT517999B1 (en) | 2015-11-20 | 2015-11-20 | Stopfaggregat and method for plugging a track |
PCT/EP2016/001747 WO2017084733A1 (en) | 2015-11-20 | 2016-10-21 | Tamping unit and method for tamping a track |
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JP (1) | JP6738420B2 (en) |
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AT14095U3 (en) * | 2014-10-17 | 2015-12-15 | Plasser & Theurer Export Von Bahnbaumaschinen Gmbh | Stopfaggregat for clogging thresholds of a track |
CN104588307B (en) * | 2015-01-09 | 2017-02-22 | 上海大学 | Circumference oscillating mechanism with adjustable amplitude |
AT517999B1 (en) * | 2015-11-20 | 2018-05-15 | Plasser & Theurer Export Von Bahnbaumaschinen Gmbh | Stopfaggregat and method for plugging a track |
-
2015
- 2015-11-20 AT ATA749/2015A patent/AT517999B1/en not_active IP Right Cessation
-
2016
- 2016-10-21 WO PCT/EP2016/001747 patent/WO2017084733A1/en active Application Filing
- 2016-10-21 EP EP16788021.0A patent/EP3377699B1/en active Active
- 2016-10-21 EA EA201800172A patent/EA036330B1/en unknown
- 2016-10-21 DK DK16788021.0T patent/DK3377699T3/en active
- 2016-10-21 ES ES16788021T patent/ES2774025T3/en active Active
- 2016-10-21 CA CA3000749A patent/CA3000749A1/en active Pending
- 2016-10-21 AU AU2016355735A patent/AU2016355735B2/en active Active
- 2016-10-21 PL PL16788021T patent/PL3377699T3/en unknown
- 2016-10-21 CN CN201680066943.1A patent/CN108291368A/en active Pending
- 2016-10-21 US US15/767,554 patent/US10808362B2/en active Active
- 2016-10-21 JP JP2018526222A patent/JP6738420B2/en active Active
Non-Patent Citations (1)
Title |
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Also Published As
Publication number | Publication date |
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DK3377699T3 (en) | 2020-05-04 |
AU2016355735A1 (en) | 2018-05-10 |
JP6738420B2 (en) | 2020-08-12 |
JP2018534454A (en) | 2018-11-22 |
AT517999A1 (en) | 2017-06-15 |
EP3377699A1 (en) | 2018-09-26 |
PL3377699T3 (en) | 2020-07-13 |
CA3000749A1 (en) | 2017-05-26 |
AU2016355735B2 (en) | 2021-08-05 |
AT517999B1 (en) | 2018-05-15 |
CN108291368A (en) | 2018-07-17 |
EA036330B1 (en) | 2020-10-27 |
US10808362B2 (en) | 2020-10-20 |
EA201800172A1 (en) | 2018-10-31 |
US20180298565A1 (en) | 2018-10-18 |
WO2017084733A1 (en) | 2017-05-26 |
ES2774025T3 (en) | 2020-07-16 |
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