• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a tamping unit (1) for plugging a track, with tamping plugs (3) which can be set into vibration by means of a vibration drive (2), wherein the vibration drive (2) comprises a housing (8) in which a shaft (7) with an eccentric (12) about a shaft axis (11) is rotatably arranged and wherein on the eccentric (12) a transmission element (9) for transmitting a vibrating movement (10) is mounted. In this case, the eccentric (12) is rotationally connected and radially displaceable connected to the shaft (7), wherein the position of the eccentric (12) relative to the shaft (7) in the radial direction by means of an adjusting device (14) is adjustable. While retaining the advantages of an eccentric drive, the possibility is thus created of adapting vibration parameters during operation.
    公开号:AT517999A1
    申请号:T749/2015
    申请日:2015-11-20
    公开日:2017-06-15
    发明作者:
    申请人:Plasser & Theurer Export Von Bahnbaumaschinen Gmbh；
    IPC主号:
    专利说明:

    description
    Stopfaggregat and method for plugging a track
    Technical Field [01] The invention relates to a tamping unit for tucking a track, with tamping plungers immersible in a ballast bed, which are vibratable by means of a vibration drive, the vibration drive comprising a housing in which a shaft with an eccentric is rotatable about a shaft axis is arranged and wherein on the eccentric a transmission element is mounted for transmitting a vibratory movement. In addition, the invention relates to a method for plugging a track by means of the tamping unit, wherein the generated vibration movement is transmitted via a Beistellzylinder on a picking arm.
    State of the art [02] Due to the high loads to which a tamping unit is exposed, the vibration drive must meet special requirements. When immersing the stuffing pick in a ballast bed of a track and the subsequent compression of the ballast below a threshold occur constantly load changes that claim the vibration drive. In particular, when tamping a non-renewed ballast bed, which is often completely encrusted, act on the vibration driven by vibrating tamping tamping high opposing forces. Even with such difficult operating conditions, the vibration drive must maintain the required vibration of the tamping picks with an approximately constant vibration amplitude to ensure a consistent tamping quality.
    For use in tamping units, therefore, a known from the patent AT 350 097 B vibration drive has proven in which an oscillating vibration movement is generated by means of a driven eccentric shaft. In this design, the vibration amplitude is fixed by the dimensioning of the eccentric shaft. The transmitted over Beistellzylinder and Pickelarme on the tamping
    Vibration movement thus remains largely unaffected by the resistance of the ballast bed.
    [04] In a known from the AT 513 973 A type, the vibration movement is generated by means of a hydraulic linear drive. Without special measures here leads to an increased ballast bed resistance to an undesirable reduction of the vibration amplitude. On the other hand, a hydraulic linear drive allows easy adjustment of the vibration parameters up to a rapid sequence of on and off operations. The latter is more difficult to implement in a known vibration drive with eccentric axis due to the inertia of the masses in rotation.
    SUMMARY OF THE INVENTION [05] The invention is based on the object of providing an improvement over the prior art for a vibration drive of the type mentioned in the introduction. Another object is to provide a corresponding method for plugging a track.
    [06] According to the invention, these objects are achieved by a tamping unit according to claim 1 and a method according to claim 12. Further developments can be found in the dependent claims.
    [07] In this case, the eccentric is rotationally connected and radially displaceable connected to the shaft, wherein the position of the eccentric relative to the shaft in the radial direction by means of an adjusting device is adjustable. In operation, a torque is transmitted by means of the shaft on the eccentric designed as a separate component. The effect on the transmission element determines an adjustable center distance between an eccentric axis and the shaft axis. Specifically, the amplitude of the transferable by means of the transmission vibratory movement is infinitely adjustable. While retaining the advantages of an eccentric drive, the possibility is thus created of adapting vibration parameters during operation. A changed distance between the eccentric axis and shaft axis not only leads to a changed vibration amplitude, but at a constant torque also to a changed impact force, which is applied by means of the vibration drive.
    [08] 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 is then connectable to a linear guided piston, by means of which the vibration is transferable to several components.
    In a simple embodiment, the shaft on a lateral surface on two opposite, mutually parallel flats, by means of which the eccentric is guided radially. In the direction of rotation, the flattenings form a positive connection together with correspondingly executed mating surfaces of the eccentric in order to securely transmit a torque.
    Furthermore, it is advantageous if the adjusting device comprises at least one hydraulic cylinder with a piston, wherein by means of the piston an adjusting force can be exerted on the eccentric. Thus, an often existing hydraulic system can be used to make an adjustment of the eccentric relative to the shaft.
    [11] Conveniently, the hydraulic cylinder is arranged in the shaft. This cylinder is connected to a guided in the shaft hydraulic line, so there is a compact and weight-saving design of the adjustment.
    Advantageously, the hydraulic cylinder is controlled by means of a pilot operated check valve. This ensures that the cylinder remains fixed in its position after an adjustment even when high counter-forces act on the eccentric.
    A development of the invention provides that the adjusting device comprises a further cylinder with a piston for fixing and / or for returning the eccentric. The eccentric is thus clamped in its position between two pistons, whereby a particularly robust fixation is given. Also, the second piston is favorably controlled by means of a pilot-operated check valve.
    An improvement of the application possibilities of Stopfaggregats is given when the adjustment to a controller and / or a
    Control is connected. In this way, the vibratory drive of the tamping unit is automatically adapted to changed conditions during operation.
    [15] To generate a feedback after an adjustment process, it is advantageous if the vibration drive comprises a sensor for detecting a current center distance between the shaft axis and an eccentric axis. In this way, it is possible to check whether a given center distance has actually been set or is maintained during operation. Disturbances are thus immediately recognizable.
    [16] 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 opportunity at any time to determine an actual speed of the shaft and, for example, the vibratory drive to specify a preferred initial or final position. In addition, several vibration drives can be operated synchronized in this way.
    A simple drive variant provides that the shaft is connected to a variable hydraulic motor. In addition to the advantageous use of an often existing hydraulic system so that a simple adaptation of a vibration frequency is possible by the rotational speed of the shaft is changed.
    To reduce a 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.
    In a method according to the invention for plugging a track by means of a tamping unit described above, the generated vibration is transmitted via a Beistellzylinder and a pimple arm to the respective tamping, wherein the vibratory motion is changed by means of the adjustment of the eccentric relative to the shaft in the radial direction is adjusted. Specifically, an adaptation of the vibration amplitude during operation takes place.
    [20] Advantageously, the method is further developed in such a way that a stuffing cycle is formed from a plurality of successive phases and that by means of a control and / or regulation, at least in one phase, a different center distance between the shaft axis and an eccentric axis relative to another phase is set. Individual phases of the stuffing cycle form, for example, a lowering of the tamping unit, an addition of tamping picks, a lifting of the tamping unit and a repositioning of the tamping unit. Due to the adjustability of the vibration drive for each phase is optimally used.
    [21] It is advantageous if, at least in one phase of the stuffing cycle, a center distance equal to zero is set in order to suspend the vibration independently of the rotational speed of the shaft for a desired duration. This is particularly useful during a repositioning of the tamping unit between two stuffing operations for noise reduction and to reduce the power consumption of the vibration drive.
    In addition, it is advantageous if during a stuffing cycle, the shaft is driven at different speeds. In this way, the vibration frequency is adaptable to different requirements during a stuffing cycle. During a dipping process, for example, a higher speed is specified, because with a higher vibration frequency the immersion resistance of a ballast bed is reduced.
    BRIEF DESCRIPTION OF THE DRAWINGS [23] The invention will now be described by way of example with reference to the accompanying drawings. FIG. 1 shows a tamping unit with two picking arms [25] FIG. 2 shows a vibration drive of the tamping unit according to FIG. 1 [26] FIG. 3 shows a sectional view of the vibratory drive in elevation [27] FIG Zero position [28] FIG. 5 sectional view with eccentric with maximum center distance [29] FIG. 6 embodiment with alternative adjusting device [30] FIG. 7 oblique view of the shaft according to FIG. 2
    DESCRIPTION OF THE EMBODIMENTS [31] The tamping unit 1 shown in FIG. 1 comprises an adjustable vibration drive 2 for oscillating two opposite tamping picks 3 or tamping picking groups. Each stuffing pike 3 is attached to a pimple 4. The respective picking arm 4 is pivotally connected to a lowerable stuffing tool carrier 5 and connected to a piston rod of an associated auxiliary cylinder 6. Also attached to the stuffing tool carrier 5 is the vibratory drive 2, to which each picking arm 4 is connected via the associated auxiliary cylinder 6. A generated vibration is thus transmitted via the respective auxiliary cylinder 6 to the respective picking arm 4 and the tamping pick 3 attached thereto.
    [32] As can be seen in Fig. 2, the vibration drive comprises a shaft 7 which is mounted in a housing 8 with sealed passages. At least one further sealed passage is provided for a transmission element 9, to which the auxiliary cylinders 6 of the tamping unit 1 are connected. The bearing of the shaft 7 in the housing 8 is conveniently carried out by means of rolling bearings. During operation, the components of the vibration drive 2 cause an oscillating vibration movement 10. In this case, the shaft 7 rotates about a shaft axis 11 and is rotationally connected to an eccentric 12.
    [33] FIGS. 3-6 show that an axis spacing 15 can be adjusted between an eccentric axis 13 and the shaft axis 11 by means of an adjusting device 14. At an adjusted center distance 15 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.
    In the exemplary embodiment, the transmission element 9 is designed as a connecting rod, which is pivotally connected to a linearly guided piston element 17. To connect the piston member 17 with the transmission element 9, a bolt 18 is provided.
    [34] To the piston member 17 those components are connected, which are to be acted upon by the vibrating movement 10. In a simpler variant, the respective auxiliary cylinder is mounted directly with a suitable connection directly to the eccentric and acts as a transmission element 9. The illustrated in Fig. 2 oil-lubricated bearings 19 between transmission element 9 and eccentric 12 is not in the figures 3-6 for clarity located.
    The adjusting device 14 conveniently comprises a hydraulic cylinder 20 which is arranged in the shaft 7 and presses a piston 21 against an inner surface of the seated on the shaft 7 eccentric 12. By means of this compressive force of the eccentric 12 relative to the shaft 7 is adjustable. To fix the eccentric 12 in its respective position or reset, generates a further element of the adjusting device 14 on an opposite inner surface of the eccentric 12, a counterforce. This is applied, for example, by means of a spring or, as shown in FIG. 3, by means of a further piston 22 of a further cylinder 23.
    [36] Instead of a hydraulic adjusting device 14, a mechanical adjusting device, not shown, can be used. This includes, for example, in the shaft 7 guided spindles or crankshafts to adjust the position of the eccentric 12 relative to the shaft 7.
    [37] Figures 4 and 5 show a simplified representation of two end positions of the adjustable eccentric 12. In Fig. 4, the axial distance 15 between the shaft axis 11 and eccentric axis 13 is equal to zero. The rotational movement 16 of the shaft 7 and the eccentric 12 lead to this no vibration movement. This adjustment of the eccentric position thus serves to suspend the vibration.
    [38] In FIG. 5, a maximum center distance 15 between the shaft axis 11 and the eccentric axis 13 is set. Trained as a connecting rod transmission element 9 then transmits an oscillating vibration movement 10 with a vibration amplitude corresponding to the maximum center distance 15. With the given kinematic arrangement of the respective auxiliary cylinder 6, the respective Pickelarms 4 and the respective stuffing pickle 3 results in a desired amplitude of vibration at the free end of the stuffing 3.
    [39] By appropriate control of the adjusting device 14, each value between zero and a maximum value can be set for the axial distance 15. This results in a constant torque a reduced center distance 15 not only to a lower vibration amplitude, but also to a higher impact force of the vibration drive 2. This is advantageous for the operation of Stopfaggregats 1, if necessary, to adapt the effect of the respective vibrating stuffing 3 on a ballast bed ,
    In an alternative adjusting device 14 according to FIG. 6, the eccentric 12 is not seated on the shaft 7, but is connected via the adjusting device 14 in a rotationally locked and radially adjustable manner to the shaft 7. For example, in the case of a hydraulic embodiment, the free ends of the pistons 21,22 are inserted in a respective longitudinal groove on an inner surface of the eccentric 12 and fixed by means of fastening means 24 in the longitudinal direction. In this way, the pistons 21, 22 serve on the one hand the adjustment in the radial direction and on the other hand as elements of a rotationally-locked connection between the shaft 7 and the eccentric 12.
    The shaft 7 shown in Fig. 7 according to the embodiment in Fig. 2 has two flats 25, by means of which the eccentric 12 is guided radially. In the region of these flats 25, two hydraulic cylinders 20, 23 are arranged as elements of the adjusting device 14 in the shaft 7. The pistons 21, 22 press in the installed state against inner surfaces of the eccentric 12, whereby it is displaced radially to the shaft axis 11. Inner surfaces of the eccentric 12 slide along the flattenings 25 of the shaft 7.
    [42] Via hydraulic lines arranged in the shaft 7, each cylinder 20, 23 is connected to a respective pilot operated check valve 26. Conveniently, the check valves 26 are also disposed within the shaft 7 to ensure very short connection lines between the pilot operated check valves 26 and the cylinders 20, 23. This will give a quick response of the
    Adjustment device 14 allows. In addition, the compressible amount of liquid is minimized, so that the compressibility of a hydraulic fluid used is negligible. The use of two controlled by pilot operated check valves 26 cylinders 20, 23 causes a secure fixation of the eccentric 12 in its adjusted position relative to the shaft. 7
    [43] Supply lines and control lines of the adjusting device 14 are guided, for example, on an end face 27 of the shaft 7 to the outside. A connection of these rotating lines to a hydraulic system by means of a known rotary feedthrough.
    [44] With the method according to the invention, the vibratory movement 10 can be adapted to individual phases of a stuffing cycle. At the beginning of the stuffing cycle, first the stuffing tool carrier 5 is lowered. During this phase, the tamping pick 3 immerse in a ballast bed of a track. In this case, the stuffing picks 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 eccentric axis 13 is set. At the free end of the respective stuffing pickle 3, this results in the largest possible vibration amplitude.
    [45] In a next phase, the density of the ballast below a threshold. The opposite in the track direction tamping 3 move towards each other with a Beistellbewegung by each side cylinder 6 exerts on the associated Pickelarm 4 a torque. In this case, the Beistellbewegung is still superimposed on the vibration generated by the vibration drive 2 vibratory motion 10. By adjusting the speed of the shaft 7, the vibration frequency is set to 35 Hertz in this phase.
    [46] If the shaft 7 is already driven with a maximum torque, the impact force of the tamping picks 3 can be increased in this phase if necessary by slightly reducing the axial distance 15 between the shaft axis 11 and the eccentric axis 13. Such a measure may be useful for a heavily encrusted ballast bed. In this case, the axial distance 15 is reduced only so far that the resulting reduction of the vibration amplitude remains negligible.
    During a period of oscillation, the masses of the auxiliary cylinders 6, the picking arms 4 and the tamping pick 3, which are in vibration, are first accelerated and decelerated in one direction and then accelerated and decelerated in the opposite direction. These vibration movements therefore constantly lead to a release and absorption of kinetic energy. Much of this fluctuating energy is cached in the continuously rotating masses of rotation of the shaft 7 and the eccentric 12.
    [48] Conveniently, the shaft 7 is additionally coupled to a flywheel to keep constant the angular velocity of the rotating masses independently of a rotational drive over a period of oscillation. 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.
    [49] Once the compaction process is completed, the tamping picks 3 are pulled out of the ballast bed by lifting the stuffing tool carrier 5. In this case, also a provision of the order cylinder 6. In this phase of Stopfzyklus the vibration is exposed to the renewed penetration of the tamping 3 by the center distance 15 between the shaft axis 11 and eccentric axis 13 is set to zero.
    [50] Specifically, the vibration amplitude is reduced to zero, during which the vibration frequency remains constant. Without the eccentric adjustment according to the invention, the shaft 7 would have to be braked in order to suspend the vibration. The vibration drive 2 would inevitably go through low frequency ranges. Components of a stuffing machine comprising the tamping unit 1 or elements of the track section usually have low natural frequencies, so that undesirable resonances would occur. In addition, a cyclical deceleration and acceleration of the rotating masses would significantly increase the power consumption of the vibration drive 2.
    [51] In order to automatically carry out the changes in the eccentric position made in the individual phases of a stuffing cycle, the adjusting device 14 is actuated by means of a controller and / or a controller. At the tamping unit 1, various sensors may be mounted to detect in real time vibration parameters such as frequency and amplitude and to report to the control or regulation. In particular, a sensor for detecting the instantaneous center distance 15 between the shaft axis 11 and the eccentric axis 13 may be provided. For a particularly precise adjustment of the axial spacing 15 can be realized.
    [52] The shaft 7 is driven by means of a hydraulic motor, which uses the existing hydraulic system in the tamping machine. Thus, a sufficiently high torque is available and the speed is infinitely adjustable.
    权利要求:
    Claims (15)
    [1]
    claims
    1. Stopfaggregat (1) for plugging a track, with plunging into a ballast bed tufts (3) which are displaceable by means of a vibration drive (2) in vibration, wherein the vibration drive (2) comprises a housing (8) in which a shaft (7) with an eccentric (12) about a shaft axis (11) is rotatably arranged and wherein on the eccentric (12) a transmission element (9) for transmitting a vibrating movement (10) is mounted, characterized in that the eccentric (12) rotationally connected and radially displaceable with the shaft (7) is connected and that the position of the eccentric (12) relative to the shaft (7) in the radial direction by means of an adjusting device (14) is adjustable.
    [2]
    2. Stopfaggregat (1) according to claim 2, characterized in that the transmission element (9) is designed as a connecting rod for transmitting an oscillating vibration movement (10).
    [3]
    3. Stopfaggregat (1) according to claim 1 or 2, characterized in that the shaft (7) on a lateral surface two opposite, mutually parallel flats (25), by means of which the eccentric (12) is guided radially.
    [4]
    4. Stopfaggregat (1) according to one of claims 1 to 3, characterized in that the adjusting device (14) comprises at least one hydraulic cylinder (20) with a piston (21) and that by means of the piston (21) an adjusting force on the eccentric (12) is exercisable.
    [5]
    5. Stopfaggregat (1) according to claim 4, characterized in that the hydraulic cylinder (20) in the shaft (7) is arranged.
    [6]
    6. Stopfaggregat (1) according to claim 4 or 5, characterized in that the hydraulic cylinder (20) by means of a pilot operated check valve (26) is driven.
    [7]
    7. Stopfaggregat (1) according to one of claims 4 to 6, characterized in that the adjusting device (14) comprises a further cylinder (23) with a piston (22) for fixing and / or for returning the eccentric (12).
    [8]
    8. Stopfaggregat (1) according to one of claims 1 to 7, characterized in that the adjusting device (14) is connected to a controller and / or a controller.
    [9]
    9. Stopfaggregat (1) according to one of claims 1 to 8, characterized in that the vibration drive (2) comprises a sensor for detecting a current center distance (15) between the shaft axis (11) and an eccentric axis (13).
    [10]
    10. Stopfaggregat (1) according to one of claims 1 to 9, characterized in that the vibration drive (2) comprises a sensor for detecting an angular position and / or angular velocity of the shaft (7).
    [11]
    11. Stopfaggregat (1) according to one of claims 1 to 10, characterized in that the shaft (7) is connected to a variable hydraulic motor.
    [12]
    12. A method for plugging a track by means of a Stopfaggregats (1) according to one of claims 1 to 11, wherein the generated vibratory movement (10) via a Beistellzylinder (6) on a Pickelarm (4) is transmitted, characterized in that the vibrational movement ( 10) is changed by means of the adjusting device (14) of the eccentric (12) relative to the shaft (7) is adjusted in the radial direction.
    [13]
    13. The method according to claim 12, characterized in that a stuffing cycle of a plurality of successive phases is formed and that by means of a control and / or regulation at least in one phase with respect to another phase different center distance (15) between the shaft axis (11) and a Eccentric axis (13) is set.
    [14]
    14. The method according to claim 13, characterized in that at least in one phase of the stuffing cycle, an axial distance (15) is set equal to zero.
    [15]
    15. The method according to any one of claims 12 to 14, characterized in that during a stuffing cycle, the shaft (7) is driven at different speeds.
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    同族专利:
    公开号 | 公开日
    CA3000749A1|2017-05-26|
    AU2016355735B2|2021-08-05|
    EP3377699A1|2018-09-26|
    CN108291368A|2018-07-17|
    US20180298565A1|2018-10-18|
    JP2018534454A|2018-11-22|
    WO2017084733A1|2017-05-26|
    DK3377699T3|2020-05-04|
    AT517999B1|2018-05-15|
    US10808362B2|2020-10-20|
    PL3377699T3|2020-07-13|
    ES2774025T3|2020-07-16|
    EA036330B1|2020-10-27|
    JP6738420B2|2020-08-12|
    AU2016355735A1|2018-05-10|
    EA201800172A1|2018-10-31|
    EP3377699B1|2020-02-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    US4617832A|1982-09-20|1986-10-21|General Kinematics|Vibratory apparatus having variable lead angle and force|
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    US9731324B2|2013-09-25|2017-08-15|Nordco Inc.|Drive for railroad ballast tamper apparatus|
    CN203695369U|2014-01-10|2014-07-09|赵广洋|Sliding type eccentric block|
    AT14095U3|2014-10-17|2015-12-15|Plasser & Theurer Export Von Bahnbaumaschinen Gmbh|Stopfaggregat for clogging thresholds of a track|
    CN104588307B|2015-01-09|2017-02-22|上海大学|Circumference oscillating mechanism with adjustable amplitude|
    AT517999B1|2015-11-20|2018-05-15|Plasser & Theurer Export Von Bahnbaumaschinen Gmbh|Stopfaggregat and method for plugging a track|AT517999B1|2015-11-20|2018-05-15|Plasser & Theurer Export Von Bahnbaumaschinen Gmbh|Stopfaggregat and method for plugging a track|
    AT16604U1|2018-02-13|2020-02-15|Plasser & Theurer Export Von Bahnbaumaschinen Gmbh|Machine for stabilizing a track|
    CN110820438A|2019-11-29|2020-02-21|泰州市万里液压工具厂|Hydraulic tamping machine capable of stably running|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA749/2015A|AT517999B1|2015-11-20|2015-11-20|Stopfaggregat and method for plugging a track|ATA749/2015A| AT517999B1|2015-11-20|2015-11-20|Stopfaggregat and method for plugging a track|
    CA3000749A| CA3000749A1|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    EP16788021.0A| EP3377699B1|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    AU2016355735A| AU2016355735B2|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    EA201800172A| EA036330B1|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    JP2018526222A| JP6738420B2|2015-11-20|2016-10-21|Tamping unit for tamping tracks and method for tamping tracks|
    ES16788021T| ES2774025T3|2015-11-20|2016-10-21|Batting unit and method of hitting a lane|
    CN201680066943.1A| CN108291368A|2015-11-20|2016-10-21|Unit and method are made firm by ramming for tamping railway|
    US15/767,554| US10808362B2|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    DK16788021.0T| DK3377699T3|2015-11-20|2016-10-21|SUPPOSITION DEVICE AND PROCEDURE FOR STOPPING A TRACK|
    PL16788021T| PL3377699T3|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
    PCT/EP2016/001747| WO2017084733A1|2015-11-20|2016-10-21|Tamping unit and method for tamping a track|
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