EP3728736A1 - Verfahren zum betreiben eines stopfaggregats einer gleisbaumaschine sowie stopfvorrichtung zur gleisbettverdichtung und gleisbaumaschine - Google Patents
Verfahren zum betreiben eines stopfaggregats einer gleisbaumaschine sowie stopfvorrichtung zur gleisbettverdichtung und gleisbaumaschineInfo
- Publication number
- EP3728736A1 EP3728736A1 EP18811471.4A EP18811471A EP3728736A1 EP 3728736 A1 EP3728736 A1 EP 3728736A1 EP 18811471 A EP18811471 A EP 18811471A EP 3728736 A1 EP3728736 A1 EP 3728736A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tamping
- force
- ballast
- tamping unit
- stress
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
- E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
- E01B27/13—Packing sleepers, with or without concurrent work on the track
- E01B27/16—Sleeper-tamping machines
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B35/00—Applications of measuring apparatus or devices for track-building purposes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
- B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- 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
-
- 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
- E01B2203/16—Guiding or measuring means, e.g. for alignment, canting, stepwise propagation
Definitions
- the invention relates to a method for operating a tamping unit of a track construction machine and also to a stuffing device for track bed compaction and to a track construction machine.
- Track-guided track-laying machines are used to maintain a
- Tamping unit on The tamping unit is repeated in operation between a reset position in which the tamping unit is out of engagement with the track bed and an engagement position in which the tamping unit is in engagement with the track bed, relocated. High static and dynamic loads act on the tamping unit. To maintain the functionality of highly stressed parts of the tamping unit time-consuming and costly inspection and maintenance are performed regularly.
- the invention has for its object to provide a method for operating a Stopfaggregats a track construction machine, which increases the performance and efficiency of Stopfaggregats.
- Displacement direction of the tamping, acting ballast force for the stress of the tamping unit is essential and that this can be determined exactly on the basis of the driving force and the acceleration.
- the ballast force By the determination and evaluation of the ballast force, the tamping unit can be operated efficiently and economically. For example, heavily used parts can be identified and designed and maintained in accordance with the requirements.
- the processing of the track bed can also under
- the displacement of the tamping unit relative to the track bed is at least, in particular exclusively, in the vertical direction. Relocating the
- Stopfaggregats preferably takes place between the return position and the engaged position. In the return position, the tamping unit is raised and is out of engagement with the track bed. In particular, that can
- the tamping unit has at least two, in particular at least four tamping picks. In the engaged position, the tamping unit, in particular the at least two tamping picks, dips into the track bed. In a between the reset position and the
- the tamping unit comes into contact with the track bed.
- the track bed compaction can be carried out during the shifting from the delivery position to the engagement position.
- Driving force is understood to mean that force which is used to displace the stuffing unit between the return position and the engaged position
- the driving force can be detected, for example, by means of a force sensor.
- the driving force may be on the tamping unit and / or on the unit carrier and / or on a acting between the tamping unit and the unit carrier
- an acceleration sensor can be used to determine the acceleration acting on the tamping unit.
- the acceleration can be detected at the tamping unit and / or at the drive device.
- the ballast force is determined by the driving force and the acceleration
- the ballast force can be reliably and accurately determined despite the harsh operating conditions.
- a method according to claim 2 ensures the increased performance and economy of the track construction machine.
- the position of the Stopfaggregats, especially in the vertical direction, can be detected very reliable and robust. Used to move the tamping unit
- Position sensors can be used, eliminating the need to integrate additional sensors.
- the detection of the acceleration is thus particularly economical.
- the position can be detected on the drive device.
- the position can also be detected on a bearing device, by means of which the tamping unit is mounted relative to the unit carrier.
- the position can be determined by means of a position sensor, in particular a
- Position encoder or a rotary encoder in the form of a potentiometer or a Hall sensor or a rope length sensor are detected.
- the time profile of the position can be differentiated by means of an evaluation unit according to time, or the change in position can be determined over a discrete time step.
- the acceleration is determined as a temporal change of the speed.
- the position and thus the acceleration are detected relative to the unit carrier. Taking into account the gravitational acceleration, the absolute
- a method according to claim 3 ensures the increased performance and economy of the track construction machine. Taking into account the inertial force dependent on the mass, the ballast force can be determined particularly accurately.
- the mass of the tamping unit can be weighed prior to installation in the track-laying machine or on the track-laying machine.
- the mass of the Stopfaggregats can be determined in the reset position by detecting the driving force. In the unaccelerated state, the weight and thus the mass of the Stopfaggregats can be determined by the driving force.
- a method according to claim 4 ensures the increased performance and economy of the track construction machine.
- Drive device is robust in operation and ensures the provision of necessary for the processing of the track bed power. Determining the driving force by detecting at least one fluid pressure acting on the drive device can be particularly robust. By using necessary for the pressure control pressure sensors can be used.
- the drive device preferably has at least one hydraulic cylinder and / or at least one pneumatic cylinder.
- a guided within the respective cylinder piston is with a
- Piston rod connected and has a piston rod facing the piston ring surface and one of the piston ring surface opposite
- the detection of the fluid pressure is effected by detecting a piston pressure acting on the piston surface and / or a piston ring pressure acting on the piston ring surface.
- a method according to claim 5 ensures the increased performance and economy of the track construction machine.
- the tamping unit in particular the at least two tamping picks, the drive device and the bearing device, heavily stressed mechanically.
- the ballast force is essential for the stress of the tamping unit.
- Stopfaggregats between the return position and the engaged position varies greatly acting on the tamping ballast power.
- the stress of the tamping aggregate is determined via at least one tamping cycle.
- a stuffing cycle involves displacing the stuffing assembly from the return position to the engaged position and back from the engaged position to the return position.
- the load on the tamping unit can also be maintained over the entire service life of the tamping unit
- Stopfaggregats be determined.
- the stress on the tamping unit in particular the at least two tamping picks, is determined at least over the duration of a tamping cycle, in particular over a plurality of tamping cycles, and in particular over the entire service life.
- the temporal course of the ballast force also provides conclusions about the dynamic load of the tamping unit. With knowledge of the dynamic load, maintenance cycles can be optimized and maintenance costs reduced.
- a method according to claim 7 ensures the increased performance and economy of the track construction machine.
- the ballast force varies within and between different stuffing cycles. It was recognized that for the stress of the tamping aggregate the ballast force amplitudes, that is the amplitudes of the changing ballast force, are of essential importance.
- the time course of the ballast force between a first and a second measuring point can be detected, wherein the ballast force to the first and to the second measuring point is the same size and wherein the second measuring point is determined by the first-time re-reaching this ballast force.
- the ballast force amplitude is called
- a method according to claim 8 ensures the increased performance and economy of the track construction machine.
- Load collective is the cumulative frequency of the ballast force amplitudes determined.
- the bandwidth of the occurring ballast force amplitudes is first divided into ballast force amplitude sections.
- the frequency of the occurring and in the respective ballast force amplitude section falling ballast force amplitude can be counted.
- the load collective thus provides information about the height and frequency of the alternating stress acting on the tamping unit. The load collective is therefore particularly suitable for evaluating the dynamic stress acting on the tamping unit.
- a method according to claim 9 ensures the increased performance and economy of the track construction machine.
- the ballast work is transferred between the tamping unit and the track bed.
- the ballast work correlates with the stress of the tamping unit.
- the stress of the tamping aggregate can be determined particularly efficiently.
- the ballast force and the position can each be determined after certain time steps. Subsequently, the change in position over this time step can be multiplied by the ballast force, in particular the mean ballast force over this time step. Alternatively, the ballast force can also be integrated via the position.
- a method according to claim 10 ensures the increased
- the stress acting on the tamping unit can be compared with a maximum permissible load.
- a prognosis can be made as to how long the tamping unit can still be operated before a failure occurs, in particular before individual parts of the tamping unit fail.
- the state of wear may also indicate the need for maintenance work, in particular replacement of the
- Tamping unit to be closed. With knowledge of the wear condition can the track construction machine, in particular the tamping, under
- a method according to claim 11 ensures the increased performance and economy of the track construction machine.
- Possible process parameters are, for example, a frequency and / or an amplitude of the vibration and / or displacement component transmitted to the at least one tamping pick, an adjustment speed of the tamping unit between the return position and the engagement position, the acceleration of the tamping aggregate and the fluid pressure acting on the drive device ,
- the at least one process parameter can be adjusted as a function of the track bed to be processed and the stress resulting from the nature of the respective track bed.
- Stopfaggregat acting stress can be optimized.
- a method according to claim 12 ensures the increased performance and economy of the track construction machine.
- the at least one process parameter when a threshold value of the stress is exceeded both an overuse of the tamping aggregate and a too low processing speed of the track bed can be counteracted.
- the at least one process parameter when a threshold value of the stress is exceeded both an overuse of the tamping aggregate and a too low processing speed of the track bed can be counteracted.
- the at least one process parameter can be changed so that the stress increases. It is advantageously achieved by a difference between the upper and the lower threshold that the at least one
- a method according to claim ⁇ 3 ensures the increased performance and economy of the track construction machine.
- the stress limit value may be a static and / or dynamic, in particular experimentally determined, strength value of the tamping aggregate, in particular of individual parts of the tamping aggregate.
- the at least one process parameter can be continuously changed based on the stress, or the change can be made in discrete steps. For example, an oscillation frequency of the at least two stuffing picks can be changed continuously between 30 Hz and 50 Hz. Alternatively, the
- the tamping unit can be operated in the first and in the second mode, which can be switched on the basis of the load between the first mode and the second mode.
- Stopfaggregat can be operated in more than two modes of operation. Each mode of operation differs from another mode of operation in at least one process parameter.
- ballast force and / or the stress can also be used to optimize the tamping unit, in particular the kinematics and / or the storage and / or the materials used and / or the structural design.
- the invention is also based on the object to provide a stuffing device for track bed compaction, which has an increased efficiency and cost-effectiveness.
- Stopfvoriques can be further developed in particular with the features of at least one of claims 1 to 13.
- the tamping unit slidably mounted on the unit carrier in the vertical direction.
- the drive device may comprise a hydraulic cylinder.
- the tamping unit preferably comprises at least two, in particular at least four tamping picks.
- the driving force sensor system can have at least one pressure sensor and / or at least one force sensor.
- the acceleration sensor system can have at least one
- Speed sensor and / or at least one position sensor and / or at least one acceleration sensor are provided.
- Position sensor can be designed as a contactless sensor.
- the position sensor can be arranged between the tamping unit and the unit carrier, in particular on the drive device.
- the at least one position sensor is designed as a potentiometer and / or as a Hall sensor and / or as a rope length sensor.
- the invention is further based on the object to provide a track construction machine with a stuffing device, which has an increased efficiency and cost-effectiveness.
- Fig. ⁇ is a schematic representation of a rail-guided
- Fig. 2 is a schematic front view of the stuffing device in Fig. ⁇ , wherein the stuffing device a tamping unit with four
- FIG. 3 is a schematic side view of the stuffing device in Fig. 1, wherein a driving force, an inertial force and a
- Fig. 7 shows a course of a position of the tamping unit, the ballast power and a ballast work over time.
- a track construction machine ⁇ has a machine frame 2, at least two axles 3 mounted on the machine frame 2, a machine drive 4 and a stuffing device 5 for track bed compaction.
- the axles 3 are spaced apart from each other along a horizontal x-direction
- Track-laying machine ⁇ arranged.
- On the axles 3 rail-guided wheels 6 are rotatably mounted.
- the machine drive 2 is designed for rotational driving of the wheels 6 of at least one of the axles 3.
- the stuffing device 5 has an assembly carrier 7 and a tamping unit 8 mounted in the z-direction relative thereto.
- the tamping unit 8 comprises four tamping picks 8a and a compacting drive 8b.
- the tamping picks 8a are each mounted on a stuffing tine carrier 8c and are rotatably mounted on the latter about a carrier axis 8d.
- the compression drive 8b By means of the compression drive 8b, the stuffing tine carriers 8c can be driven in rotation about the respective carrier axis 8d.
- the stuffing device 5 is on the unit carrier 7 on the
- the tamping unit 8 is displaceable relative to the unit carrier 7.
- a linear bearing ⁇ 0 is formed between the unit carrier 7 and the tamping unit 8.
- the linear bearing ⁇ 0 has on the unit carrier 7 mounted bearing rails ⁇ and with the
- Stopfaggregat 8 connected bearing sleeves ⁇ 2 on.
- the stuffing device further comprises a drive device 9.
- Drive device 9 comprises a hydraulic cylinder ⁇ 3.
- Hydraulic cylinder ⁇ 3 acts between the unit carrier 7 and the
- Stopfaggregat 8 In the hydraulic cylinder ⁇ 3 a hydraulic piston ⁇ 4 is mounted linearly displaceable with a piston rod attached thereto ⁇ 5.
- the hydraulic piston ⁇ 4 has a piston ring surface AKR facing the piston rod ⁇ 5 and a piston rod ⁇ 5 facing away from the piston rod
- Piston surface AK on.
- a piston pressure rk of a hydraulic fluid in the hydraulic cylinder ⁇ 3 acts on the piston surface AK.
- a piston ring pressure PKR of the hydraulic fluid acts on the piston ring surface AKR. From the piston pressure rk acting on the piston surface AK and the piston ring pressure PKR acting on the piston ring surface AKR, a total driving force FA transmitted via the piston rod ⁇ 5 to the tamping unit 8 results.
- the stuffing device 1 has a drive force sensor system for detecting a first measured variable rk, PKR, F A corresponding to the drive force F A.
- the driving force sensor includes a piston pressure sensor 16 for detecting the piston pressure rk and a piston ring pressure sensor 17 for detecting the piston ring pressure PKR. FROM acting on the piston surface AK
- Piston ring pressure PKR can be closed to the total acting on the tamping unit 8 via the piston rod 15 driving force F A.
- Driving force F A is calculated as follows:
- the stuffing device 1 has an acceleration sensor system for detecting a second measured variable corresponding to an acceleration a z of the stuffing unit 8, the position z and / or the speed v z .
- the acceleration sensor system is designed in the form of a displacement transducer 18.
- the displacement sensor 18 is on the unit carrier 7 and on the
- the displacement transducer 18 is designed to detect the position z and the speed v z of the tamping unit 8 relative to the unit carrier 7 in the z-direction.
- the tamping device 5 comprises an evaluation unit ⁇ 9.
- the evaluation unit ⁇ 9 is in signal communication with the piston pressure sensor 16, the
- the evaluation unit 19 is in signal communication with a pressure regulator 20.
- the pressure regulator 20 is for controlling the piston pressure rk and the
- Piston ring pressure PKR trained on one setpoint each.
- the respective setpoint for the piston pressure rk and the piston ring pressure PKR is of the
- Evaluation unit 19 can be specified.
- Track construction machine 1 by means of the machine drive 4 on a track 22 along the x-direction procedure.
- a central axis 23 of the stuffing device 5 is thereby positioned centrally above a railway sleeper 24 arranged on the track bed 21 and supporting the tracks 22.
- Stopfaggregat 8 in a reset position 25 The bearing sleeve 12 is located at an upper end of the linear bearing 10 and the piston rod 15 largely immersed in the hydraulic piston 14 a.
- the tamping picks 8a attached to the tamping unit 8 are disengaged from the track bed 21.
- the piston surface AK is at the piston pressure rk, and the piston ring surface AKR is acted upon at the piston ring pressure PKR.
- the evaluation unit 19 the force acting on the tamping unit 8 by the hydraulic piston 14 driving force FA is determined.
- the piston pressure rk is multiplied by the piston area AK and the piston ring pressure PKR by the piston ring area AKR.
- For the driving force FA thus applies:
- Aggregate support 7 and the tamping unit 8 acts only the
- the mass m of the tamping unit is determined in the reset position 25 before starting the operation of the stuffing device 5. Taking into account the in the reset position 25th
- Stopfaggregats 8 The mass m of Stopfaggregats 8 is in a memory element of
- Driving force FA determined.
- the speed v z of the tamping unit 8 relative to the unit carrier 7 in the z direction is first determined as a change in the position z over time t.
- the acceleration a z is again determined as a change in the speed v z over the time t.
- the acceleration a z is thus calculated as follows:
- the drive device is first of all 9 pressed.
- the piston pressure rk is increased and the piston ring pressure PKR is lowered.
- the driving force FA acting on the tamping unit 8 via the piston rod ⁇ 5 is increased counter to the z-direction.
- From the driving force F A results on the tamping unit 8 acting acceleration a z , which is oriented counter to the z-direction and to a rising
- Speed v z of Stopfaggregats 8 leads in the direction of the track bed 2 ⁇ .
- the tamping unit 8 is displaced counter to the z-direction. Contrary to the driving force FA, the amount of inertia force F, which has the same magnitude, acts.
- Ballast force Fs is equal to zero before the tamping pick 8a contacts the track bed 2 ⁇ .
- Reset position 25 and the engagement position 27 takes place in the delivery phase 28.
- the reset phase 29 connects.
- the tamping unit 8 is moved back from the engagement position 27 via the feed position 26 in the return position 25.
- the drive device 9 is actuated in such a way that the piston pressure rk is reduced and the piston ring pressure PKR is increased.
- the hydraulic cylinder ⁇ 3 thus causes the driving force FA, which is now oriented in the z-direction.
- the tamping unit 8 is due to the driving force FA in the z direction
- the acceleration a z is oriented in the z direction and results in a speed v z increasing in the z direction and the displacement of the tamping unit 8 in the z direction.
- the ballast force Fs acts on the Stopfaggregat 8.
- the delivery position 26 and the return position 25 act only the
- Compression drive 8b the tamping pickup carrier 8c substantially in the horizontal direction, whereby the stuffing tine carrier 8c and the tamping pickles 8a attached thereto rotate about the respective carrier axis 8d.
- the movement of the tamping picks 8a about the respective carrier axis 8d essentially comprises two components of movement.
- a vibration component causes only a small rotational amplitude of the tamping picks 8a about the respective carrier axis 8d, wherein an oscillation frequency fs is between 35 Hz and 45 Hz.
- the vibration component acts on the tamping picks 8a during the entire tamping cycle.
- the displacement component has a higher rotational amplitude than the vibration component and a
- Displacement frequency of about 0.5 Hz.
- the tamping picks 8a are thereby rotated about the respective carrier axis 8d such that the stuffing tacks 8a, which are spaced apart from one another in the x-direction, move towards one another.
- the displacement component is oriented in such a way that the tamping picks 8a move away from each other again.
- the loading of the tamping picks 8a with the displacement component follows in the displacement phase 30.
- Displacement component is the compression of the track bed 2 ⁇ .
- Ballast force Fs determined.
- the ballast force Fs is a temporally variable, oscillating load.
- the ballast force amplitude S Fs is determined as the difference of a maximum ballast force Fs and a minimum ballast force Fs within a vibration.
- the cumulative frequency N Fs of the respective ballast force amplitude S Fs is determined.
- a load collective is determined on the basis of the cumulative frequency N Fs .
- Fig. 6 is a curve of the ballast force amplitude S Fs above the
- a state of wear of Stopfaggregats 8 is determined. The state of wear is determined both for individual parts of the tamping unit 8, such as the tamping picks 8a, the drive device 9 and the linear bearings 10, as well as for the entire tamping unit 8.
- Process parameters p K , PKR, fs set to operate the Stopfaggregats 8 by means of the evaluation unit 19.
- the evaluation unit 19 is in signal communication with the compression drive 8b for controlling the oscillation frequency fs and with the pressure regulator 20 for controlling the piston pressure rk and the piston ring pressure PKR.
- a threshold value SW of the load is exceeded, the at least one process parameter p K , PKR, fs is changed.
- the ballast force F s is compared with the threshold SW for this purpose, wherein the at least one
- Process parameter p K , PKR, fs is changed when exceeding an upper threshold SWi such that the ballast force Fs is reduced, wherein when falling below a lower threshold SW2 the at least one process parameter p K , PKR, fs is changed such that the ballast force F s is increased.
- the ballast force Fs is increased by increasing the oscillation frequency fs and by reducing the pressure difference between the Piston pressure rk and the piston ring pressure PKR reduced and increased in the opposite manner.
- the process parameters p K PKR, fs are changed by means of the evaluation unit ⁇ 9 to the effect that an optimum between a low stress of the stuffing 5 and a high processing speed of the track bed 2 ⁇ takes place.
- ballast work Ws is determined from the ballast force Fs and a change in the position z of the tamping unit 8.
- Ballast work W s corresponds to the work brought into the track bed 21 via the tamping picks 8a.
- the change in the position z is recorded over a discrete time period. This change in position z is then multiplied by the ballast force Fs.
- the ballast work Ws is determined as the sum of the products of the ballast force Fs and the changes of the positions z.
- Ballast work Ws for a stuffing cycle over the time t applied Ballast work Ws for a stuffing cycle over the time t applied.
- the gravel work Ws can also be considered the area under the course of
- Ballast force Fs above the position z are understood.
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- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Machines For Laying And Maintaining Railways (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ATA493/2017A AT520791B1 (de) | 2017-12-21 | 2017-12-21 | Verfahren zum Betreiben eines Stopfaggregats einer Gleisbaumaschine sowie Stopfvorrichtung zur Gleisbettverdichtung und Gleisbaumaschine |
PCT/EP2018/081932 WO2019120829A1 (de) | 2017-12-21 | 2018-11-20 | Verfahren zum betreiben eines stopfaggregats einer gleisbaumaschine sowie stopfvorrichtung zur gleisbettverdichtung und gleisbaumaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3728736A1 true EP3728736A1 (de) | 2020-10-28 |
Family
ID=64559655
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18811471.4A Pending EP3728736A1 (de) | 2017-12-21 | 2018-11-20 | Verfahren zum betreiben eines stopfaggregats einer gleisbaumaschine sowie stopfvorrichtung zur gleisbettverdichtung und gleisbaumaschine |
Country Status (7)
Country | Link |
---|---|
US (1) | US11834794B2 (de) |
EP (1) | EP3728736A1 (de) |
JP (1) | JP7206278B2 (de) |
CN (1) | CN111479965B (de) |
AT (1) | AT520791B1 (de) |
EA (1) | EA202000146A1 (de) |
WO (1) | WO2019120829A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102020201689A1 (de) | 2020-02-11 | 2021-08-12 | Robel Bahnbaumaschinen Gmbh | Bearbeitungsanlage und Verfahren zum Durchführen von Gleisarbeiten |
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JPS5842321B2 (ja) * | 1975-06-14 | 1983-09-19 | 芝浦メカトロニクス株式会社 | ドウシヨウシメカタメソウチ |
AT400162B (de) * | 1990-02-06 | 1995-10-25 | Plasser Bahnbaumasch Franz | Verfahren und gleisbaumaschine zur messung des querverschiebewiderstandes |
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GB0714379D0 (en) * | 2007-07-21 | 2007-09-05 | Monition Ltd | Tamping bank monitoring apparatus and method |
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AT518195B1 (de) | 2016-01-26 | 2017-11-15 | Plasser & Theurer Export Von Bahnbaumaschinen Gmbh | Verfahren zur Verdichtung der Schotterbettung eines Gleises sowie Stopfaggregat |
AT518072B1 (de) * | 2016-04-29 | 2017-07-15 | Hp3 Real Gmbh | Stopfaggregat für eine Gleisstopfmaschine |
AT520056B1 (de) * | 2017-05-29 | 2020-12-15 | Plasser & Theurer Export Von Bahnbaumaschinen Gmbh | Verfahren und Vorrichtung zum Verdichten eines Gleisschotterbetts |
CN107227661B (zh) * | 2017-06-12 | 2018-10-23 | 东北大学 | 一种液压捣固机的激振与捣固装置及参数确定方法 |
-
2017
- 2017-12-21 AT ATA493/2017A patent/AT520791B1/de active
-
2018
- 2018-11-20 US US16/763,133 patent/US11834794B2/en active Active
- 2018-11-20 CN CN201880081399.7A patent/CN111479965B/zh active Active
- 2018-11-20 JP JP2020534408A patent/JP7206278B2/ja active Active
- 2018-11-20 WO PCT/EP2018/081932 patent/WO2019120829A1/de unknown
- 2018-11-20 EP EP18811471.4A patent/EP3728736A1/de active Pending
- 2018-11-20 EA EA202000146A patent/EA202000146A1/ru unknown
Also Published As
Publication number | Publication date |
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EA202000146A1 (ru) | 2020-09-11 |
JP7206278B2 (ja) | 2023-01-17 |
AT520791B1 (de) | 2020-08-15 |
US20200392672A1 (en) | 2020-12-17 |
CN111479965A (zh) | 2020-07-31 |
CN111479965B (zh) | 2022-08-26 |
JP2021507151A (ja) | 2021-02-22 |
WO2019120829A1 (de) | 2019-06-27 |
AT520791A1 (de) | 2019-07-15 |
US11834794B2 (en) | 2023-12-05 |
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