EP3752675B1 - Maschine zum stabilisieren eines gleises - Google Patents

Maschine zum stabilisieren eines gleises Download PDF

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Publication number
EP3752675B1
EP3752675B1 EP19701584.5A EP19701584A EP3752675B1 EP 3752675 B1 EP3752675 B1 EP 3752675B1 EP 19701584 A EP19701584 A EP 19701584A EP 3752675 B1 EP3752675 B1 EP 3752675B1
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EP
European Patent Office
Prior art keywords
machine
track
masses
phase shift
imbalance
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.)
Active
Application number
EP19701584.5A
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German (de)
English (en)
French (fr)
Other versions
EP3752675A1 (de
EP3752675C0 (de
Inventor
Samuel WOLLANEK
Nikolaus MATZINGER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Original Assignee
Plasser und Theurer Export Von Bahnbaumaschinen GmbH
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Publication of EP3752675B1 publication Critical patent/EP3752675B1/de
Publication of EP3752675C0 publication Critical patent/EP3752675C0/de
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Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
    • E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
    • E01B27/20—Compacting the material of the track-carrying ballastway, e.g. by vibrating the track, by surface vibrators
    • 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B2203/00—Devices for working the railway-superstructure
    • E01B2203/12—Tamping devices
    • E01B2203/127—Tamping devices vibrating the track surface

Definitions

  • the invention relates to a machine for stabilizing a track, with a machine frame supported on rail undercarriages and a height-adjustable stabilization unit that can be rolled on rails of the track by unit rollers, which has a vibration exciter with rotating unbalanced masses for generating an impact force that acts dynamically in a track plane perpendicular to a longitudinal direction of the track, and a Height drive for generating an effective load on the track includes.
  • the invention relates to a method for operating such a machine.
  • Machines for stabilizing a track are already known several times from the prior art.
  • a so-called dynamic track stabilizer stabilization units located between two rail chassis are lowered onto a track to be stabilized via a height adjustment and subjected to a vertical load.
  • a transverse vibration of the stabilization aggregates is transmitted to the track via aggregate rollers and pincer rollers lying on the outside of the rail heads with continuous advance.
  • the stabilization unit includes adjustable unbalanced masses in order to quickly reduce the impact force to a reduced value or to zero (e.g. in the case of bridges or tunnels) and raise it to the original value immediately after reaching a track section to be stabilized.
  • a disadvantage here is the complex structure of the moving parts.
  • a targeted setting of the required impact force is complex in terms of control technology.
  • Another stabilization unit is off the FR 1347335 A known.
  • transversely vibrating exciters can be driven out of phase with one another in order to vary the vibration effect on the track.
  • the CN 106592349A discloses a stabilization unit with an adjustable vibration exciter. This vibration exciter includes rotatable unbalanced masses, the phase position of which can be changed in relation to one another. In this way, the impact force of the vibration exciter can be adjusted.
  • the invention is based on the object of specifying an improvement over the prior art for a machine of the type mentioned at the outset. Another object is to present a method for operating such a machine.
  • the invention provides that the vibration exciter has at least four imbalance masses that can be driven with variably adjustable phase shifts. Due to the variably adjustable phase shift, the impact force acting on the track can be changed in a targeted manner. Depending on the arrangement of the unbalanced masses, a changed phase shift changes both the direction and the strength of the impact force.
  • a counterclockwise unbalanced mass and a clockwise rotating unbalanced mass form an unbalanced mass pair, wherein at least one unbalanced mass of this respective unbalanced mass pair can be driven with a first phase shift that can be variably adjusted compared to an initial position.
  • the unbalanced masses move against each other so that their centrifugal forces cancel each other out in one direction and an undesirable directional component of the impact force is thus eliminated.
  • each imbalance mass is assigned an angle sensor.
  • the respective angle encoder are the positions of Imbalance masses are always precisely known.
  • a predefined phase shift can be set by means of a control device. This is particularly useful for mechanical drives such as hydraulic motors.
  • the respective unbalanced mass is arranged on the stabilization unit with an axis of rotation aligned in the longitudinal direction of the track.
  • This orientation is particularly suitable for use in a stabilization unit, since the resulting impact force acts on the track to be stabilized perpendicular to the longitudinal direction of the track. In this way, an optimal energy input into the track is given.
  • each unbalanced mass is assigned its own drive.
  • a separate drive for each unbalanced mass offers a structurally simple solution for being able to control each unbalanced mass in a targeted manner with its own angular position.
  • a simplified further development of the invention provides that a common drive is assigned to two unbalanced masses in each case.
  • This solution is particularly suitable for compact stabilization units, with the phase shift being adjusted, for example, by means of a variable coupling.
  • the respective drive is designed as an electric drive.
  • brushless electric motors or torque motors are particularly well suited for activation in an angle loop to achieve the desired phase shift.
  • the electric drives are controlled by means of a common control device.
  • the individual drives can be optimally coordinated and precisely controlled.
  • data previously stored in the control device can be accessed in order to automatically adapt the electric drives and a phase shift to local conditions and an actual condition of the track.
  • the respective drive is designed as a hydraulic drive. Through this the drives can be integrated into an existing hydraulic system of the machine.
  • an adjusting device for a variable phase shift is assigned to the respective drive.
  • the adjusting device is particularly suitable for mechanical drives in order to set an exact phase shift.
  • the respective unbalanced mass is rotated in a simple manner relative to the drive at the required angle.
  • the adjustment device for setting the phase shift can also be used when driving two unbalanced masses with a common drive.
  • the vibration exciter has at least four rotatable unbalanced masses, of which two unbalanced masses can be driven in a clockwise direction and two unbalanced masses can be driven in a counter-clockwise direction.
  • the two counterclockwise unbalanced masses can be driven relative to one another with a variably adjustable second phase shift
  • the two clockwise unbalanced masses can be driven relative to one another with a variably adjustable second phase shift.
  • the impact force resulting from all unbalanced masses can be optimally adjusted in relation to the track level in order to precisely adapt the stabilization of the track to local conditions.
  • the method according to the invention for operating a machine provides that the stabilization unit is set down on the track via the vertical drive and subjected to an additional load and that at least four rotatable unbalanced masses are driven relative to one another with variably adjustable phase shifts. This ensures track stabilization that can be precisely adapted to the local conditions with a changeable impact force.
  • an unbalanced mass pair an unbalanced mass is driven counterclockwise and an unbalanced mass is driven clockwise, with at least one of these unbalanced masses is driven with a first phase shift that can be variably adjusted in relation to an initial position.
  • the sinking of the track during stabilization can be increased if necessary.
  • two counterclockwise unbalanced masses are driven relative to one another with a variably adjustable second phase shift, and two right-hand rotating unbalanced masses driven to each other with a variably adjustable second phase shift. This ensures a quick and precise adjustment of the impact force in the preferred direction of action.
  • ballast 1 shows a machine 1 for stabilizing a track 3 resting on ballast 2, which comprises a machine frame 6 supported on rails 5 by rail chassis 4.
  • Two stabilization units 7 are arranged one behind the other in the longitudinal direction 8 of the track between the two end-positioned rail carriages 4 . These are each connected to the machine frame 6 in a height-adjustable manner by height drives 9 .
  • each stabilization unit 7 can be positively engaged with the track 3 in order to cause it to vibrate at a desired vibration frequency.
  • the aggregate rollers 10 comprise two wheel flange rollers, which roll on the inside of the rail 5, and a pincer roller which, during operation, is pressed against the rail 5 from the outside by means of a pincer mechanism 33.
  • a static vertical load is applied to the track 3 by the height drives 9 .
  • the stabilization units 7 are controlled by means of a common control device 31 .
  • Drives 19 arranged in the stabilization unit 7 are connected to a common supply device 32 .
  • this is a motor-generator unit with an electric storage device.
  • An overhead line can also be used to supply electric drives if the machine has 1 pantograph and corresponding converter.
  • the supply device 32 is usefully integrated into a hydraulic system of the machine 1.
  • a vibration exciter 12 is arranged inside a housing 11 and comprises four rotary shafts 13 with unbalanced masses 14 arranged thereon. Two rotary shafts 13 are arranged on each of two rotary axes 15 . An unbalanced mass 14 is arranged on each rotary shaft 13 . Each rotary shaft 13 is rotatably mounted on both sides next to the unbalanced mass 14 in the housing 11 via roller bearings 16 .
  • a toothing 17 is milled into one end of the respective rotary shaft 13 protruding from the housing 11 , on which a rotor 18 of a drive 19 designed as a torque motor is positively connected to the associated rotary shaft 13 .
  • a stator 20 is arranged around the rotor 18 of the respective torque motor and is connected to the housing 11 of the vibration exciter 12 via a motor housing 21 . Cooling fins 22 are arranged outside of the motor housing 21 . As a result, heat generated during operation can be reliably dissipated.
  • the stabilization unit 7 is connected to a stabilization unit frame 23 in order to transmit vibration to the unit/pincer rollers 10 and thus to the track 3 reliably.
  • Unbalanced masses 14 shown can be driven independently of one another with freely definable phase shifts between the individual unbalanced masses 14.
  • the use of four identical drives 19, rotary shafts 13 and unbalanced masses 14 leads to easier exchangeability and spare parts supply in the event of maintenance or damage.
  • Both unbalanced masses 14 can be driven at a predetermined speed, which determines the vibration frequency transmitted to the track 3. In exceptional cases, it can make sense for the two unbalanced masses 14 to be able to be driven at different speeds in order to bring about a continuous change in impact force. Otherwise, all unbalanced masses 14 rotate at the same speed. A change in impact force is only achieved by phase shifts ⁇ 1 , ⁇ 2 , ie by one unbalanced mass 14 running ahead of the other.
  • the four unbalanced masses 14 are shown side by side and with the letters A, B, C and D denoted.
  • Two unbalanced masses A, B or C, D form an unbalanced mass pair 34 which is driven by a common drive 19 .
  • the directions of rotation 30 of the two unbalanced masses A, B or C, D are opposite.
  • the unbalanced masses A and C can be driven counterclockwise and the unbalanced masses B and D can be driven in a clockwise direction.
  • two unbalanced masses A, C or B, D can be arranged on a common axis of rotation 15 .
  • a reversing gear 24 is arranged in each case.
  • the two unbalanced masses A, C and B, D rotating in the same direction can be driven by means of a common drive 19 .
  • no reversing gear 24 is required.
  • An adjusting device 25 is arranged for setting a phase shift between the unbalanced masses 14 driven by means of a common drive 19 ( figure 5 ).
  • a first phase shift ⁇ 1 can be set in relation to an initial position in the case of the imbalance masses 14 which can be driven in opposite directions of rotation.
  • a second phase shift ⁇ 2 can be set for the unbalanced masses 14 rotating in the same direction.
  • each drive 19 can be controlled as a function of the angle of rotation, or an adjusting device 25 is arranged between each drive 19 and the associated unbalanced mass 14 .
  • figure 5 shows, for example, a mechanical adjusting device 25 for rotating the rotary shaft 13 of the unbalanced mass 14 relative to a drive shaft 26 of the drive 19.
  • the rotary shaft 13 has at least one helically running groove 28, in which an inner counterpart of the sleeve 27 is engaged.
  • the sleeve 27 and the rotary shaft 13 are rotatably connected to one another via a hydraulic cylinder 29 . If a longitudinal displacement of the sleeve 27 relative to the rotary shaft 13 is brought about by means of the hydraulic cylinder 29, the rotary shaft 13 together with the unbalanced mass 14 rotates at the desired angle relative to the drive shaft 26. By twisting the rotary shaft 13 relative to the drive shaft 26, a phase shift occurs relative to another unbalanced mass 14 ⁇ 1 , ⁇ 2 is reached.
  • the mechanical adjusting device 25 is particularly suitable in combination with uniformly driven hydraulic motors.
  • An angle sensor 35 is advantageously used here in order to receive feedback on the angular position of the respective drive shaft 26 or rotary shaft 13 .
  • Even with a simplified solution as in 3 the arrangement of an adjusting device 25 between the unbalanced masses 14 provided with a common drive 19 makes sense in order to achieve a phase shift ⁇ 1 , ⁇ 2 between the two unbalanced masses 14 .
  • a rotary shaft 13 is formed with an outer unbalanced mass 14 as a hollow shaft.
  • a free end of the other rotary shaft 13 with an inner unbalanced mass 14 is mounted within the hollow shaft.
  • the rotary shafts 13 are mounted in a housing 11 via additional roller bearings 16 and are driven by their own drives 19 .
  • the centrifugal forces of the rotating unbalanced masses 14 act in a common plane, so that no potentially disruptive tilting moments occur.
  • This storage variant is particularly suitable for a vibration exciter 12 with only two unbalanced masses 14.
  • a second phase shift ⁇ 2 of 60° is set for the second unbalanced mass 14 in the direction of rotation, so that the second unbalanced mass 14 leads the first unbalanced mass 14 by a total of 240°.
  • the maximum impact force Fs is achieved when a second phase shift ⁇ 2 of 180° in the direction of rotation is set for the second unbalanced mass 14 compared to the starting position. Then both unbalanced masses 14 rotate synchronously, so that the centrifugal forces add up ( 9 ).
  • FIG. 10 and 11 Corresponding illustrations are in Figures 10 and 11 shown for two unbalanced masses 14 driven in opposite directions.
  • the impact force component F y in the y-direction is eliminated and the greatest impact force (Fs) occurs in the x-direction ( 10 ).
  • a change in the impact force Fs occurs when a first phase shift ⁇ 1 is set for an unbalanced mass 14 in relation to the starting position.
  • the first phase shift ⁇ 1 of the second unbalanced mass 14 is, for example, 60° in the direction of rotation.
  • the impact force Fs is then reduced.
  • the effective direction of the impact force Fs has an angle of inclination relative to the x-axis which corresponds to half the first phase shift ⁇ 1 .
  • a maximum impact force Fs parallel to the y-axis thus results with a first phase shift ⁇ 1 of 180°.
  • FIGS 12 to 16 are different phase shifts ⁇ 1 , ⁇ 2 for four unbalanced masses A, B, C and D according to Figures 3 and 4 shown.
  • courses of the impact forces F AB , F CD of the pairs of unbalanced masses 34 and the resulting impact force Fs are shown over a common phase angle ⁇ .
  • the positions of the unbalanced masses 14 are shown at a phase angle ⁇ of 90°, 180° and 270°.
  • the set second phase shift ⁇ 2 is equal to 180° ( 7 ).
  • the imbalance masses A, C or B, D that can be driven in the same direction of rotation run synchronously, so that the centrifugal forces add up in the x-direction.
  • the variably adjustable second phase shift ⁇ 2 in the range from 0° to 180°, the resulting impact force Fs in the direction of the x-axis can be precisely adjusted from zero to a maximum.
  • the setting of the impact force Fs in the direction of the y-axis is based on the figures 14 and 15 explained.
  • an unbalanced mass B or D is in relative to the starting position 12 out of phase.
  • a first phase shift ⁇ 1 equal to 180° is set for both pairs of unbalanced masses 34, so that a there is complete cancellation of the resulting impact force Fs ( 14 ).
  • a second phase shift ⁇ 2 equal to 180° is set compared to this new starting position ( 15 ).
  • the control device 31 includes a computing unit in order to set the optimum impact force Fs as a function of a local track condition. Corresponding sensor signals from sensors arranged on the machine 1 or previously determined track data are fed to the control device 31 for this optimization process.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Railway Tracks (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
EP19701584.5A 2018-02-13 2019-01-14 Maschine zum stabilisieren eines gleises Active EP3752675B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT362018 2018-02-13
PCT/EP2019/050767 WO2019158288A1 (de) 2018-02-13 2019-01-14 Maschine zum stabilisieren eines gleises

Publications (3)

Publication Number Publication Date
EP3752675A1 EP3752675A1 (de) 2020-12-23
EP3752675B1 true EP3752675B1 (de) 2023-07-19
EP3752675C0 EP3752675C0 (de) 2023-07-19

Family

ID=65228509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19701584.5A Active EP3752675B1 (de) 2018-02-13 2019-01-14 Maschine zum stabilisieren eines gleises

Country Status (9)

Country Link
US (1) US11891761B2 (pl)
EP (1) EP3752675B1 (pl)
JP (1) JP2021513621A (pl)
CN (1) CN111670284A (pl)
AT (1) AT16604U1 (pl)
CA (1) CA3088341A1 (pl)
EA (1) EA039947B1 (pl)
PL (1) PL3752675T3 (pl)
WO (1) WO2019158288A1 (pl)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN211247232U (zh) * 2019-08-09 2020-08-14 济南豪特创新管理咨询合伙企业(有限合伙) 一种激振装置
AT523034A3 (de) * 2019-09-18 2024-02-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Maschine und Verfahren zum Stabilisieren eines Gleises
AT523228B1 (de) 2019-12-10 2024-06-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Maschine und Verfahren zum Stabilisieren eines Schottergleises
AT525090B1 (de) 2021-08-12 2022-12-15 Hp3 Real Gmbh Verfahren zum Stabilisieren der Schotterbettung eines Gleises
AT18205U1 (de) 2022-11-22 2024-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stabilisationsaggregat zum Stabilisieren eines Gleises
AT18204U1 (de) 2022-11-22 2024-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stabilisationsaggregat, Schienenfahrzeug und Verfahren zum Stabilisieren eines Gleises

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SU96295A1 (ru) 1952-01-18 1952-11-30 Ю.А. Чекменев Курако-грузоуборочна машина
DE1149304B (de) * 1957-04-03 1963-05-22 Losenhausenwerk Duesseldorfer Bodenverdichter mit einem Unwuchtruettler zur Erzeugung gerichteter Schwingungen
FR1347335A (fr) * 1963-01-04 1963-12-27 Procédé et machine pour tasser le ballast du remblai des voies ferrées, notaemment à l'endroit des banquettes, en liaison avec le redressement de la voie, le calage o u le bourrage des traverses ou avec le relèvement et le nivellement de la voie
AT343165B (de) * 1975-01-31 1978-05-10 Plasser Bahnbaumasch Franz Fahrbare schotterbett-verdichtmaschine zur korrektur der gleislage
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DE59600339D1 (de) * 1995-06-16 1998-08-20 Plasser Bahnbaumasch Franz Maschine zum Stabilisieren eines Gleises
SE513571C2 (sv) * 1999-03-18 2000-10-02 Ulf Bertil Andersson Anordning för alstring av mekaniska vibrationer
WO2008009314A1 (de) * 2006-07-20 2008-01-24 Franz Plasser Bahnbaumaschinen-Industriegesellschaft Mbh Verfahren und maschine zum stabilisieren eines gleises
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CN104562873B (zh) * 2014-12-26 2016-10-12 中车北京二七机车有限公司 铁路轨道稳定装置
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CN106592349B (zh) * 2016-12-13 2018-09-21 常州市瑞泰工程机械有限公司 激振力可调的激振部件和采用该部件的稳定装置
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

Also Published As

Publication number Publication date
EP3752675A1 (de) 2020-12-23
EA202000178A1 (ru) 2020-10-27
PL3752675T3 (pl) 2024-02-26
WO2019158288A1 (de) 2019-08-22
US20210071369A1 (en) 2021-03-11
US11891761B2 (en) 2024-02-06
JP2021513621A (ja) 2021-05-27
EA039947B1 (ru) 2022-03-31
CA3088341A1 (en) 2019-08-22
CN111670284A (zh) 2020-09-15
AT16604U1 (de) 2020-02-15
EP3752675C0 (de) 2023-07-19

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