EP4031712A1 - Machine et procédé de stabilisation de voie - Google Patents

Machine et procédé de stabilisation de voie

Info

Publication number
EP4031712A1
EP4031712A1 EP20757854.3A EP20757854A EP4031712A1 EP 4031712 A1 EP4031712 A1 EP 4031712A1 EP 20757854 A EP20757854 A EP 20757854A EP 4031712 A1 EP4031712 A1 EP 4031712A1
Authority
EP
European Patent Office
Prior art keywords
track
machine
rotation
unbalanced
drive
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.)
Granted
Application number
EP20757854.3A
Other languages
German (de)
English (en)
Other versions
EP4031712B1 (fr
Inventor
Josef HOFSTÄTTER
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Plasser und Theurer Export Von Bahnbaumaschinen GmbH filed Critical Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Publication of EP4031712A1 publication Critical patent/EP4031712A1/fr
Application granted granted Critical
Publication of EP4031712B1 publication Critical patent/EP4031712B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • E01B27/20—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
    • 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
    • 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
    • B06B1/186—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with rotary unbalanced masses

Definitions

  • the invention relates to a machine for stabilizing a track, with a machine frame supported on rail bogies and a height-adjustable stabilization unit that can be rolled off by unit rollers on rails of the track and that has a vibration exciter with rotating unbalanced masses to generate a dynamically acting in a track plane normal to a track longitudinal direction Includes impact force and a height drive for generating an effective load on the track.
  • the invention also relates to a method for operating such a machine.
  • the compaction effect is determined by several parameters, including
  • Compaction frequency, vibration amplitude, vertical load and dynamic impact force The frequency is limited by the material behavior of the ballast to the range of about 32-38 Hz. In this area the ballast bed shows the optimal behavior.
  • 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 bogies are lowered onto a track to be stabilized via a height adjustment and a vertical load is applied. Over aggregate rollers and on the outside of the rail heads adjacent pincer rolls, a transverse oscillation of the stabilization units is transmitted to the track with continuous forward movement.
  • the stabilization unit includes adjustable unbalanced masses in order to reduce the impact force quickly to a reduced value or to zero if necessary (e.g. in the case of fixed structures such as bridges or tunnels) and to increase it to the original value immediately after reaching a section of track to be stabilized.
  • the invention is based on the object of providing a significant improvement in the economic efficiency in operation, based on the maintenance effort, compared to the prior art for a machine of the type mentioned above by means of the simplest possible, robust construction of the stabilization unit.
  • a method for compacting the ballast bed of the track superstructure carried out by means of the machine is to be specified.
  • the invention provides that a main unbalance mass and a
  • At least one main unbalanced mass and at least one secondary unbalanced mass are assigned to a rotating shaft, the main unbalanced mass being firmly connected to the shaft.
  • This shaft-hub connection is designed with a positive, non-positive or material fit.
  • the secondary unbalance mass is mounted in such a way that it can be freely rotated in a defined angular range.
  • This defined angular range is determined depending on the direction of rotation of the drive and thus results in two possible phase shifts with different amounts between the main unbalance mass and the associated auxiliary unbalanced mass, with end stops in the respective direction of rotation determining the position of the main unbalanced mass relative to the auxiliary unbalanced mass.
  • a main unbalanced mass and an associated secondary unbalanced mass about the same axis of rotation are referred to as an unbalanced mass pair.
  • the main components of the stabilization unit in its simplest possible construction, are a rotating shaft and an unbalanced mass pair, consisting of a main unbalanced mass and a secondary unbalanced mass.
  • the secondary unbalanced masses are carried along by the main unbalanced masses in a form-fitting manner, thus purely passively by so-called drivers. It is structurally possible to design these drivers as independent components, but the driver function can also be integrated in a single component by appropriately designing the main unbalanced masses. This special shape or geometric arrangement of the drivers results in a predefined angular range in which the secondary unbalanced masses can rotate freely between the end stops.
  • the stabilization unit comprises two counter-rotating, coupled via gearwheels Rotary shafts and the imbalance mass pairs associated with each shaft.
  • the force vectors in the machine housing are added or subtracted. It is usually provided that all centrifugal force components subtract in the vertical direction, thus cancel out, while the centrifugal force components add in the horizontal direction, thus the resulting maximum possible total impact force is achieved in the horizontal effective direction. This results in at least two impact forces of different magnitude in order to be able to change the impact force acting on the track in a targeted manner.
  • the respective unbalanced mass is arranged on the stabilization unit with an axis of rotation aligned in the longitudinal direction of the track.
  • This alignment is particularly suitable for use in a stabilization unit, since the resulting impact force acts on the track to be stabilized normal to the longitudinal direction of the track. In this way, optimal energy input into the track is given.
  • the unbalanced mass pairs each comprising a main unbalanced mass and a secondary unbalanced mass about the same axis of rotation.
  • the unbalanced mass pairs can be arranged in series on a rotating shaft.
  • the respective drives are controlled by means of a common control device.
  • the individual drives can be optimally coordinated with one another and controlled precisely.
  • a phase synchronization of the non-coupled stabilization units can ensure either co-oscillating or counter-oscillating operation. This is particularly advantageous for controlling the 8 different impact forces mentioned above.
  • At least two stabilization units are operated coupled on one machine, for example via a cardan shaft.
  • a common drive enables a very compact structure of the overall arrangement.
  • the drives are designed as hydraulic actuators. This means that the drives can be integrated into an existing hydraulic system of the machine.
  • the respective drives are designed as electrical actuators. Particularly in the case of new machine concepts that provide for a modern and more efficient overall operation with supply via accumulators or overhead lines, a meaningful integration is possible.
  • the method according to the invention for operating a machine provides that at least one stabilization unit is set down on the track via a vertical drive and subjected to a load and that at least one unbalanced mass pair is driven via a rotary shaft with a reversible direction of rotation. This ensures a track stabilization that can be adapted to the local conditions with a variable impact force.
  • an increase in the drive power of a drive of the stabilization unit is regulated via a so-called soft start.
  • a pre-defined, increasing ramp course is stored in a higher-level controller, which enables a targeted start-up within a defined period of time in order to avoid jolts in the end stops of the unbalanced masses.
  • a further development of the method enables a variable adjustment of the impact force in the range between selectable impact force levels by changing the speed of the respective, associated drive. This offers the operator great flexibility and precision in track stabilization.
  • FIG. 1 Side view of a machine for stabilizing a track Fig. 2 Stabilization units independent, with their own drive Fig. 3 Stabilization units coupled, with a common drive Fig. 4 Detailed views of a stabilization unit / sectional views Intermediate area
  • ballast 1 shows a simplified machine 1 for stabilizing a track 3 resting on ballast 2, which includes a machine frame 6 supported on rails 5 by rail bogies 4. Between the two rail bogies 4 positioned at the ends, two stabilization units 7 are arranged one behind the other in the longitudinal direction 8 of the track. These are each connected to the machine frame 6 in a vertically adjustable manner by means of flea drives 9.
  • a measuring system 27 for detecting the rail geometry is attached to the machine frame 6.
  • a control device 26 is set up for processing the data received from the measuring system 27, as well as for determining the setting parameters for operating and controlling the stabilization units 7, the elevation drives 9 and the drives 13.
  • FIG. 1 depicts independent, non-coupled stabilization units 7 with their own drives 13.
  • FIGS. 2 and 3 show possible designs with both coupled and uncoupled stabilization units 7.
  • each stabilizing unit 7 can be brought into engagement with the track 3 in a form-fitting manner in order to set it to vibrate at a desired oscillation frequency.
  • the aggregate rollers 10 comprise two flange rollers for each rail 5, which roll on the inside of the rail 5, and a pincer roll which is pressed against the rail 5 from the outside by means of a pincer mechanism 11 during operation.
  • a vertical static load is applied to the track 3 by the flea drives 9.
  • the drives 13 of the stabilization unit 7 are connected to a common supply device 25.
  • this is, for example, a motor-generator unit with feed from an electrical storage device.
  • An overhead line can also be used to supply electrical drives 13 if the machine 1 has current collectors and corresponding converters. If hydraulic drives 13 are used, then the supply device 25 is expediently integrated into a hydraulic system of the machine 1.
  • FIG. 3 An alternative is shown in FIG. 3 with coupled stabilization units and a common drive.
  • the basic structure of the stabilization units 7 is identical to the embodiment in FIG. 2, the difference here lies in the coupling of the arrangement in the longitudinal direction of the track 8 and the design of the drives 13.
  • the stabilization units 7 are drive-connected together via a connecting shaft 15.
  • the drive 13 and the connecting shaft 14 are only simple.
  • FIG. 4 one of the stabilization units 7 is shown in detail in sectional views.
  • a vibration exciter 17 is arranged within a housing 16 and has a rotary shaft 18 with unbalanced masses arranged thereon on two axes of rotation 21.
  • a main unbalanced mass 19 and a secondary unbalanced mass 20 thereby form a Unbalance mass pair.
  • Each rotary shaft 18 is rotatably supported on both sides in the housing 16 via roller bearings 22.
  • the unbalanced masses 19, 20 are coupled via so-called drivers 24, which are designed here as independent elements.
  • the secondary unbalanced masses 20 are designed to be freely rotatable via sliding bearings on the rotary shaft 18, the main unbalanced masses 19 are firmly connected to the rotary shaft 18 via a feather key connection.
  • FIG. 4 shows two pairs of unbalanced masses axially arranged thereon on each of the rotary shafts 18, that is, two main unbalanced masses 19 each with two secondary unbalanced masses 20.
  • the technically simplest solution is a construction with only one rotary shaft 18 and only one imbalance mass pair arranged on it possible.
  • Fig. 5 shows the direction of rotation-dependent unbalance adjustment via driver 24 schematically.
  • the representations A, B, C, D, E, F, G, H show the angular positions 0 °, 90 °, 180 ° and 270 ° each for both directions of rotation, each representation being composed of an upper and a lower rotary shaft 18.
  • the specified direction of rotation is always related to the upper rotary shaft 18, the lower rotary shaft 18 rotates by mechanical coupling in the opposite direction of rotation.
  • the representations A to D show a clockwise rotation (direction of rotation clockwise) while the representations E to H represent a left-hand rotation (counterclockwise direction of rotation).
  • the structure in illustration A (angular position 0 °) comprises the upper, clockwise rotating shaft 18 with a pair of unbalanced masses arranged on it.
  • the main unbalanced mass 19 with associated drivers 24 (finely hatched) causes a centrifugal force F1 from the pivot point in the vertical direction
  • the secondary unbalanced mass 20 with associated drivers 24 (roughly hatched) also causes a centrifugal force F3 from Pivot point off in the vertical direction.
  • the sum of the two centrifugal forces F1 and F3 gives the total centrifugal force Fgesl.
  • the changed direction of rotation results in a different angular position of the two unbalanced masses 19, 20 with respect to one another.
  • the flaunt unbalance mass 19 with associated drivers 24 (finely hatched) causes a centrifugal force F1 from the pivot point in the vertical direction upwards
  • the secondary unbalance mass 20 with associated drivers 24 (roughly hatched) causes a centrifugal force F3 from the pivot point in the vertical direction downwards.
  • the sum of the two centrifugal forces F1 and F3 results in the total centrifugal force Ftot2.
  • the range between the impact force levels can now be compensated for by changing the speed of the respective associated drive 13 within a very narrow frequency band.
  • a so-called frequency control funnel (dotted lines) is created when all intermediate areas are passed through completely (lines in thick lines) of the impact force levels S1-S7.
  • the impact force F is shown in% over the abscissa with the frequency f in Flz.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Testing Of Balance (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne une machine (1) de stabilisation d'une voie (3), comprenant un bâti de machine (6) soutenu sur des bogies de rails (4) et au moins un ensemble de stabilisation réglable en hauteur (7), qui peut rouler par l'intermédiaire de rouleaux d'assemblage (10) sur des rails (5) de la voie (3) et qui comprend un générateur d'oscillations (17) ayant des masses non équilibrées rotatives (19, 20) pour produire une force d'impact agissant de manière dynamique dans un plan de voie perpendiculaire à une direction longitudinale de la voie (8) et un entraînement d'élévation (9) pour produire une charge agissant sur la voie (3). Selon l'invention, une masse non équilibrée principale (19) et une masse non équilibrée secondaire (20) provoquent des forces centrifuges différentes à la même vitesse de rotation et en fonction du sens de rotation, les deux masses non équilibrées (19, 20) sont accouplées de manière à ce que, lors de la rotation dans un sens de rotation, les masses non équilibrées présentent un premier décalage de phase l'une par rapport à l'autre et à ce que, lors de la rotation dans le sens de rotation opposé, les masses non équilibrées présentent un second décalage de phase l'une par rapport à l'autre, qui s'écarte du premier décalage de phase. En fonction de l'agencement des masses non équilibrées, un décalage de phase modifié change à la fois la direction et la résistance de la force d'impact.
EP20757854.3A 2019-09-18 2020-08-12 Machine et procédé de stabilisation de voie Active EP4031712B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA297/2019A AT523034A3 (de) 2019-09-18 2019-09-18 Maschine und Verfahren zum Stabilisieren eines Gleises
PCT/EP2020/072626 WO2021052684A1 (fr) 2019-09-18 2020-08-12 Machine et procédé de stabilisation de voie

Publications (2)

Publication Number Publication Date
EP4031712A1 true EP4031712A1 (fr) 2022-07-27
EP4031712B1 EP4031712B1 (fr) 2024-02-14

Family

ID=72145370

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20757854.3A Active EP4031712B1 (fr) 2019-09-18 2020-08-12 Machine et procédé de stabilisation de voie

Country Status (5)

Country Link
US (1) US20220316145A1 (fr)
EP (1) EP4031712B1 (fr)
CN (1) CN114286881A (fr)
AT (1) AT523034A3 (fr)
WO (1) WO2021052684A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT18204U1 (de) * 2022-11-22 2024-05-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stabilisationsaggregat, Schienenfahrzeug und Verfahren zum Stabilisieren eines Gleises

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0092014A1 (fr) * 1982-04-21 1983-10-26 Losenhausen Maschinenbau AG& Co Kommanditgesellschaft Dispositif de réglage pour générateur de vibrations à masses non équilibrées
DE3410449A1 (de) * 1984-03-22 1985-09-26 Uhde Gmbh, 4600 Dortmund Unwucht-schwingantrieb
DE3806897A1 (de) * 1988-03-03 1989-09-14 Wacker Werke Kg Schwingungserreger
DE4434779A1 (de) * 1994-09-29 1996-04-04 Bomag Gmbh Verfahren und Vorrichtung zum dynamischen Verdichten von Boden
DE10147957B4 (de) * 2001-09-28 2006-11-02 Wacker Construction Equipment Ag Schwingungserreger für eine Bodenverdichtungsvorrichtung
DE10241200A1 (de) * 2002-09-05 2004-03-25 Wacker Construction Equipment Ag Schwingungserreger für Bodenverdichtungsgeräte
DE102005058485A1 (de) * 2005-12-07 2007-06-14 Wacker Construction Equipment Ag Vibrationsplatte mit Stabilisationseinrichtung
WO2008009314A1 (fr) 2006-07-20 2008-01-24 Franz Plasser Bahnbaumaschinen-Industriegesellschaft Mbh Procédé et machine de stabilisation d'une voie
DE102012201443A1 (de) * 2012-02-01 2013-08-01 Hamm Ag Verdichterwalze für einen Bodenverdichter
AT16604U1 (de) * 2018-02-13 2020-02-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Maschine zum Stabilisieren eines Gleises

Also Published As

Publication number Publication date
WO2021052684A1 (fr) 2021-03-25
EP4031712B1 (fr) 2024-02-14
CN114286881A (zh) 2022-04-05
AT523034A2 (de) 2021-04-15
AT523034A3 (de) 2024-02-15
US20220316145A1 (en) 2022-10-06

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