EP0050889A1 - Railway track tamping device - Google Patents

Railway track tamping device Download PDF

Info

Publication number
EP0050889A1
EP0050889A1 EP81201120A EP81201120A EP0050889A1 EP 0050889 A1 EP0050889 A1 EP 0050889A1 EP 81201120 A EP81201120 A EP 81201120A EP 81201120 A EP81201120 A EP 81201120A EP 0050889 A1 EP0050889 A1 EP 0050889A1
Authority
EP
European Patent Office
Prior art keywords
arms
eccentric shaft
support
tamping
articulation
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
EP81201120A
Other languages
German (de)
French (fr)
Other versions
EP0050889B1 (en
Inventor
Yvo Cicin-Sain
Yvan Deliyski
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.)
Matisa Materiel Industriel SA
Original Assignee
Matisa Materiel Industriel SA
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 Matisa Materiel Industriel SA filed Critical Matisa Materiel Industriel SA
Priority to AT81201120T priority Critical patent/ATE9107T1/en
Publication of EP0050889A1 publication Critical patent/EP0050889A1/en
Application granted granted Critical
Publication of EP0050889B1 publication Critical patent/EP0050889B1/en
Expired legal-status Critical Current

Links

Images

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

Definitions

  • the present invention relates to a device for tamping railways comprising a chassis rolling on the track and at least one tamping aggregate disposed on a support movable vertically on the chassis and comprising at least one pair of tamping tools cooperating in opposition and each having an arm to which is attached at least one pick, the tamping aggregate further comprising a rotary eccentric shaft provided with an unbalanced flywheel driven by a motor and rotating in a bearing rigidly connected to the support tools and comprising two eccentric spans on each of which are articulated the arms of a pair of tamping tools for the transmission of oscillating movements to the pickaxes, and extendable connecting members connecting the arms to the support and articulated, on the one hand at points of articulation situated at a distance above the upper ends of the arms and, on the other hand, respectively on each arm and which are arranged so that q that the arms oscillate around their points of articulation at the eccentric shaft.
  • a device of this type is described in patent A T 352 159.
  • the arms of the tamping tools have a bent shape substantially at right angles in the manner of bent levers and the ends of which are opposite to the end stops. articulated to the eccentric spans of a common eccentric shaft.
  • the extendable connecting members are constituted by double-acting hydraulic cylinders oriented approximately vertically and articulated on the one hand in the region of the elbow of each arm of the tamping device and on the other hand to the support of these tools.
  • this machine does not meet all the requirements that one could wish for an optimum result.
  • a horizontal oscillation of the cleats tamping is favorable when the cleats are engaged in the ballast, such an oscillation is not necessarily favorable during the penetration of the cleats in the ballast.
  • the centers of gravity of the two bent arms are relatively very far from the vertical plane of symmetry passing through the axis of the eccentric shaft, which makes it difficult to distribute the moving masses such as the dynamic forces exerted during the rotation of the eccentric shaft on the support are at least approximately neutralized, at least when the tamping device is arranged and works in a tamping machine with one or three crosspieces.
  • the object of the present invention is to produce a tamping device of the type described above, retaining a simple and robust construction, but such that the results of the dynamic forces acting on the support are substantially zero, without additional constructive means, and that simultaneously the jam quality is improved.
  • the tamping device is characterized in that the arms of a pair of tamping tools are constituted by substantially rectilinear levers with two arms and intersect in the vicinity of the eccentric shaft, that said points of articulation are located between the arms and the connecting members, on the side of the eccentric shaft opposite to the picks and that to compensate at least approximately the dynamic forces and moments exerted by the rotation of the eccentric shaft on the support, there is provided, in addition to the unbalance fixed to the flywheel, compensation masses fixed to the connecting members, in the extension of the connecting members, above their points of articulation to the support.
  • Each of the compensation masses is preferably dimensioned and arranged in such a way that a straight rod, of uniform specific weight over its entire length and equivalent, as regards its mass and its arrangement, to the connecting member and to its compensation mass , would exceed the point of articulation of said member connecting to the support, by a third of its length.
  • the cross arrangement of the arms of a pair of tamping tools also makes it possible to bring the center of gravity of the tamping tools to proximity to the vertical plane of symmetry passing through the eccentric shaft or at least approximately in this plane, which also has a favorable effect.
  • the tamping device has the advantage that the trajectories of the oscillations of the end stops are inclined relative to the horizontal when the arms are separated, that is to say when the tamping tools descend on each side of a cross member and sink into the ballast, to gradually adopt a horizontal trajectory when they are in the ballast, for the actual tamping process.
  • the oscillations of the two end stops of a pair are symmetrical if the angle formed by the two planes passing through the axis of rotation of the eccentric shaft and each of the axes of rotation of the two eccentric spans has a well determined angle, for a given geometry, respectively a given configuration of all the points of articulation and rotation of the device, angle which can be calculated.
  • the connecting members connecting the arms of a pair of tamping tools to the support are advantageously oriented at least approximately vertically or are in any case inclined at most 30 ° relative to the vertical, the angle of said planes guaranteeing completely symmetrical and synchronous oscillations of the two picks, is between 40 and 80 0 .
  • the imbalance of the flywheel is then on the bisector of this angle, on the side of the eccentric shaft opposite the sides of this angle.
  • a tamping aggregate generally has two pairs of tamping tools arranged on either side of a rail and compacting the ballast simultaneously under a crosspiece, on each side of the rail attachment.
  • the stability and function of such a tamping aggregate can be further improved by connecting the corresponding arms of two pairs of tamping tools located on opposite sides of a rail by a rigid crossmember fixed in places of the arms opposite to the picks, relative to the eccentric shaft, preferably in the immediate vicinity of the points of articulation of the connecting members.
  • These crosspieces serve simultaneously as a counterweight to the end stops.
  • the tamping device according to the invention can be balanced so well by an adequate distribution of the moving masses, that it is possible to execute it and use it as well in machine with a cross, as in machine with two or three sleepers, no problem with regard to the vibrations transmitted to the support.
  • FIG. 1 which illustrates the geometry of a tamping aggregate comprising two cooperating tamping tools
  • each of the parts, as well as the articulations and the axes of rotation are designated by the same reference numbers as the corresponding elements in the figures 2 and 3.
  • the eccentric shaft or the crankshaft 7, perpendicular to the plane of the drawing, rotating in a bearing 6 rigidly fixed to the support of the device, carries two eccentrics, respectively two journals, the centers of which are designated by 27 and 28.
  • the lines connecting the axis of the shaft 7 and the points 27 and 28 form a fixed angle ⁇ .
  • the connecting members 17 and 18 which are preferably constituted by double-acting hydraulic cylinders, extend at least approximately vertically or are inclined at most 30 0 relative to the vertical and carry compensating masses 31 and 32 fixed to extensions extending at above articulation points 15 and 16. If one replaced each of the connecting members 17 and 18, as well as their balancing mass 31 and 32, by a uniform straight bar, equivalent, of uniform specific weight over all its length, the joints 15 and 16 of these bars would divide these bars in a ratio of 2: 1, that is to say that each bar would exceed the point of articulation 15, respectively 16 by a length equal to half the distance between joints 15 and 19, respectively 16 and 20.
  • Another balancing mass consists of the unbalance 30 of a flywheel fixed on the eccentric shaft 7, this unbalance 30 being offset from the axis 7, on the bisector of the angle ⁇ , in an opposite direction alongside this angle.
  • the upper ends of the levers of the tamping tools 4 and 5 are also rigidly connected respectively to each of the tamping tools of a second pair of tamping tools located respectively on the same side of the cross member 3, but from the other side of the rail, by a cross 33, respectively 34, perpendicular to the plane of the drawing.
  • These crosspieces 33 and 34 serve as a counterweight to the end stops 12 and 13.
  • the tamping tools 4 and 5 are driven in an oscillating movement in a plane parallel to the plane of the drawing.
  • the shortening of the connecting members 17 and 18 allows the arms 4 and 5 to pivot by bringing the end tabs 12 and 13 closer to each other.
  • the tabs 12 and 13 In the position far away from the arms, the tabs 12 and 13 have a trajectory inclined at an angle Lf relatively to the horizontal, which promotes their penetration into the ballast.
  • the inclination of the cleats trajectories gradually decreases as they approach each other to be finally approximately horizontal when the cleats are under the crosspiece, which is particularly favorable for obtaining good packing.
  • the angleo is first determined (between the radii, respectively the planes passing through the axis 7 and the centers of the two eccentrics 27 and 28, for which angle the two end stops 12 and 13 oscillate in a completely synchronous and symmetrical manner with respect to the vertical plane of symmetry passing through the axis of the eccentric shaft 7. It turns out that this important and essential condition for the quality of the stuffing is generally satisfied only for a determined angle ⁇ which is unique for a given configuration of the points of rotation and of articulation.
  • This angle varies as a function of the geometry of the points of rotation and of articulation, but in the case considered, in which the inclination of the connecting members 17 and 18 relative to the vertical does not exceed 30 °, the angle ⁇ is between 40 ° and 80 0 , for example 53 ° in a typical case.
  • the tamping devices according to the invention could be used without other as well as a machine with a cross, as a machine with two or three cross, that is to say stuffing under one, respectively two or three sleepers simultaneously, no problem with vibration of the support.
  • FIGS. 1 and 2 a packing aggregate mounted, adjustable in height, on a frame 1 capable of moving on rails 2.
  • This packing aggregate has, on either side of each of the rails 2, only one of which is shown in FIG. 3, a pair of tamping tools 4, 5, respectively 4 ′, 5 ′, attached to an eccentric shaft 7 rotating in a bearing 6.
  • the tamping tools 4 and 5 of the same pair which can be seen in Figure 2 and which appear partially hidden in the right part of Figure 3, each consist of an arm 8, respectively 9 to each of which is attached a pickaxe 10, respectively 11 provided with an end stop 12, respectively 13, these tabs being on each side of a cross member 3 in the working position of the device.
  • the tamping tools 4 'and 5' of the other pair are partially visible in Figure 3, while they are hidden in Figure 2 by tools 4 and 5. They have arms 8 'and 9' provided, like the arms 8 and 9, of two picks provided with end lugs, the lugs 12 'of the picks 10' of one of the arms being visible in FIG. 3, while the lugs of the other arm are located the other side of the cross 3.
  • All the moving parts of the tamping unit are articulated to a common support 14 for the two pairs of tamping tools 4, 5 and 4 ′, 5 ′, which is suspended by means of a hydraulic cylinder 25 vertically adjustable on the chassis 1.
  • a hydraulic cylinder 25 vertically adjustable on the chassis 1.
  • two vertical columns 21 and 22 are provided rigidly fixed to the support 14 and sliding in two axial bearings 23 and 24.
  • the piston rod of the hydraulic cylinder 25, the l the upper end is fixed to the chassis 1, is articulated to a pin 26 fixed to the upper end of a vertical bearing 14a of the support 14.
  • the assembly is arranged so that the tamping tools can be lifted by means of the hydraulic cylinder 25 above the level of the rails 2.
  • the bearing 6 of the eccentric shaft 7 On the lower side of the support 14 is fixed rigidly and transversely to the rail 2, the bearing 6 of the eccentric shaft 7, the two parts of which protrude from the bearing each carry a pair of eccentric bearings 27, 28, respectively 27 ′, 28 ', and the ends of which each carry a flywheel 29, respectively 29' provided with an unbalance 30, respectively 30 '.
  • the arms 8 and 9, respectively 8 'and 9', of the two pairs of tamping tools are articulated on the adjacent eccentric spans of each pair.
  • the work of the jacks 17 and 18 has the effect of pivoting the arms 8 and 9 around the eccentric shaft 7, so that the picks 10 and 11 with their end stops 12 and 13 come closer or closer deviate from the cross member 3.
  • the points of attachment of these arms to the shaft 7 are rotated by the eccentric bearings 27 and 28.
  • the arms 8 and 9 being attached by their ends higher this rotation results in their other ends by an oscillating movement of the cleats 12 and 13. Due to the judicious choice of the angle ⁇ , the vibrations of the cleats are symmetrical with respect to the cross-member 3 and synchronous.
  • the two tamping tools 4 'and 5', at the other end of the eccentric shaft 7, are attached in the same way by their arms 8 'and 9' to the support 14 by means of hydraulic jacks, only the jack 17 'attached at 15', with its compensating mass 31 ', being visible in FIG. 3.
  • the tamping tools 4 and 4', respectively 5 and 5 ', located on the same side of the cross-member 3 are rigidly connected by a cross member 33, respectively 34, at points located just below the joints 19 and 20.
  • These cross members 33 and 34 serve not only to increase the stability of the device, but also to compensate or balance the weight of the picks and their end stops.
  • the chassis 1 naturally carries a second aggregate, as shown in FIGS. 2 and 3, working simultaneously under the same cross member 3, on each side of the other rail of the track. All the moving masses are balanced so as to avoid vibration of the support 14 and consequently of the chassis 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
  • Train Traffic Observation, Control, And Security (AREA)
  • Railway Tracks (AREA)

Abstract

In a railway track ballast tamping device, a tamping unit is carried for vertical adjustment by a support mounted on the frame structure of a vehicle and comprises at least one pair of jointly-operating tamping tools crossing each other. The arm of these tools are adapted to pivot on opposite eccentric cranks formed on an eccentric shaft rotatably mounted in a bearing rigidly fastened to the support; the upper ends of the arms, opposite the pick-forming thereof, are each pivotally connected to a hydraulic cylinder inclined not in excess of 30 DEG to the vertical; the planes passing through the axis of rotation on the eccentric shaft and the center of the opposite eccentric cranks thereof form between them an angle of 40 DEG to 80 DEG in order to warrant a symmetrical, synchronous oscillatory motion of the packers carried by the lower ends of the picks. To prevent the transmission of detrimental vibration to the support during the rotation of the eccentric shaft, there are provided, in addition to out-of-balance weight carried by a flywheel rigid with the eccentric shaft, balance weights fastened to the hydraulic cylinders and disposed above the level of the pivotal connections between these cylinders and the support. Furthermore, the tamping tools of a pair disposed on the same side of a tie have their upper ends rigidly interconnected.

Description

La présente invention concerne un dispositif pour le bourrage des voies ferrées comportant un châssis roulant sur la voie et au moins un agrégat de bourrage disposé sur un support déplaçable verticalement sur le châssis et comportant au moins une paire d'outils de bourrage coopérant en opposition et présentant chacun un bras auquel est fixée au moins une pioche, l'agrégat de bourrage comportant en outre un arbre rotatif à excentriques muni d'un volant d'inertie à balourd mû par un moteur et tournant dans un palier rigidement lié au support d'outils et comportant deux portées excentrées sur chacune desquelles sont articulés les bras d'une paire d'outils de bourrage pour la transmission de mouvements oscillants aux pioches, et des membres de liaison extensibles reliant les bras au support et articulés, d'une part, en des points d'articulation situés à distance au-dessus des extrémités supérieures des bras et, d'autre part, respectivement à chaque bras et qui sont agencés de telle sorte que les bras oscillent autour de leurs points d'articulation à l'arbre à excentriques.The present invention relates to a device for tamping railways comprising a chassis rolling on the track and at least one tamping aggregate disposed on a support movable vertically on the chassis and comprising at least one pair of tamping tools cooperating in opposition and each having an arm to which is attached at least one pick, the tamping aggregate further comprising a rotary eccentric shaft provided with an unbalanced flywheel driven by a motor and rotating in a bearing rigidly connected to the support tools and comprising two eccentric spans on each of which are articulated the arms of a pair of tamping tools for the transmission of oscillating movements to the pickaxes, and extendable connecting members connecting the arms to the support and articulated, on the one hand at points of articulation situated at a distance above the upper ends of the arms and, on the other hand, respectively on each arm and which are arranged so that q that the arms oscillate around their points of articulation at the eccentric shaft.

Un dispositif de ce type est décrit dans le brevet AT 352 159. Dans ce dispositif, les bras des outils de bourrage présentent une forme coudée sensiblement à angle droit à la manière de leviers coudés et dont les extrémités opposées aux taquets d'extrémité sont articulées aux portées excentrées d'un arbre à excentriques commun. Les membres de liaison extensibles sont constitués par des vérins hydrauliques à double effet orientés approximativement verticalement et articulés d'une part dans la région du coude de chaque bras du dispositif de bourrrage et d'autre part au support de ces outils. Lors de la rotation de l'arbre à excentriques, les extrémités des bras articulées aux portées excentrées décrivent une trajectoire circulaire, tandis que les coudes des bras articulés aux vérins ont un mouvement oscillant selon un arc de cercle dont le centre se trouve au point d'articulation de l'autre extrémité du vérin au support d'outils et qui présente un rayon relativement grand. Ce mouvement résulte du fait que le coude de chacun des bras ne peut osciller verticalement étant donné que son vérin est immobilisé verticalement. Il se produit de cette manière une oscillation sensiblement horizontale des taquets d'extrémité, mouvement favorable à l'obtention d'un bon tassement du ballast. Ce dispositif de bourrage, dans lequel les outils de bourrage sont articulés directement à un arbre à excentriques ou à un vilebrequin tournant dans des paliers fixés au support, et sensiblement plus simple et plus robuste que d'autres machines de bourrage connues de construction et de géométrie compliquée.A device of this type is described in patent A T 352 159. In this device, the arms of the tamping tools have a bent shape substantially at right angles in the manner of bent levers and the ends of which are opposite to the end stops. articulated to the eccentric spans of a common eccentric shaft. The extendable connecting members are constituted by double-acting hydraulic cylinders oriented approximately vertically and articulated on the one hand in the region of the elbow of each arm of the tamping device and on the other hand to the support of these tools. During the rotation of the eccentric shaft, the ends of the arms articulated with the eccentric spans describe a circular trajectory, while the elbows of the arms articulated with the jacks have an oscillating movement according to an arc of circle whose center is at the point of 'articulation of the other end of the jack to the tool holder and which has a relatively large radius. This movement results from the fact that the elbow of each of the arms cannot oscillate vertically since its actuator is immobilized vertically. In this way, a substantially horizontal oscillation of the end stops occurs, a movement favorable to obtaining good compaction of the ballast. This tamping device, in which the tamping tools are articulated directly to an eccentric shaft or to a crankshaft rotating in bearings fixed to the support, and substantially simpler and more robust than other known tamping machines of construction and complicated geometry.

Malgré sa construction relativement simple et robuste, cette machine ne satisfait pas à toutes les exigences que l'on peut souhaiter pour un résultat optimum. En particulier, si une oscillation horizontale des taquets de bourrage est favorable lorsque les taquets sont engagés dans le ballast, une telle oscillation n'est pas nécessairement favorable pendant la pénétration des taquets dans le ballast. En outre, les centres de gravité des deux bras coudés sont relativement très éloignés du plan vertical de symétrie passant par l'axe de l'arbre à excentriques, ce qui rend difficile une répartition des masses en mouvement telle que les efforts dynamiques exercés lors de la rotation de l'arbre à excentriques sur le support soient au moins approximativement neutralisés, au moins lorsque le dispositif de bourrage est agencé et travaille en machine de bourrage à une ou trois traverses. Une condition importante que les machines de bourrage doivent satisfaire consiste en effet en ce que le support des outils de bourrage et par conséquent le châssis du véhicule de travail doivent être le moins possible entraînés en vibration par les masses vibrantes respectivement tournantes, vibration susceptible de mettre en danger la stabilité du dispositif et d'influencer défavorablement la qualité du bourrage.Despite its relatively simple and robust construction, this machine does not meet all the requirements that one could wish for an optimum result. In particular, if a horizontal oscillation of the cleats tamping is favorable when the cleats are engaged in the ballast, such an oscillation is not necessarily favorable during the penetration of the cleats in the ballast. In addition, the centers of gravity of the two bent arms are relatively very far from the vertical plane of symmetry passing through the axis of the eccentric shaft, which makes it difficult to distribute the moving masses such as the dynamic forces exerted during the rotation of the eccentric shaft on the support are at least approximately neutralized, at least when the tamping device is arranged and works in a tamping machine with one or three crosspieces. An important condition that the tamping machines must satisfy is that the support for the tamping tools and therefore the chassis of the work vehicle must be as little as possible driven in vibration by the respectively rotating vibrating masses, vibration capable of causing endangering the stability of the device and adversely influencing the quality of the packing.

Il est en outre désirable d'assurer que les deux pioches d'une paire oscillent de façon synchrone et symétriquement l'une par rapport à l'autre. Une éventuelle asymétrie de ces oscillations a non seulement un effet défavorable sur la qualité du bourrage, mais provoque en outre des vibrations horizontales indésirables de l'ensemble du dispositif.It is further desirable to ensure that the two pick axes of a pair oscillate synchronously and symmetrically with respect to each other. A possible asymmetry of these oscillations not only has an unfavorable effect on the quality of the stuffing, but also causes undesirable horizontal vibrations of the entire device.

La présente invention a pour but de réaliser un dispositif de bourrage du type décrit plus haut, conservant une construction simple et robuste, mais telle que les résultantes des efforts dynamiques agissant sur le support soient sensiblement nulles, sans moyen constructif supplémentaire, et que simultanément la qualité du bourrage soit améliorée.The object of the present invention is to produce a tamping device of the type described above, retaining a simple and robust construction, but such that the results of the dynamic forces acting on the support are substantially zero, without additional constructive means, and that simultaneously the jam quality is improved.

A cet effet le dispositif de bourrage selon l'invention est caractérisé en ce que les bras d'une paire d'outils de bourrage sont constitués par des leviers sensiblement rectilignes à deux bras et se croisent au voisinage de l'arbre à excentriques, que lesdits points d'articulation sont situés entre les bras et les membres de liaison, du côté de l'arbre à excentriques opposé aux pioches et que pour compenser au moins approximativement les forces et moments dynamiques exercés par la rotation de l'arbre à excentriques sur le support, il est prévu, en plus du balourd fixé au volant d'inertie, des masses de compensation fixées aux membres de liaison, dans le prolongement des membres de liaison, au-dessus de leur points d'articulation au support.To this end, the tamping device according to the invention is characterized in that the arms of a pair of tamping tools are constituted by substantially rectilinear levers with two arms and intersect in the vicinity of the eccentric shaft, that said points of articulation are located between the arms and the connecting members, on the side of the eccentric shaft opposite to the picks and that to compensate at least approximately the dynamic forces and moments exerted by the rotation of the eccentric shaft on the support, there is provided, in addition to the unbalance fixed to the flywheel, compensation masses fixed to the connecting members, in the extension of the connecting members, above their points of articulation to the support.

Il s'est avéré, de manière surprenante, qu'une transmission d'oscillations perturbatrices au support par une répartition adéquate des masses en mouvement ne peut être empêchée de façon optimale que si les deux bras d'une paire d'outils de bourrage sont disposés en croix et que s'il est prévu des masses de compensation additionnelles sur les membres de liaison, en plus d'un balourd choisi de façon adéquate.It turned out, surprisingly, that transmission of disturbing oscillations to the support by an adequate distribution of the moving masses can only be optimally prevented if the two arms of a pair of tamping tools are arranged in a cross and if additional compensation masses are provided on the connecting members, in addition to an unbalance chosen in an appropriate manner.

Chacune des masses de compensation est de préférence dimensionnée et disposée de telle sorte qu'un barreau droit, de poids spécifique uniforme sur toute sa longueur et équivalent, quant à sa masse et à sa disposition, au membre de liaison et à sa masse de compensation, dépasserait le point d'articulation dudit membre de liaison au support, d'un tiers de sa longueur.Each of the compensation masses is preferably dimensioned and arranged in such a way that a straight rod, of uniform specific weight over its entire length and equivalent, as regards its mass and its arrangement, to the connecting member and to its compensation mass , would exceed the point of articulation of said member connecting to the support, by a third of its length.

Il s'est avéré que les vibrations du support ne se laissaient pas supprimer par le seul moyen d'un balourd sur le volant d'inertie. La disposition en croix des bras d'une paire d'outils de bourrage permet en outre d'amener le centre de gravité des outils de bourrage à proximité du plan vertical de symétrie passant par l'arbre à excentriques ou au moins approximativement dans ce plan, ce qui a également un effet favorable.It turned out that the vibrations of the support could not be suppressed by the sole means of an imbalance on the flywheel. The cross arrangement of the arms of a pair of tamping tools also makes it possible to bring the center of gravity of the tamping tools to proximity to the vertical plane of symmetry passing through the eccentric shaft or at least approximately in this plane, which also has a favorable effect.

En outre, le dispositif de bourrage selon l'invention a pour avantage que les trajectoires des oscillations des taquets d'extrémité sont inclinées par rapport à l'horizontale lorsque les bras sont écartés, c'est-à-dire lorsque les outils de bourrage descendent de chaque côté d'une traverse et s'enfoncent dans le ballast, pour adopter progressivement une trajectoire horizontale lorsqu'ils sont dans le ballast, pour le processus de bourrage proprement dit.In addition, the tamping device according to the invention has the advantage that the trajectories of the oscillations of the end stops are inclined relative to the horizontal when the arms are separated, that is to say when the tamping tools descend on each side of a cross member and sink into the ballast, to gradually adopt a horizontal trajectory when they are in the ballast, for the actual tamping process.

Il s'est en outre avéré que les oscillations des deux taquets d'extrémité d'une paire sont symétriques si l'angle formé par les deux plans passant par l'axe de rotation de l'arbre à excentriques et chacun des axes de rotation des deux portées excentrées présente un angle bien déterminé, pour une géométrie donnée, respectivement une configuration donnée de tous les points d'articulation et de rotation du dispositif, angle que l'on peut calculer. Si les membres de liaison reliant les bras d'une paire d'outils de bourrage au support sont avantageusement orientés au moins approximativement verticalement ou sont en tous cas inclinés au plus de 30° par rapport à la verticale, l'angle desdits plans garantissant des oscillations tout à fait symétriques et synchrones des deux pioches, est compris entre 40 et 800. Le balourd du volant d'inertie se trouve alors sur la bissectrice de cet angle, du côté de l'arbre à excentriques opposé aux côtés de cet angle.It has also been found that the oscillations of the two end stops of a pair are symmetrical if the angle formed by the two planes passing through the axis of rotation of the eccentric shaft and each of the axes of rotation of the two eccentric spans has a well determined angle, for a given geometry, respectively a given configuration of all the points of articulation and rotation of the device, angle which can be calculated. If the connecting members connecting the arms of a pair of tamping tools to the support are advantageously oriented at least approximately vertically or are in any case inclined at most 30 ° relative to the vertical, the angle of said planes guaranteeing completely symmetrical and synchronous oscillations of the two picks, is between 40 and 80 0 . The imbalance of the flywheel is then on the bisector of this angle, on the side of the eccentric shaft opposite the sides of this angle.

Un agrégat de bourrage présente généralement deux paires d'outils de bourrage disposés de part et d'autre d'un rail et tassant le ballast simultanément sous une traverse, de chaque côté de la fixation du rail. La stabilité et la fonction d'un tel agrégat de bourrage peuvent encore être améliorées en reliant les bras correspondants de deux paires d'outils de bourrage situés sur les côtés opposés d'un rail par une traverse rigide fixée en des endroits des bras opposés aux pioches, relativement à l'arbre à excentriques, de préférence au voisinage immédiat des points d'articulation des membres de liaison. Ces traverses servent simultanément de contrepoids aux taquets d'extrémité.A tamping aggregate generally has two pairs of tamping tools arranged on either side of a rail and compacting the ballast simultaneously under a crosspiece, on each side of the rail attachment. The stability and function of such a tamping aggregate can be further improved by connecting the corresponding arms of two pairs of tamping tools located on opposite sides of a rail by a rigid crossmember fixed in places of the arms opposite to the picks, relative to the eccentric shaft, preferably in the immediate vicinity of the points of articulation of the connecting members. These crosspieces serve simultaneously as a counterweight to the end stops.

Le dispositif de bourrage selon l'invention se laisse si bien équilibrer par une répartition adéquate des masses en mouvement, qu'il est possible de l'exécuter et de l'utiliser aussi bien en machine à une traverse, qu'en machine à deux ou trois traverses, sans problème en ce qui concerne les vibrations transmises au support.The tamping device according to the invention can be balanced so well by an adequate distribution of the moving masses, that it is possible to execute it and use it as well in machine with a cross, as in machine with two or three sleepers, no problem with regard to the vibrations transmitted to the support.

Le dessin annexé représente, à titre d'exemple, une forme d'exécution de l'invention.

  • La figure 1 représente schématiquement la géométrie du dispositif.
  • La figure 2 est une vue de côté montrant les parties essentielles d'un agrégat de bourrage comprenant des outils de bourrage opposés de chaque côté.
  • La figure 3 est une vue selon la direction III de l'agrégat représenté à la figure 2.
The accompanying drawing shows, by way of example, an embodiment of the invention.
  • Figure 1 shows schematically the geometry of the device.
  • Figure 2 is a side view showing the essential parts of a packing aggregate comprising packing tools opposite on each side.
  • FIG. 3 is a view in direction III of the aggregate shown in FIG. 2.

Dans le schéma de principe représenté à la figure 1, qui illustre la géométrie d'un agrégat de bourrage comportant deux outils de bourrage coopérant, chacune des parties, ainsi que les articulations et les axes de rotation sont désignés par les mêmes chiffres de références que les éléments correspondants sur les figures 2 et 3. L'arbre à excentriques ou le vilebrequin 7, perpendiculaire au plan du dessin, tournant dans un palier 6 fixé rigidement au support du dispositif, porte deux excentriques, respectivement deux tourillons, dont les centres sont désignés par 27 et 28. Les droites reliant l'axe de l'arbre 7 et les points 27 et 28 forment un angle fixe α.In the block diagram represented in FIG. 1, which illustrates the geometry of a tamping aggregate comprising two cooperating tamping tools, each of the parts, as well as the articulations and the axes of rotation are designated by the same reference numbers as the corresponding elements in the figures 2 and 3. The eccentric shaft or the crankshaft 7, perpendicular to the plane of the drawing, rotating in a bearing 6 rigidly fixed to the support of the device, carries two eccentrics, respectively two journals, the centers of which are designated by 27 and 28. The lines connecting the axis of the shaft 7 and the points 27 and 28 form a fixed angle α.

Aux excentriques 27 et 28 sont attachés les deux bras croisés 4 et 5 d'une paire d'outils de bourrage, ces bras formant des leviers dont le point d'appui est constitué par l'axe 7. Les extrémités inférieures des leviers sont les extrémités de travail portant les taquets d'extrémité 12 et 13 travaillant de chaque côté d'une traverse 3. Les extrémités supérieures de ces leviers sont reliées aux points d'articulation 19 et 20 aux extrémités respectives inférieures de deux membres de liaison 17 et 18, eux-mêmes articulés en deux points 15 et 16 sur une portée 14a du support, les points d'articulation 15 et 16 se trouvant à une certaine distance au-dessus des outils de bourrage 4 et 5. Les membres de liaison 17 et 18, qui sont de préférence constitués par des vérins hydrauliques a double effet, s'étendent au moins approximativement verticalement ou sont inclinés d'au plus 300 relativement à la verticale et portent des masses de compensation 31 et 32 fixées à des prolongements s'étendant au-dessus des points d'articulation 15 et 16. Si l'on remplaçait chacun des membres de liaison 17 et 18, ainsi que leur masse d'équilibrage 31 et 32, par un barreau droit uniforme, équivalent, de poids spécifique uniforme sur toute sa longueur, les articulations 15 et 16 de ces barreaux diviseraient ces barreaux dans un rapport de 2 : 1, c'est-à-dire que chaque barreau dépasserait le point d'articulation 15, respectivement 16 d'une longueur égale à la moitié de la distance entre les articulations 15 et 19, respectivement 16 et 20. Une autre masse d'équilibrage est constituée par le balourd 30 d'un volant d'inertie fixé sur l'arbre à excentriques 7, ce balourd 30 étant décalé de l'axe 7, sur la bissectrice de l'angle α, dans une direction opposée aux côtés de cet angle.To the eccentrics 27 and 28 are attached the two crossed arms 4 and 5 of a pair of tamping tools, these arms forming levers whose fulcrum is constituted by the axis 7. The lower ends of the levers are the working ends carrying the end tabs 12 and 13 working on each side of a cross member 3. The upper ends of these levers are connected to the articulation points 19 and 20 to the respective lower ends of two connecting members 17 and 18 , themselves articulated at two points 15 and 16 on a bearing surface 14a of the support, the articulation points 15 and 16 being at a certain distance above the tamping tools 4 and 5. The connecting members 17 and 18 , which are preferably constituted by double-acting hydraulic cylinders, extend at least approximately vertically or are inclined at most 30 0 relative to the vertical and carry compensating masses 31 and 32 fixed to extensions extending at above articulation points 15 and 16. If one replaced each of the connecting members 17 and 18, as well as their balancing mass 31 and 32, by a uniform straight bar, equivalent, of uniform specific weight over all its length, the joints 15 and 16 of these bars would divide these bars in a ratio of 2: 1, that is to say that each bar would exceed the point of articulation 15, respectively 16 by a length equal to half the distance between joints 15 and 19, respectively 16 and 20. Another balancing mass consists of the unbalance 30 of a flywheel fixed on the eccentric shaft 7, this unbalance 30 being offset from the axis 7, on the bisector of the angle α, in an opposite direction alongside this angle.

Les extrémités supérieures des leviers des outils de bourrage 4 et 5 sont en outre reliées rigidement et respectivement à chacun des outils de bourrage d'une seconde paire d'outils de bourrage se trouvant respectivement du même côté de la traverse 3, mais de l'autre côté du rail, par une traverse 33, respectivement 34, perpendiculaire au plan du dessin. Ces traverses 33 et 34 servent de contrepoids aux taquets d'extrémité 12 et 13.The upper ends of the levers of the tamping tools 4 and 5 are also rigidly connected respectively to each of the tamping tools of a second pair of tamping tools located respectively on the same side of the cross member 3, but from the other side of the rail, by a cross 33, respectively 34, perpendicular to the plane of the drawing. These crosspieces 33 and 34 serve as a counterweight to the end stops 12 and 13.

Lors de la rotation de l'arbre à excentriques 7, les outils de bourrage 4 et 5 sont entraînés en un mouvement oscillant dans un plan parallèle au plan du dessin. Le raccourcissement des membres de liaison 17 et 18 permet aux bras 4 et 5 de pivoter en rapprochant l'un de l'autre les taquets d'extrémité 12 et 13. En position fortement écartée des bras, les taquets 12 et 13 ont une trajectoire inclinée d'un angle Lf relativement à l'horizontale, ce qui favorise leur pénétration dans le ballast. Une fois que les taquets ont pénétré dans le ballast, l'inclinaison des trajectoires des taquets diminue progressivement au fur et à mesure qu'ils se rapprochent l'un de l'autre pour être finalement approximativement horizontale lorsque les taquets sont sous la traverse, ce qui est particulièrement favorable pour obtenir un bon bourrage.During rotation of the eccentric shaft 7, the tamping tools 4 and 5 are driven in an oscillating movement in a plane parallel to the plane of the drawing. The shortening of the connecting members 17 and 18 allows the arms 4 and 5 to pivot by bringing the end tabs 12 and 13 closer to each other. In the position far away from the arms, the tabs 12 and 13 have a trajectory inclined at an angle Lf relatively to the horizontal, which promotes their penetration into the ballast. Once the cleats have entered the ballast, the inclination of the cleats trajectories gradually decreases as they approach each other to be finally approximately horizontal when the cleats are under the crosspiece, which is particularly favorable for obtaining good packing.

Pour construire un dispositif de bourrage selon l'invention, on détermine tout d'abord l'angleo(entre les rayons, respectivement les plans passant par l'axe 7 et les centres des deux excentriques 27 et 28, pour lequel angle les deux taquets d'extrémité 12 et 13 oscillent de façon tout à fait synchrone et symétrique par rapport au plan vertical de symétrie passant par l'axe de l'arbre à excentriques 7. Il s'est avéré que cette condition importante et essentielle pour la qualité du bourrage n'est généralement satisfaite que pour un angle α déterminé et unique pour une configuration donnée des points de rotation et d'articulation. Cet angle varie en fonction de la géométrie des points de rotation et d'articulation, mais dans le cas considéré, dans lequel l'inclinaison des membres de liaison 17 et 18 par rapport à la verticale ne dépasse pas 30°, l'angle α est compris entre 40° et 800, par exemple 53° dans un cas typique.To build a tamping device according to the invention, the angleo is first determined (between the radii, respectively the planes passing through the axis 7 and the centers of the two eccentrics 27 and 28, for which angle the two end stops 12 and 13 oscillate in a completely synchronous and symmetrical manner with respect to the vertical plane of symmetry passing through the axis of the eccentric shaft 7. It turns out that this important and essential condition for the quality of the stuffing is generally satisfied only for a determined angle α which is unique for a given configuration of the points of rotation and of articulation. This angle varies as a function of the geometry of the points of rotation and of articulation, but in the case considered, in which the inclination of the connecting members 17 and 18 relative to the vertical does not exceed 30 °, the angle α is between 40 ° and 80 0 , for example 53 ° in a typical case.

Après avoir calculé l'angle α, on répartit toutes les masses en mouvement de telle sorte que lors de la rotation de l'arbre à excentriques 7 les efforts dynamiques s'exerçant sur le support du dispositif, en particulier les vibrations, disparaissent au moins approximativement. Ceci est possible au moyen des masses additionnelles 30, 31 et 32 servant à l'équilibrage de l'ensemble du dispositif. Cet équilibrage est facilité par le fait que les centres de gravité des outils de bourrage 4 et 5 avec leurs traverses 33 et 34 peuvent être déplacés au moins approximativement dans le plan vertical de symétrie passant par l'axe de l'arbre à excentriques 7 ou à proximité de celui-ci. Les calculs nécessaires susmentionnés peuvent être exécutés par des méthodes connues, de préférence à l'aide d'un ordinateur. Il s'est avéré que les dispositifs de bourrage selon l'invention pouvaient être utilisés sans autre aussi bien comme machine à une traverse, que comme machine à deux ou trois traverses, c'est-à-dire bourrant sous une, respectivement deux ou trois traverses simultanément, sans problème en ce qui concerne une vibration du support.After having calculated the angle α, all the moving masses are distributed so that during the rotation of the eccentric shaft 7 the dynamic forces exerted on the support of the device, in particular the vibrations, disappear at least approximately. This is possible by means of additional masses 30, 31 and 32 serving for balancing the entire device. This balancing is facilitated by the fact that the centers of gravity of the tamping tools 4 and 5 with their cross members 33 and 34 can be moved at least approximately in the vertical plane of symmetry passing through the axis of the eccentric shaft 7 or close to it. The above-mentioned necessary calculations can be carried out by known methods, preferably using a computer. It turned out that the tamping devices according to the invention could be used without other as well as a machine with a cross, as a machine with two or three cross, that is to say stuffing under one, respectively two or three sleepers simultaneously, no problem with vibration of the support.

Aux figures 1 et 2 est représenté un agrégat de bourrage monté, de façon réglable en hauteur, sur un châssis 1 susceptible de se déplacer sur des rails 2. Cet agrégat de bourrage présente, de part et d'autre de chacun des rails 2, dont un seul est représenté à la figure 3, une paire d'outils de bourrage 4, 5, respectivement 4', 5', attachés à un arbre à excentriques 7 tournant dans un palier 6. Les outils de bourrage 4 et 5 d'une même paire, que l'on peut voir sur la figure 2 et qui apparaissent partiellement cachés dans la partie droite de la figure 3, sont constitués chacun d'un bras 8, respectivement 9 à chacun desquels est fixée une pioche 10, respectivement 11 munie d'un taquet d'extrémité 12, respectivement 13, ces taquets se trouvant de chaque côté d'une traverse 3 en position de travail du dispositif. Les outils de bourrage 4' et 5' de l'autre paire sont partiellement visibles à la figure 3, tandis qu'ils sont cachés à la figure 2 par les outils 4 et 5. Ils présentent des bras 8' et 9' munis, comme les bras 8 et 9, de deux pioches pourvues de taquets d'extrémité, les taquets 12' des pioches 10' de l'un des bras étant visibles à la figure 3, tandis que les taquets de l'autre bras sont situés de l'autre côté de la traverse 3.In FIGS. 1 and 2 is shown a packing aggregate mounted, adjustable in height, on a frame 1 capable of moving on rails 2. This packing aggregate has, on either side of each of the rails 2, only one of which is shown in FIG. 3, a pair of tamping tools 4, 5, respectively 4 ′, 5 ′, attached to an eccentric shaft 7 rotating in a bearing 6. The tamping tools 4 and 5 of the same pair, which can be seen in Figure 2 and which appear partially hidden in the right part of Figure 3, each consist of an arm 8, respectively 9 to each of which is attached a pickaxe 10, respectively 11 provided with an end stop 12, respectively 13, these tabs being on each side of a cross member 3 in the working position of the device. The tamping tools 4 'and 5' of the other pair are partially visible in Figure 3, while they are hidden in Figure 2 by tools 4 and 5. They have arms 8 'and 9' provided, like the arms 8 and 9, of two picks provided with end lugs, the lugs 12 'of the picks 10' of one of the arms being visible in FIG. 3, while the lugs of the other arm are located the other side of the cross 3.

Toutes les parties mobiles de l'agrégat de bourrage sont articulées à un support 14 commun pour les deux paires d'outils de bourrage 4, 5 et 4', 5', lequel est suspendu au moyen d'un vérin hydraulique 25 ajustable verticalement sur le châssis 1. Pour le guidage du support 14 lors de son déplacement vertical il est prévu deux colonnes verticales 21 et 22 fixées rigidement au support 14 et coulissant dans deux paliers axiaux 23 et 24. La tige de piston du vérin hydraulique 25, dont l'extrémité supérieure est fixée au châssis 1, est articulée à un tourillon 26 fixé à l'extrémité supérieure d'une portée verticale 14a du support 14. L'ensemble est agencé de telle sorte que les outils de bourrage peuvent être levés au moyen du vérin hydraulique 25 au-dessus du niveau des rails 2.All the moving parts of the tamping unit are articulated to a common support 14 for the two pairs of tamping tools 4, 5 and 4 ′, 5 ′, which is suspended by means of a hydraulic cylinder 25 vertically adjustable on the chassis 1. For guiding the support 14 during its vertical displacement, two vertical columns 21 and 22 are provided rigidly fixed to the support 14 and sliding in two axial bearings 23 and 24. The piston rod of the hydraulic cylinder 25, the l the upper end is fixed to the chassis 1, is articulated to a pin 26 fixed to the upper end of a vertical bearing 14a of the support 14. The assembly is arranged so that the tamping tools can be lifted by means of the hydraulic cylinder 25 above the level of the rails 2.

Sur le côté inférieur du support 14 est fixé rigidement et transversalement au rail 2, le palier 6 de l'arbre à excentriques 7, dont les deux parties dépassant le palier portent chacune une paire de portées excentrées 27, 28, respectivement 27', 28', et dont les extrémités portent chacune un volant d'inertie 29, respectivement 29' muni d'un balourd 30, respectivement 30'. Sur les portées excentrées voisines de chaque paire sont articulés les bras 8 et 9, respectivement 8' et 9', des deux paires d'outils de bourrage. Ces bras se croisent dans la zone de leurs points d'attache, c'est-à-dire dans la zone de l'arbre à excentriques 7 et peuvent dès lors être considérés comme des leviers à deux bras prenant appui sur l'arbre 7. Les plans passant par l'axe de l'arbre à excentriques et par les axes de chacune des portées excentrées forment entre eux un angle « et les balourds 30 et 30' des volants d'inertie 29 et 29' se trouvent sur la bissectrice de cet angle α .On the lower side of the support 14 is fixed rigidly and transversely to the rail 2, the bearing 6 of the eccentric shaft 7, the two parts of which protrude from the bearing each carry a pair of eccentric bearings 27, 28, respectively 27 ′, 28 ', and the ends of which each carry a flywheel 29, respectively 29' provided with an unbalance 30, respectively 30 '. On the adjacent eccentric spans of each pair are articulated the arms 8 and 9, respectively 8 'and 9', of the two pairs of tamping tools. These arms cross in the area of their attachment points, that is to say in the area of the eccentric shaft 7 and can therefore be considered as two-arm levers resting on the shaft 7 The planes passing through the axis of the eccentric shaft and through the axes of each of the eccentric bearings form an angle between them "and the imbalances 30 and 30 'of the flywheels 29 and 29' are on the bisector of this angle α.

La description qui suit se réfère seulement à la paire d'outils de bourrage 4 et 5. Elle est toutefois également valable pour l'autre paire 4' et 5' de construction identique. Les extrémités supérieures des bras 8 et 9 opposées aux taquets d'extrémité 12 et 13 sont attachées par les articulations 19 et 20 aux extrémités inférieures de deux vérins hydrauliques à double effet 17 et 18 qui constituent les membres de liaison extensibles et qui sont eux-mêmes attachés à la portée 14a du support 14 par des articulations 15 et 16 situées au-dessus des extrémités supérieures des bras. Au-dessus des points d'articulation 15 et 16, les vérins hydrauliques 17 et 18 sont prolongés par des masses de compensation 31 et 32, dont les dimensions sont déterminées comme décrit plus haut en relation avec la figure 1.The following description refers only to the pair of tamping tools 4 and 5. It is however also valid for the other pair 4 'and 5' of identical construction. The upper ends of the arms 8 and 9 opposite the end tabs 12 and 13 are attached by the joints 19 and 20 to the lower ends of two double-acting hydraulic cylinders 17 and 18 which constitute the extendable connecting members and which are themselves same attached to the bearing surface 14a of the support 14 by joints 15 and 16 situated above the upper ends of the arms. Above the articulation points 15 and 16, the hydraulic cylinders 17 and 18 are extended by compensation masses 31 and 32, the dimensions of which are determined mined as described above in relation to Figure 1.

Le travail des vérins 17 et 18 a pour effet de faire pivoter les bras 8 et 9 autour de l'arbre à excentriques 7, de telle sorte que les pioches 10 et 11 avec leurs taquets d'extrémité 12 et 13 se rapprochent ou s'écartent de la traverse 3. Par la rotation de l'arbre 7, les points d'attache de ces bras sur l'arbre 7 sont entraînés en rotation par les portées excentrées 27 et 28. Les bras 8 et 9 étant attachés par leurs extrémités supérieures cette rotation se traduit à leurs autres extrémités par un mouvement oscillant des taquets 12 et 13. En raison du choix judicieux de l'angle<, les vibrations des taquets sont symétriques par rapport à la traverse 3 et synchrones.The work of the jacks 17 and 18 has the effect of pivoting the arms 8 and 9 around the eccentric shaft 7, so that the picks 10 and 11 with their end stops 12 and 13 come closer or closer deviate from the cross member 3. By the rotation of the shaft 7, the points of attachment of these arms to the shaft 7 are rotated by the eccentric bearings 27 and 28. The arms 8 and 9 being attached by their ends higher this rotation results in their other ends by an oscillating movement of the cleats 12 and 13. Due to the judicious choice of the angle <, the vibrations of the cleats are symmetrical with respect to the cross-member 3 and synchronous.

Les deux outils de bourrage 4' et 5', à l'autre extrémité de l'arbre à excentriques 7, sont attachés de la même manière par leurs bras 8' et 9' au support 14 au moyen de vérins hydrauliques, seul le vérin 17' attaché en 15', avec sa masse de compensation 31', étant visible à la figure 3. Les outils de bourrage 4 et 4', respectivement 5 et 5', situés d'un même côté de la traverse 3 sont reliés rigidement par une traverse 33, respectivement 34, en des points situés juste en-dessous des articulations 19 et 20. Ces traverses 33 et 34 servent non seulement à augmenter la stabilité du dispositif, mais également de masse de compensation ou d'équilibrage du poids des pioches et de leurs taquets d'extrémité.The two tamping tools 4 'and 5', at the other end of the eccentric shaft 7, are attached in the same way by their arms 8 'and 9' to the support 14 by means of hydraulic jacks, only the jack 17 'attached at 15', with its compensating mass 31 ', being visible in FIG. 3. The tamping tools 4 and 4', respectively 5 and 5 ', located on the same side of the cross-member 3 are rigidly connected by a cross member 33, respectively 34, at points located just below the joints 19 and 20. These cross members 33 and 34 serve not only to increase the stability of the device, but also to compensate or balance the weight of the picks and their end stops.

Le châssis 1 porte bien entendu un second agrégat, tel que représenté aux figures 2 et 3, travaillant simultanément sous la même traverse 3, de chaque côté de l'autre rail de la voie. Toutes les masses en mouvement sont équilibrées de manière à éviter la vibration du support 14 et par conséquent du châssis 1.The chassis 1 naturally carries a second aggregate, as shown in FIGS. 2 and 3, working simultaneously under the same cross member 3, on each side of the other rail of the track. All the moving masses are balanced so as to avoid vibration of the support 14 and consequently of the chassis 1.

Claims (4)

1. Dispositif pour le bourrage des voies ferrées comportant un châssis roulant sur la voie et au moins un agrégat de bourrage disposé sur un support déplaçable verticalement sur le châssis et comportant au moins une paire d'outils de bourrage coopérant en opposition et présentant chacun un bras auquel est fixée au moins une pioche, l'agrégat de bourrage comportant en outre un arbre rotatif à excentriques muni d'un volant d'inertie à balourd mû par un moteur et tournant dans un palier rigidement lié au support d'outils et comportant deux portées excentrées sur chacune desquelles sont articulés les bras d'une paire d'outils de bourrage pour la transmission de mouvements oscillants aux pioches et des membres de liaison extensibles reliant les bras au support et articulés, d'une part, en des points d'articulation situés à distance au-dessus des extrémités supérieures des bras et, d'autre part, respectivement à chaque bras, et qui sont agencés de telle sorte que les bras oscillent autour de leurs points d'articulation à l'arbre excentriques, caractérisé en ce que les bras (8,9) d'une paire d'outils de bourrage (4,5) sont constitués par des leviers sensiblement rectilignes à deux bras et se croisent au voisinage de l'arbre à excentriques (7), que lesdits points d'articulation (19,20) sont situés entre les bras (8,9) et les membres de liaison, du côté de l'arbre à excentriques (7) opposé aux pioches (10,11) et que pour compenser au moins approximativement les efforts dynamiques exercés par la rotation de l'arbre à excentriques (7) sur le support (14,14a), il est prévu en plus du balourd du volant d'inertie (29) , des masses de compensations (31,32) fixées aux membres de liaison (17,18) dans le prolongement de ces membres de liaison, au-dessus de leurs points d'articulation (15,16) au support (14, 14a).1. Device for stuffing railway tracks comprising a chassis rolling on the track and at least one packing aggregate disposed on a support movable vertically on the chassis and comprising at least one pair of tamping tools cooperating in opposition and each having a arm to which is attached at least one pick, the tamping aggregate further comprising a rotary eccentric shaft provided with an unbalanced flywheel driven by a motor and rotating in a bearing rigidly connected to the tool support and comprising two eccentric spans on each of which are articulated the arms of a pair of tamping tools for the transmission of oscillating movements to the pickaxes and extendable connecting members connecting the arms to the support and articulated, on the one hand, at points d joint located at a distance above the upper ends of the arms and, on the other hand, respectively to each arm, and which are arranged so that the arms oscillate around their points of articulation to the eccentric shaft, characterized in that the arms (8, 9) of a pair of tamping tools (4.5) consist of substantially rectilinear levers with two arms and intersect at near the eccentric shaft (7), that said points of articulation (19,20) are located between the arms (8,9) and the connecting members, on the opposite side of the eccentric shaft (7) picks (10,11) and that to compensate at least approximately the dynamic forces exerted by the rotation of the eccentric shaft (7) on the support (14,14a), it is provided in addition to the unbalance of the flywheel inertia (29), compensation masses (31,32) fixed to the link members (17,18) in the extension of these link members, above their points of articulation (15,16) to the support ( 14, 14a). 2. Dispositif pour le bourrage des voies ferrées selons la revendication 1, caractérisé en ce que les membres de liaison (17,18), constitués de préférence par des vérins hydrauliques à double effet, sont orientés au moins approximativement verticalement ou inclinés de 30° au maximum par rapport à la verticale, et que les plans contenant l'axe de rotation de l'arbre à excentriques (7) et respectivement l'axe de chacune des portées excentrées (27,28) forment un angle compris entre 40° et 800, de telle sorte que pour une configuration donnée de tous les points d'articulation, respectivement de rotation, les oscillations des taquets d'extrémité (12,13) d'une paire d'outils de bourrage sont symétriques.2. Device for stuffing railways according to claim 1, characterized in that the connecting members (17,18), preferably constituted by double-acting hydraulic cylinders, are oriented at least approximately vertically or inclined by 30 ° at maximum with respect to the vertical, and that the planes containing the axis of rotation of the eccentric shaft (7) and respectively the axis of each of the eccentric bearings (27,28) form an angle between 40 ° and 80 0 , so that for a given configuration of all the points of articulation, respectively of rotation, the oscillations of the end stops (12, 13) of a pair of tamping tools are symmetrical. 3. Dispositif pour le bourrage des voies ferrées selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que les bras (8,8';9,9') correspondants de deux paires d'outils de bourrage (4,4';5,5') situés sur le côté opposé d'un rail (2) sont reliés entre eux par une traverse rigide (33;34) fixée en des endroits des bras opposés aux pioches (10,11), relativement à l'arbre à excentriques, de préférence au voisinage immédiat des points d'articulation (19,20) des membres de liaison (17,18).3. Device for stuffing railways according to any one of claims 1 or 2, characterized in that the arms (8.8 '; 9.9') corresponding to two pairs of stuffing tools (4.4 '; 5.5') located on the opposite side of a rail (2) are interconnected by a rigid crosspiece (33; 34) fixed in places of the arms opposite to the pickaxes (10,11), relative to the 'eccentric shaft, preferably in the immediate vicinity of the points of articulation (19,20) of the connecting members (17,18). 4. Dispositif pour le bourrage des voies ferrées selon l'une quelconque des revendications 1, 2 ou 3, caractérisé en ce que chacune des masses de compensation (31,32) fixées aux membres de liaison (17,18) est dimensionnée et disposée de telle sorte qu'un barreau droit de poids spécifique uniforme sur toute sa longueur et équivalent, quant à sa masse et à sa disposition, au membre de liaison et à sa masse de compensation, dépasserait le point d'articulation dudit membre de liaison au support, d'un tiers de sa longueur.4. Device for stuffing railway tracks according to any one of claims 1, 2 or 3, characterized in that each of the compensation masses (31,32) fixed to the connecting members (17,18) is dimensioned and arranged in such a way that a straight bar of uniform specific weight over its entire length and equivalent, as regards its mass and its disposition, to the connecting member and to its compensating mass, would exceed the point of articulation of said connecting member at support, of a third of its length.
EP81201120A 1980-10-29 1981-10-08 Railway track tamping device Expired EP0050889B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81201120T ATE9107T1 (en) 1980-10-29 1981-10-08 DEVICE FOR TAMPING RAILWAY TRACKS.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH8037/80 1980-10-29
CH8037/80A CH650819A5 (en) 1980-10-29 1980-10-29 TRACKING DEVICE.

Publications (2)

Publication Number Publication Date
EP0050889A1 true EP0050889A1 (en) 1982-05-05
EP0050889B1 EP0050889B1 (en) 1984-08-22

Family

ID=4334173

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81201120A Expired EP0050889B1 (en) 1980-10-29 1981-10-08 Railway track tamping device

Country Status (7)

Country Link
US (1) US4440089A (en)
EP (1) EP0050889B1 (en)
JP (1) JPS57133903A (en)
AT (1) ATE9107T1 (en)
CH (1) CH650819A5 (en)
DE (1) DE3165697D1 (en)
ZA (1) ZA817248B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2142069A (en) * 1983-06-22 1985-01-09 Dobson Park Ind Tamping machine
WO2022002520A1 (en) * 2020-07-03 2022-01-06 Plasser & Theurer Export Von Bahnbaumaschinen Gesellschaft M.B.H. Machine and method using a tamping assembly

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4676936A (en) * 1985-12-23 1987-06-30 The Dow Chemical Company Controlled coextrusion of barrier sheet
CN103132407B (en) * 2011-11-24 2014-10-29 金鹰重型工程机械有限公司 Drag chain device
CN112160196A (en) * 2020-10-21 2021-01-01 中国铁建高新装备股份有限公司 Tamping device and tamping vehicle
CN112160197A (en) * 2020-10-21 2021-01-01 中国铁建高新装备股份有限公司 Tamping device and tamping vehicle
AT526293A1 (en) * 2022-07-05 2024-01-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Tamping unit and method for tamping under sleepers on a track

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2806898A1 (en) * 1977-02-18 1978-08-24 Matisa Materiel Ind Sa DEVICE FOR COMPRESSING THE BALL BED OF A RAILWAY TRACK

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3625156A (en) * 1969-09-05 1971-12-07 Jackson Vibrators Ballast tamping workhead
US3799059A (en) * 1972-11-24 1974-03-26 Research Corp Packing apparatus for railroad track packing machines

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2806898A1 (en) * 1977-02-18 1978-08-24 Matisa Materiel Ind Sa DEVICE FOR COMPRESSING THE BALL BED OF A RAILWAY TRACK

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2142069A (en) * 1983-06-22 1985-01-09 Dobson Park Ind Tamping machine
WO2022002520A1 (en) * 2020-07-03 2022-01-06 Plasser & Theurer Export Von Bahnbaumaschinen Gesellschaft M.B.H. Machine and method using a tamping assembly

Also Published As

Publication number Publication date
ATE9107T1 (en) 1984-09-15
ZA817248B (en) 1982-09-29
JPH0130962B2 (en) 1989-06-22
JPS57133903A (en) 1982-08-18
EP0050889B1 (en) 1984-08-22
CH650819A5 (en) 1985-08-15
DE3165697D1 (en) 1984-09-27
US4440089A (en) 1984-04-03

Similar Documents

Publication Publication Date Title
EP0050889B1 (en) Railway track tamping device
EP0058117A1 (en) Simplified antiresonant suspension device for a helicopter
FR2800396A1 (en) DEVICE FOR NEEDING A FIBER MATTRESS
BE1000024A7 (en) Device for installation of iron or rebar in a floor covering.
FR2574388A1 (en) LIFTING DEVICE, IN PARTICULAR FOR FORK-LOADING FORKLIFTS
EP0494125B1 (en) Apparatus for the treatment of soil or vegetation, incorporating a ramp which can pivot around longitudinal and transverse axes
FR2464864A1 (en) IMPROVEMENTS FOR SUSPENSION OF RAILWAY CARS
BE1004145A3 (en) Device for rail jam jam track machines by jams under three rails.
WO2018100109A1 (en) Tuned dynamic damper and method for reducing the amplitude of oscillations
FR2498219A1 (en) JUMELE MURDER DEVICE FOR RAILWAY MACHINERY MACHINES
FR2693278A1 (en) Device comprising a vibrator fixed to a vehicle for producing seismic vibrations.
FR2501254A1 (en) FERROUS TRACK JAM DEVICE
CH658689A5 (en) RAILWAY CONVEYOR.
EA039948B1 (en) Tamping assembly for tamping sleepers of a track
FR2466567A1 (en) JAM DEVICE FOR RAILWAY MACHINE
BE517958A (en)
FR2501255A1 (en) FERROUS TRACK MACHINE WITH COMPLETELY ASYNCHRONOUS FILLING EQUIPMENT
EP0691481B1 (en) Improvements to connecting rods connecting certain vibrating elements of vehicles to the body of these vehicles
FR2527945A1 (en) SHAKING MACHINE
CA2289000C (en) Power puller motor bogie
EP0424322B1 (en) Railway ballast tamping machine
FR2624431A1 (en) STAPLING MACHINE WITH OSCILLATING STAPLER HEAD
EP0273813B1 (en) Device for supporting and masuring a load
FR2666357A1 (en) Ballast tamping unit for a railway track, of the type using forced vibration
BE541049A (en) ARTICULATED INTERCONNECTION DEVICE FOR SELF-PROPELLED TRAINS

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT DE FR GB IT

17P Request for examination filed

Effective date: 19821008

ITF It: translation for a ep patent filed

Owner name: BUGNION S.P.A.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MATISA MATERIEL INDUSTRIEL S.A.

AK Designated contracting states

Designated state(s): AT DE FR GB IT

REF Corresponds to:

Ref document number: 9107

Country of ref document: AT

Date of ref document: 19840915

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3165697

Country of ref document: DE

Date of ref document: 19840927

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19881118

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19921014

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19931008

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19981030

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000801

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20001017

Year of fee payment: 20