EP0050889B1 - Vorrichtung zum Unterstopfen von Eisenbahngleisen - Google Patents

Vorrichtung zum Unterstopfen von Eisenbahngleisen Download PDF

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Publication number
EP0050889B1
EP0050889B1 EP81201120A EP81201120A EP0050889B1 EP 0050889 B1 EP0050889 B1 EP 0050889B1 EP 81201120 A EP81201120 A EP 81201120A EP 81201120 A EP81201120 A EP 81201120A EP 0050889 B1 EP0050889 B1 EP 0050889B1
Authority
EP
European Patent Office
Prior art keywords
eccentric shaft
arms
support
tamping
pair
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.)
Expired
Application number
EP81201120A
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English (en)
French (fr)
Other versions
EP0050889A1 (de
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/de
Publication of EP0050889A1 publication Critical patent/EP0050889A1/de
Application granted granted Critical
Publication of EP0050889B1 publication Critical patent/EP0050889B1/de
Expired legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
    • E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
    • E01B27/13—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 located 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 ue the arms oscillate around their points of articulation to the eccentric shaft.
  • a device of this type is described in b revet AT 352 169 or DE-A-2 806 898.
  • the arms of the tamping tools have a bent shape substantially at right angles to the manner of bent levers and whose ends opposite to the end stops are articulated to the eccentric bearings of a common eccentric shaft.
  • the extendable connecting members consist of 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 tamping cleats is favorable when the cleats are engaged in the ballast, such an oscillation is not necessarily favorable during the penetration of the cleats into 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 allows in addition to bringing the center of gravity of the tamping tools near 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 cross member, 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 at arm locations opposite to the picks, relative to the eccentric shaft, preferably in the immediate vicinity of the points of articulation of the connecting members.
  • Cestraverses serve simultaneously as a counterweight to the end studs.
  • 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 FIGS. 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 a.
  • 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 ° 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 of the distance between the 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 by l axis 7, on the bisector of angle a, in a direction opposite to the sides of 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 cp relatively to the horizontal, which promotes their penetration into the ballast.
  • the inclination of the trajectories of the cleats progressively decreases as they approach each other to be finally approximately horizontal when the cleats are under the cross-member, which is particularly favorable for get a good stuffing.
  • the angle a 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 tabs end 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 has turned out that this important and essential condition for the quality of the tamping is generally satisfied only for a determined angle and unique for a given configuration of the points of rotation and articulation.
  • This angle varies according to 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 a is between 40 ° and 80 °, 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, that as a machine with two or three cross, that is to say stuffing under one, respectively two or three sleepers simultaneously, no problem with regard to 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 adjustable vertically on the chassis 1.
  • a hydraulic cylinder 25 adjustable vertically 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 move away from the cross-member 3.
  • the attachment points of these arms on the shaft 7 are rotated by the eccentric bearings 27 and 28.
  • the arms 8 and 9 being attached by their ends upper halves this rotation results at their other ends in an oscillating movement of the lugs 12 and 13. Due to the judicious choice of the angle a, the vibrations of the lugs 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 Figure 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 of 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.

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

Claims (4)

1. Gleisstopfvorrichtung mit einem auf dem Gleis verfahrbaren Chassis und mit wenigstens einem Stopfaggregat, das an einem vertikal am Chassis verstellbaren Träger (14) angeordnet ist, wobei das Stopfaggregat wenigstens ein Paar von zusammenwirkenden, gegenüberliegenden Stopfwerkzeugen mit je einem Arm (8, 9) und mindestens einem daran befestigten Stopfer (10, 11 ), eine in einem starr mit dem Träger (14) verbundenen Lager gelagerte, durch einen Motor angetriebene Exzenterwelle mit wenigstens einem eine Unwucht tragenden Schwungrad (29, 30) und einem Paar von Exzenterlaufflächen, an denen die Arme (8, 9) eines Stopfwerkzeug-Paares zur Übertragung der Schwingbewegungen auf die Stopfer angelenkt sind, und die Arme mit dem Träger verbindende, ausziehbare Verbindungsglieder (17, 18) aufweist, welche einerseits an im Abstand über den oberen Enden der Arme liegenden Gelenkpunkten am Träger, andererseits an je einem Arm gelenkig gelagert und so angeordnet sind, dass die Arme um ihre Gelenkpunkte an der Exzenterwelle hin- und herschwenken, dadurch gekennzeichnet, dass die Arme (8, 9) eines Paares von Stopfwerkzeugen (4, 5) als zweiarmige, im wesentlichen geradlinige Hebel ausgebildet sind und sich im Bereich der Exzenterwelle (7) kreuzen, dass die erwähnten Gelenkpunkte (19, 20) zwischen den Armen (8, 9) und den Verbindungsgliedern (17, 18) auf der den Stopfern (10, 11) abgewandten Seite der Exzenterwelle (7) liegen und dass zur wenigstens näherungsweisen Kompensation der dynamischen Kräfte, welche beim Drehen der Exzenterwelle (7) auf den Träger (14, 14a) ausgeübt werden, ausser der am Schwungrad (29) befestigten Unwucht ferner an den Verbindungsgliedern (17, 18) Ausgleichsmassen (31, 32) befestigt sind, welche in Verlängerung dieser Verbindungsglieder oberhalb der sie mit dem Träger (14, 14a) verbindenden Gelenkpunkte (15, 16) liegen.
2. Gleisstopfvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die vorzugsweise durch doppelwirkende Hydraulikzylinder gebildeten Verbindungsglieder (17, 18) wenigstens näherungsweise vertikal orientiert oder unter einem Winkel von maximal 30° gegen die Vertikale geneigt sind und dass die Ebenen, welche durch die Drehachse der Exzenterwelle (7) und die Drehachse der einen Exzenterlauffläche (27) bzw. der anderen Exzenterlauffläche (28) verlaufen, einen Winkel zwischen 40° und 80 derart einschliessen, dass für eine gegebene Konfiguration aller Gelenk- bzw. Drehpunkte die Schwingungen der Stopferanschläge (12, 13) eines Stopfwerkzeug-Paares zueinander symmetrisch sind.
3. Gleisstopfvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die einander entsprechenden Arme (8, 8'; 9, 9') zweier auf den gegenüberliegenden Seiten einer Schiene (2) befindlichen Paare von Stopfwerkzeugen (4, 4'; 5, 5') durch je eine starre Traverse (33; 34) verbunden sind, welche an den den Stopfern (10, 11) relativ zur Exzenterwelle abgewandten Bereichen der betreffenden Arme, vorzugsweise in unmittelbarer Nähe der Gelenkpunkte (19, 20) der Verbindungsglieder (17, 18), befestigt sind.
4. Gleisstopfvorrichtung nach einem der Ansprüche 1, 2 oder 3, dadurch gekennzeichnet, dass jede der an den Verbindungsgliedern (17, 18) befestigten Ausgleichsmassen (31, 32) derart bemessen und angeordnet ist, dass ein gerader Stab, welcher über seine ganze Länge ein gleichförmiges spezifisches Gewicht hat und hinsichtlich seiner Masse und seiner Anordnung dem Verbindungsglied (17, 18) und seiner Ausgleichsmasse (31, 32) äquivalent ist, den Gelenkpunkt des Verbindungsgliedes am Träger um ein Drittel seiner Länge überragt.
EP81201120A 1980-10-29 1981-10-08 Vorrichtung zum Unterstopfen von Eisenbahngleisen Expired EP0050889B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81201120T ATE9107T1 (de) 1980-10-29 1981-10-08 Vorrichtung zum unterstopfen von eisenbahngleisen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH8037/80 1980-10-29
CH8037/80A CH650819A5 (de) 1980-10-29 1980-10-29 Gleisstopfvorrichtung.

Publications (2)

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

Family

ID=4334173

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81201120A Expired EP0050889B1 (de) 1980-10-29 1981-10-08 Vorrichtung zum Unterstopfen von Eisenbahngleisen

Country Status (7)

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

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2142069B (en) * 1983-06-22 1987-01-28 Dobson Park Ind Tamping machine
US4676936A (en) * 1985-12-23 1987-06-30 The Dow Chemical Company Controlled coextrusion of barrier sheet
CN103132407B (zh) * 2011-11-24 2014-10-29 金鹰重型工程机械有限公司 拖链装置
AT523825B1 (de) * 2020-07-03 2021-12-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Maschine und Verfahren mit einem Stopfaggregat
CN112160197B (zh) * 2020-10-21 2024-07-16 中国铁建高新装备股份有限公司 捣固装置及捣固车
CN112160196A (zh) * 2020-10-21 2021-01-01 中国铁建高新装备股份有限公司 捣固装置及捣固车
AT526293A1 (de) * 2022-07-05 2024-01-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat und Verfahren zum Unterstopfen von Schwellen eines Gleises

Family Cites Families (3)

* 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
CH597429A5 (de) * 1977-02-18 1978-04-14 Matisa Materiel Ind Sa

Also Published As

Publication number Publication date
JPH0130962B2 (de) 1989-06-22
DE3165697D1 (en) 1984-09-27
US4440089A (en) 1984-04-03
CH650819A5 (de) 1985-08-15
ATE9107T1 (de) 1984-09-15
EP0050889A1 (de) 1982-05-05
ZA817248B (en) 1982-09-29
JPS57133903A (en) 1982-08-18

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