US3016023A - Actuating mechanism for pivotal and vibratory ballast tamping tools - Google Patents

Actuating mechanism for pivotal and vibratory ballast tamping tools Download PDF

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Publication number
US3016023A
US3016023A US856074A US85607459A US3016023A US 3016023 A US3016023 A US 3016023A US 856074 A US856074 A US 856074A US 85607459 A US85607459 A US 85607459A US 3016023 A US3016023 A US 3016023A
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tamping
tools
eccentric shaft
tamping tools
tool
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US856074A
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English (en)
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Plasser Franz
Theurer Josef
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    • 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 ballast tamping machines carrying one or several ballast tamping tools, preferably pairs of cooperating tamping tools which are simultaneously vibrated and pivoted together to compact ballast between their jaws. More particularly, this invention relates to the actuating mechanism for such tamping tools.
  • the tamping tools are preferably mechanically vibrated by the rotation of an eccentric shaft engaging mounting arms for the tools while the distance between the tamping tool jaws of cooperating tools is varied by pressure fluid, preferably hydraulically, operated means.
  • pressure fluid preferably hydraulically, operated means.
  • the nut constitutes a relatively satisfactory dead center for the tool but the mechanical distance adjustment of the tamping tools is generally not satisfactory for modern, fast-operating tampers.
  • hydraulic means is used to move the vibration centers of the tamping tools and thereby to vary their distance, it has been found difficult, if not impossible, to eliminate vibrations which are then transferred by the hydraulic means to the tamping tool carrier and thence to the mobile track tamping carriage and the rails themselves.
  • the present invention is based on the concept that no harm is done to a pressure fluid operated pivoting mechanism if it is subjected to vibrations and that such vibrations will not interfere with its operation and will not be transmitted to its fixed support. On the other hand, it is relatively simple to retain the vibration center of each tamping tool against vibration when the pivoting mechanism is structurally separated from the vibration center retaining means.
  • FIG. 1 is a schematic side view, partly in section, of an actuating mechanism for a pair of cooperating tamping tools according to one embodiment of the invention
  • FIG. 2 is a view similar to that of FIG. 1 of another embodiment of the actuating mechanism.
  • FIG. 3 illustrates a modification of the embodiment of FIG. 2.
  • the present invention constitutes an improvement of an otherwise well known type of track tamping machine exemplified but in no way limited to the type dis closed in our U. S. Patent No. 2,876,709, the description is confined to the specific improvement and to such parts as necessarily cooperate with it or as may be necessary to a complete understanding of it. For this reason the only conventional part of the mobile track tamping machine per se, which is indicated in the drawing, is the vertically adjustable tamping tool carrier.
  • FIG. 1 there is shown an eccentric shaft 1 journaled in the bearings 7 of vertically adjustable tamping tool carrier 11.
  • the eccentric shaft vibrates the tamping tools 3 by reciprocating or oscillating tool mounting arms 2 when the shaft is rotated.
  • the upper ends of the tamping tools 3 are pivoted to mounting arms 2 at 4 whereby the oscillating motion of the mounting arms is transferred to the tamping tools to vibrate the same.
  • the mounting arms for the tamping tools are constituted for a fixed element and an element which is relatively glidable by pressure fluid means whereby the arm length may be adjusted.
  • the illustrated mechanism is a hydraulic cylinder-and-piston device used for varying the relative distance of the cooperating tamping tools 3 in a manner known per so.
  • the tools are held in fixed bearings 8 which are mounted on tamping tool carrier 11.
  • the closing and opening movement of the lower ends or jaws 5 of the tamping tools, which are immersed in the ballast during the tamping operation, is effected by the hydraulic cylinder-and-piston device which will now be described.
  • the cylinders 26 are divided by piston 27 into two chambers. Chambers 9 receive pressure fluid from conduits 23 while a compression spring 29 is mounted in each chamber 10.
  • Piston rod 23, which is the glidable element, is fixedly connected to piston 27 and has the upper end of a respective tamping tool linked to its outer end at 4.
  • spring 29 biases the piston and its piston rod inwardly, thus swinging the associated tamping tool outwardly about its pivot 6, in which position the jaws 5 are at their farthest distance from each other, i.e., the cooperating tamping tools are open.
  • the pressure fluid is a hydraulic liquid which may be supplied to cylinder chambers 9 from a hydraulic liquid supply constituted by tank 19.
  • a control valve 24, with alternate positions I and H, is mounted in pressure fluid supply line 23 and pump 18 will supply hydraulic liquid to the cylinder chambers 9 when the control valve is in one position while the liquid will be returned to the storage tank by return conduit 25 when the valve 24 is in the other or closed position.
  • a pressure safety line 21 with its pressure relief valve 22 regulates the maximum pressure in conduit 23 at all times.
  • FIG. 2 illustrates an embodiment in which each tamping tool forms a unitary element with its mounting arm, thus constituting a bell crank lever.
  • the horizontal or mounting arm of each tamping tool 3a is engaged by eccentric shaft 1a whereby rotation of the shaft transmits an oscillatory or vibratory motion to the tamping tools and their tamping jaws a.
  • Each bell crank is pivoted at its apex 6a to tamping tool carrier 11a. It may be advantageous to mount the pivots of the tamping tools yieldingly at least in one plane. In the illustrated embodiment, the pivots are yieldingly mounted in a horizontal plane on leaf springs 36 which are securely clamped to the tamping tool carrier at brackets 37.
  • the pincer movement of tamping jaws 5a is effected by vertically moving the eccentric shaft 1a in its bearing 38.
  • the eccentric shaft serves not only to vibrate the tamping tools by its rotation but also as a fulcrum for the pivoting motion of the two mounting arms which form a unit with the tamping tools.
  • the vertical adjustment of the eccentric shaft is effected in the illustrated embodiment by a cylinder-and-piston mechanism including a cylinder 39 glidably holding a piston 31 with its piston rod 32 which operatively engages the eccentric shaft so that the shaft is vertically reciprocated by reciprocation of piston rod 32.
  • Pressure fluids such as hydraulic liquid
  • the hydraulic system may be the same or similar to that illustrated in FIG. 1 to supply pressure fluid to the cylinder when it is desired to close the jaws.
  • the compression spring 33 Upon discontinuance of the pressure fluid supply, the compression spring 33 will automatically move the eccentric shaft down again into the illustrated or open position, for which purpose no great force is required.
  • the cylinder 30 is pivotally mounted in bracket 34 of carrier 11a.
  • the horizontal vibrations generated by the rotation of the eccentric shaft are absorbed by leaf springs 36.
  • FIG. 3 A modification of the embodiment of FIG. 2 is shown in FIG. 3 wherein the horizontal vibrations are absorbed in a ditferent manner.
  • the apex 6b of bell crank tamping tool 31 is pivoted to a fixed bracket 39 of tamping tool carrier 1112 while the mounting arms include elements 2b telescoped in the mounting arm elements of the bell cranks so that the two mounting arm elements may glidably move in relation to each other in guide slots 40 of the horizontal arms of the bell cranks.
  • rotation of eccentric shaft ia will oscillate or vibrate the tamping tools but the horizontal component of this vibratory motion will not be transmitted to the tools because the mounting arms 2b freely glide in slots 40 and thus absorb this motion.
  • eccentric shaft 1a also serves as fulcrum for a pivoting motion of the two mounting arms which engage the tamping tools and pivot them simultaneously.
  • Closing and opening of the tamping jaws 5b is effected by the same mechanism as described in connection with FIG. 2, identical reference numerals being applied to these parts.
  • the cylinder 30 is fixedly mounted in the tamping tool carrier 11]) of this embodiment, rather than being pivoted thereto, as in FIG. 2.
  • the embodiments of FIGS. 2 and 3 are structurally and functionally identical.
  • a tamping mechanism comprising a pivotal and vibratory ballast tamping tool, a tamping tool carrier, a fixed pivot mounting said tamping tool on said carrier, the tool being pivotal about said pivot, a mounting arm connected to the tamping tool, an eccentric shaft mounted on said carrier and operatively engaging the mounting arm whereby the mounting arm and the associated tamping tool are vibrated upon rotation of the eccentric shaft, and a pressure fluid operated means operatively connected with said tamping tool for pivoting the tamping tool about said fixed pivot, the vibratory and pivoting motion being applied at the same point of the tamping tool, which point is removed from the vibration or dead center of the tool.
  • a tamping mechanism comprising a pair of pivotal and vibratory, cooperating ballast tamping tools, a tamping tool carrier, a substantially horizontal mounting arm connected to each of the cooperating tamping tools, a substantially horizontal eccentric shaft mounted on said carrier and extending perpendicularly to and between the mounting arms, the eccentric shaft operatively engaging the mounting arms whereby the mounting arms and the associated tamping tools are vibrated upon rotation of the eccentric shaft, a fixed pivot mounting each of the cooperating tamping tools on said carrier intermediate the ends of the tamping tools, and a hydraulic pressure means operatively connected with and pivoting each of said tamping tools about a respective one of said pivots for varying the distance between the lower ends of the tamping tools, the vibratory and pivoting motion being applied at the same point of the tamping tools, which points are removed from the respective fixed pivots of said tools.
  • a tamping mechanism comprising a pair of pivotal and vibratory, cooperating ballast tamping tools, a tamping tool carrier, a substantially horizontal mounting arm for each of the cooperating tamping tools, each mounting arm being constituted by a fixed element and an element glidable in relation to the fixed element whereby the length of the arm may be adjusted, pressure fluid means for moving the two elements relative to one another, the upper end of each tamping tool being linked to a respective one of said glidable elements of the mounting arms, a substantially horizontal eccentric shaft mounted on said carrier and extending perpendicularly to and between the mounting arms, the eccentric shaft operatively engaging the fixed elements of the mounting arms whereby the mounting arms and the associated tamping tools are vibrated upon rotation of the eccentric shaft, and a fixed pivot mounting the tamping tools on said carrier approximately mid-point at the dead center of each tamping tool.
  • a tamping mechanism comprising a pair of pivotal and vibratory, cooperating ballast tamping tools, each tool being constituted by a bell crank consisting of a tamping arm and a substantially horizontal mounting arm, the two arms of the bell crank meeting at an apex, a tamping tool carrier, a substantially horizontal eccentric shaft mounted on said carrier and extending perpendicularly to and between the mounting arms, the eccentric shaft operatively engaging the mounting arms whereby the mounting arms and the associated tamping tools are vibrated upon rotation of the eccentric shaft, a fixed pivot mounting each of the cooperating tamping tools at the apex of each bell crank on the carrier, and a hydraulic pressure means operatively connected with and vertically moving the eccentric shaft, the eccentric shaft forming a fulcrum for said mounting arms whereby the bell cranks are pivoted about their respective pivots upon vertical movement of the fulcrum.
  • a tamping mechanism comprising a pair of pivotal and vibratory, cooperating ballast tamping tools, each tool being constituted by a bell crank consisting of a tamping arm and a substantially horizontal mounting arm, the two arms of the bell crank meeting at an apex, a tamping tool carrier, a substantially horizontal eccentric shaft mounted on said carrier and extending perpendicularly to and between the mounting arms, the eccentric shaft operatively engaging the mounting arms whereby the mounting arms and the associated tamping tools are vibrated upon rotation of the eccentric shaft, a fixed pivot mounting each of the cooperating tamping tools at the apex of each bell crank on the carrier, means for yieldingly supporting each pivot in a horizontal plane defined by the mounting arms and the eccentric shaft, and a hydraulic pressure means operatively connected with and vertically moving the eccentric shaft, the eccentric shaft forming a fulcrum for said mounting arms whereby the bell cranks are pivoted about their respective pivots upon vertical movement of the fulcrum.
  • a tamping mechanism comprising a pair of pivotal and vibratory, cooperating ballast tamping tools, each tool being constituted by a bell crank consisting of a tamping arm and a substantially horizontal mounting arm, the two arms of the bell crank meeting at an apex and each mounting arm consisting of two elements telescoped into each other for relative gliding motion, a tamping tool carrier, a substantially horizontal eccentric shaft extending perpendicularly to and between the mounting arms, the eccentric shaft mounted on said carrier and operatively engaging one of said mounting arm elements of each tamping tool whereby the mounting arms and the associated tamping tools are vibrated upon rotation of the eccentric shaft, a fixed pivot mounting each of the cooperating tamping tools at the apex of each bell crank on the carrier and a hydraulic pressure means operatively connected with and vertically moving the eccentric shaft, the eccentric shaft forming a fulcrum for said mounting arms whereby the bell cranks are pivoted about their respective pivots upon vertical movement of the fulcrum

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
US856074A 1958-12-02 1959-11-30 Actuating mechanism for pivotal and vibratory ballast tamping tools Expired - Lifetime US3016023A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT835658A AT209933B (de) 1958-12-02 1958-12-02 Gleisstopfmaschine

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US3016023A true US3016023A (en) 1962-01-09

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US856074A Expired - Lifetime US3016023A (en) 1958-12-02 1959-11-30 Actuating mechanism for pivotal and vibratory ballast tamping tools

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US (1) US3016023A (de)
AT (1) AT209933B (de)
CH (1) CH380769A (de)
DE (1) DE1147613B (de)
FR (1) FR1242519A (de)
GB (1) GB903006A (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3190234A (en) * 1962-02-08 1965-06-22 Matisa Materiel Ind Sa Method of tamping the ballast of a railway track and device for the execution of this method
US3429277A (en) * 1966-08-05 1969-02-25 Plasser Bahnbaumasch Franz Ballast tamping assembly
US3430579A (en) * 1966-03-15 1969-03-04 Australian Railway Equipment Tamping tool
US4218978A (en) * 1977-02-18 1980-08-26 Matisa Materiel Industriel S.A. Apparatus for tamping or packing the bed of railway tracks
CN108291368A (zh) * 2015-11-20 2018-07-17 普拉塞-陶伊尔铁路机械出口股份有限公司 用于捣固轨道的捣固单元和方法
EP3320144A4 (de) * 2015-07-10 2019-02-27 Harsco Technologies LLC Werkstückspindelstockanordnung für schienenanwendungen

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT258339B (de) * 1963-11-29 1967-11-27 Plasser Bahnbaumasch Franz Hydraulisch betätigbare Einrichtung zur gegenläufigen Verstellung paarweise einander gegenüberliegend angeordneter Werkzeuge von Gleisstopfmaschinen
CN114808566B (zh) * 2022-04-20 2023-01-31 昆明理工大学 一种铁路道床变频捣固机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1043245A (en) * 1911-11-10 1912-11-05 Bertil Ohman Tamping-machine.
DE830352C (de) * 1950-03-01 1952-02-04 Frankfurter Maschb A G Vorm Po Gleisstopfmaschine
FR1089185A (fr) * 1952-12-10 1955-03-15 Machine à bourrer le ballast
US2791971A (en) * 1952-08-22 1957-05-14 Meer Ag Maschf Track-packing machines
AT201644B (de) * 1957-02-04 1959-01-10 Matisa Materiel Ind Sa Geleisestopfmaschine
US2919656A (en) * 1957-04-11 1960-01-05 Plasser Franz Ballast moving attachment for track tamping machines

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT182113B (de) * 1953-11-30 1955-05-25 Plasser Bahnbaumasch Franz Einrichtung bei Geleisstopfmaschinen zum gegenseitigen Verstellen paarweise angeordneter Stopfwerkzeuge
CH315255A (fr) * 1954-04-06 1956-08-15 Matisa Materiel Ind Sa Bourreuse de ballast de voies ferrées
BE548351A (de) 1955-06-14
DE1017639B (de) 1955-09-19 1957-10-17 Deutsche Bundesbahn Gleisstopfmaschine mit als heb- und senkbare, schwenkbare Kniehebel ausgebildeten Stopfwerkzeugen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1043245A (en) * 1911-11-10 1912-11-05 Bertil Ohman Tamping-machine.
DE830352C (de) * 1950-03-01 1952-02-04 Frankfurter Maschb A G Vorm Po Gleisstopfmaschine
US2791971A (en) * 1952-08-22 1957-05-14 Meer Ag Maschf Track-packing machines
FR1089185A (fr) * 1952-12-10 1955-03-15 Machine à bourrer le ballast
AT201644B (de) * 1957-02-04 1959-01-10 Matisa Materiel Ind Sa Geleisestopfmaschine
US2919656A (en) * 1957-04-11 1960-01-05 Plasser Franz Ballast moving attachment for track tamping machines

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3190234A (en) * 1962-02-08 1965-06-22 Matisa Materiel Ind Sa Method of tamping the ballast of a railway track and device for the execution of this method
US3430579A (en) * 1966-03-15 1969-03-04 Australian Railway Equipment Tamping tool
US3429277A (en) * 1966-08-05 1969-02-25 Plasser Bahnbaumasch Franz Ballast tamping assembly
US4218978A (en) * 1977-02-18 1980-08-26 Matisa Materiel Industriel S.A. Apparatus for tamping or packing the bed of railway tracks
EP3320144A4 (de) * 2015-07-10 2019-02-27 Harsco Technologies LLC Werkstückspindelstockanordnung für schienenanwendungen
US10844550B2 (en) 2015-07-10 2020-11-24 Harsco Technologies LLC Workhead assembly for rail applications
CN108291368A (zh) * 2015-11-20 2018-07-17 普拉塞-陶伊尔铁路机械出口股份有限公司 用于捣固轨道的捣固单元和方法

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Publication number Publication date
CH380769A (de) 1964-08-15
GB903006A (en) 1962-08-09
DE1147613B (de) 1963-04-25
FR1242519A (fr) 1960-09-30
AT209933B (de) 1960-07-11

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