US2915018A - Track tamping machine - Google Patents

Track tamping machine Download PDF

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Publication number
US2915018A
US2915018A US644638A US64463857A US2915018A US 2915018 A US2915018 A US 2915018A US 644638 A US644638 A US 644638A US 64463857 A US64463857 A US 64463857A US 2915018 A US2915018 A US 2915018A
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Prior art keywords
tamping
pump
tool
tools
pressure
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Expired - Lifetime
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US644638A
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English (en)
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Plasser Franz
Theurer Josef
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Individual
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Individual
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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 track tamping machines which are movable along railroad tracks to pack ballast under the railroad ties. More particularly, this invention relates to ballast tamping machines of the type wherein vibratory tamping tools are arranged in pairs, each tool being linked to a nut mounted on a rotatable threaded spindle whereby the distance between the tamping tools of each pair may be varied by rotating the spindle and thereby moving the nut therealong.
  • ,It is the principal object of the present invention to provide a track tamping machine wherein the advantages of the mechnical and hydraulic operation of the tamping tool distance varying devicesare' combined While the respective disadvantages of each of these prior systems are fully tavoided.
  • each tamping tool has its own, separately rotatable spindle and, accordingly, its own hydraulically operated driving means so :that the tools may be adjusted asynchronously and individually 2,915,018 Patented Dec. 1, 1959 ice in response to the pressure encountered by each tool in the ballast.
  • the separate driving means for each tool of a tamping tool aggregate are preferably connected to a single hydraulic fluid pump and are interconnected by a single conduit system.
  • the prior hydraulically-operated tamping tool distance varying devices had additional. disadvantages. While the tamping tools remained immobile, the hydraulic fluid coming from the continuously operating pump had to be returned to the fluid storage tank by means of safety valves mounted in the fluid conduit to delimit the maximum pressure therein. During extended operations, the passage of the fluid through the safety valve caused it to be undesirably heated. Furthermore, while the tamping tool's stood idle, the entire driving energy applied to the pump was uselessly, wasted.
  • an infinitely variable pump is provided to supply hydraulic fiuid to the spindle driving means.
  • the capacity or delivery rate of this pump is automatically varied between zero and a predetermined maximum by the pressure the moving tamping tools encounter in the ballast or at a stop.
  • Fig. l' is aside view, partly in section, of the front part of 'a track tamping machine
  • Fig. 2 schematically illustrates the hydraulic fluid conduit and control means actuating the driving mechanism for the spindle of each tamping tool
  • Fig. 3 is a sectional view of the hydraulic fluid pump.
  • Fig. 4 shows a detail of the pump control means.
  • a track tamping machine moving on track 42 mounted on ties 43 which are supported in ballast 41.
  • the tamping tool carrier 3 is vertically slidably supported on posts 2 mounted in the carriage frame.
  • Eccentric'shaft 5 is journaled in the carrier 3 and vibrates the tamping tools 4 by reciprocating or oscillating tool mounting arms '6 when the shaft is rotated.
  • the tamping tools are pivoted to arms 6 at their upper ends. .All .this structure is conventional and is described, for instance, in our above-mentioned patent application.
  • Each tool is pivoted intermediate its ends at 10 to a longitudinally s'hiftable nut 7 mounted on a rotatable threaded spindle 8.
  • the spindles are rotatably journaled in bearings '8 and 8", 8 being centrally mounted to receive the inner ends of two adjacent spindles controlling themovement of one pair of tamping tools and a bearing 8" being mounted for receiving the outer end of each tool.
  • an integral portion 7 of each nut is slidably supported and guided on longitudinal guide rod 9 rigidly mounted in tamping tool carrier 3.
  • stops 11 being removable from guide rod 9 to permit a wider outward stroke of the tamping tools to fixed stops 11'. This is desirable in case of tamping wider ties.
  • A'preferred arrangement for moving stops 11 is described and claimed in our copending application Serial No. 629,183, filed December 18, 1956, now Patent No. 2,872,878.
  • a gear wheel 15 is keyed to each rotatable spindle 8 outside bearing 8", each gear 15 meshing with a gear wheel 14 which, in turn, is engaged by pinion 13.
  • This gear transmission serves to transmit rotary motion from the hydraulically operated drive 12 to the associated spindle 8.
  • Hydraulically operated driving systems which convert the hydraulic pressure of a fluid supplied to it under pressure by a pump, for instance, into a rotary motion like a turbine are well known per se. Many types of such hydraulically operated rotary driving systems are known and, since their specific structure is of no importance in respect of the present invention, they are not further described so as to limit the description to the specific improvement provided by this invention 1.
  • the supply conduit system of hydraulic fluid, such as oil from storage tank 18 to the driving systems 12 is schematically illustrated in Fig. 2.
  • Pump 19 is mounted on the tamping tool carrier 3 in supply pipe 16 which leads from the oil storage tank to the pump.
  • the hydraulic fluid is delivered through pump output pipe 21 to the cylinder 22 which houses a slidable rod with a plurality of pistons 23 to regulate the fluid supply to the driving systems 12.
  • Return pipe 26 is connected to cylinder 22, leading back to the oil storage tank.
  • FIG. 2 there are four driving systems with their pinions 13 to drive the associated spindles 8 moving the four tamping tools of a tool aggregate adapted to tamp ballast at both sides of track 42.
  • Supply conduit systems 24 and 25 lead from cylinder 22 to each of the driving systems 12.
  • the slidable rod with its pistons 23 is reciprocable in cylinder 22 by actuating the lever 27.
  • a branch pipe 28 leads from pump output pipe 21 to a control element which consists of cylinder 29 housing piston rod 31 with piston 30.
  • the piston is biased by spring 34.
  • the piston rod is linked to rod 32 which engages pin 33 mounted on the pivotable element 20 of pump 19, the pin cooperating with longitudinal slot 32' of rod 32 (see Fig. 4).
  • Another branch pipe 35 leads from supply conduit 25 to a second control element consisting of cylinder 36 housing piston rod 37 with piston 37.
  • Piston 37 is biased by spring 38.
  • Piston rod 37' is connected to rod 39 which also engages pin 33 with its longitudinal slot 39' (see Fig. 4).
  • the pivotable element 20 of the pump is biased by spring 40 connected to its outer end and to the tamping tool carrier to hold the element 20 normally at an angle in position I (see Fig. 3).
  • Infinitely variable pumps are well known and have been used for many purposes where it is desired to adjust the pump delivery rate or capacity smoothly and gradually.
  • a preferred pump of this type is shown in Fig. 3.
  • Pump drive shaft 17 is journaled in the fixed pump portion 19, inlet pipe 16 and output pipe 21 being connected to portion 19 at opposite sides thereof.
  • Cylinder 19" is mounted on pump portion 19 and glidably houses two pistons 19' whose piston rods are connected to pivotable pump portion 20 by means of universal X joints 20".
  • the pivotable pump portion is mounted on cylinder 19" by means ofa shaft with the universal joint 20'.
  • Position I indicates the maximal angle of pivotable pump element 20, at which point the capacity of the pump is also at a maximum because the length of the stroke of pistons 19' is at a maximum.
  • vIn position H the pump portions are coaxial and the pump will deliver for instance in Letters Patent No. 956,570, dated May 3, 1910.
  • the tamping tool distance varying mechanism of the invention operates as follows:
  • control lever 27 When the track tamping machine is moved into tamping position so that the pairs of tamping tools forming the tamping tool aggregate are placed over a tie and the tamping tool carrier is lowered to position the lower ends of the tamping tools into the ballast, as shown in Fig. 1, control lever 27 is thrown into position A (full lines). In this position, the rotating pump will deliver hydraulic fluid, i.e. oil, through output pipe 21 to cylinder 22 whence the fluid will flow under pressure through conduit system 24 into the four driving systems 12. The hydraulic pressure in the driving systems will rotate pinions 13 and accordingly meshing gears 14 and 15.
  • hydraulic fluid i.e. oil
  • the characteristics of spring 34 are preferably so chosen that that pressure in conduit system 24 and, therefore, the compression force of tamping tools 4 increases slowly.
  • the pivotable portion 20 is moved into axial alignment with the pump portion 19 so that the pump is in position II. In this position, no further fluid is delivered by the pump. Thus, the pump will use no energy when the tamping tools stand still or only so much energy as is required to maintain the pressure in the conduits.
  • the pump delivery rate is thus slowly decreased to zero.
  • the pump will also stop until control lever 27 is thrown into position A again to start a new tamping cycle.
  • the second control element 36, 37, 38' is so dimensioned and arranged that it responds much more quickly to increased pressure in the pipe 35 than the first control element 29, 30, 34 responds to increased pressure in pipe 28.
  • the reason for this is that the first control element is designed to become effective during the tamping movement of the tamping tools, i.e., at high pressure, while the second control element should act quickly during the pressureless opening movement of the tamping tools.
  • Fig. 4 illustrates the purpose of elongated slots 32' and 39 used to connect the above control elements to the pivotable pump portion 20.
  • each control element can act upon pin 33 of portion 20 independently of the other control element, i.e. the rod 32 can depress pin 33 by the length of slot 39' without moving rod 39 while rod 39 can pull the pin down by the length of slot 32 without disturbing rod 32.
  • the present invention is based on the concept that unexpected improvements in a tamping tool distance varying mechanism can be achieved when the known tool spindle drives are actuated hydraulically, inasmuch as such an arrangement avoids all the disadvantages of the purely mechanically operated drives while eliminating the faults of the newer purely hydraulic drive means.
  • the hydraulically-operated driving system includes a separate drive for each spindle and the hydraulic pressure fluid supply means comprises a single fluid pump and fluid conduit system interconnecting the separate spindle drives, and comprising means for reversing the direction of rotation of each spindle drive, said reversing means comprising an adjustable control valve connected in the fluid conduit system between the pump and the separate spindle drives, said conduit system including two separate conduits each connected between the control valve and all spindle drives, and means for adjusting the control valve to connect selectively one and the other of said two separate conduits to the pump.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
US644638A 1956-03-10 1957-03-07 Track tamping machine Expired - Lifetime US2915018A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT342595X 1956-03-10

Publications (1)

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US2915018A true US2915018A (en) 1959-12-01

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ID=3672178

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Application Number Title Priority Date Filing Date
US644638A Expired - Lifetime US2915018A (en) 1956-03-10 1957-03-07 Track tamping machine

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US (1) US2915018A (en(2012))
CH (1) CH342595A (en(2012))
DE (1) DE1051307B (en(2012))
FR (1) FR1172785A (en(2012))
NL (1) NL98235C (en(2012))

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH285504A (de) * 1949-12-06 1952-09-15 Maerklin & Cie Gmbh Geb Kugelgelenkkupplung für Antriebswellen in Spielzeug- und Modellbahnfahrzeugen.
FR1029682A (fr) * 1949-12-05 1953-06-04 Matisa Materiel Ind Sa Perfectionnements aux machines à bourrer le ballast des voies de chemin de fer
FR1101408A (en(2012)) * 1953-06-02 1955-10-06
US2791971A (en) * 1952-08-22 1957-05-14 Meer Ag Maschf Track-packing machines

Family Cites Families (2)

* 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.
BE524944A (en(2012)) * 1952-12-10

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1029682A (fr) * 1949-12-05 1953-06-04 Matisa Materiel Ind Sa Perfectionnements aux machines à bourrer le ballast des voies de chemin de fer
CH285504A (de) * 1949-12-06 1952-09-15 Maerklin & Cie Gmbh Geb Kugelgelenkkupplung für Antriebswellen in Spielzeug- und Modellbahnfahrzeugen.
US2791971A (en) * 1952-08-22 1957-05-14 Meer Ag Maschf Track-packing machines
FR1101408A (en(2012)) * 1953-06-02 1955-10-06

Also Published As

Publication number Publication date
NL98235C (en(2012))
CH342595A (de) 1959-11-30
FR1172785A (fr) 1959-02-16
DE1051307B (de) 1959-02-26

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