US3735708A - Drive for vibrating a track maintenance machine tool - Google Patents

Drive for vibrating a track maintenance machine tool Download PDF

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Publication number
US3735708A
US3735708A US00132048A US3735708DA US3735708A US 3735708 A US3735708 A US 3735708A US 00132048 A US00132048 A US 00132048A US 3735708D A US3735708D A US 3735708DA US 3735708 A US3735708 A US 3735708A
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Prior art keywords
tool
motor
pressure
chamber
spring
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US00132048A
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English (en)
Inventor
F Plasser
J Theurer
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Franz Plasser Bahnbaumaschinen Industrie GmbH
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • 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
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B2203/00—Devices for working the railway-superstructure
    • E01B2203/12—Tamping devices
    • E01B2203/127—Tamping devices vibrating the track surface

Definitions

  • a drive for vibrating a track maintenance tool such as a ballast tamper or a track lining unit, comprises a pneumatic or hydraulic motor with two pistons which are linearly reciprocated under the pressure of a unidirectionally flowing pressure fluid whose altemating pressure direction is controlled by a valve in the motor.
  • a ballast tamping tool has a holder which carries the ballast engaging tool part and a hydraulic motor causing the tool part to vibrate while it engages the ballast.
  • the entire unit forms a vertically adjustable lever reciprocable in the direction of tract elongation for tamping ballast under an adjacent tie.
  • Such a structural unit may be mounted on the machine at the most advantageous position for effectuating the work without being tied to a specific location of a drive since the drive is incorporated into the unit itself.
  • Hydraulic of pneumatic drives in the form of motors with linearly reciprocating piston means have been proposed for causing the oscillating motion of vibratory conveyors and the like because of their compact construction.
  • the drive must pro prise a sufiiciently high vibratory frequency of the tools to make them efficient in commercial operations and, additionally, must be so compact and readily connectable to the tool or tools it is to vibrate that the entire operating unit may be advantageously positioned on the machine for most efficient tamping, lining, etc.
  • a pressure fluid operated motor operatively connected to the tool and including a linearly reciprocating piston means and means for continuously supplying a unidirectionally flowing pressure fluid to the piston means for reciprocating the same.
  • the pressure fluid is supplied continuously to the motor in a unidirectional flow, rather than being supplied for constantly alternating flow in opposite directions, the efiiciency of the drive, i.e. the vibratory frequency, is greatly increased in comparison with the type of hydraulic drive motor conventionally used for vibrating track maintenance tools.
  • the motor comprises a housing with a transverse wall dividing the housing into two chambers and having a bore for interconnecting the chambers.
  • a flip-flop valve means is mounted on the transverse dividing wall for alternately opening and closing the bore upon linear reciprocation.
  • a piston rod is slidably journaled in the dividing wall and extends axially through the housing, with two pistons respectively mounted on the rod in respective ones of the housing chambers.
  • a pressure fluid inlet leads to one chamber and a pressure fluid return line is connected to the other chamber.
  • the flip-flop valve means is positioned to close the return line when it opens the connecting bore and to open the return line when it closes the connecting bore.
  • Spring means is mounted in the housing to exert axial pressure on the flip-flop valve means in alternate directions to produce the linear reciprocation thereof.
  • a pressure fluid operated motor of this type is not only readily adjustable in respect of the frequency of piston reciprocations, i.e. vibratory frequency, in dependence on the flow rate of the pressure fluid but also in respect of the reciprocatory stroke of the pistons in dependence on the pressure of the fluid.
  • This ready ad-. justability of the motor makes it possible to attune the vibratory drive as much as desirable to the local operating conditions, particularly the spot conditions of the ballast bed.
  • the frequency and amplitude of the vibrations may be readily changed in accordance with such parameters as the size of the ballast rocks and the density of the ballast, etc.
  • a mechanism may be operatively connected respectively to the linearly reciprocating piston means of the motor and to the tool for changing the direction of the reciprocating movement.
  • a vertical reciprocation of the motor pistons may be converted into a horizontal vibratory motion of the tool extending in the same direction, for instance, as the reciprocation of the tool in the direction of track elongation.
  • FIG. It is a vertical section showing a hydraulic motor used as a drive for vibrating track maintenance tools, including a mechanism for changing the direction of the reciprocatory movement and a hydraulic supply circuit for the motor;
  • FIG. 2 schematically illustrates a motor of this type associated, respectively, with a single surface ballast tamper and a single tie tamping tool;
  • FIG. 3 is a schematic front view of an arrangement wherein the motor is associated with surface tampers designed to tarnp the flanks of a ballast bed;
  • FIG. 4 is a schematic side view of a twin tie tamping unit and a track lining unit each associated with a motor of the indicated type;
  • FIG. 5 is a top view of the track lining unit shown in FIG. 4;
  • FIG. 6 is a schematic side view of another type of twin tie tamping unit incorporating the motor
  • FIG. 7 is a schematic side view of another tamping arrangement incorporating the motor
  • FlG. 1-3 is a top view of the arrangement of FIG. 7;
  • FIG. 9 is a schematic side view of yet another tamping arrangement incorporating the motor.
  • the motor is shown to comprise a housing 1 having two axially spaced end walls and a transverse wall 4 dividing the motor housing into two chambers 5 and 6.
  • a bore 7 in the dividing wall interconnects the chambers.
  • a flip-flop valve means 3 is mounted on the transverse dividing wall for alternately opening and closing the bore 7 upon linear reciprocation.
  • the illustrated flip-flop valve means 3 includes two valve plates 3a and 3b each of which is mounted in one of the chambers 5, 6 adjacent the dividing wall 4.
  • a plurality of spacing rods 3c interconnects the two valve plates, the length of the spacing rods exceeding the width of the dividing wall 4 and the spacing rods being slidably journaled in the wall for linear reciprocation therein in an axial direction.
  • a piston rod 2 is slidably journaled in the dividing wall and extends axially through the motor housing 1.
  • Two pistons 2a and 2b are mounted on the rod in respective ones of the motor housing chambers 5 and 6 to constitute a piston means mounted for linear reciprocation in the direction of the axis of the motor.
  • the piston rod 2 slidably passes through the valve plates 3a and 3b, and the pistons 2a and 2b are respectively slidably journaled in axial bores in the end walls of housing 1.
  • a pressure fluid inlet in the one chamber 5 receives pressure fluid from supply line 12 and a pressure fluid return line 14- is connected to the other chamber 6.
  • valve plate 3a in the one chamber 5 extends over bore 7, which interconnects the chambers, and the plate 31) in the other chamber 6 extends of another bore 17 in wall 4, which is connected to the return line 34, while leaving the chamber interconnecting bore 7 uncovered by means of a port lid in regisu'y with bore 7.
  • the flip-flop valve means 7 is thus positioned to close the return line 14 when it opens the connecting bore 7 and to open the return line when it closes the connecting bore.
  • Spring means is mounted in the motor housing to exert axial pressure on the flip-flop valve means in alternate directions to produce the linear reciprocation thereof.
  • the illustrated spring means comprises a compression spring 3 in chamber 5 and a compression spring 9 in chamber 6.
  • One end of each spring bears against a respective one of valve plates 3a, 3b and the other end of each spring bears against a respective spring seat in, 11 movable with, and in the direction of, a respective one of pistons 2a, 2b.
  • each spring seat is an annular member having an outer diameter exceeding the diameter of the associated piston and an inner diameter smaller than the diameter of the piston to leave an annular clearance between the piston rod and the associated piston whereby the pressure fluid has access to the pistons.
  • the motor In the piston means position illustrated in FIG. 1, the motor is shown in the idling condition, i.e. no hydraulic fluid is supplied to the motor.
  • the bias of spring 9 having been chosen to exceed that of spring 8, the flip-flop valve 3 is depressed in the absence of fluid pressure in the motor housing so that valve plate 3a is spaced from bore 7 and thus keeps communication between the chambers 5 and 6 open through this bore 7 and port 3d while valve plate 3b is pressed against the other bore 17 in dividing wall 4 to close access to pressure fluid return line 1. 2.
  • the hydraulic circuit for the motor includes a hydraulic fluid sump 15, an adjustable pump 13 delivering fluid from the sump to supply line 12, and a pressure relief valve 16 connecting the supply line with the sump.
  • the flip-flop valve means can never be in an unstable condition because the compression springs 8, 9 cause each axial movement of the piston rod to be effected by instantaneous impact.
  • the valve plates could assume an intermediate position when neither of plates 30, 3b is in contact with the dividing wall 4. This could cause some difficulty in starting the motor, wherefore the pressure of one spring is set dfierently from that of the other spring so that one of the valve plates will be pressed against the dividing wall 4i.
  • the motor also comprises a mechanism lid operatively connected respectively to the linearly reciprocating piston means and to a tool for changing the direction of the reciprocating movement although it will be clearly understood that such a mechanism will be required or desirable only for the operation of certain types of track maintenance working tools.
  • the illustrated mechanism is arranged to convert the linear reciprocating movement of the piston means 20, 2b into a reciprocating movement extending in a direction perpendicular thereto, i.e. fi'orn vertical to horizontal.
  • a tool holder 22 has a connecting head 2i which is mounted for transverse vibrating movement (see horizontal, two-headed arrow) on an intermediate mount fixed to one of the end walls of the motor housing l.
  • the connecting head is slidably mounted on a guide track in the mount and is biased against the piston means of the motor by a spring 23 hearing respectively against the connecting head and a stop 241 projecting from mount 2th.
  • the mechanism lid includes two cooperating inclined planes l3 respectively mounted coaxially with the piston means and projecting from one free end of piston rod 2 and in a recess in the connecting head 211 so that the vertical reciprocating motion of the piston rod is translated into a horizontal reciprocating motion of the tool holder.
  • the stop 2d may be adjustably mounted on mount 2b so as to regulate the bias of spring 23.
  • PEG. 2 shows a tie tarnping tool 25 with ballast tamping jaw 25a which is constituted as a lever reciprocable in the direction of arrow A for tamping ballast under an adjacent tie.
  • the reciprocating piston rod of motor l extends along the longitudinal axis of the tool and the vertical reciprocation is translated into a horizontal oscillation or vibration by mechanism lid so that the vibratiorl of the tool is efifectuated in the same direction as its reciprocation in the direction of track elongation.
  • the tamping jaw 25a is further pivotal about pivot 27 to assure proper transmission of the vibratory motion from mechanism 118 to tamping jaw 25a.
  • FIG. 2 also shows a ballast surface tamper 26 which is vibrated by a coaxially mounted motor 1 in a vertical direction.
  • Arrow B indicates the sequence of operation of the two tampers 25, 265 which are mounted on the same machine.
  • FIG. 3 illustrates the use of the invention in connection with a surface ballast tamper 36 for tamping the flank of the ballast bed.
  • One of the tampers 30 is shown mounted on a bracket 32 extending laterally from the machine frame 29, and this tamper is pressed vertically downwardly by a hydraulic motor 2% mounted coaxially with the tamper and the piston rod of vibrating motor l, the motors 2d and l forming a structural unit together with the tamper.
  • the other tamper 30 is mounted on a laterally extending lever 31 one end of which is linked to the machine frame 29 while the ballast tamping plate is linked to the other end of the lever.
  • the coaxially mounted vibrating motor 1 and hydraulic motor 2% for pressing the lever 31 and thus the tamping plate against the ballast bed flank form a structural unit extending in a plane oblique to the plane of the track.
  • FIGS. 4 to 6 The universal application of the motor l to a great variety of track maintenance tools is further illustrated in FIGS. 4 to 6.
  • FIGS. 41 and 5 there is shown the frame 3% of a track tamping and lining machine which supports a vertically movable carrier 37 on which is mounted a twin tarnping tool unit which consists, in a generally known manner, of two groups of pairs of opposing tie tamping tools which are reciprocable in the direction of track elongation by hydraulic motor 36. Vibrating motors l for each group of tools are mounted coaxially with the hydraulic motor 36 to form a compact structural unit therewith.
  • the machine frame 38 also supports a generally known type of track lining unit comprising pairs of rail gripping rollers 34 engaging the track rails.
  • a hydraulic motor 39 and vibrating motor ll form a structural unit operatively connected to the track gripping rollers and extending therebetween for substantially horizontal movement, as best seen in H6. 5.
  • ballast surface tampers 35 which are also vibrated by motors l arranged between the tamping plates and the points of attachment to machine frame 3%.
  • the modified twin tie tamping tool unit of FIG. 6 has separate hydraulic motors 36 for reciprocation of the tools of each group while a single vibrating motor 1 is centrally mounted for vibration of the tools of both groups.
  • the motor 1 is shown operatively connected to the upper ends of the outer tools of each pair of tools while a transmission element connects one of the inner tools of one pair to the outer tool of this pair for transmitting the vibration to the inner tool.
  • This inner tool is linked to the inner tool of the other pair to transmit its vibration thereto.
  • FIGS. 7 and 8 show a track tamping machine combining a ballast surface tamper 40 with a pivotal tie tamping tool jaw 41.
  • the surface tamper is operated by the structural unit of coaxially mounted hydraulic motor 42 for depressing the tamper and vibrating motor fl arranged vertically below hydraulic motor 42.
  • the tie tamping tool 44 is reciprocated in the direction of track elongation by hydraulic motor 43 which moves the upper end of the tool in this direction while vibrating motor 1 is linked to the intermediate pivot of the tool.
  • This type of tamping machine is intermittently moved from tie to tie during the tamping operation so that each tie is first tamped and the subsequent crib is then tamped.
  • a pair of pivotal tie tamping tools 46 are so arranged that the tools enter into the cribs adjacent to two adjacent ties while a surface tamper 45 is aligned with the crib between the two ties.
  • the surface tamper 45 is vibrated by vertically extending motor 1 provided with mechanism 18 for converting the vertical reciporcation of the motor into a horizontal vibration.
  • the pair of tools 46 are operated by the structural unit consisting of hydraulic motor 47 and vibrating motor 1, the hydraulic motor moving the upper ends of the tamping tools in the direction of track elongation to pivot the tools about intermediate fulcrums. This type of tamping machine is intermittently moved by distances of two ties during the tamping operation.
  • a drive for vibrating a tool of a railroad track maintenance machine comprising a track working apparatus and a pressure fluid operated motor operatively connected to the tool and including a linearly reciprocating piston means and means for continuously supplying a unidirectionally flowing pressure fluid to the piston means for reciprocating the same.
  • the motor comprises a housing, a transverse wall dividing the motor housing into two chambers and having a bore for interconnecting the chambers, a flip-flop valve means mounted on the transverse dividing wall for alternately opening and closing the bore upon linear reciprocation, a piston rod slidably joumaled in the dividing wall and extending axially through the housing, the piston means consisting of two pistons respectively mounted on the rod in respective ones of the motor housing chambers, a pressure fluid inlet in one of the chambers and a pressure fluid return line connected to the other chamber, the flip-flop valve means being positioned to close the return line when it opens the connecting bore and to open the return line when it closes the connecting bore, and spring means exerting axial pressure on the flipflop valve means in alternate directions to produce the linear reciprocation thereof.
  • the flipflop valve means includes two plates, each of the valve plates being mounted in one of the chambers adjacent the dividing wall, and a plurality of spacing rods interconnecting the two plates and exceeding in length the width of the dividing wall, the spacing rods being slidably joumaled in the wall for linear reciprocation therein in an axial direction, the piston rod slidably passing through the valve plates, the plate in the one chamber extending over the bore, the pressure fluid return line being connected to the other chamber through another bore in the dividing wall, and the plate in other chamber extending over the other bore while leaving the chamber interconnecting bore in the dividing wall uncovered.
  • the spring means comprises a compression spring in each of the motor housing chambers, one end of each spring bearing against a respective one of the valve plates and the other end of each spring bearing against a respective spring seat movable with, and in the direction of, a respective one of the pistons, pressure fluid supply against the piston in the other motor housing chamber from the inlet through the connecting bore causing the piston rod to move in one direction and thus to move the spring seat in the one chamber in the same direction to compress the spring associated therewith until the pressure of the associated spring exceeds the fluid pressure, at which point the spring pressure axially moves the associated valve plate in said one direction to close the bore in the dividing wall and simultaneously causes the valve plate in the other chamber to open the return line to relieve the fluid pressure in the chamber while causing the fluid pressure in the one chamber to increase against the piston in the one chamber to move the piston rod and the spring seat in the other chamber in the opposite axial direction, thus compressing the spring associated therewith until the pressure of the latter spring exceeds the fluid pressure in the one chamber,
  • each of the spring seats is .an annular member having an outer diameter exceeding the diameter of the associated piston and an inner diameter smaller than the diameter of the piston to leave a clearance between the piston rod and the associated piston, the annular member being fixed to the associated piston for movement therewith.
  • the vibrating drive of claim d wherein the direction changing mechanism is arranged to convert the linear reciprocating movement of the piston means into a reciprocating movement extending in a direction perpendicular thereto.
  • the vibrating drive of claim h wherein the tool has a connecting head connected to said mechanism, a stop is mounted on the motor laterally adjacent the connecting head and the piston means, a spring is mounted between the connecting head and the stop, the connecting head being mounted for transverse movement respect of the piston means against the bias of the spring, and the mechanism including two co operating inclined planes respectively mounted on the piston means and the connecting head for translating the reciprocating movement of the piston means into the transverse movement of the connecting head.
  • the vibrating drive of claim 1, wherein the tool is a tie tamping tool.
  • each of the motors further comprises a mechanism operatively connected respectively to the linearly reciprocating piston means and to the respective tool for changing the direction of the reciprocating movement, the reciprocating movement of the piston means being vertical and the reciprocating movement of the tool being horizontal.
  • the vibrating drive of claim ll wherein the tool is a track lining unit including track gripping members engag'ng the track rails, and the motor is operatively connected to the track gripping members and extends therebetween for substantially horizontally reciprocating the piston means of the motor.
  • the vibrating drive of claim 1 further comprising a pressure fluid drive for moving the tool in a working direction, and the pressure fluid operated motor being associated with the pressure fluid drive in a constructional unit.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
US00132048A 1970-04-17 1971-04-07 Drive for vibrating a track maintenance machine tool Expired - Lifetime US3735708A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT353770A AT303106B (de) 1970-04-17 1970-04-17 Gleisbaumaschine

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US3735708A true US3735708A (en) 1973-05-29

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US00132048A Expired - Lifetime US3735708A (en) 1970-04-17 1971-04-07 Drive for vibrating a track maintenance machine tool

Country Status (7)

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US (1) US3735708A (de)
AT (1) AT303106B (de)
CA (1) CA951177A (de)
CH (1) CH538570A (de)
DE (1) DE2114282A1 (de)
GB (1) GB1347706A (de)
SE (1) SE370257B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3965822A (en) * 1974-11-11 1976-06-29 Canron, Inc. Shoulder tamping lifting jack
FR2302382A1 (fr) * 1975-02-27 1976-09-24 Plasser Bahnbaumasch Franz Machine a bourrer les voies et a compacter le ballast
US3998165A (en) * 1974-04-08 1976-12-21 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Ballast tamping tool unit
US4111129A (en) * 1976-03-31 1978-09-05 Canron Railgroup Method and apparatus for the vibratory tamping of railway tracks
US5862759A (en) * 1996-01-25 1999-01-26 Mauli; Enzo Self-propelled machine for stabilizing, by hammering and compacting, tracks laid on ballast
US20160010287A1 (en) * 2013-02-22 2016-01-14 System7-Railsupport Gmbh Tamping unit for a track tamping machine
US10473551B2 (en) * 2017-09-14 2019-11-12 Actuant Corporation Track loading tool

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT339358B (de) * 1974-05-09 1977-10-10 Plasser Bahnbaumasch Franz Antriebs- und steuereinrichtung fur vibrier- und verstellbare werkzeuge einer gleisbearbeitungsmaschine, insbesondere fahrbare gleisstopfmaschine
WO2012028895A1 (en) * 2010-08-30 2012-03-08 Porr Alpine Austriarail Gmbh Road-rail vehicle with framework for modular employment of service equipment for railway track superstructures
AT516547B1 (de) * 2015-02-27 2016-06-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat zum Unterstopfen von Schwellen eines Gleises

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1441017A (en) * 1919-09-22 1923-01-02 John L Crump Pneumatic hammer
US1572060A (en) * 1923-12-20 1926-02-09 William W Yarnall Shock-absorbing spring and snubber
US1838802A (en) * 1929-04-25 1931-12-29 George F Bischof Shock absorber
US2191359A (en) * 1937-11-30 1940-02-20 John Henry Onions Landing gear for aircraft
US3177813A (en) * 1960-09-09 1965-04-13 Stewart John Kenneth Railroad maintenance device
US3504635A (en) * 1968-01-15 1970-04-07 Canada Iron Foundries Ltd Workhead positioning means
US3606818A (en) * 1968-07-03 1971-09-21 Rilco Maschf Fluid-operated reciprocating motors

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1441017A (en) * 1919-09-22 1923-01-02 John L Crump Pneumatic hammer
US1572060A (en) * 1923-12-20 1926-02-09 William W Yarnall Shock-absorbing spring and snubber
US1838802A (en) * 1929-04-25 1931-12-29 George F Bischof Shock absorber
US2191359A (en) * 1937-11-30 1940-02-20 John Henry Onions Landing gear for aircraft
US3177813A (en) * 1960-09-09 1965-04-13 Stewart John Kenneth Railroad maintenance device
US3504635A (en) * 1968-01-15 1970-04-07 Canada Iron Foundries Ltd Workhead positioning means
US3606818A (en) * 1968-07-03 1971-09-21 Rilco Maschf Fluid-operated reciprocating motors

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3998165A (en) * 1974-04-08 1976-12-21 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Ballast tamping tool unit
US3965822A (en) * 1974-11-11 1976-06-29 Canron, Inc. Shoulder tamping lifting jack
FR2302382A1 (fr) * 1975-02-27 1976-09-24 Plasser Bahnbaumasch Franz Machine a bourrer les voies et a compacter le ballast
US4043271A (en) * 1975-02-27 1977-08-23 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Mobile track tamping machine
US4111129A (en) * 1976-03-31 1978-09-05 Canron Railgroup Method and apparatus for the vibratory tamping of railway tracks
US5862759A (en) * 1996-01-25 1999-01-26 Mauli; Enzo Self-propelled machine for stabilizing, by hammering and compacting, tracks laid on ballast
US20160010287A1 (en) * 2013-02-22 2016-01-14 System7-Railsupport Gmbh Tamping unit for a track tamping machine
US9957668B2 (en) * 2013-02-22 2018-05-01 System 7-Railsupport Gmbh Tamping unit for a track tamping machine
US10473551B2 (en) * 2017-09-14 2019-11-12 Actuant Corporation Track loading tool

Also Published As

Publication number Publication date
GB1347706A (en) 1974-02-27
DE2114282A1 (de) 1971-10-28
SE370257B (de) 1974-10-07
CA951177A (en) 1974-07-16
AT303106B (de) 1972-11-10
CH538570A (de) 1973-06-30

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