EP3556478B1 - Entraînement vibratoire doté d'un cylindre multi face - Google Patents

Entraînement vibratoire doté d'un cylindre multi face Download PDF

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Publication number
EP3556478B1
EP3556478B1 EP19168620.3A EP19168620A EP3556478B1 EP 3556478 B1 EP3556478 B1 EP 3556478B1 EP 19168620 A EP19168620 A EP 19168620A EP 3556478 B1 EP3556478 B1 EP 3556478B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
valve
piston surface
vibration
Prior art date
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Application number
EP19168620.3A
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German (de)
English (en)
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EP3556478A1 (fr
Inventor
Leopold Sandberger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP3556478A1 publication Critical patent/EP3556478A1/fr
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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • F15B11/0365—Tandem constructions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1466—Hollow piston sliding over a stationary rod inside the cylinder
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers
    • F15B2211/7056—Tandem cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7733—Control of direction of movement of the output member providing vibrating movement, e.g. dither control for emptying a bucket

Definitions

  • the invention relates to the use of a cylinder for driving vibrations.
  • the invention relates to a fluid circuit for driving vibrations, comprising a cylinder.
  • the invention relates to a driving method for a vibration-driven cylinder.
  • track beds made of ballast or the like are used as a base for sleepers.
  • the ballast is pressed ("tamped") under the sleepers, and the tracks are thus lifted.
  • Tamping units are used, which pierce the ballast with a tamping tool, such as a tamping pick, or a pair of tamping tools, and which then move the ballast under the respective slide threshold.
  • a vibrating or swinging or oscillating tool is of dual benefit in order to facilitate penetration of the tool into the ballast on the one hand and to achieve a solidifying compaction of the ballast on the other hand.
  • a vibration drive such as a fluidic vibration drive, serves to drive at least one tamping tool.
  • the WO 2014 / 127393 A1 states as state of the art mechanically connecting a hydraulic cylinder for an infeed movement and a hydraulic cylinder for a vibration movement in series for tamping tools, with the disadvantage that, in addition to a high level of maintenance, is that an amplitude size cannot be freely adjusted.
  • WO 2014/127393 A1 discloses generically to provide a single hydraulic cylinder, such as a differential cylinder, with a displacement sensor for determining the position of the hydraulic cylinder, the hydraulic cylinder as an auxiliary drive depending on the displacement sensor signal and is controlled as a vibratory drive, with at least one servo or proportional valve preferably being provided for actuation.
  • the WO 2016 / 054667 A1 discloses a track tamping machine with two tamping units that can be displaced transversely independently of one another and that carry auxiliary cylinders for pivoting tamping arms for compacting ballast.
  • the EP 2 902 546 A1 discloses a ballast bed compaction device which provides a stabilization unit on a machine frame, which is equipped for gripping around a rail head.
  • a stabilization unit By oscillating the stabilization unit by means of a hydraulic cylinder vibrator, a horizontal oscillating of the track is achieved, which leads to a settlement of the track on the ballast bed.
  • DE 199 12 984 A1 discloses a double acting piston actuator having a floating piston assembly provided at one end of a piston rod.
  • the invention is based on the object of creating a vibration drive with a high level of efficiency. Aspects of series production and/or aspects of productive use, such as producibility with little effort, maintainability with little effort and/or a small installation space requirement, can advantageously be taken into account.
  • a further advantage is that several functions can be integrated into a multi-surface cylinder as a single assembly, so that on the one hand assembly work during production and maintenance can be reduced and on the other hand space can be saved or for other functions, such as a larger piston surface and/or a longer piston extension stroke, can be used. If it is a piston-extending feed drive, a high extension force can be achieved.
  • a multi-surface cylinder can be understood to mean a fluid cylinder on whose piston there are at least three fluidically active piston surfaces.
  • the piston surfaces can be pressurized, for example, via cylinder chambers or fluid chambers that do not fluidly communicate with one another.
  • a rapid traverse cylinder as a multi-surface cylinder.
  • a rapid travel cylinder can be described as having at least one annular piston surface on the piston rod side, an oppositely directed annular piston surface or one facing away from the piston rod and a rotary piston surface facing away from the piston rod, with the piston surfaces facing away from the rod being structurally separate and not communicating fluidically.
  • a tandem cylinder can be described as a fluid cylinder on the piston rod of which at least two piston heads are arranged offset in the longitudinal direction, with two piston surfaces facing one another and arranged one behind the other not communicating fluidly in a structurally separate manner.
  • a preferred fluid is a hydraulic fluid because of the higher pressures that can be achieved, in particular a hydraulic fluid for mobile applications because of the biodegradability.
  • the fluid circuit Z according to the invention has the advantage that the piston surfaces of the multi-surface cylinder and/or the valves can be optimized, such as optimized in terms of efficiency.
  • Z has a high overall force available, for example for a penetration movement of the tamping tine to be driven into a ballast bed.
  • the first two piston surfaces each have an effective piston surface that is at least approximately the same size. That's how it's done the areas of the same amount in terms of amount when the piston is displaced achieves an approximately equally large volume flow in/out of the respective cylinder chamber.
  • Having an accumulator in communication with the third piston surface has several advantages.
  • compression of the fluid in the cylinder chamber belonging to the third piston surface can be replaced by compression (e.g. a gas bubble) and/or compensatory movement (e.g. a spring-loaded pressure accumulator base) and/or the like in/on the pressure accumulator.
  • compensatory movement e.g. a spring-loaded pressure accumulator base
  • a minimum amplitude and/or a maximum amplitude of the vibration movement can be ensured and/or optimized, such as efficiency-optimized and/or function-optimized, by appropriate dimensioning of the pressure accumulator (e.g. a gas bladder volume and/or a pressure accumulator bottom travel path).
  • the first valve is a vibratable rain valve, this facilitates a vibratory movement of the piston and thus of the tamping tine to be driven.
  • Preferred control valve designs include a proportional valve and/or a servo valve.
  • the control valve is connected Z to a control device for specifying vibration, in order to bring about a vibration that can be specified according to amplitude and/or frequency and/or energy.
  • the control valve is therefore acted upon in an oscillating manner.
  • the control valve is an electrically and/or hydraulically and/or pneumatically pilot-controlled valve with one and/or two stages.
  • the fluid circuit and in particular the multi-surface cylinder and the first valve are suitable for a frequency of up to approximately 50 Hz, more preferably with a frequency of up to approximately 40 Hz, even more preferably with a frequency of up to approximately 35 Hz , and/or to vibrate at a frequency of about 25 to about 40 Hz.
  • these frequency ranges are particularly advantageous for compacting a ballast bed.
  • the hydraulic circuit and in particular the multi-surface cylinder and the first valve are suitable for the piston relative to the cylinder housing with an amplitude of up to approximately 6 mm, more preferably up to approximately 3 mm, even more preferably of at least approximately 3 mm, and/or most preferably oscillates to about 2mm.
  • this vibration promotes rapid and efficient compaction of a ballast bed.
  • the fluid circuit has a measuring device for measuring the fluid pressure in/on the cylinder and/or in/on the first valve. By measuring the (vibrating) fluid pressure profile, a ballast bed compaction can be checked, for example.
  • Driving method Z includes Z both pressurizing the third piston face and vibrating the first valve about a shifted zero point to simultaneously vibrate drive and piston extend.
  • the method step thus contains two parallel steps which can preferably be carried out independently of one another, can be carried out independently of one another in terms of amount and/or can be started and ended independently of one another.
  • the two parallel steps allow, for example, a constantly progressive compaction of a ballast bed by taking two relatively simple control actions.
  • the control method for the multi-surface cylinder is preferably particularly simple and reliable in terms of control technology, the first piston surface and the second piston surface each having an effective piston surface of the same size, and the vibration according to a zero-point symmetrical function, such as such a sine function.
  • Driving with a zero-point symmetrical function, in particular a sine function, is particularly uniform and scalable.
  • a fluid circuit 1 for driving vibrations comprises a multi-surface cylinder or multi-surface fluid cylinder designated as a whole with 2, a vibration valve 4 as the first valve, an extension valve 6 as the second valve and a pressure accumulator 8.
  • the multi-surface cylinder 2 is a rapid travel cylinder 10. It has a cylinder housing 12 with a cylinder wall 18 closed at each end with a cylinder base 14 and a cylinder cover 16 and with a stamp 20 concentric thereto and fixed to the cylinder base.
  • a piston 24 with an annular piston head 26 , an adjoining hollow-cylindrical piston rod 28 and a piston rod head 30 at the axial end is accommodated therein so as to be displaceable along a longitudinal axis 22 defined by the cylinder wall 18 .
  • the rapid travel cylinder 10 has three piston surfaces which are operatively arranged for the axial displacement of the piston and which are collectively designated as 32 .
  • a first piston surface 34 is located on the side of the piston rod 28 on the piston head 26.
  • a second piston surface 36 is located on the inside of the piston rod head 30, facing the punch 20.
  • a third piston surface 38 is located on the side facing away from the piston rod 28 on the piston head 26.
  • the piston surfaces 32 each axially delimit a chamber 40 .
  • a first chamber 42 is defined by the first piston surface 34 , the cylinder wall 18 , the cylinder cover 16 and the piston rod 28 .
  • An overpressure in the first chamber 42 acts on the first piston surface 34 to retract the piston rod 28 .
  • a second chamber 44 is presently defined by the second piston surface 36 , the piston rod 28 and the plunger 20 .
  • An overpressure in the second chamber 44 acts on the second piston surface 36 to extend the piston rod 28.
  • a third chamber 46 is presently defined by the piston 24, the cylinder wall 18, the cylinder base 14 and the plunger 20.
  • An overpressure in the third chamber 46 acts on the third piston surface 38 to extend the piston rod 28.
  • the vibration valve 4 is a valve that can be vibrated in a predetermined manner. It is provided as a 4/3-way valve with two working connections 48 and supply connections 50. For example, it is a proportional spool valve and has an electrically controllable pilot device that can deflect the spool (not shown), such as stimulating preferably symmetrical oscillations about an adjustable operating point/zero point.
  • One working connection 48 of the vibration valve 4 communicates fluidly with the first chamber 42.
  • the other working connection 48 of the vibration valve 4 communicates fluidly through the plunger 20 with the second chamber 44.
  • the extension valve 6 is a switchable valve, for example a pilot-operated pressure-limiting valve with two supply connections 50 and a working connection 48 which communicates fluidly with the third chamber 46 .
  • the pressure accumulator 8 communicates fluidly with the third chamber 46.
  • the pressure accumulator 8 branches off the line between the extension valve 6 and the third chamber 46.
  • the vibration valve 4 is vibrated so that the chambers 42 and 44 are alternately pressurized with fluid at a frequency of up to 35 Hz.
  • fluid pressure is built up and released once in each period in each of the chambers 42,44.
  • the piston 24 is, for example, by one Amplitude of up to 2mm shifted relative to the cylinder body.
  • the piston movement pumps the fluid back and forth between the third chamber 46 and the pressure accumulator 8 . Since the piston areas 34 and 36 are of the same size, a symmetrical oscillation of the disc of the vibration valve about a zero point for pressurizing the chambers 42, 44 is made possible.
  • fluid is fed under pressure to the third chamber 46 via the extension valve 6 , fluid is fed under pressure to the second chamber 44 via the vibration valve 4 , and fluid is discharged from the first chamber 42 via the vibration valve 4 .
  • Fluid is supplied under pressure through the extension valve 6 to the third chamber 46 to simultaneously extend and vibrate the piston 24 .
  • the zero point of the vibration valve and the amplitude of the oscillation of the slide of the vibration valve 4 are shifted in such a way that on the one hand fluid pressure is built up and released once in each period in each of the chambers 42, 44, and on the other hand compared with the volume flow in the first chamber 42 the volume flow in the third chamber 46 piston path corresponding volume flow excess flows into the second chamber 44.
  • the cylinder housing is coupled to a (not shown) machine frame or the like, such as fixed, articulated and/or pivoted, and the piston is coupled to a tamping tine (not shown) to be driven, such as fixed, articulated and/or pivoted .
  • a machine frame or the like such as fixed, articulated and/or pivoted
  • the piston is coupled to a tamping tine (not shown) to be driven, such as fixed, articulated and/or pivoted . Since the mass of the cylinder piston is usually smaller than the mass of the cylinder housing, this construction is energetically favorable and therefore has a high level of efficiency.
  • the multi-surface cylinder 2, the valves 4 and 6 and the pressure accumulator 8 form a compact assembly, so that space can be saved and the entire assembly can be exchanged for a replacement assembly to increase the productive time.
  • a cylinder housing-side coupling to the tamping tine and a piston rod-side coupling to the machine frame are provided, for example due to space considerations and/or in the case of different mass ratios.
  • the 2 shows a second embodiment of the invention.
  • the multi-surface cylinder 2 is a tandem cylinder 52 .
  • This has in the cylinder housing 12 axially approximately centrally between the cylinder base 14 and the piston rod-side axial end of the cylinder housing 12 an annular intermediate cylinder base 54 fixed to the cylinder wall 18, which divides the cylinder 2 into two cylinder working chambers 56 arranged axially one behind the other.
  • an intermediate piston base 58 that is axially displaceable in a fluid-tight manner in the working chamber 56 remote from the cylinder base.
  • the piston surfaces 32 each axially delimit a chamber 40 .
  • the first chamber 42 is defined by the first piston surface 34 , the cylinder wall 18 , the intermediate cylinder floor 54 and the piston rod 28 .
  • An overpressure in a first chamber 42 acts on the first piston surface 34 to retract the piston rod 28.
  • the second piston surface 36 is located on the cylinder (intermediate) base side on the intermediate piston base 58.
  • the second chamber 44 is defined by the second piston surface 36, the cylinder wall 18, the piston rod 28 and the cylinder intermediate base 54 are defined.
  • An overpressure in the second chamber 44 acts on the second piston surface 36 to extend the piston rod 28.
  • the third chamber 46 is defined by the piston 24, the cylinder wall 18 and the cylinder base 14.
  • An overpressure in the third chamber 46 acts on the third piston surface 38 to extend the piston rod 28.
  • the piston surfaces 34 and 36 are of equal size.
  • a space between the intermediate piston base 58 and the axial end of the cylinder housing 12 on the piston rod side is preferably vented.
  • a fourth piston surface 62 is located on the cylinder cover side on the intermediate piston floor 58.
  • a fourth chamber 60 is defined by the fourth piston surface 62, the cylinder wall 18, the cylinder cover 16 and the piston rod.
  • An overpressure in the fourth chamber 60 acts on the fourth piston surface 62 to retract the piston rod 28.
  • the extension valve 6 is an on/off valve, like a controlled 4/3-way valve. Compared to the basic variant of the second embodiment, more fluid pressure can be applied to the piston rod for retracting, for example in order to retract a heavier attachment or to raise a rail.
  • the fourth chamber 60 communicates with a pressure accumulator 8 in order to enable the piston 24 to vibrate with improved efficiency.
  • a sub-variant not shown includes, instead of or in addition to the pressure accumulator 8, a compensating piston (compensating element as well as compensating membrane) that can be displaced between two compensating chambers of approximately the same size, of which one compensating chamber communicates fluidly with the third chamber 46, and the other compensating chamber communicates with the fourth Chamber 60 communicates fluidly.
  • a compensating piston dispenser element as well as compensating membrane

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (5)

  1. Circuit de fluide pour l'entraînement vibratoire, le circuit comportant un cylindre multiface (2, 10 52), une première soupape (4), qui est reliée aux deux premières faces de piston (34, 36) antagonistes d'un piston (24) du cylindre multiface (2, 10 52), et une deuxième soupape (6), qui est reliée à une troisième face de piston (38), le cylindre multiface (2, 10 52) présentant une première face de piston (34), une deuxième face de piston (36) disposée de manière agir de façon antagoniste par rapport à la première face de piston (34) et une troisième face de piston (38) disposée de manière à agir de façon identique par rapport à la deuxième face de piston (36),
    la première soupape (4) étant une soupape de régulation apte à vibrer, qui est reliée à un dispositif de commande pour prédéfinir une vibration ; caractérisé en ce que la troisième face de piston (38) est une face de piston agissant de manière à faire sortir le piston lorsqu'elle est sollicitée en pression, et en ce que la deuxième soupape (6) est configurée pour permettre une sortie du piston (24) tandis que le piston (24) vibre.
  2. Circuit de fluide selon la revendication 1, les deux premières faces de piston (34, 36) présentant respectivement une face de piston active de même taille.
  3. Circuit de fluide selon l'une des revendications 1 et 2, un réservoir sous pression (8) étant relié de manière communicante à la troisième face de piston (38).
  4. Procédé de commande pour l'entraînement vibratoire pour un cylindre multiface (2, 10 52), qui présente une première face de piston (34), une deuxième face de piston (36) disposée de manière agir de façon antagoniste par rapport à la première face de piston (34) et une troisième face de piston (38) disposée de manière à agir de façon identique par rapport à la deuxième face de piston (36), la première face de piston (34) et la deuxième face de piston (36) étant sollicitées en pression en alternance pour l'entraînement vibratoire ;
    la première face de piston (34) et la deuxième face de piston (36) étant reliées à une première soupape (4), un tiroir de la soupape (4) étant mis en vibration pour l'entraînement vibratoire ; caractérisé en ce que pour l'entraînement vibratoire et la sortie de piston simultanés, la troisième face de piston (38) est sollicitée en pression, et la première soupape (4) est mise en vibration autour d'un point zéro décalé.
  5. Procédé de commande selon la revendication 4 pour le cylindre multiface (2, 10 52), la première face de piston (34) et la deuxième face de piston (36) présentant respectivement une face de piston active de même taille, et la vibration étant prédéfinie selon une fonction sinusoïdale symétrique autour d'un point zéro.
EP19168620.3A 2018-04-17 2019-04-11 Entraînement vibratoire doté d'un cylindre multi face Active EP3556478B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102018205821.0A DE102018205821A1 (de) 2018-04-17 2018-04-17 Vibrationsantreiben mit einem Mehrflächenzylinder

Publications (2)

Publication Number Publication Date
EP3556478A1 EP3556478A1 (fr) 2019-10-23
EP3556478B1 true EP3556478B1 (fr) 2022-06-15

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EP19168620.3A Active EP3556478B1 (fr) 2018-04-17 2019-04-11 Entraînement vibratoire doté d'un cylindre multi face

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19912984A1 (de) * 1998-03-23 1999-10-07 Team Corp Vorspannungs-Kolben-Betätigungsglied

Family Cites Families (6)

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AT339358B (de) * 1974-05-09 1977-10-10 Plasser Bahnbaumasch Franz Antriebs- und steuereinrichtung fur vibrier- und verstellbare werkzeuge einer gleisbearbeitungsmaschine, insbesondere fahrbare gleisstopfmaschine
DE102012020581A1 (de) * 2012-10-22 2014-04-24 Robert Bosch Gmbh Hydraulische Schaltung für eine hydraulische Achse und eine hydraulische Achse
AT513973B1 (de) 2013-02-22 2014-09-15 System7 Railsupport Gmbh Stopfaggregat für eine Gleisstopfmaschine
NO2902546T3 (fr) 2014-01-30 2018-03-24
AT516311B1 (de) 2014-10-06 2016-06-15 System 7 - Railsupport GmbH Gleisstopfmaschine zum Verdichten der Schotterbettung eines Gleises
ES2583373B1 (es) * 2015-03-18 2017-06-15 Jose Antonio Ibañez Latorre Máquina de mantenimiento de vía férrea para nivelación y alineación de vía, con capacidad de operar sin interrupciones en su avance en vía corrida y operar en cambios de vía bateando la vía desviada.

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19912984A1 (de) * 1998-03-23 1999-10-07 Team Corp Vorspannungs-Kolben-Betätigungsglied

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DE102018205821A1 (de) 2019-10-17

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