EP3556478A1 - 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
EP3556478A1
EP3556478A1 EP19168620.3A EP19168620A EP3556478A1 EP 3556478 A1 EP3556478 A1 EP 3556478A1 EP 19168620 A EP19168620 A EP 19168620A EP 3556478 A1 EP3556478 A1 EP 3556478A1
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EP
European Patent Office
Prior art keywords
piston
cylinder
valve
vibration
piston surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19168620.3A
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German (de)
English (en)
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EP3556478B1 (fr
Inventor
Leopold Sandberger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
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 a use of a cylinder for vibration driving.
  • the invention relates to a fluid circuit for vibration driving comprising a cylinder.
  • the invention relates to a driving method for a vibration-driven cylinder.
  • track construction track beds made of gravel or the like are used to support sleepers. To produce and / or reprocess the crushed stone is pushed ("stuffed") under the sleepers, and thus the tracks are lifted.
  • Stopfaggregate be used which pierce with a stuffing tool, such as a tamping pick, or a Stopftechnikmaschinefar in the gravel, and which then with an example pivoting movement ("Beistellen” or "infeed” or “swinging") the gravel under the respective Push threshold.
  • a vibrating or oscillating tool is of dual use, on the one hand to facilitate penetration of the tool into the ballast, and on the other hand to achieve a consolidating compaction of the ballast.
  • a vibration drive such as a fluidic vibration drive, serves to drive at least one stuffing tool.
  • WO 2014/127393 A1 discloses generically forming to provide a single hydraulic cylinder, such as a differential cylinder, with a displacement sensor for determining the hydraulic cylinder position, wherein the hydraulic cylinder allegedlysororsignalcommun as Beistellantrieb and is driven as a vibration drive, wherein for actuation preferably at least one servo or proportional valve is provided.
  • Fluids are compressible.
  • the fluids designated as “incompressible fluids” also have elasticity; For example, for mineral oils, one may assume a compressibility factor of 0.7% to 0.8% per 100 bars. It follows for the above construction with a single hydraulic cylinder in differential cylinder design that for generating the vibration, the entire volume of fluid in the respective cylinder chamber, so the volume for the Kolbenausfahrmos in addition to the vibration volume, each cycle must be compressed under energy use (and relaxed).
  • the WO 2016/054667 A1 discloses a track tamping machine with two independently transversely displaceable tamping units, which carry auxiliary cylinders for pivoting Stopfarmen for compacting ballast.
  • the EP 2 902 546 A1 discloses a ballast bed compaction apparatus which provides on a machine frame a stabilizer assembly equipped to engage around a rail head. By swinging the stabilization unit by means of a hydraulic cylinder vibrator, a horizontal swinging of the track is achieved, which leads to a settlement of the track on the ballast bed.
  • the present invention seeks to provide a vibration drive with a high efficiency.
  • the object is achieved by the features of claim 1.
  • the object is achieved by the features of claim 4.
  • the driving method for vibration driving the object is achieved by the features of claim 9.
  • each function (such as feed motion, vibration in the first direction, vibration in the opposite direction and the like) can be assigned a fluid chamber, so that each function is optimized, such as efficiency-optimized, can be designed and / or controlled.
  • Another advantage is that in a multi-surface cylinder than a single module several functions are integrated, so on the one hand assembly costs during manufacture and maintenance can be reduced, and on the other hand saves space or for other functions, such as a larger piston area and / or a longer Kolbenausfahrweg, can be used. If it is a piston-extending feed drive, a high extension force can be achieved.
  • a multi-surface cylinder may be understood to mean a fluid cylinder on the piston of which at least three fluidically effective piston surfaces are present.
  • the piston surfaces can be pressurized, for example, via cylinder chambers or fluid chambers that are not fluidly communicating with one another.
  • a rapid traverse cylinder can be described as having at least one piston rod-side annular piston surface, an oppositely directed or piston rod-remote annular piston surface and a piston rod-remote circular piston surface, wherein the rod-facing piston surfaces structurally separated do not communicate fluidly.
  • a tandem cylinder can be described as a fluid cylinder, at the piston rod offset in the longitudinal direction at least two piston plates are arranged, wherein two mutually facing and successively arranged piston surfaces structurally separated do not communicate fluidly.
  • a preferred fluid is a hydraulic fluid because of the higher achievable pressures, in particular a hydraulic fluid for mobile application because of biodegradability.
  • a multi-surface cylinder wherein the feed drive and the vibration drive in the feed direction in each case at least one piston surface is assigned.
  • a tamping pick to be driven can be driven into a ballast bed in a structurally simple manner with high force.
  • these at least two piston surfaces are fluidly separate. Two fluidically separate piston surfaces are, even hydrostatically, and preferably over the entire piston stroke, acted upon with different pressure levels, they are not fluidly communicating.
  • a multi-surface cylinder as above, wherein the vibratory drive is associated with a vibratable valve, so that the vibratory driving control technology is simple and reliable implemented by a vibration excitation of the valve.
  • a valve associated with the delivery drive valve may be provided, wherein the valves are separate or independent of each other in order to separately optimize the vibration drive and the delivery drive, such as optimizing efficiency.
  • a pressure accumulator connected to a cylinder chamber of a fluid cylinder and connected in a fluidically communicating manner.
  • the fluidically communicating pressure accumulator can inhibit the compression of the fluid in the connected cylinder chamber, so that an energy compressing the fluid can be saved effect-increasing.
  • This advantage is achieved in all cylinder designs, such as a plunger cylinder with external vibration drive or a differential cylinder with vibrating pressurization.
  • a pressure accumulator which is connected to a cylinder chamber of a divided by a piston in at least two cylinder chambers fluid cylinder, as fluidly communicating connected.
  • a fluid circuit for vibratory driving such as for driving a stuffing plug, comprises, according to the invention, a multi-surface cylinder, a first valve and a second valve.
  • the first valve is connected to first two counteracting or oppositely disposed piston surfaces of a piston of the multi-surface cylinder, as communicatively connected.
  • the first valve may be connected via separate connections and / or lines to the first two piston surfaces.
  • a connection such as a communicating connection of a valve and a piston surface may mean that the valve is valve position-dependent for pressurizing (including vacuum pressurizing) and connected to the cylinder.
  • the second valve is connected to a third piston surface as communicatively connected.
  • the circuit according to the invention has the advantage that the piston surfaces of the multi-surface cylinder and / or the valves optimized, as optimized efficiency, can be designed.
  • the third piston surface is a piston-pressure-acting piston surface pressurized, by applying pressure to the third piston surface and the piston surface of the first two piston surfaces acting the same way, a high overall force is available, for example for a penetration of the tamping chip to be driven into a ballast bed.
  • the first two piston surfaces each have an at least approximately equal effective piston area. This is how it works the same amount in terms of areas when Kolbenverlagern reaches an approximately equal volume flow in / out of the respective cylinder chamber.
  • a compression of the fluid in the cylinder chamber belonging to the third piston surface can be replaced by a compression (for example a gas bubble) and / or compensation movement (for example of a spring-biased pressure storage bottom) and / or the like in / at the pressure accumulator.
  • a corresponding dimensioning of the pressure accumulator for example, a gas bubble volume and / or Druck Amsterdamteilverfahrwegs
  • a minimum amplitude and / or a maximum amplitude of the vibratory motion ensured and / or optimized, such as efficiency-optimized and / or optimized function.
  • the first valve is a vibratable control valve, this facilitates a vibratory movement of the piston and thus of the stuffing plug to be driven.
  • Preferred control valve designs include a proportional valve and / or a servo valve.
  • the control valve is connected to a control device for vibration preselection in order to effect a vibration that can be predetermined according to amplitude and / or frequency and / or energy.
  • the control valve can therefore be applied oscillating.
  • the control valve is an electrically and / or hydraulically and / or two-stage pilot-operated valve.
  • the fluid circuit and in particular the multi-surface cylinder and the first valve are suitable, with a frequency of up to about 50 Hz, more preferably with a frequency of up to about 40 Hz, even more preferably with a frequency of up to about 35 Hz , and / or oscillate at a frequency of about 25 to about 40 Hz. According to experience, 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 having an amplitude up to about 6 mm, more preferably up to about 3 mm, more preferably at least about 3 mm, and / or most preferably oscillates to about 2 mm.
  • 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 curve, for example, a ballast bed compaction can be tested.
  • a fluid circuit for vibratory driving comprising a divided by a piston in at least two cylinder chambers fluid cylinder and at least one arranged to pressurize at least one of the chambers and / or fluidly communicating connected and / or connected valve, such as a vibratable valve, wherein a pressure accumulator with at least one of the cylinder chambers, in particular the piston surface larger cylinder chamber, fluidically communicates.
  • the fluidically communicating pressure accumulator can inhibit the compression of the fluid in the connected cylinder chamber, so that an energy that compresses the fluid can be saved in terms of efficiency. This advantage is thus achievable not only in multi-surface cylinders, but also in differential cylinders and the like.
  • the accumulator can be structurally simple volume compensating executed.
  • the accumulator may advantageously be dimensioned to compensate for piston area differential to inhibit unsymmetrical fluid compression.
  • An inventive driving method for vibration driving for example, a stuffing peg, is provided for a multi-surface cylinder, a first piston surface, a piston surface of the first counteracting arranged, and preferably fluidly separated, second piston surface and a second piston surface with the same effect, and preferably fluidly separated, third Has piston surface.
  • the driving method according to the invention may include, for vibrational driving, the piston surfaces first piston surface and second piston surface alternately pressurized.
  • the pressure may be a negative pressure or, preferably, an overpressure with respect to the pressure level applied to the respective other of the two piston surfaces. This process step advantageously causes a force-and-degradation for solidifying beispielswiese a ballast bed.
  • the driving method according to the invention may include pressurizing the second piston surface and / or the third piston surface for piston extension (or alternatively for piston retraction).
  • the pressure may be a negative pressure or, preferably, an overpressure, see above.
  • This method step advantageously brings about a displacement of a coupling point of the piston rod relative to the cylinder housing, in order, for example, to advance penetration of a stuffing plug to be driven into a ballast bed.
  • the driving method according to the invention may include for vibrationally driving the piston surfaces first piston surface and second piston surface alternately or oscillatingly pressurized, and for piston extension or piston retraction to pressurize the second piston surface and / or the third piston surface with pressure.
  • This process step causes a simultaneous or superimposed piston extension / retraction and vibration driving, so that, for example, a constantly progressive compression of a ballast bed with time savings becomes possible.
  • the driving method for the multi-surface cylinder wherein the piston surfaces first piston surface and second piston surface with a first valve or respectively connected to working ports of a first valve, as communicatively connected, be suitable.
  • the driving method in the vibration driving step may include vibrating a spool of the valve.
  • the driving method may include simultaneous vibration driving and piston extension to both pressurize the third piston surface and to vibrate the first valve by a shifted zero point.
  • the method step thus contains two parallel steps, which can preferably be performed independently of one another, how they can be arranged independently of one another and / or can be started and ended independently of one another.
  • the two parallel steps allow a progressively compacting of a ballast bed by making two relatively simple control actions.
  • the control method for the multi-surface cylinder is particularly simple in terms of control technology, with the piston surfaces having the first piston surface and the second piston surface each having an equal effective piston area, and the vibration being predetermined in accordance with a zero-point symmetrical function, such as such a sinusoidal function.
  • a control with a zero-point symmetric function, in particular sine function, is particularly uniform and scalable.
  • a fluid circuit 1 for vibration drive comprises a multi-surface cylinder or multi-surface fluid cylinder designated as a whole by 2, a vibration valve 4 as a first valve, an extension valve 6 as a second valve and a pressure reservoir 8.
  • the multi-surface cylinder 2 is a rapid-action cylinder 10. It has a cylinder housing 12 with a cylinder wall 18, which is closed on each end with a cylinder bottom 14 and a cylinder cover 16, and with a cylinder-bottom-fixed punch 20 concentric therewith. Therein, along a longitudinal axis 22 defined by the cylinder wall 18, a piston 24 with an annular piston head 26, an adjoining hollow cylindrical piston rod 28 and an axially end piston rod bottom 30 are accommodated.
  • the rapid traverse cylinder 10 has three effective for axial piston displacement arranged piston surfaces, which are designated together with 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 piston rod bottom 30 facing the punch 20.
  • a third piston surface 38 is located on the piston rod 28 side facing away from the piston head 26th
  • the piston surfaces 32 respectively delimit a chamber 40 axially.
  • a first chamber 42 is defined here 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 for retraction of the piston rod 28.
  • a second chamber 44 is defined here 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 for extending the piston rod 28.
  • a third chamber 46 is defined here by the piston 24, the cylinder wall 18, the cylinder bottom 14 and the plunger 20. An overpressure in the third chamber 46 acts on the third piston surface 38 for extending the piston rod 28.
  • the vibration valve 4 is a predeterminably vibratable valve. It is provided as a 4/3-way valve with two working ports 48 and 50 supply connections. For example, it is a proportional slide valve, and it has an electrically controllable pilot control device, which can deflect the slide (not shown), for example, to stimulate preferably symmetrical vibration by an adjustable operating point / zero point.
  • a working connection 48 of the vibration valve 4 communicates fluidically with the first chamber 42.
  • the other working connection 48 of the vibration valve 4 communicates fluidically through the ram 20 with the second chamber 44.
  • the deployment valve 6 is a switchable valve, such as a pilot-operated pressure relief valve having two supply ports 50 and a working port 48 that fluidly communicates with the third chamber 46.
  • the accumulator 8 communicates fluidly with the third chamber 46.
  • the pressure accumulator 8 branches off from the line between the extension valve 6 and third chamber 46.
  • the vibration valve 4 is vibrated, so that the chambers 42 and 44 are alternately applied with a frequency of up to 35 Hz with fluid pressure. For example, in each period in each of the chambers 42, 44 fluid pressure is built up and released once. In this case, the piston 24, for example, a Amplitude of up to 2mm relative to the cylinder housing shifted.
  • the piston movement pumps the fluid between the third chamber 46 and the accumulator 8 back and forth. Since the piston surfaces 34, and 36 are the same size, a symmetrical vibration of the disk of the vibration valve is made possible by a zero point for pressurizing the chambers 42, 44.
  • the piston 24 fluid is supplied, for example, via the extension valve 6 of the third chamber 46 under pressure fluid is supplied via the vibration valve 4 of the second chamber 44 under pressure fluid, and is discharged via the vibration valve 4 from the first camera 42 fluid.
  • the cylinder housing is coupled to a (not shown) machine frame or the like, as fixedly mounted, hinged and / or pivotally mounted, and the piston is coupled to a (not shown) to be driven tamping pick, as fixedly mounted, articulated and / or pivotally mounted , 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 efficiency.
  • valves 4 and 6 and the pressure accumulator 8 form a compact assembly, so that space can be saved, and for productive time increase, the entire assembly is exchangeable for a replacement module.
  • a cylinder housing-side coupling to the tamping pommel and a piston rod-side coupling to the machine frame are provided, for example, for space considerations and / or other mass ratios.
  • the Fig. 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 bottom 14 and the piston rod-side axial end of the cylinder housing 12 an established on the cylinder wall 18, annular cylinder intermediate bottom 54, which divides the cylinder 2 into two axially successively arranged cylinder working spaces 56.
  • the piston 24 includes fixed to each other in addition to the cylinder bottom near-cylinder working space 56 fluid-axially displaceable, disc-shaped piston head 26 and the cylinder intermediate bottom 54 fluid-tight piston rod 28 a fluid-tight axially displaceable in the cylinder bottom working space 56 piston intermediate bottom 58th
  • the piston surfaces 32 respectively delimit a chamber 40 axially.
  • the first chamber 42 is defined by the first piston surface 34, the cylinder wall 18, the cylinder intermediate bottom 54 and the piston rod 28.
  • An overpressure in a first chamber 42 acts on the first piston surface 34 for retraction of the piston rod 28.
  • the second piston surface 36 is located on the bottom side of the piston intermediate bottom 58.
  • the second chamber 44 is defined by the second piston surface 36, the cylinder wall 18 defining the piston rod 28 and cylinder intermediate bottom 54.
  • An overpressure in the second chamber 44 acts on the second piston surface 36 for extending the piston rod 28.
  • the third chamber 46 is defined by the piston 24, the cylinder wall 18 and the cylinder bottom 14.
  • An overpressure in the third chamber 46 acts on the third piston surface 38 for extending the piston rod 28.
  • the piston surfaces 34 and 36 are the same size. A space between the piston intermediate bottom 58 and the piston rod-side axial end of the cylinder housing 12 is preferably vented.
  • the Fig. 3 shows a variant of the second embodiment.
  • a fourth piston surface 62 is located on the cylinder head side on the piston intermediate bottom 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 deployment valve 6 is an on / off valve, such as a controlled 4/3 way valve. Compared to the basic variant of the second embodiment, more fluid pressure can be applied for retraction onto the piston rod, for example to retract a heavier attachment, or for lifting a rail.
  • the fourth chamber 60 communicates with a pressure accumulator 8 in order to allow an efficiency-enhanced vibration of the piston 24.
  • compensation piston piston (compensating element, as well as compensating diaphragm)
  • a compensation chamber communicates fluidically with the third chamber 46
  • the other compensation chamber with the fourth Chamber 60 fluidly communicates.
  • a multi-surface cylinder as combined feed drive and vibration drive for efficient vibration drive is disclosed.
  • a fluid circuit for efficient vibration driving comprising a multi-surface cylinder, a first valve connected to first two opposing piston surfaces of a piston of the multi-surface cylinder, and a second valve connected to a third piston surface.
  • a driving method for vibratory driving for a multi-surface cylinder having a first piston surface, a second piston surface counteracting the first piston surface, and a third piston surface equally disposed with the second piston surface, wherein the piston surfaces alternately pressurize the piston surface and second piston surface to vibrate be, and / or wherein the piston extension, the second piston surface and / or the third piston surface is pressurized / be.

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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)
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

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

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4450704A1 (fr) * 2023-04-18 2024-10-23 Plasser & Theurer, Export von Bahnbaumaschinen, Gesellschaft m.b.H. Appareil de bourrage et commande de cet appareil de bourrage
EP4484645B1 (fr) 2023-06-27 2026-03-11 Plasser & Theurer, Export von Bahnbaumaschinen, Gesellschaft m.b.H. Procédé de commande de l'état de fonctionnement d'un actionneur hydraulique d'une unité de bourrage d'un engin de construction de voies ferrées et engin de construction de voies ferrées pour la mise en oeuvre du procédé

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112610542B (zh) * 2020-12-15 2022-03-25 库卡机器人(广东)有限公司 平衡缸液压系统

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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
EP2722165A2 (fr) * 2012-10-22 2014-04-23 Robert Bosch Gmbh Circuit hydraulique pour un axe hydraulique et axe hydraulique
WO2014127393A1 (fr) 2013-02-22 2014-08-28 System7-Railsupport Gmbh Groupe de bourrage pour bourreuse de traverses
EP2902546A1 (fr) 2014-01-30 2015-08-05 System7-Railsupport GmbH Dispositif de compression du lit de ballast d'une voie ferrée
WO2016054667A1 (fr) 2014-10-06 2016-04-14 System 7 - Railsupport GmbH Bourreuse mécanique servant à compacter le lit de ballast d'une voie
EP3073012A1 (fr) * 2015-03-18 2016-09-28 Ibañez Latorre, Jose Antonio Machine d'entretien de voie ferrée pour nivellement et alignement des voies dotée de la capacité de fonctionner sans interruptions dans son avance sur rails rectilignes et pour fonctionner sur branchement et tasser la piste divergente

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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
EP2722165A2 (fr) * 2012-10-22 2014-04-23 Robert Bosch Gmbh Circuit hydraulique pour un axe hydraulique et axe hydraulique
WO2014127393A1 (fr) 2013-02-22 2014-08-28 System7-Railsupport Gmbh Groupe de bourrage pour bourreuse de traverses
EP2902546A1 (fr) 2014-01-30 2015-08-05 System7-Railsupport GmbH Dispositif de compression du lit de ballast d'une voie ferrée
WO2016054667A1 (fr) 2014-10-06 2016-04-14 System 7 - Railsupport GmbH Bourreuse mécanique servant à compacter le lit de ballast d'une voie
EP3073012A1 (fr) * 2015-03-18 2016-09-28 Ibañez Latorre, Jose Antonio Machine d'entretien de voie ferrée pour nivellement et alignement des voies dotée de la capacité de fonctionner sans interruptions dans son avance sur rails rectilignes et pour fonctionner sur branchement et tasser la piste divergente

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4450704A1 (fr) * 2023-04-18 2024-10-23 Plasser & Theurer, Export von Bahnbaumaschinen, Gesellschaft m.b.H. Appareil de bourrage et commande de cet appareil de bourrage
EP4484645B1 (fr) 2023-06-27 2026-03-11 Plasser & Theurer, Export von Bahnbaumaschinen, Gesellschaft m.b.H. Procédé de commande de l'état de fonctionnement d'un actionneur hydraulique d'une unité de bourrage d'un engin de construction de voies ferrées et engin de construction de voies ferrées pour la mise en oeuvre du procédé

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DE102018205821A1 (de) 2019-10-17
EP3556478B1 (fr) 2022-06-15

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