EP1843048B1 - Dispositif de vérin - Google Patents

Dispositif de vérin Download PDF

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Publication number
EP1843048B1
EP1843048B1 EP20070006623 EP07006623A EP1843048B1 EP 1843048 B1 EP1843048 B1 EP 1843048B1 EP 20070006623 EP20070006623 EP 20070006623 EP 07006623 A EP07006623 A EP 07006623A EP 1843048 B1 EP1843048 B1 EP 1843048B1
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EP
European Patent Office
Prior art keywords
cylinder
piston
line
working chamber
fluid cylinder
Prior art date
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Application number
EP20070006623
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German (de)
English (en)
Other versions
EP1843048A2 (fr
EP1843048A3 (fr
Inventor
Leopold Ing. Reisinger
Johann Ing. Schmollngruber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Weber Hydraulik GmbH Austria
Original Assignee
Weber Hydraulik GmbH Austria
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Publication of EP1843048A2 publication Critical patent/EP1843048A2/fr
Publication of EP1843048A3 publication Critical patent/EP1843048A3/fr
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Classifications

    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • 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
    • F15B11/003—Systems with load-holding valves
    • 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
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a fluid cylinder, in particular a double-acting hydraulic cylinder, as described in the preamble of claim 1.
  • a continuously lockable cylinder in which a piston rod has a longitudinal bore extending through the piston with a tooth-like or wave-like profiling of the inner wall into which a stationarily held tube is guided with a rod arranged displaceably therein, wherein the rod has at least one radial and Having parallel to the longitudinal extent of the rod extending ball circulation channel.
  • Such a measure may be to provide an additional, lockable third working chamber in a double-acting fluid cylinder. This is connected in parallel with one of the other two working chambers and blocked in the locked state each piston movement even with pressure loss in one of the other two chambers.
  • Such fluid cylinders are for example made DE 44 05 938 A1 known.
  • a frequently used in double-acting fluid cylinders measure to secure unintentional piston movements at pressure loss is the use of load-holding valve assemblies with control valves or shut-off valves, in particular hydraulically releasable check valves in the supply lines to the working chambers of the fluid cylinder.
  • the object of the invention is to provide a fluid cylinder in which the fixing of the piston or the piston rod takes place in an equally reliable manner, as in the known from the prior art solutions, but the fluid cylinder is simple and robust and inexpensive to produce.
  • a first line leading to the first line connection and a third line leading to the third line connection having a pressure connection and a second line leading to the second line connection Line fluidly connected to a return port and for moving the piston assembly in the retraction direction, the first line and the third line to the return port and the second line to the pressure port fluidly connected. Since, during operation, the pressure medium inflow or pressure medium outflow to the first and third working chamber must always occur simultaneously, it makes sense to combine the associated connection lines to form a common pressure connection.
  • the connection of the fluid cylinder to a hydraulic unit can thereby be accomplished as in conventional working cylinders with only two connection points.
  • a control valve in the form of a directional opening to the cylinder unlockable check valve, in particular check valve is arranged.
  • This allows for the execution of a stroke pressure medium into the first and third working chamber and prevents in case of a possible pressure drop, e.g. by hose breakage, an unforeseen retraction of the piston assembly under the load.
  • a possible pressure drop e.g. by hose breakage
  • an unforeseen retraction of the piston assembly under the load In order to carry out a retraction movement of the piston assembly must be provided a way to create a flow path for the outflow of pressure medium from the first and third working chamber.
  • the check valve itself is preferably designed as a seat valve, whereby a largely leak-free sealing of the first and third working chamber takes place. Mainly for ball seat elements or cone seat elements are in use.
  • the check valves by means of a common control piston unlocked simultaneously.
  • a control valve in the form of a lowering brake valve is arranged in the first line and in the third line between the cylinder and directional control valve, wherein the control valve in a rest position caused by a spring element forms a flow path with a directional opening to the cylinder check valve and in a through an actuating element effected switching position forms a flow path for the outflow of pressure medium from the first and the third working chamber.
  • control valves or the actuators in the first and third line synchronously from the rest position to the changeover position are formed by a common control piston.
  • Such control valves in the form of Senkbremsventilen are proven many times and easily available.
  • An advantage is an embodiment in which the check valve is unlocked via a control line leading to the second line. Since the second working chamber is pressurized via the second line for carrying out a retraction movement of the piston assembly, this pressure can be guided via a control line to the check valve and thereby a flow path for the pressure medium discharge from the first and third working chamber are released.
  • the actuating elements of the control valves can be acted upon by means of a control line with the pressure in the second line.
  • the changeover of the control valve or the actuating elements from the rest position to the switching position is ensured for the implementation of a retraction movement of the piston assembly.
  • the control line can further be installed a throttle element, whereby abrupt switching operations and resulting pressure peaks on the control valve can be avoided.
  • the piston tube and the opening have a circular cross-section.
  • the circular cross-sectional shape can be produced with simple means and nevertheless with high accuracy, as a result of which the first working chamber can be reliably sealed against the third working chamber. Furthermore, in the case of a circular cross section, insertion of an additional piston tube seal is easily possible, as a result of which leakages between the first and third working chambers can be largely prevented.
  • the formation of a fluid cylinder according to another claim as limited by the cylinder bottom and cylinder cover cylinder tube is also inexpensive to manufacture. Furthermore, the same dimensions of the fluid cylinder, as in conventional working cylinders, can be achieved by this design, whereby an exchange against the fluid cylinder according to the invention is easily possible.
  • the piston assembly is tubular. This is e.g. achievable by the piston rod is formed from a tube.
  • the volume of the third working chamber can be made relatively large, as a result of which the effective area of the third working chamber on the piston arrangement can also be made relatively large.
  • the first and third working chambers act in parallel on the piston assembly; if the pressure drops in one of the two working chambers, a load to be held must be held by the other working chamber, so it is advantageous if the active surfaces of the first and third working chambers on the piston assembly are not too different.
  • a further advantageous embodiment of the fluid cylinder is that the piston tube and the piston assembly are arranged coaxially.
  • the piston tube can also be arranged offset relative to the longitudinal axis of the piston arrangement or of the cylinder, it is advantageous for a uniform distribution of forces and the avoidance of transverse forces and bending moments on the piston arrangement to arrange the piston tube and piston arrangement coaxially.
  • the cross-sectional area of the opening is at least 33%, preferably about 40% of the cylinder cross-sectional area.
  • the pressure in the third working chamber may increase to a maximum of three times the nominal pressure when the outflow from the pressure medium is completely blocked.
  • Another advantage is an embodiment of the fluid cylinder according to another claim, according to which the mechanically limited maximum stroke of the piston assembly is shorter than the maximum effective immersion depth of the piston tube, measured from the opening or the piston tube seal to an end face of the piston tube. This design ensures that the third working chamber is functional over the entire stroke of the piston assembly, since the seal is given to the first working chamber through the piston tube in any position.
  • the lines are connected to the working chambers via a directional control valve, in particular a 4/3-way valve with a hydraulic unit according to another claim.
  • a directional control valve in particular a 4/3-way valve with a hydraulic unit according to another claim.
  • Such directional valves are also in conventional working cylinders in use and therefore need not be replaced when replacing a conventional working cylinder against the fluid cylinder according to the invention.
  • the operation of the directional control valve is in many cases mechanically by the operator, but may also include other or additional actuators.
  • check valves or control valves are installed in the cylinder bottom in the cylinder.
  • the cylinder bottom is thus formed as a valve block.
  • check valves or control valves can be designed as valve cartridges inserted in the cylinder bottom, whereby also a compact design of the fluid cylinder is given.
  • a pressure sensor is fluid-connected to the first working chamber and the third working chamber. Since failure of one of the two working chambers, the holding function is taken over by the second intact working chamber, the monitoring by means of pressure sensors is helpful to detect any pressure drop early and further determine which of the two working chambers is inoperative.
  • the pressure sensor emits a signal when falling below a threshold pressure.
  • This signal e.g. in optical or acoustic form can be detected directly by the operator of the fluid cylinder, but also be handed over in the form of a control signal of a control and monitoring device.
  • the pressure sensor connected to a prestressed spring comprises the volumetric flask charged with the pressure in the line.
  • the signal can be generated according to another claim by an optical display element connected to the volumetric flask. If the pressure force acting on the volumetric flask exceeds the oppositely acting biasing force of the spring, which is the case with an intact working chamber, the volumetric flask is displaced against the spring force and an optical display element becomes visible to the operator. In the case of a pressure drop in a working chamber, the volumetric flask is displaced by the spring to its initial position and the change of the optical display element, e.g. a disappearance visually indicates a malfunction to the operator.
  • Another advantage is an embodiment according to a wide claim, according to which there is a signal connection between the pressure sensor and a control and monitoring device.
  • a corresponding control and monitoring device may additionally or alternatively to the operator in the event of a pressure drop in one of the two working chambers perform necessary measures or functions.
  • the signal connection comprises a radio transmission device.
  • the fluid cylinder according to the invention can advantageously according to three further claims for positioning and fixing a tiltable or liftable construction on a vehicle, for moving and fixing an access ramp, in particular on a flatbed trailer or a passenger car transporter, as a lifting cylinder or support cylinder for positioning and fixing of movable Platforms, especially lifts and platforms, are used on vehicles.
  • Fig. 1 is a section through a fluid cylinder 1 according to the invention connected thereto, shown symbolically shown controls schematically and simplified.
  • the fluid cylinder 1 serves, for example, for positioning and fixing a tiltable or liftable structure on a vehicle, for moving and fixing an access ramp, in particular on a flatbed trailer or a passenger car transporter, as a lifting cylinder or support cylinder for positioning and fixing movable platforms, in particular lifting platforms and platforms, on vehicles - the integration of a working cylinder in these applications is known from the prior art and not explained or illustrated in consequence.
  • the fluid cylinder 1 is in particular a hydraulic cylinder 2 with a hydraulic fluid as the working medium.
  • the fluid cylinder 1 comprises a cylinder 3 with a longitudinal axis 4, with which a piston assembly 5 is mounted adjustably in the direction of the longitudinal axis 4.
  • the cylinder 3 is formed in the embodiment of a cylinder tube 6, which is limited in the direction of the longitudinal axis 4 by a cylinder bottom 7 and a cylinder cover 8.
  • the cylinder bottom 7 is welded to the cylinder tube 6, while the cylinder cover 8 is preferably bolted to the cylinder tube 6.
  • the piston assembly 5 comprises the actual piston 9, which divides the interior of the cylinder 3 into a first working chamber 10 and a second working chamber 11.
  • a piston rod 12 connects, which leads through the cylinder cover 8 sealed from the cylinder interior to the outside.
  • the piston assembly 5 has in its interior a cavity 13 which is open through an opening 14 in the form of a bore in the direction of the cylinder bottom 7.
  • the clear cross section of the cavity 13 may coincide with the clear cross section of the opening 14, so for example be prepared by a hole with a constant diameter, the diameter of the cavity 13 may also, as in the FIG. 1 shown to be greater than the diameter of the opening 14.
  • the cavity 13 is formed in the embodiment by a tubular piston rod 12 which is pressure-tight at its free end by a lid 15 and at the opposite end by the piston 9 with the opening 14.
  • the piston assembly 5 may, as in the FIG. 1 shown simplified, be made in one piece, but is also composed for the sake of easier production of the piston 9, the tubular piston rod 12 and the lid 15.
  • a piston tube 16 into the cavity 13.
  • the length of the cavity 13 and the piston tube 16 in the direction of the longitudinal axis 4 is chosen so that an end portion 17 of the piston tube 16 also at maximum extended plunger assembly 5 protrudes at least into the opening 14, ie the maximum effective depth of immersion of the piston tube 16 is greater than the maximum stroke of the piston assembly 5.
  • the piston tube 16 is sealed through the opening 14, said sealing by a tight fit between a Outer diameter 18 of the piston tube and the clear diameter of the opening 14 can be effected.
  • the opening 14 may be provided with a piston tube seal 19 which seals the passage of the piston tube 16 through the opening 14 in the piston 9.
  • the cavity 13 is thus sealed from the first working chamber 10 at the opening 14 by the piston tube 16 itself or the piston tube seal 19 and forms a third working chamber 20.
  • the piston tube 16 is concentric with the longitudinal axis 4 of the piston assembly 5 and the cylinder in the illustrated embodiment 3, but may, if necessary, also be arranged offset to the longitudinal axis 4, for example when an inventive Fluid cylinder 1 with a continuous piston rod 12 is required.
  • the first working chamber 10 of the fluid cylinder 1 is bounded by the cylinder inner wall 21, a cylinder bottom 7 facing the second piston surface 22 and an outer shell 23 of the piston tube 16, that is annular in the embodiment and has to inflow or outflow of pressure medium to a first line connection 24
  • the piston rod side second working chamber 11 is bounded by the cylinder inner surface 21, a cylinder cover 8 facing the second piston surface 25 and the outer shell 26 of the piston rod 12, as in a conventional working cylinder annular, and has to inlet and outlet of pressure medium, a second line connection 27th on.
  • the third working chamber 20 is bounded by an inner surface 28 of the cavity 13, an outer jacket 29 of the piston tube 16, which is identical to the outer jacket 23 of the piston tube 16 in the first working chamber 10, and an end face 30 of the piston tube 16 and is to Zu or Outflow of pressure medium via a channel 31 in the piston tube 16 connected to a third line connection 32.
  • the piston 9 is additionally provided with a piston seal 33, for sealing the second working chamber 11 in the passage of the piston rod 11 to the outside, the cylinder cover 8 is provided with a piston rod seal 34.
  • the piston tube seal 19, the piston seal 33 and the piston rod seal 34 are movement seals and, for example, performs as a mechanical seal, as sealing material all known in the art materials are conceivable.
  • the piston tube 16 is guided in the direction of the longitudinal axis 4 through the piston head 7, but it is also possible to guide the piston tube 16 laterally through the cylinder tube 6, as long over the entire stroke of the piston assembly 5 at the opening 14, the seal between first working chamber 10 and third working chamber 20 is given and a displacement of the piston tube 16 relative to the cylinder 3 is prevented for example by a support.
  • the piston assembly 5 is moved relative to the cylinder 3 in the extension direction 36, while at the same time via the second line connection 27 pressure fluid from the second working chamber 11 flows.
  • a supply unit for example, a hydraulic unit pressurized pressure medium.
  • a pressure port 39 through which the pressure medium to the fluid cylinder 1 can flow, and a return port 40 is guided via the pressure fluid from the fluid cylinder 1 back to the hydraulic unit is arranged.
  • the movement of the fluid cylinder 1, ie extension, retraction or stoppage of the piston assembly 5 is, as applied in conventional working cylinders, controlled by means of a directional control valve 41, in particular a 4/3-way valve 42.
  • the three possible positions of the 4/3-way valve 42 cause the extension movement, the retraction movement or the stoppage of the piston assembly 5.
  • the pressure port 39 fluidly connected to a first working port 43 to the valve assembly 38, to carry out the Retraction, the pressure port 39 is fluidly connected to a second working port 44.
  • a first line 45 leads to the first line connection 24 of the first working chamber 10, from the second working connection 44 a line 46 to the second line connection 27 of the second working chamber 11, and from the first working connection 43 a third line 47 to the third line connection 32 of the third working chamber 20. Since the flow of pressure medium into or out of the first working chamber 10 must always take place simultaneously with the flow of pressure medium into or out of the third working chamber 20, the first line 45 and the third line 47 can be combined in at least a partial section in a single line.
  • the lines 45, 46, 47 may be formed at least in sections as separate pipelines or as drilled channels in solid valve blocks, in particular the cylinder base 7 executed.
  • An important function of the fluid cylinder 1 according to the invention is one in the retraction direction 37 to reliably hold the load acting on the piston rod 12 and to prevent uncontrolled retraction of the piston assembly 5.
  • This setting of the piston assembly 5 in the cylinder 3 can be effected by selecting the blocking position on the directional control valve 41, since thereby the pressure medium inflow or outflow via the first working port 43 and the second working port 44 is prevented.
  • a reliable fixation of the piston assembly 5 is not guaranteed, since on the one hand the directional control valve 41 leakage can occur in the control system of the fluid cylinder 1 or by damage to the lines from the directional control valve 41 to the working ports 43, 44, often in the form are formed by hose lines, can enter and thereby also an uncontrolled pressure drop could occur in the fluid cylinder 1.
  • a first safety valve 48 is arranged in the first line 45 to the first working chamber 10, and arranged in the third line to the third working chamber 20, a second safety valve 49.
  • These safety valves 48, 49 allow an inflow of pressure medium to the first working chamber 10 and the third working chamber 20 at a correspondingly high pressure at the first working port 43, but prevent drainage of pressure medium from the first working chamber 10 and the third working chamber 20, so long as the directional control valve 21 a retraction movement of the piston assembly 5 is triggered.
  • the safety valves 48, 49 are designed as control valves 50 in the form of two-way valves and form in each case in a rest position caused by a spring element 51 a secured by a check valve 52 flow path and in an actuated by an actuator 53, eg as a control piston switching position by a throttle element 54 throttled flow path in the first conduit 45 and the third conduit 47.
  • the actuators 53 are each fluidly connected via a control line 55 to the second conduit 46, so hydraulically triggered as soon as triggering the retraction position on the directional control valve, the pressure in the second Line 46 is increased to the second working chamber 11.
  • the pressure medium which is delayed by the throttle elements 54, can flow out of the first working chamber 10 and the third working chamber 20 and reach the return port 40, thus retracting the piston arrangement 5.
  • the actuators 53 may additionally be fluidly connected via further control lines 56 to the conduits 45, 47 between the control valves 50 and the line ports 24, 32. Through these control lines 56, the control valves 50 in the occurrence of very high Press, for example, in an overload on the piston rod 4, which would damage the system, be controlled and the load thus, delayed by the throttle elements 54, drop.
  • the control valves 50 can also be embodied as unlockable shut-off valves, in particular check valves 52, which open in the direction of the fluid cylinder 1. For a secure holding of the load, these are designed as seat valves due to the negligible leakage losses, e.g. with ball seat or conical seat.
  • control valves 50 may be embodied as lowering brake valves, which have proven themselves many times and are available in many embodiments.
  • the fluid cylinder 1 can be referred to as a two-circuit cylinder due to its design with two secure supply lines to the working chambers 10, 20.
  • a pressure sensor 57 comprises a pressure piston in the working chamber 10, 20 applied to the volumetric piston 58, which is displaced by a pressure overcoming the spring bias against the force of a biased spring 59, whereby an optically visible display element 60 is visible outside of the pressure sensor 57 , If the display element 60 is not visible, this indicates that the pressure in the associated working chamber 10, 20 falls below a limit that can be defined by the spring preload, whereby the operator is made aware of this condition and can take appropriate measures to prevent the occurrence of a dangerous situation prevent.
  • the safety valves 48, 49 or control valves 50 are installed in the cylinder 3 in the cylinder 3 in the region of the cylinder bottom.
  • the cylinder bottom 7 is thus formed as a stable valve block and may contain the entire valve assembly 38.
  • Fig. 2 is a possible embodiment of the safety valves 48, 49 shown in a simplified, schematic sectional view.
  • the two safety valves 48, 49 are formed in this embodiment by two control valves 50, which are designed substantially as a pilot-operated check valves 52.
  • a control piston 62 By pressure in the fluidically connected to the second line 46 control line 55, a control piston 62 is pressed from the illustrated rest position against the force of the spring element 51 in a switching position, not shown, whereby blocking elements 63 of the check valves 52 the flow path for the outflow of pressure medium from the first Release working chamber 10 and the third working chamber 20.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Claims (20)

  1. Vérin de fluide (1), en particulier vérin hydraulique (2) à action double, comprenant un vérin (3) avec un fond de vérin (7) et un couvercle de vérin (8), un agencement de piston (5) guidé dans le vérin (3), où est délimitée par une première face de piston (22) de l'agencement de piston (5) orientée vers le fond de vérin (7) et une paroi de vérin (21) une première chambre de travail (10) avec un premier raccordement de conduite (24) et est délimitée par une deuxième face de piston (25) de l'agencement de piston (5) orientée vers le couvercle de vérin (8) et la paroi intérieure de vérin (21) une deuxième chambre de travail (11) avec un deuxième raccordement de conduite (27), où une tige de piston (12) de l'agencement de piston (5) est guidée d'une manière étanche à travers le couvercle de vérin (8), un espace creux (13) dans l'agencement de piston (5) avec une ouverture (14) orientée vers le fond de vérin (7), qui forme une troisième chambre de travail (20) ainsi qu'un tube de piston (16) fixe relativement au vérin (3), relié fluidement à un troisième raccordement de conduite (32), dont une section d'extrémité (17) du tube de piston (16) est guidée à travers la première chambre de travail (10) et fait saillie à travers l'ouverture (14) dans la troisième chambre de travail (20), et la troisième chambre de travail (20) est rendue étanche par rapport à la première chambre de travail (10) par le tube de piston (16) et/ou par une garniture d'étanchéité de tube de piston (19) disposée entre le tube de piston (16) et l'agencement de piston (5), où pour le déplacement de l'agencement de piston (5) dans la direction de sortie (36), une première conduite (45) menant au premier raccordement de conduite (24) et une troisième conduite (47) menant au troisième raccordement de conduite (32) est reliée fluidement à un raccordement de pression (43) et une deuxième conduite (46) menant au deuxième raccordement de conduite (27) à un raccordement de reflux (44), et pour le déplacement de l'agencement de piston (5) dans la direction d'entrée (37), la première conduite (45) et la troisième conduite (47) est reliée fluidement au raccordement de reflux (44) ainsi que la deuxième conduite (46) au raccordement de pression (43), et en outre, dans la première conduite (45) et dans la troisième conduite (47) est disposée respectivement une soupape de commande (50) sous la forme d'une soupape de retenue (52) ou d'une soupape de descente freinée déverrouillable, s'ouvrant en direction du vérin (3), caractérisé en ce que les soupapes de commande (50) peuvent être déverrouillées simultanément au moyen d'un piston de commande commun (62).
  2. Vérin de fluide (1) selon la revendication 1, caractérisé en ce que les soupapes de commande peuvent être déverrouillées par une conduite de commande (55) menant du piston de commande (62) à la deuxième conduite (46).
  3. Vérin de fluide (1) selon la revendication 1 ou 2, caractérisé en ce que le tube de piston (16) et l'ouverture (14) ont une section transversale circulaire.
  4. Vérin de fluide (I) selon l'une des revendications 1 à 3, caractérisé en ce que le vérin (3) est formé essentiellement par un tube de vérin (6) délimité par le fond de vérin (7) et le couvercle de vérin (8).
  5. Vérin de fluide (1) selon l'une des revendications 1 à 4, caractérisé en ce que l'agencement de piston (5) est réalisé en une forme tubulaire.
  6. Vérin de fluide (1) selon l'une des revendications 1 à 5, caractérisé en ce que le tube de piston (16) et l'agencement de piston (5) sont disposés coaxialement.
  7. Vérin de fluide (1) selon l'une des revendications 1 à 6, caractérisé en ce que la face en section transversale de l'ouverture (14) représente au moins 33%, de préférence environ 40% de la face en section transversale du vérin.
  8. Vérin de fluide (1) selon l'une des revendications 1 à 7, caractérisé en ce que la course maximale mécaniquement limitée de l'agencement de piston (5) est plus courte qu'une profondeur de plongée maximale efficace du tube de piston (16) mesurée depuis l'ouverture (14) respectivement la garniture d'étanchéité de tube de piston (19) jusqu'à une face frontale (30) du tube de piston (16).
  9. Vérin de fluide (1) selon l'une des revendications 1 à 8, caractérisé en ce que pour la commande du déplacement de l'agencement de piston (5), les conduites (45, 46, 47) sont reliées par un distributeur (41), en particulier un distributeur à 4/3 voies (42) au raccordement de pression (43) respectivement au raccordement de reflux (44).
  10. Vérin de fluide selon l'une des revendications 1 à 9, caractérisé en ce que les vannes de commande (50) sont installées dans la zone du fond de vérin (7) dans le vérin (3).
  11. Vérin de fluide (1) selon l'une des revendications 1 à 10, caractérisé en ce que les vannes de commande (50) sont réalisées comme des cartouches à vanne.
  12. Vérin de fluide (1) selon l'une des revendications 1 à 11, caractérisé en ce qu'un capteur de pression (57) est relié fluidement à la première chambre de travail (10) et à la troisième chambre de travail (20).
  13. Vérin de fluide (1) selon la revendication 12, caractérisé en ce que le capteur de pression (57), lors du passage en dessous d'une pression limite, émet un signal.
  14. Vérin de fluide (1) selon la revendication 12 ou 13, caractérisé en ce que le capteur de pression (57) comprend un piston de mesure (58) relié à un ressort précontraint (59), chargé par la pression dans la conduite (45), respectivement la conduite (47).
  15. Vérin de fluide (1) selon la revendication 14, caractérisé en ce que le signal est produit par un élément d'affichage optique (60) relié au piston de mesure (58).
  16. Vérin de fluide (1) selon l'une des revendications 12 à 15, caractérisé en ce qu'il existe entre le capteur de pression (57) et une installation de commande et de surveillance une liaison par signaux.
  17. Vérin de fluide (1) selon la revendication 16, caractérisé en ce que la liaison par signaux comprend une installation de transmission radio.
  18. Utilisation du vérin de fluide (1) selon l'une des revendications 1 à 17 pour le positionnement et pour la fixation d'une construction basculable ou relevable à un véhicule.
  19. Utilisation du vérin de fluide (1) selon l'une des revendications 1 à 17, pour le déplacement et la fixation d'une rampe de montée, en particulier à une remorque à chargement bas ou un transporteur de voitures particulières.
  20. Utilisation du vérin de fluide (1) selon l'une des revendications 1 à 17, comme vérin de levage ou vérin d'appui pour le positionnement et la fixation de plateformes mobiles, en particulier des ponts élévateurs et de plateformes à des véhicules.
EP20070006623 2006-04-07 2007-03-30 Dispositif de vérin Active EP1843048B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT6082006A AT503408B1 (de) 2006-04-07 2006-04-07 Fluidzylinder-anordnung

Publications (3)

Publication Number Publication Date
EP1843048A2 EP1843048A2 (fr) 2007-10-10
EP1843048A3 EP1843048A3 (fr) 2008-07-09
EP1843048B1 true EP1843048B1 (fr) 2010-07-14

Family

ID=38226480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070006623 Active EP1843048B1 (fr) 2006-04-07 2007-03-30 Dispositif de vérin

Country Status (3)

Country Link
EP (1) EP1843048B1 (fr)
AT (1) AT503408B1 (fr)
DE (1) DE502007004365D1 (fr)

Cited By (1)

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RU217841U1 (ru) * 2023-02-20 2023-04-20 Общество с ограниченной ответственностью "ГИДРО-СТАР" Распределительный узел насоса

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US9435359B2 (en) * 2012-02-13 2016-09-06 Schlumberger Technology Corporation Adaptive hydraulic cylinder with floating seal interface
CN103357671B (zh) * 2012-03-26 2015-06-17 苏州泰克诺机电有限公司 压力流量闭环可调的液压系统
AU2015213448C1 (en) 2014-02-06 2019-07-04 Ensign Drilling Inc. Hydraulic multi-displacement hoisting cylinder system
RU2665762C2 (ru) * 2016-08-11 2018-09-04 Российская Федерация, от имени которой выступает Государственная корпорация по атомной энергии "Росатом" Гидропривод
CN108999836B (zh) * 2018-09-30 2024-05-24 中船重庆液压机电有限公司 活塞杆进油双作用多级液压缸

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SU561812A1 (ru) * 1975-09-08 1977-06-15 Всесоюзный Научно-Исследовательский Институт Резинотехнического Машиностроения Система управлени скоростью движени гидроцилиндра
DE3140266A1 (de) * 1981-10-10 1983-04-28 Mannesmann Rexroth GmbH, 8770 Lohr "vorrichtung zum steuern eines hydromotors"
JPS58501833A (ja) * 1981-11-03 1983-10-27 トウモ−タ−　コ−ポレ−シヨン ロック弁
DE3807669A1 (de) 1988-03-09 1989-09-21 Andexser Lucie Stufenlos verriegelbarer arbeitszylinder
US5090296A (en) * 1991-01-09 1992-02-25 Todd Motion Controls Inc. Piston assembly and method
DE4405938A1 (de) * 1994-02-24 1995-08-31 Werner Prof Dr Ing Moeller Kolben-Zylinder-Einheit
DE19543876A1 (de) * 1995-11-24 1997-05-28 Rexroth Mannesmann Gmbh Verfahren und Vorrichtung zur Ansteuerung einer Hydroanlage eines Arbeitsgerätes
US6659240B2 (en) * 1999-08-10 2003-12-09 Lars Dernebo Arrangement for a piston and cylinder device
AT4094U1 (de) 1999-12-07 2001-01-25 Weber Hydraulik Gmbh Linearverstellantrieb
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RU217841U1 (ru) * 2023-02-20 2023-04-20 Общество с ограниченной ответственностью "ГИДРО-СТАР" Распределительный узел насоса

Also Published As

Publication number Publication date
EP1843048A2 (fr) 2007-10-10
EP1843048A3 (fr) 2008-07-09
AT503408A1 (de) 2007-10-15
DE502007004365D1 (de) 2010-08-26
AT503408B1 (de) 2008-06-15

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