EP2016290A1 - Procede pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci - Google Patents

Procede pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci

Info

Publication number
EP2016290A1
EP2016290A1 EP07724673A EP07724673A EP2016290A1 EP 2016290 A1 EP2016290 A1 EP 2016290A1 EP 07724673 A EP07724673 A EP 07724673A EP 07724673 A EP07724673 A EP 07724673A EP 2016290 A1 EP2016290 A1 EP 2016290A1
Authority
EP
European Patent Office
Prior art keywords
piston
working cylinder
cylinder
fluid
stroke
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
EP07724673A
Other languages
German (de)
English (en)
Other versions
EP2016290B1 (fr
Inventor
Josef-Gerhard Tünkers
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.)
Tuenkers Maschinenbau GmbH
Original Assignee
Tuenkers Maschinenbau GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Tuenkers Maschinenbau GmbH filed Critical Tuenkers Maschinenbau GmbH
Publication of EP2016290A1 publication Critical patent/EP2016290A1/fr
Application granted granted Critical
Publication of EP2016290B1 publication Critical patent/EP2016290B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • 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
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • 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
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a method for pressurizing a piston-cylinder unit by a pressurized fluid, primarily for use in the bodywork of the automotive industry.
  • the invention relates to a control for pressurizing a piston-cylinder unit by a pressurized fluid, primarily for use in the bodywork of the automotive industry.
  • the invention also relates to a piston-cylinder unit to be actuated by a pressurized fluid as a working cylinder, in particular for use in the bodywork of the motor vehicle industry.
  • the invention relates to the use of such a working cylinder for driving devices for clamping, pressing, joining, punching, embossing, punching and welding, in particular with the interposition of a toggle joint or other gear parts, z. B. for use in the bodywork of the automotive industry.
  • Piston-cylinder units are referred to in the industry as "working cylinders.” If the term “working cylinder” is used below, not only a cylinder, but a functioning drive unit comprising at least one cylinder and at least one longitudinally displaceable therein and sealingly guided pistons with piston rod arranged on one side of the relevant piston, which is preferably brought out of the respective cylinder chamber in a sealed manner, and devices, primarily for clamping, and / or pressing, and / or joining, and / or punching, and / or embossing, and / or punching and / or welding drives. In such devices z. B.
  • the piston rod often with the interposition of at least one toggle joint other device parts, for example a clamping arm, which interacts with an abutment (pine), or an expanding mandrel, or a centering mandrel, or a joining device or a die, a device part for punching, or device parts , for example with the interposition of a toggle joint, actuatable welding electrodes on.
  • a clamping arm which interacts with an abutment (pine), or an expanding mandrel, or a centering mandrel, or a joining device or a die, a device part for punching, or device parts , for example with the interposition of a toggle joint, actuatable welding electrodes on.
  • Clamping devices for clamping, pressing, joining, punching, embossing, punching and welding are used in great variety, for example in the body construction of the automotive industry.
  • Clamping devices are often designed as so-called “toggle clamps” and keep body panels to their permanent connection by spot welding, gluing, clinching or the like in position, while other devices, for example, serve as underbody tensioner and a centering mandrel with the interposition of a linkage, z.
  • pressurized fluid for example hydraulic fluid or compressed air and thus the pumping power and its drive energy is required in the prior art for the entire stroke of the associated piston with piston rod, for example toggle joint and the like, which means that constantly most of the drive energy is lost.
  • the invention has for its object to overcome the disadvantages of the prior art and in all areas, that is, both in the hitherto known method for pressurizing working cylinders, primarily for use in the bodywork of the automotive industry, as well as in the control of pressurized fluid for applying such working cylinders and in the application of working cylinders for devices for clamping, pressing, joining, punching, embossing, punching and welding to contribute to a very significant improvement in the energy balance and thus to save costs.
  • a working cylinder during the idle stroke on both sides of the piston pressurized medium so that during the idle stroke (Anstellhub) only the Differential force in the direction of the working stroke is effective, which results from the difference between the acted upon by the fluid pressure piston surface and the opposite side of the piston annular surface.
  • Fluid and in particular energy consumption for the pump and its drive motor, in particular compressed air and hydraulic fluid consumption thereby significantly, for example by 50%, reduced.
  • the piston ring side is relieved of pressure, while the piston surface is acted upon by fluid pressure.
  • the fluid pressure force can thereby develop and, for example the clamping arm of a toggle lever jig, or a pressing device, a joining device, a stamped part, a device part for embossing or punching, or welding jaws, for example, with the interposition of a toggle joint act.
  • the control for the Druckstoffstoffbuchbuchung takes place in the invention either away or pressure-dependent.
  • a valve for example a piston valve, actuated, whereby the piston ring side is depressurized and the piston surface is acted upon by the full fluid pressure.
  • the full pressure force can unfold in the working direction in order to be able to act, for example, to a toggle lever clamping device or a device for pressing, joining, stamping, embossing, punching or welding, primarily with the interposition of a toggle joint.
  • the retraction of the piston rod and thus the return movement of the associated piston takes place by the pressurization of the piston ring side by the previously reversed valve.
  • control parts of the control system for example spool valves and channels in the cylinder cover and / or in the cylinder bottom, if necessary, also in side walls of the cylinder, completely or partially integrate, resulting in the dimensions of the previously conventional devices such as those for clamping, pressing, joining , Stamping, embossing, punching or welding, primarily using toggle levers, in the bodywork of the automotive industry, are needed, not enlarge, so that the existing, for example, in the automotive industry standards are retained in terms of external dimensions.
  • the arrangement can be made both in circular cylinders, as in so-called flat (rectangular), and also in oval or flat oval cylinders.
  • Working cylinders designed in accordance with the invention can be used with great advantage, in particular in the automotive industry, for example in devices for clamping, pressing, joining, stamping, embossing, punching and welding in the bodywork of the motor vehicle industry.
  • Existing production lines can be provided without structural changes with such working cylinders, as they are the subject of the invention, whereby the energy costs for operating such production lines can be significantly reduced.
  • an inventive cylinder is used for the fact that the piston rod controls a valve, for example a spool with completion of the idle stroke (Anstellhubes) such that the full pressure medium pressure acts on the force effective piston side is particularly advantageous.
  • Working cylinders which are designed in this way, can be used with particular advantage in so-called toggle lever tensioning devices in the bodywork of the automotive industry.
  • Claim 26 describes a particularly advantageous embodiment in which a releasable coupling is provided which does not make a connection between the piston rod and valve during the idle stroke, but with the termination of Leerhubes (Einstellhub) automatically takes effect and controls the valve so that the pressure medium pressure fully acts on the force-effective piston side.
  • Leerhubes Eustellhub
  • FIG. 2 shows the apparent from Figure 1 working cylinder in the end position of the working stroke (power stroke), in longitudinal section.
  • 3 shows a further embodiment of a working cylinder in the intermediate position of an idle stroke in the direction of arrow Y, in longitudinal section;
  • FIG. 4 shows the working cylinder shown in FIG. 3 in an intermediate position when the piston is moved back in the direction X (opening stroke), likewise in axial longitudinal section;
  • FIG. 5 shows a toggle lever clamping device in longitudinal section with a working cylinder according to the invention
  • FIG. 6 shows a further embodiment of a working cylinder with an external control device, partly in longitudinal section with an interrogation device
  • FIG. 8 shows a toggle lever clamping device with a working cylinder according to the invention during the power stroke (clamping), end position, partly in the axial longitudinal section, partly in the view; 9 in the open position (piston) in the opposite end position after completion of the opening stroke and
  • Fig. 10 the apparent from Figs. 8 and 9 toggle lever device when executing the Anstellhubes (idle stroke) (intermediate position of the piston).
  • reference numeral 1 designates a cylinder having a cylinder bottom 2 and a cylinder cover 3. Cylinder bottom and / or cylinder cover can be detachably and interchangeably connected to the actual cylinder 1 by screws (not shown).
  • a piston rod 6 On one side of the piston 4, a piston rod 6 is assigned, are driven by the appropriate device parts for clamping 7, for pressing, joining, stamping, embossing, punching or welding.
  • These device parts 7 or the like are indicated only schematically in FIGS. 1 and 2.
  • a toggle lever arrangement can also be arranged between these device parts 7, as shown in FIG. 5 and designated overall by the reference numeral 8.
  • the device part 7 is shown in Fig. 5 by a clamping arm, with other device parts, for example with a non-illustrated abutment, also called jaw, cooperates.
  • the cylinder 1 in a guided orthogonal to its longitudinal axis cross-section circular, but also oval, rectangular, flat oval or otherwise designed.
  • a longitudinal channel 10 which is fluid-conductively connected at the end section facing the cylinder cover 3 to a transverse channel 11 which extends at one end into the working cylinder space 12 and at its other end the working cylinder chamber 12 opens and is connected here to a not drawn control system for a suitable fluid supply and discharge or vent.
  • This fluid may be hydraulic fluid, compressed air or a quasi-liquid as used in operating working cylinders. In the bodywork of the automotive industry, one will primarily use compressed air, as these everywhere in the Operated and especially in production lines is available, but this is not absolutely necessary for the realization of the invention.
  • the longitudinal channel 10 is fluid-conductively connected to a branch channel 13 arranged in the cylinder base 2, while the longitudinal channel 10 is also fluid-conductively connected at its end in fluid-conducting connection with a channel section 14 which opens into a chamber 15 in a fluid-conducting manner.
  • a further channel 16 is arranged, which opens into a cylindrical bore 17.
  • a chamber channel 18 connects, which opens fluid-conducting at one end with the channel 16 and at the other end into the chamber 15.
  • a piston slide 19 is longitudinally displaceable and sealingly guided, which protrudes with a certain length in the Zylinder Weghubraum 21 and is guided in the chamber 15 with a piston 20 longitudinally displaceable and sealing.
  • the chamber 15 is thereby divided into two cylinder chambers, wherein in the one cylinder chamber 22 of the chamber channel 18 opens fluid-conducting, while in the cylinder chamber 23, the channel portion 14 opens fluid-conducting.
  • the spool 19 has a longitudinal channel 24, which extends in the illustrated embodiment coaxially to the longitudinal axis of the spool 19 over a portion of its length and has a orthogonal to the longitudinal axis of fluid-conducting, connected to the longitudinal channel 24 branch channel 25 up.
  • FIGS. 1 and 2 working cylinder is installed in the apparent from Fig. 5 toggle lever device.
  • the operation of the apparent from Figs. 1 and 2 and 5 working cylinder is the following:
  • the transverse channel 11 is connected to a fluid source, not shown, which supplies pressurized fluid, for example compressed air.
  • pressurized fluid for example compressed air.
  • the working cylinder space 12 is pressurized with pressure medium pressure via the longitudinal channel 10, the branch channel 13, the branch channel 13 and the branch channel 25 and the longitudinal channel 24 in the spool valve 19 and the Zylinder Weghubraum 21 with the same pressure medium pressure.
  • both the working cylinder space 12 and the cylinder return space 21 are simultaneously acted upon by the pressurized fluid.
  • the fluid pressure acts on the piston 4 from both sides.
  • This venting can be done via a suitable not shown control system.
  • the retraction of the piston rod 6, so a movement in the direction X (opening stroke) is done by appropriate control of the control device, not shown, whereby the Druckstoffstoffbuchstoffung the piston ring side, so the Zylinder Weghubraums 21 by the previously reversed, in this case designed as a spool valve 19 valve.
  • the channel 16 is connected via the controller to the pressure medium pressure.
  • the fluid is thereby introduced via the channel 16 and the longitudinal channel 24 in the spool 19 in the Zylinder Weghubhaum 21.
  • Via the chamber channel 18, the pressure medium pressure also propagates into the chamber part 22 and acts on the piston 20 and thereby holds the piston valve 19 in its position shown in FIG. 2.
  • a valve chamber 26 is arranged transversely to the lifting movement of the piston 4, in which a piston valve 27 is arranged longitudinally displaceable in opposite directions longitudinally displaceable and sealing.
  • the piston slide 27 has at its ends piston-like thickenings and approximately in its central longitudinal section 28 a reduction in diameter, so that an annular space 29 results in the circumferential direction.
  • a transverse channel 11 and a channel 16 are in turn connected at a distance, which are connected via a suitable fluid control (not shown) alternately to the full pressure medium pressure or to vent.
  • longitudinal channel 10 is connected via the transverse channel 11 in turn to the working cylinder space 12, also opens fluidly into a channel 30, which opens into the valve chamber 26, in the region of the annular space 29, fluid-conducting.
  • the channel 16 is also connected via a channel section 31 to a part of the valve chamber 26, in which a plunger 32 projects longitudinally displaceable and sealing, which is integrally connected to a piston 33 which is longitudinally displaceable and sealingly arranged in a chamber 34 and through one Compression spring element 35, which is under bias, is always loaded in the direction of the spool 27 away.
  • the compression spring element 35 is supported at one end on an intermediate wall 36 and at the other end against the piston 33 from.
  • a branch channel 37 opens, which is in fluid communication with a channel section 38, which can be fluid-conductively connected to the transverse channel 11 (FIG. 3).
  • the channel section 38 opens into the Zylinder Weghubraum 21 fluidly conductive.
  • the piston 4 executes an idle stroke in the direction Y.
  • the transverse channel 11 is connected via a control, not shown, to a suitable fluid source, for example compressed air, whereby the channel section 38 is acted upon by fluid pressure and thereby the Zylinder Weghubraum 21 and the annular space 29 and the channel 30 and the transverse channel 11 and the working cylinder space 12 pressurized fluid pressure.
  • a suitable fluid source for example compressed air
  • the piston 4 and the piston rod 6 and any connected device parts not shown in FIGS. 3 and 4, for example, a toggle lever assembly 8 with a device part 7, for example, a Clamping arm (Fig. 5), with the differential force resulting from the pressure-effective piston surfaces moves.
  • the pressure medium pressure propagates via the channel section 38 and the branch channel 37 into the chamber 34 and acts on the piston 33, which then overcomes the restoring force of the compression spring element 35, the plunger 32 presses against the piston slide 37 and thereby shuts off the transverse channel 11 of the annular space 29, so that the cylinder return stroke 21 is no longer acted upon by the pressure medium pressure.
  • the full pressure medium pressure acts on the pressure-effective surface of not provided with the piston rod 6 side of the piston 4, whereupon the device in question, for example, a toggle lever device, or a device for clamping, pressing, joining, punching, embossing, punching or welding, can exercise their full stroke.
  • the Zylinder Weghubraum 21 is then depressurized.
  • a multi-way valve 39 is included in a system control, not shown, outside of the actual working cylinder and works with a fluid source, not shown, for example, a compressed air source or a hydraulic fluid source together, in a suitable manner, for example via at least one motor-driven pump, pressure medium under pressure, is supplied.
  • a fluid source not shown, for example, a compressed air source or a hydraulic fluid source together, in a suitable manner, for example via at least one motor-driven pump, pressure medium under pressure, is supplied.
  • the channel section 38 can be connected to the cylinder return stroke chamber 21 and the transverse channel 11 to the working cylinder chamber 12 via the multi-way valve 39. During the idle stroke, in turn, only the differential pressure acts on the piston 4 and shifts it during the working stroke in the direction Y.
  • the reference numeral 40 denotes a device only schematically indicated for detecting the position of the piston rod 6.
  • This device may be a so-called cassette known from toggle-type clamping devices, in which the respective position of the piston rod 6, for example via a switching lug 41, can be detected by pneumatic switches, microswitches, inductive switches or the like.
  • the device 40 may also be associated directly with cylinder 1 in the form of a cassette, for example in a recess thereof, as shown for example in FIG. 5, where the device for detecting the various positions of the piston rod 6 and thus indirectly also the angular position of the clamping arm in one the rear side of the clamping head 42 located slot 43 is arranged.
  • This slot 43 may preferably extend in the longitudinal axis direction of the clamping head 42 and thus parallel to the stroke direction of the piston rod 6 or transversely thereto.
  • the device 40 largely seals the slot outwardly, for example, liquid and dust tight.
  • the device can also be designed as a so-called adaptive cassette, in which by single or multiple driving certain positions these positions in a memory electronically stored and Careabbaubar, for example, to assign a clamping arm different angular positions.
  • the device parts 44, 45 may be relatively mutually adjustable to take into account different working positions, for example, clamping positions.
  • the device parts 44, 45 may switch, z. B. electrical switches or inductive switches, which are damped by the switching flag 41.
  • the data is retrieved via a suitable electrical or electronic plug 46 and transmitted via a line, for example to a remote control station, a data processing system or the like. These data may be included in a production control or regulation and may be located in, for example, a production line in the body shop of the automotive industry.
  • the reference numeral 47 denotes a seal, through which the piston rod 6 can be guided out of the working cylinder in a fluid-tight manner.
  • the piston 4 is assigned a against the restoring force of a compression spring element 48 hubbewegaji control pin 49 which is longitudinally displaceable and sealingly arranged in a bore of the piston 4 and the stimendmen cooperates with the spool 19, such that with the termination the idle stroke of the control pin 49 meets stimend soup on the end face of the spool valve 19 and hineinverschiebt this in the direction Y, ie in the cylinder cover 3.
  • the coupling rod 50 is at one end connected to the spool 19 materially or functionally in one piece, for example by thread. Moreover, the coupling rod 50 protrudes into a space 54 of the clamping head and is arranged at a distance from the outer periphery of the piston rod 6. At its end portion facing away from the piston slide 19, the coupling rod 50 has a diameter enlargement 55. In addition, in this area a cup-shaped spring sleeve 56 is arranged with its outer diameter at the enlargement of the enlargement 55 facing end, outwardly projecting flange 57. The spring sleeve 56 slides with a bore 58 on the outer periphery of the circular cross-section coupling rod 50th
  • a prestressed compression spring element 59 is provided, which in the present case is designed as a helical compression spring.
  • the compression spring element 59 is axially and radially guided and held by the spring sleeve over a large part of its axial length.
  • the compression spring element 59 has a tendency to expand and the spring sleeve 56 to move with its front side to a stop 60 which is integrally connected to the coupling rod 50.
  • the stopper 60 may be formed by a transverse pin, a screw, an expanding mandrel or the like, which is fixedly disposed in a bore orthogonal to the longitudinal axis of the coupling rod 50 and limits the displacement of the spring sleeve 56 in the X direction.
  • a coupling 62 is fixedly connected, which thus moves during the lifting movement of the piston rod 6 in the direction of X and Y respectively.
  • the coupling 62 is designed as a sheet projecting orthogonally to the longitudinal axis of the piston rod 6 with a through-bore which is larger than the outer diameter of the spring sleeve 56, so that it can slide through this bore of the coupling 56.
  • the bore in the coupling 66 is smaller than the outer diameter of the flange 57 of the coupling sleeve, so that the coupling 62 engage under the flange 57 and can take with a stroke in the direction Y under compression of the compression spring element 59 (FIG. 8).
  • 10 shows how the coupling 62 slides over the spring sleeve 56, while FIG. 9 relates to a representation in which the spring sleeve is located below the spring sleeve 56, FIG. speaking relaxation of the compression spring element 59 has been moved against the stop 60 in the X direction.
  • the opening 63 in the coupling 62 is also sized so that it can slide over the stopper 60 away.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

L'invention présente comment des cylindres moteurs peuvent être alimentés en fluide sous pression avec économie d'énergie, pour entraîner par exemple des dispositifs pour tendre (dispositifs de tension avec levier à genouillère), et/ou pour presser, et/ou jointer, et/ou découper, et/ou estamper, et/ou perforer et/ou souder, pour entraîner éventuellement avec commutation intermédiaire de pièces d'engrenage comme des bielles, des engrenages à parallélogramme, des agencements à articulation de genouillère ou similaires, l'alimentation en fluide étant commandée pendant la course à vide (course de démarrage) du piston (4) de façon à ce que seuls les forces d'inertie et/ou le poids et/ou les forces de friction de pièces mobiles soient surmontés et que l'alimentation avec la pression fluidique ne s'effectue que lors de la course de puissance des pistons (4).
EP07724673A 2006-05-10 2007-04-27 Procede pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci Not-in-force EP2016290B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006022030 2006-05-10
DE102006041707A DE102006041707B4 (de) 2006-05-10 2006-09-06 Kolben-Zylinder-Einheit (Arbeitszylinder) zum Spannen, und/oder Pressen, und/oder Fügen, und/oder Stanzen, und/oder Prägen, und/oder Lochen und/oder Schweißen, zum Beispiel unter Zwischenschaltung einer Kniehebelgelenkanordnung
PCT/EP2007/003745 WO2007128437A1 (fr) 2006-05-10 2007-04-27 Procédé pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci

Publications (2)

Publication Number Publication Date
EP2016290A1 true EP2016290A1 (fr) 2009-01-21
EP2016290B1 EP2016290B1 (fr) 2012-08-15

Family

ID=38358019

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07724673A Not-in-force EP2016290B1 (fr) 2006-05-10 2007-04-27 Procede pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci

Country Status (7)

Country Link
US (1) US8100046B2 (fr)
EP (1) EP2016290B1 (fr)
JP (2) JP2009536296A (fr)
CN (1) CN101421521B (fr)
DE (1) DE102006041707B4 (fr)
ES (1) ES2391987T3 (fr)
WO (1) WO2007128437A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130809A1 (fr) 2015-08-13 2017-02-15 Pneumax S.p.A. Unité d'actionnement d'efficacité optimisée du type de levier articulé

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008007256B3 (de) * 2008-02-01 2009-08-20 Tünkers Maschinenbau Gmbh Arbeitszylinder, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie zum Antreiben von Vorrichtungen zum Spannen und/oder Fügen und/oder Stanzen und/oder Prägen und/oder Schweißen und/oder Lochen und/oder Clinchen
DE202009002141U1 (de) 2009-02-14 2009-04-23 Tünkers Maschinenbau Gmbh Vorrichtung mit einem über ein Stellglied und einer Kniehebelgelenkanordnung durch einen Antrieb in entgegengesetzten Richtungen antreibbaren Hebel, dem eine oder mehrere Massen zugeordnet ist bzw. sind, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
DE102009011441B4 (de) * 2009-02-25 2012-11-29 Voith Patent Gmbh Hydraulikantrieb
JP2011002041A (ja) * 2009-06-18 2011-01-06 Smc Corp 流体圧シリンダ
KR101289503B1 (ko) 2009-12-18 2013-07-24 턴커스 마시넨바우 게엠베하 자동차 차체 제조를 위해 듀얼 피스톤 기능이 구비되고 압축 공기 구동식 장치
DE102010024723B4 (de) 2010-06-23 2014-02-13 Samson Aktiengesellschaft Pneumatischer Stellantrieb und Verfahren zum Betreiben des pneumatischen Stellantriebs
WO2012045320A1 (fr) 2010-10-06 2012-04-12 Tünkers Maschinenbau Gmbh Unité piston-cylindre (cylindre de travail) économe en énergie, en particulier pour une utilisation dans la construction de carrosserie de l'industrie automobile
DE102011009302A1 (de) * 2011-01-24 2012-07-26 Helmut Steinhilber Fluidzylinder und Pressvorrichtung
CN102175444B (zh) * 2011-02-17 2012-08-29 中国航空工业集团公司西安飞机设计研究所 一种多油门杆加载测量装置
DE102011051400B3 (de) * 2011-06-28 2012-06-06 Parker Hannifin Gmbh Pneumatikzylinder mit selbstjustierender Endlagendämpfung
DE102012007170B3 (de) * 2012-04-07 2013-08-08 Festo Ag & Co. Kg Antriebsvorrichtung
DE102012213651B3 (de) * 2012-08-02 2013-08-01 Keiper Gmbh & Co. Kg Haltevorrichtung und Verfahren zum Betrieb einer Haltevorrichtung
DE102013215566A1 (de) * 2013-08-07 2015-02-12 Mahle International Gmbh Verfahren zur Bearbeitung einer Nockenwelle
KR101536636B1 (ko) * 2013-11-12 2015-07-15 주식회사알피엠텍 유공압 실린더의 스트로크 제한장치
JP2015174289A (ja) * 2014-03-14 2015-10-05 株式会社フロンティア 点字打刻装置
JP6288768B2 (ja) * 2014-04-04 2018-03-07 パスカルエンジニアリング株式会社 クランプ装置
DE102014014857B3 (de) * 2014-10-06 2015-11-12 Olaf Und André Tünkers Gbr (Vertretungsberechtigter Gesellschafter: Dipl.-Ing. Olaf Tünkers, 40885 Ratingen) Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
DE102015115180A1 (de) * 2015-09-09 2017-03-09 GDS Präzisionszerspanungs GmbH Spannvorrichtung, insbesondere hydraulische Spannvorrichtung
JP7297401B2 (ja) * 2017-03-07 2023-06-26 住友重機械工業株式会社 ショベル
US10982690B2 (en) * 2017-03-15 2021-04-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US10941790B2 (en) * 2017-03-15 2021-03-09 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
CN106864020B (zh) * 2017-04-06 2023-08-04 广东东纳数码印刷科技有限公司 安全高效烫金机
JP7025976B2 (ja) * 2018-03-30 2022-02-25 新明和工業株式会社 端子圧着装置および端子圧着方法
ES2919566T3 (es) 2019-07-23 2022-07-27 Beumer Group Gmbh & Co Kg Disposición con cilindro de vástago de pistón neumático o hidráulico
EP3770444B1 (fr) 2019-07-23 2022-08-31 BEUMER Group GmbH & Co. KG Ensemble avec un vérin pneumatique ou hydraulique
DE102019121433B4 (de) * 2019-08-08 2022-12-29 SMC Deutschland GmbH Fluidrückführvorrichtung für einen doppeltwirkenden Zylinder und Verfahren zum Betreiben eines solchen Zylinders
EP3792504B1 (fr) * 2019-09-12 2023-06-07 Ratier-Figeac SAS Régulation de la charge/pression en butée de fin de course d'un actionneur hydraulique
JP7395131B2 (ja) * 2020-04-14 2023-12-11 Smc株式会社 流体圧シリンダ

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE333903C (de) 1919-03-29 1921-03-05 Richter Hans Hydraulisches Presswerk
DE1941785U (de) * 1966-04-30 1966-07-07 Metall G M B H & Co In breite und neigung verstellbares drehgestell.
DE1941785A1 (de) 1969-08-16 1971-03-04 Metrawatt Ag Fabrik Elek Scher Pneumatischer oder hydraulisch angetriebener Arbeitshubzylinder
JPS51124594U (fr) * 1975-04-04 1976-10-08
JPS5838003U (ja) * 1981-09-08 1983-03-12 焼結金属工業株式会社 差動シリンダの駆動装置
DE3513680A1 (de) * 1985-04-16 1986-10-30 Josef Gerhard 4030 Ratingen Tünkers Kniehebelspannvorrichtung mit handzustellvorrichtung, insbesondere zur verwendung im karosseriebau
JPH0440014Y2 (fr) * 1986-08-19 1992-09-18
JPH01109603U (fr) * 1988-01-18 1989-07-25
JPH0842511A (ja) * 1994-08-02 1996-02-13 Konan Denki Kk 空気圧シリンダ装置
JPH08277811A (ja) * 1995-04-03 1996-10-22 Pabotsuto Giken:Kk エアーシリンダ
DE19512429A1 (de) 1995-04-03 1996-10-10 Montan Hydraulik Gmbh & Co Kg Differentialzylinder als Betätigungsorgan insbesondere für zangenartige Brechwerkzeuge
DE19616441C1 (de) * 1996-04-25 1997-06-26 Tuenkers Maschinenbau Gmbh Kniehebelspannvorrichtung für den Karosseriebau
DE29700887U1 (de) * 1997-01-20 1997-03-13 Tuenkers Maschinenbau Gmbh Vorrichtung zur Ausübung hoher Drücke beim Nieten, Ausklinken, Lochen, Fügen, Stanzen, Clinchen, Pressen, Biegen o.dgl.
DE19824579C1 (de) * 1998-06-02 1999-06-17 Tuenkers Maschinenbau Gmbh Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
DE19930990C1 (de) * 1999-07-05 2000-12-28 Tuenkers Maschinenbau Gmbh Kraftangetriebene Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
JP3672782B2 (ja) * 1999-12-08 2005-07-20 Ｓｍｃ株式会社 クランプ装置
DE10260138A1 (de) * 2002-12-20 2004-07-15 Rexroth Mecman Gmbh Programmierbarer Linearantrieb, insbesondere für eine Schweißzange sowie Verfahren zur Ansteuerung des Linearantriebs
DE102004027849A1 (de) 2004-06-08 2006-01-05 Bosch Rexroth Aktiengesellschaft Antriebseinheit
DE102004034280A1 (de) * 2004-07-15 2006-02-23 Schema-Hydraulik Gmbh Selbststeuer-Eilgangzylinder
DE102004063463C5 (de) * 2004-12-23 2013-10-31 Norgren Gmbh Verfahren zur Steuerung einer Ausgleichszylindereinheit insbesondere für eine Schweißvorrichtung und Ausgleichszylindereinheit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007128437A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130809A1 (fr) 2015-08-13 2017-02-15 Pneumax S.p.A. Unité d'actionnement d'efficacité optimisée du type de levier articulé

Also Published As

Publication number Publication date
ES2391987T3 (es) 2012-12-03
WO2007128437A1 (fr) 2007-11-15
CN101421521A (zh) 2009-04-29
EP2016290B1 (fr) 2012-08-15
JP2009536296A (ja) 2009-10-08
JP2012092981A (ja) 2012-05-17
US20090000468A1 (en) 2009-01-01
DE102006041707A1 (de) 2007-11-15
DE102006041707B4 (de) 2009-01-02
US8100046B2 (en) 2012-01-24
CN101421521B (zh) 2013-01-16

Similar Documents

Publication Publication Date Title
EP2016290A1 (fr) Procede pour alimenter un cylindre moteur, commande de ce dernier, cylindre moteur et utilisation de celui-ci
EP3378581B1 (fr) Dispositif d'assemblage en plusieurs étapes et procédé d'assemblage correspondant
EP2329153B1 (fr) Dispositif à entraînement par air comprimé, équipé d'une fonction double piston et destiné à être utilisé dans le domaine de la carrosserie pour l'industrie automobile
DE4042070C2 (de) Druckmittelbetriebener Kraftschrauber
EP1247599A1 (fr) Dispositif d' entraínement pour outil d' insertion
EP3416783B1 (fr) Dispositif et procédé de conversion d'une force mécanique pour l'entraînement d'un dispositif de compression de raccords à compression
DE202009008068U1 (de) Vorrichtung zum Spannen und/oder Fügen und/oder Stanzen und/oder Prägen und/oder Schweißen und/oder Lochen und/oder Clinchen und/oder Schwenken, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie sowie Steuerung für eine derartige Vorrichtung und die Verwendung einer solchen Vorrichtung, vornehmlich für den Karosseriebau der Kfz-Industrie
EP1055466B1 (fr) Système d'entraínement hydraulique pour une machine d'assemblage
DE10202374A1 (de) Zweiplatten-Schließsystem einer Spritzgießmaschine
EP2229537B1 (fr) Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression
DE19822439A1 (de) Vorrichtung zur Durchführung von Betätigungen in einer Druckmaschine
WO2010051913A1 (fr) Convertisseur de forces hydraulique
DE102008007256B3 (de) Arbeitszylinder, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie zum Antreiben von Vorrichtungen zum Spannen und/oder Fügen und/oder Stanzen und/oder Prägen und/oder Schweißen und/oder Lochen und/oder Clinchen
EP1984132B1 (fr) Pince d'usinage hydraulique
DE102014014857B3 (de) Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
DE2524017A1 (de) Hydraulischer druckzylinder und einrichtung zur druckerzeugung
DE10206600B4 (de) Mehrstufenhubzylinder
DE3537337C2 (fr)
DE2842174C2 (de) Sicherheitsschaltung für hydraulische Pressen
EP3731997B1 (fr) Outil hydraulique pour un dispositif de traction et/ou de pressage
DE2920236A1 (de) Schalteinrichtung
DE1627811B2 (de) Presse zum aufpressen von huelsen, kabelschuhen oder dergleichen
DE102005004769A1 (de) Hydraulische Bearbeitungszange
DD219720A1 (de) Werkstueckgreifer fuer handhabegeraete
DE10140191A1 (de) Schnellspannvorrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20080715

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17Q First examination report despatched

Effective date: 20101118

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

DAX Request for extension of the european patent (deleted)
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 570994

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120815

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502007010391

Country of ref document: DE

Effective date: 20121011

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2391987

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20121203

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121215

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121116

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121217

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20130516

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007010391

Country of ref document: DE

Effective date: 20130516

BERE Be: lapsed

Owner name: TUNKERS MASCHINENBAU G.M.B.H.

Effective date: 20130430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130430

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130430

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130427

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 570994

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130427

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130427

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130427

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20070427

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190313

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20190503

Year of fee payment: 13

Ref country code: DE

Payment date: 20190416

Year of fee payment: 13

Ref country code: IT

Payment date: 20190419

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20190424

Year of fee payment: 13

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007010391

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200430

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201103

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200427

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200427

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20210906

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200427

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200428