EP2934784B1 - Presse de formage - Google Patents

Presse de formage Download PDF

Info

Publication number
EP2934784B1
EP2934784B1 EP13818671.3A EP13818671A EP2934784B1 EP 2934784 B1 EP2934784 B1 EP 2934784B1 EP 13818671 A EP13818671 A EP 13818671A EP 2934784 B1 EP2934784 B1 EP 2934784B1
Authority
EP
European Patent Office
Prior art keywords
tool carrier
unit
pressure
hydraulic
forming press
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.)
Active
Application number
EP13818671.3A
Other languages
German (de)
English (en)
Other versions
EP2934784A1 (fr
Inventor
Vaclav Hejplik
Patrick STICKER
Carsten Baumgartner
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.)
Uniflex Hydraulik GmbH
Original Assignee
Uniflex Hydraulik 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 Uniflex Hydraulik GmbH filed Critical Uniflex Hydraulik GmbH
Publication of EP2934784A1 publication Critical patent/EP2934784A1/fr
Application granted granted Critical
Publication of EP2934784B1 publication Critical patent/EP2934784B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B30B1/323—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure using low pressure long stroke opening and closing means, and high pressure short stroke cylinder means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • B21D39/048—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods using presses for radially crimping tubular elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B7/00—Presses characterised by a particular arrangement of the pressing members
    • B30B7/04—Presses characterised by a particular arrangement of the pressing members wherein pressing is effected in different directions simultaneously or in turn

Definitions

  • the present invention relates to a fluidic forming press, in particular a radial press, with two tool carriers movable relative to one another along a working direction.
  • Such forming of workpieces serving presses are known in various designs. They differ, for example, with regard to their purpose (eg radial press) and the associated construction (eg yoke press) as well as the drive concept (eg hydraulically). Hydraulically driven yoke presses for radial deformation of workpieces are known, for example from the DE 199 12 976 A1 , of the DE 10 2009 057 726 A1 , of the DE 4135465 A1 and the US 4,854,031 A ,
  • the DE 10 2004 035 590 A1 discloses a - formed in particular as a deep-drawing press - forming press with a fixedly connected to the frame structure lower tool carrier and a movable up and down main plunger. This is after the Zustellhub with a fixed part of the press (especially the lower crosshead) lockable. In it, a plunger, which forms the upper tool carrier and performs the forming of the workpiece serving stroke, and a blank holder (including associated drive cylinder) was added.
  • the present invention is directed to provide a particularly efficient fluidic forming press in the sense of providing extremely high pressing forces, in particular a particularly powerful radial press for the radial forming of relatively large-dimensioned workpieces.
  • the at least one of the first tool carrier associated with the first drive unit is designed as Eilhub unit, by means of which the first tool carrier between a relative to the second tool carrier relatively remote home position and the second tool carrier relatively close closed position movable, ie to close the tool around the workpiece or to open.
  • the first tool carrier In its closed position, which relates to the second tool carrier, the first tool carrier can be locked mechanically relative to the frame structure by means of at least one positionally variable locking body.
  • At least one of the second tool carrier associated, fluidic piston-cylinder unit is at least for a part of the movement of the second tool carrier in the direction of the (locked) first tool carrier, namely for a subsequent to a pre-pressing actual pressing (see below), as high-pressure Unit executed, which is operable with a lying substantially above the working pressure of the associated pressure fluid assembly operating pressure.
  • a fluidic pressure booster is integrated for this purpose. This is to be understood as meaning a component within which the pressure prevailing in the working fluid is raised from a first level to an upper second level. This is ideally done without the supply of external energy, in particular by pressure ratio in the inverse ratio of the surfaces of a stepped piston on the low pressure and the high pressure side.
  • both the first and the second drive unit comprise hydraulic piston-cylinder units that run at least one pressure fluid unit as a hydraulic unit is, a hydraulic pressure booster is provided and the at least one first tool carrier associated with the first hydraulic piston-cylinder unit is designed as a maximum with the delivery pressure of the associated hydraulic unit operable low-pressure unit.
  • the hydraulic forming press comprises a frame structure, along a working direction relative to the frame structure movable first tool carrier, one along the working direction relative to the frame structure movable second tool carrier, acting on the first and second tool carrier hydraulic drive system and the hydraulic drive system controlling press control, wherein the hydraulic drive system to the individual tool carriers associated hydraulic piston-cylinder units, at least one of these beauf fileddes hydraulic unit and preferably controlling the admission comprising valves actuated by a press control.
  • the at least one of the first tool carrier associated first hydraulic piston-cylinder unit is designed as a maximum with the delivery pressure of the associated hydraulic unit operable low pressure unit, by means of which the first tool carrier (typically in "rapid") between a relative to the second tool carrier basic position and a second tool carrier relatively close closed position is movable. In its closed position, the first tool carrier mechanically lockable relative to the frame structure by means of at least one position-adjustable locking body.
  • the at least one second piston-cylinder unit associated with the second tool carrier is designed as a high-pressure unit at least for a part of the movement of the second tool carrier in the direction of the (locked) first tool carrier, which means that it is substantially above the delivery pressure the associated hydraulic unit operating pressure is operable.
  • the high-pressure unit with the associated hydraulic unit connecting feed line for this purpose (at least) integrated a hydraulic pressure booster.
  • both the first and the second tool carrier along the working direction are movable relative to the frame structure in the hydraulic forming press according to the invention, the receiving space for the workpiece to be formed relatively wide open.
  • This is an essential aspect, for example, for those applications in which a complex workpiece is to be placed in the receiving space for the workpiece between the two tool carriers (or between the partial tools used therein).
  • Also for laterally loaded radial presses is a correspondingly large stroke essential to provide between the two tool carriers a lateral insertion of the workpiece enabling clearance.
  • the hydraulic forming press according to the invention can provide far higher than previously realized pressing forces. This contributes significantly to the fact that the at least one of the second tool carrier associated with the second hydraulic piston-cylinder unit, by being assigned a arranged in the associated supply line hydraulic pressure booster is designed as a high pressure unit whose operating pressure substantially, typically by a multiple of the delivery pressure the associated hydraulic unit and the operating pressure of the at least one first tool carrier associated with the first hydraulic piston-cylinder unit.
  • the second tool carrier for force pressing via a hydraulic pressure booster needs the high hydraulic pressure, as he - in Interest of a particularly compact design of the forming press - small cross sections of the second piston-cylinder unit required for the required high pressing forces, not be provided by the hydraulic unit itself. Consequently, that hydraulic unit which serves to act on the at least one piston cylinder unit assigned to the first tool carrier can also be used for the high-pressure unit (in each case in phases via the pressure booster), so that as a result the forming press according to the invention can manage with a single hydraulic unit. This allows a comparatively simple design of the drive system even with, as stated, the highest performance data of the forming press according to the invention.
  • first drive unit is assigned to the first tool carrier
  • first drive unit necessarily acts between the first tool carrier and the frame structure.
  • first drive unit between the first and the second tool carrier acts particularly preferably, as explained in more detail below, so that the two tool carriers form a (as a whole replaceable) tool carrier unit connected to the first drive unit, to which preferably also a guide bracket counts, which ensures the leadership of the two tool carrier relative to each other along the working direction.
  • a preferred development of the forming press according to the invention is characterized in that the cylinder of the at least one high-pressure unit is designed in a frame component which forms part of the frame structure and engages via lateral profiles in corresponding profiles of two side plates also associated with the frame structure.
  • the cylinder of the at least one high-pressure unit is designed in a frame component which forms part of the frame structure and engages via lateral profiles in corresponding profiles of two side plates also associated with the frame structure.
  • that support surface can run more or less at right angles to the respective load surface; their function consists primarily in the reception or support of moments which are induced in the side plates by the introduction of forces on the load surfaces, possibly also in the side plates and the said frame member in such an engagement to hold each other that the Load surfaces of side plates and frame member safely and permanently force-bearing abut each other.
  • the mutually corresponding profiles of frame member and side plates are preferred, however, not necessarily as a positive profile (projection) on the frame member and negative profile (recess) executed on the side plates.
  • the respective profile can extend continuously over the entire depth (transversely to the working direction) in the sense of an optimal force flow characteristic.
  • the profiles adjacent to the load surfaces preferably follow at least a substantial part of an ellipse, which in turn is favorable with regard to the force flow characteristic.
  • the hydraulic pressure intensifier is also used is structurally integrated into the frame structure, that its cylinder is designed in the same frame member as the cylinder of the at least one high-pressure unit.
  • the entire high-pressure region is "encapsulated" in a single component, so that in particular the highest pressures exposed (exposed) line connections are avoided; and it requires in this case only shortest connection channels for the hydraulic fluid from the pressure booster to the at least one high pressure unit, which is also particularly advantageous because the forming press according to the invention - on the high pressure side - typically operates in a pressure range in which hydraulic oil is compressible.
  • a minimal pressure oil volume therefore has considerable advantages in terms of the hydraulic rigidity of the drive system. Also from the point of view of a particularly compact construction is advantageous if the hydraulic pressure booster is oriented with an axis perpendicular to the working direction of the forming press axis.
  • the aspects set forth above in connection with the positive connection between the side plates of the frame structure and that frame component, in which the cylinder of the at least one high-pressure unit is embodied apply correspondingly to the at least one locking body on which the first tool carrier is pressed during force pressing supported.
  • the at least one locking body engages positively in at least in its locking position via lateral profiles in corresponding profiles of two side plates associated with the frame structure.
  • the profilings of the at least one locking body and each of the two side plates rest against one another in each case on at least one load surface which is essentially perpendicular to the working direction.
  • An additional support of the at least one locking body in the area of a support surface (for example on the first tool carrier) which is substantially perpendicular to the load surface and is offset therefrom, counteracts moments induced by off-axis force application.
  • the mutually corresponding profiles of locking body (s) and side plates are preferably designed as a positive profile (projection) on the / the locking body (s) and negative profile (recess) on the side plates and in cross section adjacent to the load surfaces preferably follow at least a substantial part of an ellipse.
  • the at least one locking body is displaceable with a direction of movement perpendicular to the working direction. In this way, the pressing force exerted on the at least one locking body during force pressing via the workpiece and the first tool carrier does not result in a displacement component, so that the fixation of the locking body in its locking position can be realized with relatively little effort.
  • a guide bracket is provided for the first tool carrier.
  • Said guide bracket is preferably fixedly connected to the second tool carrier.
  • Yet another preferred embodiment of the invention is characterized in that in addition to that supply line through which the high-pressure unit communicates with the hydraulic pressure booster, a further feed line is provided, via which the high-pressure unit, bypassing the hydraulic booster from an associated hydraulic unit can be acted upon.
  • a further feed line is provided, via which the high-pressure unit, bypassing the hydraulic booster from an associated hydraulic unit can be acted upon.
  • the drive system particularly preferably has a pressure sensor connected to the press control on the supply side associated with the second tool carrier, wherein when the second tool carrier moves in the direction of the first tool carrier as a function of the pressure signal, switching over from the (direct) admission of the high-pressure Unit via the second feed line to the admission of the high pressure unit via the pressure booster takes place.
  • a filling valve with a high-pressure-resistant blocking function is particularly preferably connected to it.
  • the said high-pressure-resistant blocking function is particularly preferably realized via a poppet valve, wherein the closing body of the poppet valve can be hydraulically actuated by being in communication with an actuating piston, which in turn is part of a housed in the housing of the filling hydraulic piston-cylinder unit , By means of the latter, the closing body is advantageously both in the direction Closing and operable in the direction of opening the filling valve.
  • a high-pressure-resistant blocking function having filling valve has in yet another preferred development on a mounted on the frame structure of the forming valve housing, which are provided for fastening the valve housing preloaded expansion screws and the sealing of the valve housing relative to the frame structure in the region of a clearance compensation by means of a radial seal he follows.
  • the at least one high-pressure unit is designed to be single acting in the sense, as over them alone during the pre-pressing and force pressing expires movement of the second tool carrier in the direction of the first tool carrier (from the closed position to the pressing position ), but not the return from the press position to the closed position.
  • two high-pressure units are provided on the side of the second tool carrier, between which the low-pressure unit serving as the return is arranged.
  • the second tool carrier results in a high degree of tilt stability, so that the function impairing tilting can be avoided; Rather, an introduction of the pressing force into the second tool carrier takes place via an arrangement of two high-pressure units at a distance from one another in an optimum manner for the subsequent force curve within the second tool carrier. In this way, the stresses within the second tool carrier are minimized, so that it can be dimensioned relatively small.
  • the at least one first hydraulic piston-cylinder unit is particularly preferably carried out double-acting, so that with her equally the first tool holder - in the sense of Closing the forming press - can be moved to the second tool carrier, as well as - in the sense of opening the forming press - away from the second tool carrier.
  • embodiments of forming presses in particular of radial presses, in which the fluid pressure booster associated with the second drive unit is dispensed with-with an otherwise unchanged design-are dispensable. This is especially true when the aspect of compactness of the forming press in the specific application concerned has comparatively little importance, so that without serious detriment to the usability of the forming press for the application in question, the cross sections of the second drive unit can be increased.
  • the in the Fig. 1 to 12 It comprises a frame structure 2, which consists essentially of four main components, namely two side plates 3, a lower frame member 4 and an upper bracket 5.
  • the in the side plates 3 Holes 6 arranged around the press axis A extend as far as the one shown on the right in the drawing Edge 7 of the side plates 3 to allow lateral loading of the radial press; this explains the name of this radial press concept (cf. DE 19940744 A1 ) as "C-press".
  • two tool carriers added, namely an upper, first tool carrier 8 and a lower, second tool carrier 9.
  • Der Malawi Tool carrier 8 forms in the present press design an upper yoke 10, the second tool carrier a lower yoke 11.
  • the recorded in the upper yoke 10 and the lower yoke 11 tool comprises a total of eight pressing jaws 12, which on the upper yoke 10 and the lower yoke 11 in the known as such Way - partially sliding - support, with two of the pressing jaws are performed divided in a known manner.
  • the guide of the upper yoke 10 serves a recorded between the side plates 3 of the frame structure 2, with the lower yoke 11 firmly bonded guide bracket 13 to which the upper yoke 10 by means of a linear guide 14 is slidably guided up and down.
  • the upper yoke 10 associated components of the linear guide 14 are not rigidly connected to the upper yoke 10, but rather with the interposition of an elastomer body comprehensive Entkoppelungsaku. In this way affect operation - within certain limits - occurring deformations not the reliability of the press.
  • the lower frame member 4 and the two side plates 3 engage each other via substantially corresponding profiles 15 form-fitting manner into each other (see. Fig. 11 ).
  • the profiles 15 are designed so that the lower frame member 4 and each of the two side plates 3 not only abut on a substantially perpendicular to the working direction B load surface 16 in the direction of force to each other, but also at least one of them remote on the cooperating support surfaces 17 not only cause the engagement of side plates 3 and lower frame component 4 to be maintained;
  • the support surfaces 17 additionally each cause a support torque C, which counteracts a deformation of the side plates 3 during pressing.
  • the profiling 15 of the side plates 3, starting from the respective load surface 16 in the direction of the full wall thickness (ie in Fig. 11 upward) follows, avoiding all too large discontinuities of an ellipse E with adjoining transition slope S.
  • two locking body 18 is arranged, which on the upper bracket. 5 the frame structure 2 along linear guides 19 are guided transversely to the direction B displaced.
  • These two (mutually coupled) locking body 18 can be moved together by means of the hydraulic Verfahrzylinders 20, ie synchronously in a lying above the Oberjochs 10 locking position when the Oberjoch - by means of the associated first hydraulic piston-cylinder unit 21 - is lowered correspondingly far ( see below).
  • the upper yoke 10 is mechanically locked relative to the frame structure 2 by means of the two position-adjustable locking body 18 in the sense that the (during pressing) of the lower yoke 11 on the workpiece 1 on the upper yoke 10 exerted, essentially in the direction of working B upwards directed force is introduced via the two locking body 18 in the side plates 3.
  • the upper yoke 10 rests in the region of upper end faces 22 against corresponding contact surfaces 23 of the two locking bodies 18; and the two locking bodies 18 engage - at least in their locking position - via lateral profiles 24 in corresponding profiles 25 of the side plates 3.
  • the said profiling 24 or 25 of the locking body 18 and the respective associated side plate 3 are in each case at one on the working direction B substantially perpendicular load surface 26 to each other. Furthermore, the two side plates 3 are supported at the top by a support surface 27 perpendicular to the load surface 26 on the bracket 5; and the two locking bodies 18 Moreover, they are supported on the underside of supporting surfaces 28, which are provided on both sides on a web 29 arranged on the upper side of the upper yoke 10.
  • the radial press also has a hydraulic drive system which acts on the upper yoke 10 and the lower yoke 11.
  • This drive system comprises a first drive unit 75 in the form of an upper yoke 10, whose movement relative to the lower yoke 11 (and thus relative to the frame structure) causing, first hydraulic piston-cylinder unit 21, a second drive unit 76 in the form of three the lower yoke eleventh associated, the movement of which relative to the frame structure 2 causing the second hydraulic piston-cylinder units 30, a hydraulic piston-cylinder units 21, 30 acting on the hydraulic unit 31 and the said admission controlling valves.
  • the - controlled by the press control - valves are housed in two valve and Verteilblöcken 32 and 33.
  • the three second piston-cylinder units 30 are single-acting, with two Press units 34 and arranged between these restoring unit 35 are provided.
  • the cylinders 36 of the three second piston-cylinder units 30 are each made in the lower frame member 4; and the pistons 37 of the three second piston-cylinder units 30 are connected to a mounting plate 38 for the lower yoke 11.
  • the lower yoke 11 is braced against the mounting plate 38 in the sense that it is displaceable on the surface of the mounting plate 38 sideways, ie transversely to the working direction B.
  • the surface of the mounting plate 38 is designed as a roller conveyor 39.
  • the high-pressure side cylinder 40 of a hydraulic differential pressure booster 41 housed, ie in the present case executed directly in the lower frame member 4.
  • the low-pressure side piston 42 of the hydraulic Differential pressure booster 41 is sealingly guided in a cylinder housing 44 flanged to the lower frame component 4 by means of a screw flange 43.
  • a stiffening plate 45 is arranged, which rests with its peripheral edge on the inside of the threaded projection 46 of the cylinder housing 44.
  • the high-pressure side cylinder 40 of the hydraulic pressure booster 41 communicates via a connecting channel 47 directly with the cylinders 36 of the two press units 34, which are connected in parallel with one another via the channel 57 and which thus constitute high-pressure units 48.
  • the cylinders 36 of the two high-pressure units 48 communicate with a further feed line 49, via which the high-pressure units 48 - during the first part of the pressing process, the "pre-pressing" until the pressing jaws 12 abut against the workpiece 1 or encounter considerable resistance - bypassing the hydraulic pressure booster 41 can be acted upon by the hydraulic unit 31.
  • a filling valve 50 is connected in the second feed line 49, which has a high-pressure-resistant blocking function, which is realized by a present example, 3000 bar designed check valve 51.
  • the filling valve 50 actually represents a filling and shut-off valve.
  • the filling valve 50 is designed as a seat valve with a hydraulically actuated Closing member 52 which communicates with an actuating piston 53 in conjunction, which in turn is part of a housed in the housing 54 of the filling valve 50 hydraulic piston-cylinder unit 55.
  • the actuation of the closing body 52 of the filling valve 50 serving hydraulic piston-cylinder unit 55 is - applied via the valve and distribution block 32 accommodated pilot valves - via the pressure regulator 73 and the valve and Verteilblock 33 from the hydraulic unit 31.
  • the valve housing 54 of the filling valve 50 is attached by means of prestressed expansion screws 56 to the frame structure 2 of the forming press.
  • the sealing of the valve housing 54 relative to the frame structure 2 takes place (on both sides) in the region of the outer circumferential surface 58 of a sleeve-like projection 59 of an adapter 60 attached to the valve housing 54, on which a sealing ring 61 rests.
  • the hydraulic drive system is further designed and adapted to be used for a temperature control of the hydraulic fluid and / or the press.
  • the piston rod 62 of the hydraulic pressure booster 41 a longitudinal bore 63, which is the end face, that is limited in the region of the high-pressure side piston 64 by a presently designed to 3000 bar check valve 65.
  • the longitudinal bore 63 communicates via a connecting bore 66 with the piston rod working chamber 67 of the hydraulic pressure booster 41.
  • 41 check valves 68 are also provided in the low-pressure side piston 42 of the hydraulic pressure booster 41, which for a flow direction from the piston rod working chamber 67 of the hydraulic pressure booster 41st open to the piston working space 69.
  • Other Naturalströmungs- or hydraulic oil circulation concepts that serve the temperature of the press or the hydraulic oil are possible in a corresponding manner.
  • the first hydraulic piston-cylinder unit 21 is acted upon by the hydraulic unit 31 via the valve and distributor blocks 33 and 32 in the sense that the top yoke 10 downward toward the lower yoke 11 is moved, until the tool closes, that is, until the pressing jaw portions 71 of the split dies associated with the two part dies abut one another (cf. Fig. 2 ). In this position, the pressing jaw system is in the closed, prepared for the actual pressing process state.
  • the cylinders 36 of the two high-pressure units 48 are acted upon by the hydraulic unit 31 via the valve and distribution block 33 and the open filling valve 50 in such a way that the lower yoke 11 is raised, until the further pressed together pressing jaw system on the workpiece 1 ("pre-pressing") and which the first tool carrier 8 and the second tool holder 9 comprehensive tool carrier unit (including the tool received therein) is raised to the abutment of the upper yoke 10 on the two locking bodies 18 in the region of mutually corresponding surfaces.
  • the first piston-cylinder unit 21 is switched to its floating position in this phase.
  • One - connected to the press control - pressure sensor determines the thereby adjusting (erratic) pressure increase in the hydraulic drive system and triggers a switch from the application of the high pressure units 48 via the filling valve 50 and the other feed line 49 to the admission of high pressure units 48 via the hydraulic pressure booster 41.
  • the filling valve 50 is closed by appropriate action on the closing body 52 associated piston-cylinder unit 55 of the hydraulic unit 31 via the valve and distribution blocks 33 and 32.
  • a decompression phase to compress the hydraulic fluid compressed at the existing extreme pressure conditions (eg at 3,000 bar to about 80% of the initial volume) at least essentially to the pressure level of the incompressibility or even further (to relax more or less on the tank pressure).
  • This relaxation of the high-pressure side clamped hydraulic fluid is effected by a (via the relevant valves of the valve and distributor blocks 33 and 32) controlled movement of the piston unit of the hydraulic pressure booster 41st
  • Fig. 11 is to point out the schematic character.
  • the radial press is simplified in several ways.
  • the high-pressure unit 48 and the support of the lower yoke 11 are shown roughly simplified.
  • Fig. 14 illustrates the possibility of the entire unit consisting of the first tool carrier 8 and the upper yoke 10, the second tool carrier 9 and the lower yoke 11, fixed to the lower yoke guide bracket 13 and the - extending between the lower yoke 11 and the upper yoke 10 - first piston-cylinder unit 21 (including recorded between the two tool carriers pressing tool) to remove from the frame structure of the radial press, for example, to convert the presses from one pressing task to another.
  • the removal of the unit to be removed from the press and the positioning of the unit to be accommodated in the press is facilitated by the arrangement of the roller conveyor 39 on the mounting plate 38.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Press Drives And Press Lines (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)

Claims (19)

  1. Presse de formage fluidique, en particulier presse radiale, avec une structure de cadre, un premier porte-outil (8) déplaçable le long d'une direction de travail (B) par rapport à la structure de cadre, un deuxième porte-outil (9) déplaçable le long d'une direction de travail (B) par rapport à la structure de cadre, un système d'entraînement agissant sur les premier et deuxième porte-outils, lequel comprend une première unité d'entraînement (75) associée au premier porte-outil (8) et une deuxième unité d'entraînement (76) associée au deuxième porte-outil (9) avec au moins une unité fluidique de piston-cylindre (30), au moins un agrégat de fluide sous pression alimentant cette dernière et - de préférence - des soupapes commandant l'alimentation, et avec une commande de presse commandant le système d'entraînement, avec les caractéristiques suivantes :
    - l'au moins une unité d'entraînement (75) associée au premier porte-outil (8) est réalisée en tant qu'unité de course rapide au moyen de laquelle le premier porte-outil (8) est déplaçable entre une position de base relativement éloignée par rapport au deuxième porte-outil (9) et une position de fermeture relativement proche du deuxième porte-outil ;
    - dans sa position de fermeture, le premier porte-outil (8) étant verrouillable mécaniquement par rapport à la structure de cadre au moyen d'au moins un corps de verrouillage (18) à position variable ;
    - au moins une deuxième unité fluidique de piston-cylindre (30) associée au deuxième porte-outil (9) étant réalisée, au moins pour une partie du déplacement du deuxième porte-outil en direction vers le premier porte-outil (8), en tant qu'unité à haute pression (48) laquelle peut être exploitée avec une pression de service se situant sensiblement au-dessus de la pression de service de l'agrégat de fluide sous pression associé ;
    - un multiplicateur de pression fluidique étant intégré dans la conduite d'alimentation reliant l'unité à haute pression (48) et l'agrégat de fluide sous pression associé.
  2. Presse de formage selon la revendication 1, caractérisée en ce qu'elle comprend un système d'entraînement hydraulique, dans laquelle la première et la deuxième unité d'entraînement (75 ; 76) comprennent des unités hydrauliques de piston-cylindre (21 ; 30), en ce qu'au moins un agrégat de fluide sous pression est réalisé en tant qu'agrégat hydraulique (31), en guise de multiplicateur de pression fluidique, un multiplicateur de pression hydraulique (41) étant prévu, et l'au moins une première unité hydraulique de piston-cylindre (21) associée au premier porte-outil (8) étant réalisée en tant qu'unité de basse pression exploitable au maximum avec la pression de refoulement de l'agrégat hydraulique (31) associé.
  3. Presse de formage selon la revendication 2, caractérisée en ce qu'un cylindre (36) de l'au moins une unité à haute pression (48) est réalisé dans un élément de cadre (4) qui forme une partie de la structure de cadre et est en prise via des profilages latéraux (15) dans des profilages (15) correspondants de deux plaques latérales (3) faisant également partie de la structure de cadre, dans laquelle les profilages (15), correspondants entre eux, de l'élément de cadre (4) et des plaques latérales (3) sont de préférence réalisés en tant que profil positif (saillie) sur l'élément de cadre (4) et profil négatif (évidement) sur les plaques latérales (3).
  4. Presse de formage selon la revendication 3, caractérisée en ce que les profilages (15), au voisinage de surfaces de charge (16, 26) en coupe transversale, suivent une ellipse sur au moins une partie essentielle.
  5. Presse de formage selon l'une des revendications 3 ou 4, caractérisée en ce que les profilages (15) de l'élément de cadre (4) et de chacune des deux plaques latérales (3) reposent les uns contre les autres respectivement au niveau d'une surface de charge (16) sensiblement à la verticale de la direction de travail (B) et au niveau d'au moins une surface de support (17) décalée par rapport à la surface de charge.
  6. Presse de formage selon la revendication 4 ou la revendication 5, caractérisée en ce que le multiplicateur de pression hydraulique (41) est également intégré du point de vue constructif dans la structure de cadre de manière à ce que son cylindre (40) soit réalisé dans l'élément de cadre (4).
  7. Presse de formage selon l'une des revendications 2 à 6, caractérisée en ce que le multiplicateur de pression hydraulique (41) est orienté avec un axe perpendiculaire à l'axe de travail (B).
  8. Presse de formage selon l'une des revendications 2 à 7, caractérisée en ce que l'au moins un corps de verrouillage (18) est en prise, au moins dans sa position de verrouillage, via des profilages latéraux (24), dans des profilages (25) correspondants de la structure de cadre, dans laquelle les profilages (24 ; 25) de l'au moins un corps de verrouillage (18) et de la structure de cadre reposent l'un contre l'autre au niveau d'une surface de charge (26) sensiblement à la verticale de la direction de travail (B).
  9. Presse de formage selon l'une des revendications 2 à 8, caractérisée en ce que l'au moins un corps de verrouillage (18) est déplaçable avec une direction de déplacement à la verticale de la direction de travail (B).
  10. Presse de formage selon l'une des revendications 2 à 9, caractérisée en ce que deux corps de verrouillage (18) gardant une distance l'un par rapport à l'autre sont prévus.
  11. Presse de formage selon la revendication 10, caractérisée en ce que, dans l'espace intermédiaire entre les deux corps de verrouillage (18), on prévoit une console de guidage (13) pour le premier porte-outil (8), dans laquelle le premier porte-outil (8) est de préférence guidé au moyen d'un guidage linéaire (14) sur la console de guidage (13), dans laquelle les éléments constitutifs du guidage linéaire (14) associés au premier porte-outils (8) sont reliés au premier porte-outil en montant de façon intermédiaire une unité de découplage élastique.
  12. Presse de formage selon la revendication 11, caractérisée en ce que la console de guidage (13) est reliée de façon fixe au deuxième porte-outil (9) d'une manière telle, et l'au moins une première unité hydraulique de piston-cylindre (21) agissant entre le premier et le deuxième porte-outil (8, 9) d'une manière telle, que l'unité complète de porte-outils comprenant les deux porte-outils, la console de guidage et l'au moins une première unité hydraulique de piston-cylindre, peut être enlevée de la structure de cadre.
  13. Presse de formage selon l'une des revendications 2 à 12, caractérisée en ce que l'on prévoit une autre conduite d'alimentation (49) par l'intermédiaire de laquelle l'unité à haute pression (48), en contournant le multiplicateur de pression hydraulique (41), peut être alimentée par un agrégat hydraulique (31) associé, dans laquelle le système d'entraînement présente de préférence, sur le côté d'alimentation associé au deuxième porte-outil (9), un capteur de pression ou un pressostat relié à la commande de presse, dans laquelle, lors du déplacement du deuxième porte-outil (9) en direction vers le premier porte-outil (8), en fonction du signal de pression, il y a une commutation pour passer de l'alimentation de l'unité à haute pression (48) via la deuxième conduite d'alimentation (49) à l'alimentation de l'unité à haute pression via le multiplicateur de pression hydraulique (41).
  14. Presse de formage selon la revendication 13, caractérisée en ce qu'une soupape de remplissage (50) avec une fonction de verrouillage résistant à la haute pression est montée dans la deuxième conduite d'alimentation (49), dans laquelle la soupape de remplissage (50) est de préférence réalisée en tant que robinet à soupape avec un corps de fermeture (52) actionnable hydrauliquement, lequel est en liaison avec un piston d'actionnement (53) lequel fait, quant à lui, partie d'une unité hydraulique de piston-cylindre (55) logée dans un boîtier de soupape (54) de la soupape de remplissage (50).
  15. Presse de formage selon la revendication 14, aractérisée en ce que la soupape de remplissage (50) présente un boîtier de soupape (54) aménagé sur la structure de cadre de la presse de formage, dans laquelle on prévoit des vis d'expansion (56) précontraintes pour la fixation du boîtier de soupape, et l'étanchéification du boîtier de soupape par rapport à la structure de cadre s'effectuant dans la plage d'une compensation de jeu au moyen d'un joint radial (61).
  16. Presse de formage selon l'une des revendications 2 à 15, caractérisée en ce que l'au moins une unité à haute pression (48) est réalisée à effet simple et en ce que l'on associe au deuxième porte-outil (9), pour son éloignement du premier porte-outil (8), une unité de repositionnement (35) sous la forme d'une autre unité hydraulique de piston-cylindre (30) réalisée en tant qu'unité de basse pression, dans laquelle on prévoit de préférence deux unités à haute pression (48) entre lesquelles l'unité de basse pression est disposée.
  17. Presse de formage selon l'une des revendications 2 à 16, caractérisée en ce que l'au moins une première unité hydraulique de piston-cylindre (21) est réalisée à effet double.
  18. Presse de formage selon l'une des revendications 2 à 17, caractérisée en ce que l'ensemble des unités hydrauliques de piston-cylindre (21 ; 30) peut être alimenté à partir d'exactement un agrégat hydraulique (31).
  19. Presse de formage selon l'une des revendications 2 à 18, caractérisée en ce qu'elle se présente en tant que presse radiale pouvant être chargée latéralement, en ce que l'espace de réception (70) pour la pièce à usiner (1) disposé entre les porte-outils (8 ; 9) est accessible via une ouverture latérale.
EP13818671.3A 2012-12-21 2013-12-20 Presse de formage Active EP2934784B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012025134.3A DE102012025134A1 (de) 2012-12-21 2012-12-21 Umformpresse
PCT/EP2013/003887 WO2014095078A1 (fr) 2012-12-21 2013-12-20 Presse de formage

Publications (2)

Publication Number Publication Date
EP2934784A1 EP2934784A1 (fr) 2015-10-28
EP2934784B1 true EP2934784B1 (fr) 2016-11-30

Family

ID=49943309

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13818671.3A Active EP2934784B1 (fr) 2012-12-21 2013-12-20 Presse de formage

Country Status (5)

Country Link
US (1) US9314984B2 (fr)
EP (1) EP2934784B1 (fr)
CN (1) CN104884184B (fr)
DE (1) DE102012025134A1 (fr)
WO (1) WO2014095078A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015002556B3 (de) * 2015-03-02 2016-05-12 Uniflex-Hydraulik Gmbh Radialpresse
BR112021017887A2 (pt) * 2019-03-29 2021-12-07 Uniflex Hydraulik Gmbh Processo para produção de uma pluralidade de estruturas compostas
DE102020121143B4 (de) * 2020-08-11 2022-03-10 Uniflex - Hydraulik GmbH Radialpresse
CN113119014B (zh) * 2021-04-19 2022-05-31 河北白沙烟草有限责任公司 一种气管快插结构的专用插拔工具
EP4144456A1 (fr) 2021-09-02 2023-03-08 Uniflex-Hydraulik GmbH Procédé de fabrication d'une conduite hydraulique à haute pression

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3451249A (en) * 1966-10-10 1969-06-24 Wilfred J Sharon Forming machine
US4854031A (en) * 1989-02-09 1989-08-08 The Goodyear Tire & Rubber Company Hose crimper and method of using same
DE4135465A1 (de) 1991-10-28 1993-04-29 Schroeck Peter Dipl Ing Fh Radialpresse mit zwei radial gegeneinander beweglichen pressenjochen
DE4412224A1 (de) * 1994-04-09 1995-10-12 Graebener Pressensysteme Gmbh Presse für eine Kaltverformung von Metallwerkstücken
DE19642635A1 (de) * 1996-03-28 1997-10-02 Horst Baltschun Feinschneidpresse mit hydraulisch gekoppeltem Ringzacken- und Gegenhalterzylinder
US6519998B2 (en) * 1998-04-22 2003-02-18 Uniflex-Hydraulik Gmbh Radial press
DE19912976C2 (de) 1999-03-23 2001-12-13 Uniflex Hydraulik Gmbh Radialpresse
DE19940744B4 (de) 1999-08-27 2008-11-06 Uniflex-Hydraulik Gmbh Radialpresse
DE10339291B3 (de) * 2003-08-27 2004-12-16 Schröck-Horn, Ursula Radialpresse zum Verpressen von rotationssymmetrischen Hohlkörpern
DE102004006126B4 (de) * 2004-02-07 2006-12-28 Horst Baltschun Presse mit verriegeltem Stößel
DE102004035590A1 (de) * 2004-02-07 2006-03-16 Horst Baltschun Presse mit verriegeltem Stößel
WO2006120765A1 (fr) * 2005-05-09 2006-11-16 Falcom Inc. Dispositif de pressurisation
DE102005034260B3 (de) * 2005-07-22 2006-07-27 Schröck-Horn, Ursula Radialpresse zum Verpressen von rotationssymmetrischen Hohlkörpern
DE102009017624B4 (de) * 2009-04-16 2012-02-16 Horst Baltschun Tiefziehpresse
DE102009052531A1 (de) * 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102009057726A1 (de) 2009-12-10 2011-06-16 Uniflex-Hydraulik Gmbh Radialpresse

Also Published As

Publication number Publication date
EP2934784A1 (fr) 2015-10-28
CN104884184A (zh) 2015-09-02
US9314984B2 (en) 2016-04-19
WO2014095078A1 (fr) 2014-06-26
CN104884184B (zh) 2017-06-09
US20150283775A1 (en) 2015-10-08
DE102012025134A1 (de) 2014-06-26

Similar Documents

Publication Publication Date Title
EP2934784B1 (fr) Presse de formage
EP2280178B1 (fr) Dispositif et méthode de contôle pour un ensemble piston-cylindre
EP2867009B1 (fr) Presse
EP2509725B1 (fr) Presse radiale
WO2011035828A1 (fr) Entraînement hydraulique précontraint doté d'une pompe à vitesse variable
DE102005037377A1 (de) Hydraulische Presse
EP0696960B1 (fr) Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse
AT502339B1 (de) Antriebsvorrichtung
DE19928422A1 (de) Presse zum Außenhochdruckformen
DE102009005998A1 (de) Hydraulische Antriebsvorrichtung mit zwei Druckräumen und Verfahren zum Betreiben einer hydraulischen Antriebsvorrichtung mit zwei Druckräumen
DE10005023A1 (de) Presse
DE102004035590A1 (de) Presse mit verriegeltem Stößel
WO2015024902A1 (fr) Vérin hydraulique d'actionnement d'un frein électromagnétique sur rails
DE102004006126A1 (de) Presse mit verriegeltem Stößel
DE102010012126A1 (de) Presse mit vorgespanntem Rahmen
DE102006057051A1 (de) Umformpresse mit im Schiebetisch integrierter Ziehkissenfunktionalität
EP1243353B1 (fr) Dispositif de fermeture pour des outils ouverts par des forces d'ouverture
DE10215003A1 (de) Hydraulische Presse
DE10041397C2 (de) Stößelverstellung an Pressen
EP1344585B1 (fr) Dispositif d'emboutissage profond hydroélastique
DE102010006602B4 (de) Werkstück-Spanneinrichtung
EP0406792A1 (fr) Couplage de réglage pour la course supérieure pour la jumelle de pression d'un dispositif d'emboutissage
EP3338909B1 (fr) Dispositif d'estampage
DE19729384C2 (de) Presse zum Hydro-Umformen
DE102004011253B3 (de) Innenhochdruckumformanlage

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: 20150707

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HEJPLIK, VACLAV

Inventor name: BAUMGARTNER, CARSTEN

Inventor name: STICKER, PATRICK

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20160617

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 849317

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161215

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: 502013005622

Country of ref document: DE

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

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: 20161130

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20161130

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: 20161130

Ref country code: NO

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: 20170228

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: 20170301

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: 20161130

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

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: 20161130

Ref country code: RS

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: 20161130

Ref country code: BE

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

Effective date: 20161231

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: 20161130

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: 20170330

Ref country code: ES

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: 20161130

Ref country code: HR

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: 20161130

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: 20161130

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

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: 20161130

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: 20161130

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: 20161130

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: 20161130

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: 20161130

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20170228

Ref country code: IT

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: 20161130

Ref country code: SM

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: 20161130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013005622

Country of ref document: DE

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: 20161130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

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: 20161231

Ref country code: LU

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

Effective date: 20161220

Ref country code: LI

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

Effective date: 20161231

26N No opposition filed

Effective date: 20170831

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20171025

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

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: 20161130

Ref country code: IE

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

Effective date: 20161220

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: 20170130

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20161231

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

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: 20131220

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

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: 20161130

Ref country code: MK

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: 20161130

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: 20161130

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

Effective date: 20171220

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: 20161130

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: 20161130

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: 20171220

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 849317

Country of ref document: AT

Kind code of ref document: T

Effective date: 20181220

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: 20181220

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

Ref country code: AL

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: 20161130

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230529

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

Ref country code: DE

Payment date: 20240226

Year of fee payment: 11