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EP2629901B1 - Presse d'emboutissage à maintien dynamique optimisé de la tôle et methode d'emboutissage - Google Patents

Presse d'emboutissage à maintien dynamique optimisé de la tôle et methode d'emboutissage Download PDF

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Publication number
EP2629901B1
EP2629901B1 EP11770114.4A EP11770114A EP2629901B1 EP 2629901 B1 EP2629901 B1 EP 2629901B1 EP 11770114 A EP11770114 A EP 11770114A EP 2629901 B1 EP2629901 B1 EP 2629901B1
Authority
EP
European Patent Office
Prior art keywords
ram
drive
press
gear
servomotor
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.)
Not-in-force
Application number
EP11770114.4A
Other languages
German (de)
English (en)
Other versions
EP2629901A1 (fr
Inventor
Dietmar Schöllhammer
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.)
L Schuler GmbH
Original Assignee
L Schuler GmbH
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Filing date
Publication date
Application filed by L Schuler GmbH filed Critical L Schuler GmbH
Publication of EP2629901A1 publication Critical patent/EP2629901A1/fr
Application granted granted Critical
Publication of EP2629901B1 publication Critical patent/EP2629901B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/20—Deep-drawing
    • 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
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/20—Deep-drawing
    • B21D22/22—Deep-drawing with devices for holding the edge of the blanks
    • 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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • B21D24/12—Devices controlling or operating blank holders independently, or in conjunction with dies mechanically
    • 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
    • B30B1/10—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 toggle mechanism
    • B30B1/14—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 toggle mechanism operated by cams, eccentrics, or cranks
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/261—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 cams, eccentrics, or cranks by cams
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/28—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 cams, eccentrics, or cranks the cam, crank, or eccentric being disposed below the lower platen or table and operating to pull down the upper platen or slide
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses
    • B30B15/148—Electrical control arrangements
    • 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
    • B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
    • B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes

Definitions

  • the invention relates to a drawing press and a method for Tiefzichen, which is particularly suitable for integration in press lines, press lines, hybrid presses or transfer presses for the production of body parts.
  • the drawing press according to the invention is particularly suitable for high stroke rates.
  • the first press stage is usually a drawing press, which gives a previously flat board a spatial form. This is done in a drawing tool that clamps the edge of the board, and also allows controlled to slide towards the center of the sheet, while the enclosed by the blank holder part of the sheet between a die and a stamp receives the desired spatial shape.
  • the plunger takes the reversal point U t in at least two temporally spaced points in time TA, TB in a single press stroke, running servo motor and closed die tool.
  • closed tool is understood to mean that state in which the die tool is in contact with the workpiece, for example a sheet metal part.
  • the plunger drive has the task of closing movement and the generation of the plate holding force. Instead of braking to the reversal point U t , the braking of the servomotor is initiated late, such that an overflow takes place.
  • the area of the overflow is preferably of the order of magnitude which results, for example, in an eight-membered press drive with a blank holder.
  • the forming process in which the stamping tool deforms the board held at the edge, can be started upon reaching the reversal point U t , ie, clearly before reaching the holding position of the plunger.
  • the table drive associated with the plunger tool can be started.
  • the servomotor accelerates the sheet metal holding drive, So the ram, in the reverse direction of rotation such that the second reaching the reversal point coincides with still closed die tool at least approximately to the time of reaching the movement end point of the table drive.
  • the movement end point of the table drive may be an extended position of its coupling elements, if it is designed as a toggle mechanism or as an eccentric or other coupling mechanism.
  • the tappet with the die tool that is to say the sheet metal holding drive
  • the tappet with the die tool already has an initial rotational speed at the second reaching of the reversal point, which accelerates the lifting of the die tool from the sheet metal part.
  • the open time of the tool is increased overall, so that the press in turn can work faster overall.
  • the servomotor of the ram drive stops exactly at the reversal point U t , can be achieved by significantly more than 10% increased stroke rates.
  • the table drive is designed as a coupling transmission, whose elements are in an extended position upon reaching the upper end position.
  • structurally simple eccentric drives can be used both in the ram drive and in the table drive.
  • the ram drive already extending to only 200 ° degree of the circumference of the drive wheel of the eccentric teeth sufficient.
  • a toothing extends, which extends by 120 ° degrees to the drive of the eccentric. 360 ° all-round gears are superfluous. This leads to significantly less expensive designs of the drives.
  • the concept presented allows the provision of a sheet metal holder, which may be supported for example on a stationary abutment.
  • This blank holder rests relative to the punch tool which is moved into the die tool by the movement of the table during the drawing operation.
  • the purpose of the table drive Due to the stationary during the drawing operation positioning of the sheet holder, no, or at least almost no energy is required to apply the sheet holding force.
  • the plunger carrying the die tool is held by the plunger drive substantially in the vicinity of the reversal point U t . While this is done with cam gears ideal and without reversal of motion of the corresponding servo motor, this is achieved when using a linkage with extended position with expiring and reversing servomotor by the almost maintained stretched position of the coupling elements.
  • the occurring movements of the plunger in the direction of movement are small and can be compensated for example by the elastic springing of the press frame.
  • the plunger drive preferably has a blocking position, in which acts on the plunger Forces are at least largely, if not completely bypassed the actual drive source, such as a servomotor, are introduced into the press frame. It can find eccentric, toggle, cam or similar gear application.
  • the extended position is the position in which the lever arm of the eccentric (connecting line between the center of rotation of the eccentric and the center of the eccentric) is aligned with the connected connecting rod.
  • the table drive provides the punch stroke, which is required for shaping the sheet metal part, preferably while the ram drive is in blocking position or other rest position.
  • the die tool rests during the drawing process, in particular, it applies the sheet holding force against the likewise stationary sheet holder.
  • the sheet-holding force is thus preferably initiated statically in the press frame both on the part of the plunger and the die carried by him, as well as on the part of the sheet holder and does not have to be applied by drives. This considerably reduces the power required to drive the ram as well as to drive the table. The power required to move the plunger is low.
  • the ram drive need only be uniquely constructed prior to the start of a pull stroke, after placing the die tool on the board. It is then held statically by the press frame.
  • the sheet holding force can also be applied by a short-stroke plate holder drive.
  • the plate holder drive may also have a blocking position.
  • it can be used as a short-stroke eccentric drive or be designed as a cam drive, which biases the blank holder against the edge of the die tool and introduces the clamping forces directly into the press frame.
  • a blocking position is reached here when the eccentric drive is in an extended position or a cam drive is on a cam portion of maximum radius.
  • a movement of the driving servomotor has no or only a negligible minimum sheet holder movement result.
  • the proposed press concept minimizes the power to be applied to the ram drive and the table drive and the power exchange between these drives.
  • the press comes, compared to presses where an intense exchange of energy between ram drive and die cushion takes place, with the same power with smaller drives.
  • the otherwise required total stroke of, for example, 1300 mm in two strokes namely the stroke of the plunger and the stroke of the table, divided.
  • the stroke of the ram mainly serves to open and close the tool
  • the stroke of the table is used to move the punch and thus to carry out the actual drawing process.
  • the ram stroke may e.g. only 100 mm and the table lift, e.g. only 300 or 400 mm.
  • the plunger drive can turn out smaller than a conventional drive.
  • the linearly movable table can have a group of passages through which supporting elements extend. These support elements, for example in the form of straight pressure pins, extend through these passages and support the blank holder on an abutment.
  • the abutment is preferably arranged stationary with respect to the press frame. This means that the position of the sheet holder with respect to the press frame is fixed or optionally fixed by an adjustment.
  • the blanking force is determined by the springing of the press frame.
  • This springing can be in the range of a few millimeters to a few 10 mm.
  • the elastically stored in the press frame energy can be transferred back on the return stroke of the plunger on the ram drive, which further reduces the gross energy consumption of the drawing press.
  • abutment hydraulic or mechanical nature of the abutment It is, as mentioned, also possible to associate an abutment hydraulic or mechanical nature of the abutment.
  • a short-stroke toggle mechanism or an eccentric or the like The adjustment stroke will typically be at most a few 10 mm.
  • This concept is particularly advantageous when the plunger drive between the two times in which it has its reversal position U t , performs a certain movement, or if he can drive with little force in its blocking position and lock there, as it is in a Cam mechanism may be the case.
  • the blank holder force can be applied after blocking the plunger of the short-stroke plate holder drive.
  • the Verstellhub the sheet holder drive is then preferably at least as large as the total occurring springing of the press frame.
  • both the ram drive and the table drive are preferably servomotor drives.
  • the servomotors work on the plunger or the table preferably via gears that have at least one rest position.
  • a rest position is a position in which the reduction between servo motor and plunger or table in at least one point is very large or even infinite. This applies to eccentric gear as well as toggle mechanism in the extended position of the elements involved. Multi-unit transmissions with multiple stretched positions can be used to advantage.
  • FIG. 1 a drawing press 10 is illustrated, which can be used for the production of large sheet metal parts, such as body parts.
  • the drawing press 10 includes a press frame, the at least one, preferably a plurality, preferably vertically oriented stand 11, 12, a head 13, which is supported by the uprights 11, 12 and a pedestal 14 belonging under or between the uprights 11 , 12 is arranged.
  • the head 13, the stand 11, 12 and the base 14 form a closed frame.
  • a plunger 15 is mounted linearly movable in a vertical movement direction 16, for example.
  • linear guides 17 provided on the uprights 11, 12 are used.
  • the plunger 15 serves to receive an upper tool part, which is designed as a die tool 18. It is in FIG. 1 shown in section and has a rim 19, which serves for clamping and holding the edge of a workpiece during the drawing process.
  • the workpiece is formed by a board 20, ie an initially flat sheet.
  • the rim 19 surrounds a tool cavity 21 into which the workpiece is to be deformed.
  • a ram drive 22 which comprises one or more servo motors 23, 24 which are connected via one or more gear 25, 26 with the plunger 15.
  • the two gear 25, 26 are coupling gear suitable design.
  • each example is an eccentric gear designed mirror-symmetrically with respect to one another. They each comprise an eccentric 27, 28, which is coupled via a connecting rod 29, 30 with the plunger 15.
  • the drawing press 10 has a press table 31, on which a travel table 32 can be arranged.
  • a travel table 32 is used in a known manner the tool change.
  • the drive table 32 carries the lower tool part, to which a tool support 33, with a punch tool 34 arranged thereon and a blank holder 35 belong.
  • the punch tool 34 is a male whose upper contour corresponds to the cavity 31. It is surrounded by the rectangular-shaped sheet holder 35 in most cases, wherein the sheet holder 35 and the punch tool 34 are movable relative to each other with respect to the movement direction 16.
  • the unit consisting of the punch tool 34, the tool support 33, the drive table 32 and the press table 31 rests on a table drive 36 which is movable in the direction of movement 16 (see corresponding arrow) in the direction of the plunger 15 and away from it.
  • the press table 31, or its table drive 36 is linearly movable in the press frame on the uprights 11, 12 and / or the base 14 by means of guide means 37 in the direction of movement.
  • the gear 38, 39 each comprise an eccentric 42, 43, which is connected via a connecting rod 44, 45 with the press table 31.
  • the blank holder 35 is supported on suitable abutment elements, for example in the form of pressure pins 46, on an abutment 47.
  • the abutment 47 may be arranged stationary in the simplest case with respect to the base 14. Alternatively, it may be associated with an adjustment device 48 which can adjust the position of the abutment 47 with respect to the direction of movement 16, for example. this happens usually in no-load condition.
  • the adjustment 48 may also be designed so that it can adjust the abutment 47 under load, for example, to specifically influence or regulate the force acting on the blank holder 35 and thus on the drawing edge of the workpiece force.
  • the adjusting apparatus 48 may be in the form of hydraulic cylinders, toggle adjusters, Hubspindelverstellapparaten or the like. Between the abutment 47 and the table drive 36 16 oriented linear guides 49 may be provided in the direction of movement.
  • the drawing press 10 in the in FIG. 2 illustrated position transferred.
  • the servo motors 23, 24 not shown here have the eccentric 27, 28 turned so far that the plunger 15 has reached its lower reversal point U t for the first time.
  • the edge 19 of the Matrizentechnikzeugs 18 on the edge of the board 20 and begins this against the Sheet holder 35 to press.
  • the blank holder 35 rests unrelentably on the abutment 47 via the support elements 46, so that now the press frame is tensioned in the direction of movement 16. Its spring constant determined in conjunction with the set position of the sheet holder 35, the force acting on the edge of the board 20 clamping force very precise.
  • the servomotors 23, 24 are completely or at least almost free of load.
  • the sheet-holding force is supported on the head 13 via the Pleuelexzenteran Aunt located in the extended position of the transmission 25 and 26. No energy is consumed to maintain the holding force acting on the edge of the board 20. There is also no energy exchange between ram drive and any die cushion instead.
  • the servo motors 23, 24 begin to brake when approaching the reversal point U t , pass through the reversal point U t and then stop, as shown in the diagram FIG. 7 , there curve I emerges.
  • the plunger 15 thus performs after passing through the time TA a barely noticeable movement away from the reversal point U t .
  • the servomotors 23, 24 then stop at time TC and immediately or shortly thereafter reverse their direction of rotation to again pass through the reversal point U t . This happens at the time TB.
  • the gears 38, 39 reach their extended positions at this exact time, marking the completion of the drawing operation.
  • the opening movement of the die tool 18 starts by moving away from the turnaround point U t in the case of already rotating, ie, in the time interval from TC to TB, pre-accelerated servomotors 23, 24.
  • the opening of the tool is done very quickly, faster in any case, than it the case would be, the servomotors would still stand still at time TB.
  • the braking of the servomotors when approaching the plunger position to the reversal point U t can be done relatively late, so that despite possibly full braking power at TA still no engine stall is reached, but only at TC.
  • the actual drawing process is initiated via TC to TB, the end of which in FIG. 3 is illustrated.
  • the servomotors 40, 41 are activated, so that the eccentrics 42, 43 with the connecting rods 44, 45 go into an extended position, and thus reach the top dead center of the table drive 36.
  • the punch tool 34 is fully retracted into the die tool 18.
  • the reduction between the servomotors 41, 42 and the press table 31 approaches infinity, so that the punch tool 34 can apply very high pressures to the workpiece.
  • the tool consisting of the die tool 18 and the punch tool 34 is opened again as described above, by moving the plunger 15 upwards and the press table 31 downwards while the sheet holder 35 continues to rest.
  • the drawing press 10 so far described offers a concept which is suitable for the further use of drawing tools which have hitherto been used in presses with drawing cushions arranged at the bottom.
  • the press table 31 has a group 50 of openings 51, 52, 53, through which the support elements 46 can optionally be inserted therethrough.
  • tools of different sizes can be used, whose blank holder 35 span different distances. This results in a geometrically variable introduction of force for the sheet holder 35. This also provides increased freedom or comfort in tool design.
  • the presented operating concept with at least two passes of the reversal point U t during a press cycle shortens the cycle time and increases the stroke rate and output.
  • the plunger 15 can be moved by the gear 25, 26 pulling when the servomotors 23, 24 are arranged on the base 14.
  • the drive of the press table 31 in this and in all other embodiments by a single servo motor 40 can be effected when the gears of the eccentric 42, 43 mesh with each other or when the eccentric 42, 43 are connected in any other way by suitable transmission means.
  • the eccentric 42, 43 may optionally be formed as a full circle. This measure can also be found in the eccentrics 27, 28 and their gears application.
  • FIG. 5 a drive device which can be used either as a ram drive 22 as well as a table drive 36 application. Also, this drive has a rest position when its links 52, 53 are in an extended position. In this extended position causes a rotation of the driving servo motor 23, 24 (or corresponding to 40, 41) no or only an extremely low linear adjustment of the connected member, such as the plunger 15. These forces acting on straight paths by the handlebars 52, 53 at the machine frame supported without the Load servo motors.
  • FIG. 6 schematically shows a transmission 22, which is designed as a cam gear 54. It has a driven by the servo motor 23 cam 55 and a cam follower 56, for example in the form of a roller, which follows the curve circumference and thus performs a predetermined by the different radii of the cam linear, reciprocating motion.
  • the cam follower 56 is guided in a linear guide 57 and connected to the plunger 15.
  • the cam gear can the movement curve II of FIG. 7 provide.
  • the cam 55 has at its one portion 58 of constant radius. This determines the reversal point U t .
  • the servomotor 23 can be operated not only reversing, but alternatively also continuously.
  • the plunger 15 then moves to the reversal point U t , takes this during the time TA, the time TB and possibly other times eg between TA and TB.
  • the plate holding force does not have to be applied by the rotating servomotor in this phase, because forces acting on the plunger 15 produce no torque because of the radius of the cam which is constant in this section 58.
  • the servomotor 23 can be operated at a constant speed, at a varying speed, with a constant direction of rotation or with alternating directions of rotation.
  • these acceleration phases can be moved into the period of the drawing process.
  • at least in the embodiment of FIG 6 are partly or completely dispensed with acceleration and braking operations.
  • the drawing press (10) has for driving its plunger (15) a direction-reversing gear (22, 54), for example a coupling gear, and at least one servo motor (23).
  • the servo motor (23) passes through that of the reversal point U t of the plunger movement is determined by the kinematics of the linkage, for example, the extended position of an eccentric drive.
  • the servo motor (23) is driven in such a way that it first passes through this reversal point U t , then stops, reverses and then again passes through again to open the tool (18) ,
  • the still braking and re-accelerating the servomotor for the upper plunger (15) still or even during the actual drawing operation, ie during the sheet metal forming takes place, which significantly shortens the cycle time.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)

Claims (12)

  1. Presse d'emboutissage (10)
    comprenant un bâti de presse,
    comprenant un coulisseau (15) qui est prévu pour la réception d'un outil de matrice (18) et est monté de façon déplaçable dans une direction de déplacement (16),
    comprenant au moins un moyen d'entraînement de coulisseau (22) qui présente au moins un servomoteur (23) qui est relié au coulisseau par l'intermédiaire d'un mécanisme à manivelle ou d'un mécanisme à came (54) qui présente au moins un point d'inversion (Ut),
    sachant qu'en vis-à-vis du coulisseau (15), il est prévu un serre-flan (35) qui est en appui sur un élément de contre-appui (47), et
    sachant qu'il est prévu une table (31) qui est destinée à recevoir un outil porte-poinçon (34) et à laquelle est associé un moyen d'entraînement de table (36) afin de la déplacer dans la direction de déplacement (16), sachant que le moyen d'entraînement de table (36) associé à l'outil porte-poinçon est démarré lorsque le point d'inversion Ut du coulisseau (15) et de l'outil de matrice (18) est atteint pour la première fois, caractérisé en ce qu'elle comporte une commande qui est conçue pour activer le servomoteur (23), au nombre d'au moins un, de telle manière que le coulisseau (15), avec une course de presse unique, avec le servomoteur (23) en marche et l'outil de matrice (18) fermé, occupe le point d'inversion (Ut) à au moins deux instants (TA, TB) espacés dans le temps, et le servomoteur (23) effectue une inversion de sens de rotation entre les instants (TA, TB).
  2. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le mécanisme à manivelle est un mécanisme à excentrique.
  3. Presse d'emboutissage selon la revendication 1, caractérisée en ce que l'élément de contre-appui (47) est disposé de manière fixe sur le bâti de presse.
  4. Presse d'emboutissage selon la revendication 1, caractérisée en ce que l'élément de contre-appui (47) et le coulisseau (15) sont disposés de manière élastique l'un par rapport à l'autre.
  5. Presse d'emboutissage selon la revendication 1, caractérisée en ce qu'un moyen d'entraînement en déplacement (48) est associé à l'élément de contre-appui (47), en vue de la régulation de la force de maintien de tôle.
  6. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le moyen d'entraînement de table (36) présente un mécanisme (25, 38) avec au moins une position de repos dans laquelle il n'y a pas de transmission de mouvement depuis sa sortie de mécanisme jusqu'à un servomoteur (24, 40) raccordé à son entrée de mécanisme.
  7. Presse d'emboutissage selon la revendication 6, caractérisée en ce que le mécanisme (22, 38) est un mécanisme à manivelle.
  8. Presse d'emboutissage selon la revendication 7, caractérisée en ce que le mécanisme à manivelle est un mécanisme à excentrique.
  9. Presse d'emboutissage selon la revendication 8, caractérisée en ce que le moyen d'entraînement de table (36) présente respectivement au moins un servomoteur (23, 40) qui fonctionne en mode d'inversion.
  10. Presse d'emboutissage selon la revendication 9, caractérisée en ce que le moyen d'entraînement de table (36) comporte un mécanisme à excentrique dont l'excentrique (42) parcourt un angle de rotation inférieur à 90 degrés lors d'une course de presse.
  11. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le bâti de presse présente une tête (13), une table (32) et des colonnes (11, 12) disposées entre les deux.
  12. Procédé d'emboutissage profond d'une pièce de tôle, en particulier d'une pièce de carrosserie, avec une presse d'emboutissage (10) qui présente un coulisseau (15) pouvant être déplacé entre une position d'ouverture et une position de fermeture et destiné à recevoir un outil de matrice (18), sachant que lors d'une course de presse, le coulisseau (15) atteint et passe par un point d'inversion (Ut) et donc une position de point mort bas, caractérisant la position de fermeture, sachant que le servomoteur (23) qui l'entraîne est alors freiné et inversé afin de ramener le coulisseau (15) dans la position d'ouverture, après que celui-ci est de nouveau passé par la position de point mort, sachant que le moyen d'entraînement de table (36) associé à l'outil porte-poinçon est démarré lorsque le point d'inversion (Ut) du coulisseau (15) et de l'outil de matrice (18) est atteint pour la première fois.
EP11770114.4A 2010-10-21 2011-10-14 Presse d'emboutissage à maintien dynamique optimisé de la tôle et methode d'emboutissage Not-in-force EP2629901B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010060103A DE102010060103B4 (de) 2010-10-21 2010-10-21 Ziehpresse mit dynamisch optimierter Blechhaltung
PCT/EP2011/068041 WO2012062532A1 (fr) 2010-10-21 2011-10-14 Presse d'emboutissage à retenue dynamique optimisée de la tôle

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EP2629901A1 EP2629901A1 (fr) 2013-08-28
EP2629901B1 true EP2629901B1 (fr) 2016-07-20

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US (1) US9713832B2 (fr)
EP (1) EP2629901B1 (fr)
CN (1) CN103402666B (fr)
BR (1) BR112013009639A2 (fr)
CA (1) CA2814593C (fr)
DE (1) DE102010060103B4 (fr)
ES (1) ES2587231T3 (fr)
MX (1) MX346221B (fr)
WO (1) WO2012062532A1 (fr)

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DE102013105468B4 (de) * 2013-05-28 2015-10-01 Schuler Pressen Gmbh Verfahren zur Steuerung einer Presse mit variabler Getriebeübersetzung
DE102013105596B4 (de) 2013-05-31 2015-10-29 Schuler Pressen Gmbh Presse und Verfahren zum Betreiben der Presse
EP2843779A1 (fr) * 2013-09-03 2015-03-04 Exmore Group NV Presse de gaufrage
US9352375B2 (en) * 2013-09-11 2016-05-31 Stolle Machinery Company, Llc Actuator with variable speed servo motor for redraw assembly
CN104353753B (zh) * 2014-11-11 2018-04-06 营口锻压机床有限责任公司 汽车滤清器壳体拉伸机
DE102015110748A1 (de) * 2015-07-03 2017-01-05 Schuler Pressen Gmbh Verfahren zur Einstellung eines Phasenversatzes einer mehrfach wirkenden mechanischen Querwellenpresse sowie eine Presse nach diesem Verfahren
DE102015113267A1 (de) * 2015-08-12 2017-02-16 Rainer Naroska Verpackungsmaschinen Gmbh & Co. Kg Tiefziehwerkzeug zum Tiefziehen von Rohlingen
CN111185513B (zh) * 2020-02-24 2024-07-02 苏州斯莱克精密设备股份有限公司 高速罐体拉伸机的压边机构
US11511332B2 (en) * 2020-05-28 2022-11-29 Stolle Machinery Company, Llc Cam driven bodymaker
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CN112139339B (zh) * 2020-09-15 2021-08-10 大连理工大学 一种金属薄壁曲面件超低温成形设备
CN112845787A (zh) * 2021-01-04 2021-05-28 哈尔滨工业大学 一种大尺寸薄壁曲面件超低温成形装置及成型方法
CN117259545A (zh) * 2023-02-20 2023-12-22 南皮县安德五金制造有限公司 一种用于拉深的钢性压边装置

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MX346221B (es) 2017-03-09
CN103402666A (zh) 2013-11-20
CA2814593C (fr) 2016-12-13
DE102010060103A1 (de) 2012-04-26
CA2814593A1 (fr) 2012-05-18
ES2587231T3 (es) 2016-10-21
DE102010060103B4 (de) 2013-04-11
US20130333437A1 (en) 2013-12-19
MX2013004469A (es) 2013-10-30
EP2629901A1 (fr) 2013-08-28
BR112013009639A2 (pt) 2016-07-12
US9713832B2 (en) 2017-07-25
CN103402666B (zh) 2016-01-20
WO2012062532A1 (fr) 2012-05-18

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