EP2603334B1 - Presse d'emboutissage munie d'un serre-tôle statique - Google Patents

Presse d'emboutissage munie d'un serre-tôle statique Download PDF

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Publication number
EP2603334B1
EP2603334B1 EP11743835.8A EP11743835A EP2603334B1 EP 2603334 B1 EP2603334 B1 EP 2603334B1 EP 11743835 A EP11743835 A EP 11743835A EP 2603334 B1 EP2603334 B1 EP 2603334B1
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EP
European Patent Office
Prior art keywords
drive
press
slide
tool
press according
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
EP11743835.8A
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German (de)
English (en)
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EP2603334A1 (fr
Inventor
Dietmar Schöllhammer
Martin Schmeink
Andreas Dangelmayr
Jürgen Fahrenbach
Hans Hofele
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
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L Schuler GmbH
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Priority claimed from DE201010037950 external-priority patent/DE102010037950B4/de
Application filed by L Schuler GmbH filed Critical L Schuler GmbH
Publication of EP2603334A1 publication Critical patent/EP2603334A1/fr
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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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/04—Blank holders; Mounting means therefor
    • 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
    • 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
    • B21D53/00—Making other particular articles
    • B21D53/88—Making other particular articles other parts for vehicles, e.g. cowlings, mudguards
    • 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
    • B30B1/18—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 screw means
    • 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

Definitions

  • the invention relates to a drawing press, which is particularly suitable for integration in press lines, press lines, hybrid presses or transfer presses for the production of body parts.
  • the first press stage is usually a drawing press, which gives a previously flat board a spatial form. This is done in a pulling tool that clamps the edge of the board, or also allows controlled to slide towards the sheet metal center, while the enclosed by the blank holder part of the sheet between a die and a stamp receives the desired spatial shape.
  • drawing presses have become established in which the stamp is supported in a resting position on a press table and the associated die is held on the vertically movable plunger up and down. The blank holder surrounds the plunger and is pressed down against the force of a die cushion from the edge of the die during the drawing operation.
  • the convex curved sheet side is formed on the sheet metal part above, as it is also desired for the subsequent press stages.
  • Stansvortician in particular are carried out, which is usually required in body parts that the resulting burr on the hollow side, ie the concave side of the sheet metal part is located.
  • the design mentioned here has established itself as a standard. Designs with bottom die and top punch (and overhead plate holder) such as from the DE 10117578 B4 Therefore, they are less commonly used.
  • the deep drawing press has a ram with an upper tool.
  • the press also has on a table construction arranged drawing dies that perform the Tiefziehhub.
  • the plunger is moved with the upper tool in a closed position. Then it is coupled via Switzerlandholme and a hydromechanical locking device with the table construction.
  • the force acting on the upper tool and the plunger is supported by means of the Buchholme on the table construction of the deep drawing press.
  • GB 388,566 A describes a double-acting press.
  • a crankshaft drive actuates a ram with a tool part of the upper tool, while another crankshaft drive acts on another tool part on the upper tool.
  • these two tool parts of the upper tool is associated with a lower tool, wherein a tool part of the lower tool is supported by a fluid cylinder.
  • the forming of a workpiece is carried out by a downward movement of the two tool parts of the upper tool against the lower tool.
  • the pressure in the fluid cylinder, which supports a tool part of the lower tool is set via a valve control.
  • GB 512,631 A describes a double-acting press.
  • the press has a ram with an upper tool, a carriage with a lower tool is moved via an eccentric drive. On the carriage, a sheet holder is further arranged and supported via pressure cylinder. By a coordinated downward movement of the plunger and an upward movement of the carriage with the lower tool is a forming process. It is therefore an object of the invention to provide a press concept and a forming process, with which can be produced with low energy consumption while providing the desired subsequent in the subsequent press stages component orientation, thermoforming.
  • the plunger drive has a blocking position in which forces acting on the plunger are introduced into the press frame under at least largely, if not completely, circumvention of the actual drive source, such as a servomotor.
  • a blocking position is provided for example by an eccentric, a toggle mechanism or a similar gear in the respective extended position.
  • 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 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.
  • the platen drive need only be uniquely constructed by the plunger drive prior to commencing a pull stroke, after seating 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 designed as a short-stroke eccentric drive or as a cam drive, which clamps the sheet metal 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 for the opening and closing of the tool Method of the stamp and thus to carry out the actual drawing process.
  • the ram stroke can only be 1000 mm and the table lift can be 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 a Einsteiivorraum.
  • the sheet holding 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.
  • the adjustment drive as explained above may be a short-stroke toggle mechanism or an eccentric gear or the like.
  • the adjustment stroke will typically be at most a few 10 mm. This concept is particularly advantageous when the ram drive drive only with little force in its blocking position and can lock there. In this 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.
  • the servomotor of the ram drive is operated in reverse operation. It stops near the bottom plunger dead point and thus brings the eccentric and its connecting rod in an extended position.
  • the servo motor In order to move the plunger again after the forming of the sheet metal part in the opposite direction from the bottom dead center, ie to open the tool, the servo motor, if desired, can be rotated in the opposite direction until the plunger has performed the desired stroke.
  • the one of the eccentric continuous rotation angle can be limited to a value ⁇ 180 degrees, or preferably ⁇ 90 degrees. The same applies to the table drive, where the rotation angle can even be limited to values ⁇ 60 ° degrees.
  • 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 11, the at least one, preferably a plurality, preferably vertically oriented stand 12, a head 13, which is supported by the uprights 12, and a pedestal 14, which is arranged below or between the uprights 12.
  • the head 13, the stand 12 and the base 14 form a closed frame.
  • a plunger 15 is movably mounted in an example vertical direction of movement 16.
  • For the storage of the plunger 15 are provided for example on the uprights 12 provided linear guides 17th
  • 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 that is, 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 mirror-symmetrical to each other in the present embodiment and each constructed as an eccentric gear. They each include an eccentric 27, 28, which is connected 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.
  • the drive 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 convex die 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 12 and / or the base 14 by means of guide means 37 in the direction of movement.
  • To the table drive 36 includes one or more gear 38, 39, which, like the transmission 25, 26, each having a blocking position. They are e.g. designed as an eccentric gear that bring the press table 31 with one or more servomotors 40, 41 in drive connection.
  • 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 is usually done 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 servomotors 23, 24 not shown here have the eccentric 27, 28 turned so far that the plunger 15 has reached its bottom dead center.
  • the edge 19 of the die tool 18 sets on the edge of the board 20 and begins to press against the blank holder 35.
  • the blank holder 35 rests on the support elements 46 relentless on the abutment 47, so that now the press frame is stretched in the direction of movement 16.
  • 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.
  • FIG. 4 already illustrates the plunger 15 in the upper position, while the punch tool 34 is still in working position. It will still driven by appropriate rotation of the eccentric 42, 43 down, after which it is only on the plate holder 35, and can be driven out of the drawing press 10 by a workpiece transport device, such as suction spider or the like.
  • 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.
  • 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 can be effected in this and in all other embodiments by a single servo motor 40 when the gears of the eccentric 42, 43 mesh with each other or if the eccentric 42, 43 are connected in any other way by suitable transmission means.
  • the eccentric 42, 43 can be reduced to segment wheels, so that a toothing can be limited to a part of the circumference. To reduce costs can This measure also in the eccentrics 27, 28 and their edges find application.
  • FIG. 6 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 54, 55 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 links 54, 55 at the press frame 11 supported without burdening the servomotors.
  • a tensioning device 60 which serves to clamp the sheet metal holder 35 against the upper plunger 15.
  • the clamping device 60 comprises a plurality of clamping units which are preferably distributed along the annular plate holder 35.
  • To the clamping unit 60 includes a tension member in the form of a clamping bolt 61, which is held on the plunger 15 and on the plate holder 35 and away, at least slightly, is movably mounted.
  • the minimal to be traversed by the clamping bolt 61 movement stroke corresponds to the stroke, which is required after mounting of the plunger 15 on the board 20 for tightening the same. In individual cases, this stroke can be very small and amount to a few millimeters or fractions of a millimeter. Preferably, however, the stroke is much larger and indeed so large that clamping bolt 61 can be substantially completely retracted into the plunger 15.
  • the clamping bolt 61 is associated with a force generating device 62, which is formed here for example in the form of a hydraulic drive device. It is formed by a hydraulic cylinder 63 with two working chambers 64, 65, which are separated from each other by a piston 66.
  • the clamping bolt 61 forms, for example, the piston rod of the piston 66. This is sealed out of the Hyd-raulikzylinder 63 led out.
  • the clamping bolt 61 has at its lower end a locking means 67, for example according to a recess, for example in the form of a locking groove 68 which is formed as an annular groove.
  • a locking groove 68 is limited at the force-generating device 62 side facing a conical edge and on the opposite side with a flat edge.
  • To the clamping unit 60 also includes a clamping bolt 61 associated locking device 69, which has at least one, preferably a plurality of radially movable latch 70, 71. These are by a hydraulic or other actuator 72, z. B. actuated in the form of an annular piston which is arranged coaxially to a clamping bolt 61 receiving bore 73 in an annular chamber. He actuates the latch 35, 36 via a wedge gear and thus can selectively adjust the latch 35, 36 radially.
  • the clamping bolt 61 can extend when opening and closing the tool in the bore 73 and out of this. However, it can also have a length that is so large that it always slides in the bore 73 without extending out of this. It is also possible to provide clamping units with long and clamping units mixed with short bolts, with clamping units with short clamping pins 61, which extend from its bore 73, are arranged where they would otherwise the workpiece for its transport would be in the way.
  • the locking device 69 provides a positive and / or positive connection with the clamping bolt 61 of the plunger.
  • the latches 69, 70 engage in the locking groove 68 on the associated clamping bolt 61.
  • the force-generating device 62 the sheet-holding force between sheet metal holder 35 and the plunger 15 can then be set to save energy.
  • the edge 19 facing and provided for contact with the board 20 plate holder clamping surface 74 is configured just ( FIG. 8 ). That is, the blank holder clamping surface 74 has no projections or depressions, in particular no terminal strips, which lead to a corresponding local indentation in the board 20 during clamping.
  • the surface normal N on the blank holder clamping surface 74 is aligned at any point perpendicular to the associated surface of the board 20 and the surface of the edge 19.
  • the plunger drive 22 is formed by a Füziehebelantrieb.
  • a position sensor 76 may be assigned. Via the position sensor 76, it is detected whether the toggle lever arrangement, to which the lever 75 belongs, has assumed its extended position and thus its blocking position, which is illustrated in FIG.
  • the position sensor 76 is provided with a Control unit 77 connected to this the position sensor signal S to transmit.
  • the position sensor 76 may simultaneously serve as a stop and / or damping element for the lever 75 or have a stop 76a and / or a damping element 76a. As a result, the blocking position can be exactly pre-tanned.
  • the ram drive 22 operates in this embodiment, preferably in oscillating operation, wherein the servo motor or the servomotors of the plunger drive 22 reverse their direction of rotation at the upper and lower end position of the plunger 15 respectively.
  • the ram drive 22 could also be designed as an eccentric drive, as shown in the previous embodiments.
  • the matrix tool 18 can optionally be assigned a permeability sensor 78 which generates a tension signal Z and transmits it to the control unit 77.
  • the tension signal Z describes the tension acting on the board 20 during forming.
  • the permeability sensor 78 detects the permeability of the circuit board 20 that changes due to the tensile stress.
  • the tensile signal z can be used to optimize the sheet holding force of the sheet holder 35 and / or the forming force between the punch tool 34 and the circuit board 20.
  • the table drive 36 is formed by one or more spindle drives 79.
  • Each spindle drive 79 has a spindle 80, a spindle nut 81 and an example according to the spindle nut 81 driving electric motor 82.
  • the electric motor 82 could also drive the spindle 80.
  • the electric motor 82 is preferably designed as a hollow shaft motor with an internal rotor, which coaxially surrounds the driven component, ie the spindle 80 or the spindle nut 81.
  • Such spindle motors 79 are, for example, also provided as an adjusting device 48 for adjusting the plate-holding force of the plate holder 35.
  • the spindle drives 79, or the electric motors 82 of the spindle drives 79, are controlled by the control unit 77.
  • the translation between the spindle nut 81 and the spindle 80 can be chosen in particular in the adjusting device 48 so that a self-locking occurs in the spindle gear.
  • the associated electric motor 82 only has to be operated if the plate holding force has to be changed or readjusted. To maintain a set plate holding force of the electric motor must not be energized.
  • the control unit 77 also controls the ram drive 22 and in the embodiment shown here, a blocking device 83.
  • the blocking device 83 is disposed between the press frame 11, for example, the head 13, and the plunger 15. Regardless of whether the plunger drive 22 is exactly in its blocking position or not, a rigid connection between the plunger 15 and the press frame 11 can be made via blocking device 83. This rigid coupling prevents movement of the plunger 15 in the direction of movement 16 due to the forces acting on the plunger 15 forces by the blank holder 35 or the punch tool 34th
  • the blocking device 83 between a coupling position K (solid lines in FIG. 9 ) and a release position F (dotted lines in FIG. 9 ) are switched.
  • the blocking device 83 transversely to the direction of movement 16 slidable blocking elements 84, which cooperate in their coupling position K with counter-elements 85 on the plunger 15.
  • the blocking elements 84 are aligned with their respective associated counter element 85 in the direction of movement 16 and abut against each other at associated end faces 86.
  • the plunger 15 is therefore supported on the press frame 11 and, according to the example, on the head 13.
  • the coupling position K thus a very rigid coupling during the forming process of the board 20 between the plunger 15 and the press frame 11 is ensured.
  • no holding force must be generated, which improves the energy efficiency of the drawing press 10.
  • the blocking elements 84 are offset transversely to the direction of movement 16 to the counter-elements 85, so that by the plunger drive 22 of the plunger 15 can be moved from its lower end position in the direction of movement 16 upwards.
  • the blocking device 83 For moving the blocking elements 84 between the coupling position K and the release position F, the blocking device 83 has a linear drive 87, which is controlled by the control unit 77.
  • a linear drive 87 can serve, for example, a spindle drive, by an electric motor is controlled. Other linear drives can also be used.
  • the displaceable blocking elements 84 can also be arranged on the plunger 15. Then the counter-elements 85 are arranged on the press frame 11 and preferably on the head 13.
  • the adjusting device 48 may then be assigned to an existing on the plunger 15 edge part, which cooperates with the plate holder 35 for clamping the board and is movable in the direction of movement 16 by the adjusting device 48.
  • the drawing press 10 has an abutment 47 for supporting a stationary plate holder 35, which is part of a tool and can be supported on the press frame 11 via the abutment 47.
  • the blank holder 35 is associated with a tappet 15 with a die tool 18, wherein the plunger 15 is moved via a ram drive with blocking position.
  • the blocking position is achieved for example by a gear 22 that transmits in the blocking position no movement from the transmission output to the driving servomotor 23 and / or 24.
  • this is achieved by an eccentric gear 25, 26, when this is in an extended position.
  • the associated in the drive table 32 is raised or lowered by the press table 31 via a table drive 36.
  • the table drive 36 is preferably again a servomotor drive with a non-linear gear, for example an eccentric gear.

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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)

Claims (14)

  1. Presse d'emboutissage (10),
    comprenant un bâti de presse (11),
    comprenant un coulisseau (15) qui est monté dans le bâti de presse (11) à l'aide d'un moyen d'entraînement de coulisseau (22), avec possibilité de déplacement dans une direction de déplacement (16),
    le moyen d'entraînement de coulisseau (22) présentant un mécanisme de transmission (25) avec au moins une position de blocage dans laquelle il n'y a pas de transmission de mouvement depuis sa sortie de mécanisme vers un servomoteur (23, 24) raccordé à son entrée de mécanisme,
    comprenant un élément de contre-appui (47) qui est conçu pour l'appui d'un serre-flan (35),
    comprenant une table (31) sur laquelle est monté un outil formant poinçon (34),
    comprenant un moyen d'entraînement de table (36) qui est relié à la table (31) afin de déplacer celle-ci dans la direction de déplacement (16),
    le moyen d'entraînement de table (36) étant agencé pour effectuer la course d'emboutissage de la table (31) et de l'outil formant poinçon (34), qui est nécessaire pour la mise en forme de la pièce de tôle, pendant que le moyen d'entraînement de coulisseau (22) se trouve dans la position de blocage.
  2. Presse d'emboutissage selon la revendication 1, caractérisée en ce que la table (31) présente un groupe (50) de passages (51, 52, 53) et en ce qu'il est prévu des éléments d'appui (46) qui s'étendent à travers au moins quelques-uns des passages (51) et par l'intermédiaire desquels le serre-flan (35) est en appui sur l'élément de contre-appui (47).
  3. Presse d'emboutissage selon la revendication 1, caractérisée en ce que l'élément de contre-appui (47) est disposé de manière stationnaire sur le bâti de presse (11).
  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 façon 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 la tôle.
  6. Presse d'emboutissage selon la revendication 5, caractérisée en ce que le moyen d'entraînement en déplacement (48) présente au moins un moyen d'entraînement à vis (79).
  7. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le mécanisme de transmission (25, 38) est un mécanisme à excentrique.
  8. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le mécanisme de transmission (25, 38) est un mécanisme à genouillère.
  9. Presse d'emboutissage selon la revendication 1, caractérisée en ce que le moyen d'entraînement de coulisseau (22) et/ou le moyen d'entraînement de table (36) présentent chacun au moins un servomoteur (23, 24, 40, 41) ou un moteur électrique (82) qui fonctionne en mode réversible.
  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 la presse.
  11. Presse d'emboutissage selon la revendication 9, caractérisée en ce que le moyen d'entraînement de table (36) et/ou le moyen d'entraînement de coulisseau (22) présentent au moins un moyen d'entraînement à vis (79).
  12. Presse d'emboutissage selon la revendication 11 et/ou la revendication 6, caractérisée en ce que le moyen d'entraînement de table (36) et/ou le moyen d'entraînement de coulisseau (22) et/ou le moyen d'entraînement en déplacement (48) sont activés séparément par l'intermédiaire d'un dispositif de commande (77).
  13. Presse d'emboutissage selon la revendication 1, caractérisée en ce qu'il est prévu un dispositif de serrage (60) qui est apte à établir une liaison entre le coulisseau (15) et le serre-flan (35).
  14. Procédé d'emboutissage profond d'une pièce de tôle avec une presse d'emboutissage (10) qui présente un coulisseau (15), entraîné par un moyen d'entraînement de coulisseau (22) et destiné à recevoir un outil formant matrice (18), et une table (31) entraînée et destinée à recevoir un outil formant poinçon (34),
    le moyen d'entraînement de coulisseau (22) présentant un mécanisme de transmission (25) avec au moins une position de blocage dans laquelle il n'y a pas de transmission de mouvement depuis sa sortie de mécanisme vers un servomoteur (23, 24) raccordé à son entrée de mécanisme,
    le coulisseau (15) et la table (31) pouvant être déplacés de manière contrôlée pour être rapprochés et éloignés l'un de l'autre,
    le coulisseau (15) n'ayant plus que pour fonction réduite d'effectuer l'ouverture et la fermeture de l'outil (18, 34) et le serrage du bord d'emboutissage de la pièce (20),
    et la table (31) exécutant la course d'emboutissage par déplacement de l'outil formant poinçon (34), pendant que le coulisseau (15) est au repos et le serre-flan (35) est au repos et pendant que le moyen d'entraînement de coulisseau (22) se trouve dans la position de blocage.
EP11743835.8A 2010-08-16 2011-08-15 Presse d'emboutissage munie d'un serre-tôle statique Active EP2603334B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010034518 2010-08-16
DE201010037950 DE102010037950B4 (de) 2010-10-04 2010-10-04 Ziehpresse mit statischer Blechhaltung
PCT/EP2011/064043 WO2012022720A1 (fr) 2010-08-15 2011-08-15 Presse d'emboutissage munie d'un serre-tôle statique

Publications (2)

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EP2603334A1 EP2603334A1 (fr) 2013-06-19
EP2603334B1 true EP2603334B1 (fr) 2018-04-25

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US (1) US10160023B2 (fr)
EP (1) EP2603334B1 (fr)
JP (1) JP2014501617A (fr)
BR (1) BR112013003446A2 (fr)
ES (1) ES2670848T3 (fr)
MX (1) MX358381B (fr)
WO (1) WO2012022720A1 (fr)

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CN103433343A (zh) * 2013-08-19 2013-12-11 苏州市胜能弹簧五金制品有限公司 一种适用于薄型模板冲压的线性冲压装置
DE102013114693A1 (de) * 2013-12-20 2015-06-25 Fette Engineering GmbH Stopfstempelstation und Verfahren zum Füllen von Kapseln in einer Stopfstempelstation
US9931684B2 (en) 2014-04-18 2018-04-03 Honda Motor Co., Ltd. Forming die and method of using the same
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US10105742B2 (en) 2014-12-09 2018-10-23 Honda Motor Co., Ltd. Draw press die assembly and method of using the same
DE102018201629B4 (de) * 2018-02-02 2023-10-19 Volkswagen Aktiengesellschaft Stelleinrichtung zur Einstellung der Flächenpressung in einem Blechumformwerkzeug und Blechumformwerkzeug mit wenigstens einer solchen Stelleinrichtung

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Publication number Publication date
BR112013003446A2 (pt) 2021-05-25
JP2014501617A (ja) 2014-01-23
US20180264536A9 (en) 2018-09-20
MX2013001896A (es) 2013-08-01
MX358381B (es) 2018-08-15
US20130180301A1 (en) 2013-07-18
EP2603334A1 (fr) 2013-06-19
ES2670848T3 (es) 2018-06-01
WO2012022720A1 (fr) 2012-02-23
US10160023B2 (en) 2018-12-25

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