EP2104578B1 - Dispositif de coussin hydraulique à entraînement hybride modulaire - Google Patents

Dispositif de coussin hydraulique à entraînement hybride modulaire Download PDF

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Publication number
EP2104578B1
EP2104578B1 EP07856049A EP07856049A EP2104578B1 EP 2104578 B1 EP2104578 B1 EP 2104578B1 EP 07856049 A EP07856049 A EP 07856049A EP 07856049 A EP07856049 A EP 07856049A EP 2104578 B1 EP2104578 B1 EP 2104578B1
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EP
European Patent Office
Prior art keywords
drive
die cushion
cushion device
die
pressure
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Not-in-force
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EP07856049A
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German (de)
English (en)
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EP2104578A2 (fr
Inventor
Markus Müller
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Mueller Weingarten AG
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Mueller Weingarten AG
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Publication of EP2104578A2 publication Critical patent/EP2104578A2/fr
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    • 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
    • B21D24/02—Die-cushions

Definitions

  • the invention relates to a die cushion device which, in combination of fluid and electric drive, is designed as a module and which can be adapted as a drawing device in a press by the use of one or more modules to different part geometries.
  • presses are used to pull blanks hydraulic pulling devices, which are arranged in the press table and apply pressure in the press table via movable pressure plates and a defined force on the blank holder, which presses the edge of the drawn part against the upper tool.
  • Complicated and large-scale drawn parts require a different force setting on the drawing part edge.
  • a pulling device which consists of several independently acting pressure cylinders and each pressure cylinder is associated with a pressure cheek, which applies an individually adjustable force on the blank holder and Ziehteilrand.
  • the disadvantage here is the high control and control effort that must be operated in particular for the synchronization during pre-acceleration and elevating and for the safety-oriented locking of the pulling device.
  • the use of complex hydraulic controls also requires the operator to have specially trained personnel for the maintenance and service of the die cushion device.
  • Pneumatic drawing cushions have also been used for some time in forming technology.
  • pneumatic cylinders are located in the area of the press table. These pneumatic cylinders usually act on a pressure cheek and pressure pins on a blank holder.
  • the pressure chambers of the pneumatic cylinder are usually connected to a large-volume accumulator, which reduces the pressure increase to the lower reversal point.
  • the type of pneumatic cushions are closed systems and have no power control but no further control options. They are displaced by the press ram and immediately follow it in the downward movement, the force in the downward movement being equal to the force in the upward movement.
  • nitrogen cylinders are sometimes used in forming technology.
  • the use of the Nitro-Dyne gas spring system instead of steel springs, strips, sheets, tubes 11-1974 describes the applications of such nitrogen cylinders.
  • the nitrogen cylinders act similar to a mechanical spring, but offer some advantages. For example, nitrogen springs have full power right from the start. In addition, the increase in force over the travel of a nitrogen spring is much lower than conventional springs. Another advantage of nitrogen springs is the very high power density.
  • the so-called single-chamber system piston and piston rod form one unit. The seal happens here on the piston. There is a scraper on the piston rod.
  • the upper chamber is thus vented to the atmosphere.
  • the single-chamber system is characterized by a short stroke and a progressive force curve.
  • a tank system When such a system is connected to an external storage volume, it is referred to as a tank system.
  • a tank system In a tank system, it is possible to adapt the force increase of the spring over the spring travel to the requirements.
  • the invention is based on the object, starting from the prior art, to improve a die cushion device with hybrid drive such that for one of the drives a safe and easy-built overload protection is given and further that the space required for a single die cushion module is reduced ,
  • the first drive and the second drive form a die cushion module
  • the die cushion module comprises a component, by means of which the sinker holder of at least one of the drives with a lifting movement is movable upwards or with a lowering movement downwardly, while a a pulling operation of the upper tool on the component transferable, downwardly directed, a Niederfahrterrorism causing compressive force to avoid overstressing the second drive only by the first drive blockable or braked and wherein the component is decoupled from the second drive in the downward movement down.
  • the core of the invention is to integrate the second drive in the hybrid drive, that this can meet without any impairment of its tasks, in particular a sensitive control and regulation of a lifting movement of the board holder, but of forces or movements with which the upper tool on the board holder also acts on the hybrid drive or the die cushion module is decoupled.
  • a decoupling is achieved mechanically by a freewheel acting in a direction of movement between the second drive and the component which is directly or indirectly tucked with the sinker holder.
  • the freewheel protects the second drive against overloads, as they can not be transferred to the second drive by utilizing the freewheeling function.
  • the invention provides, in particular, to use the hybrid principle to arrange the electric drive with its power transmission mechanism in an axis to a hydraulic cylinder or a nitrogen cylinder or a mechanically sprung cylinder or a similar drive and pass the piston rod of the cylinder through the power transmission mechanism of the electric drive and the Piston rod directly or indirectly, in particular to bring about the pressure cheek with the board holder in operative connection.
  • a particularly compact design is achieved, since a component of the first drive, in particular a piston rod of both drives used as an operative connection to the downstream components and does not need to be performed twice as is the case with known hybrid drives.
  • the electric drive which is also referred to as a second drive
  • no immediate or no all forces and movements transmitting connection to the board holder or the pressure cheek has and at the moment of impact of the press ram on the board holder and disengaged in the event of overload.
  • the electric drive preferably acts on a collar of the piston rod of the hydraulic cylinder via a ball or roller screw drive.
  • the hydraulic system consisting of cylinder, arranged on the outlet side proportional valve and pressure sensor, and arranged on the inlet side check valve and low-pressure accumulator, active and counteracts with a defined force the plunger.
  • the force is applied by a cylinder-controlled pressure acting on the piston surface.
  • the pressure is generated passively by oil displacement against a proportional valve.
  • the electric drive follows the piston rod and does not necessarily have to be in operative connection with it.
  • the overload protection is common as with hydraulic drawing cushion, given by a further discharge side arranged pressure relief valve.
  • the dimensioning of the electric drive also depends on the value of the resulting force, which generally corresponds to approximately 10% to 20% of the nominal force of the cylinder. This is a further advantage in order to reduce the space compared to purely electrically driven die cushion devices.
  • the lower required nominal force of the electric drive allows a more favorable dimensioning of the power transmission elements, leads to lower mass moments of inertia, to a better dynamics of the drive and at the same time reduces heat generation.
  • the strict division of tasks of hydraulic and electrical system, the known advantages of a hybrid drive arise: the generation of pulling force required for pulling done by the hydraulic system with its high power density and its compact design and not executed in contact with the press ram movements of the die cushion device by run the simpler electric drive. It accounts z. As the additionally required safety valves in the hydraulic system, as dangerous movements can be safely prevented by the electric drive with simpler means.
  • the invention also provides for the first drive to use a nitrogen cylinder instead of a hydraulic cylinder or a mechanical cylinder.
  • a nitrogen cushion module is produced, consisting of an electric drive and a nitrogen cylinder, which acts like a spring during the forming process.
  • the amount of nitrogen in the cylinder during the operation of the nitrogen pad module remains constant, since the cylinder can be decoupled from the nitrogen supply during operation.
  • the nitrogen supply system consisting essentially of a high-pressure accumulator, a low pressure accumulator and a pressure booster, serves for presetting a spring force by filling or discharging nitrogen outside of the operation.
  • the overall system of the nitrogen cushion module can still operate regulated.
  • the control is effected by a superimposition of the nitrogen spring force and a force resulting from the electric drive.
  • the electric drive can generate a force which counteracts the nitrogen spring force.
  • the effective force is thus reduced during the drawing process by the electric drive.
  • a braking effect can be achieved by the electric drive.
  • an energy recovery in the upward gear can be realized.
  • Another advantage of the inventive design of the die cushion device as a nitrogen cushion module is the ability to operate the die cushion uncoupled from the nitrogen supply. This allows the construction of modular multi-point drawing devices, which can be arranged both in the press table, as well as directly in the sliding table.
  • FIG. 1 is the schematic structure of a forming press 51 for drawing large-area parts 10, which are designed for example as boards 53 made of plastic or sheet metal.
  • the press has a mechanical drive 1, which moves the plunger 2 with upper tool 3 up and down.
  • a die cushion device 50 is arranged with hybrid drives 52, which consists of a press table 8 vertically displaceable pressure cheek 7 and several die cushion modules 9 and hybrid drives 52.
  • pressure pin 6 On the pressure cheek 7 are pressure pin 6, which hold the board holder 4 with the drawn part 10 and from below with a board holding force F53 on the Pull part 10 act.
  • the upper tool 3 comes via the drawn part 10 with the board holder 4 in conjunction and displaces this against the pressure pin 6, the pressure cheek 7 and the die cushion modules 9, which support the pressure cheek 7.
  • Each die cushion module 9 counteracts with an adjustable force of the plunger movement and thus braces the drawing part edge between the board holder 4 and upper tool 3 in a defined manner.
  • the inflow of material of the drawn part 10 can be selectively controlled or regulated in the form formed by the upper tool 3 and the lower tool 5.
  • FIG. 2 the basic structure of a die cushion module 9 is shown.
  • the hydraulic system consists of a plunger cylinder 11 designed as a hydraulic cylinder with a piston rod 12 with a splined shaft profile 13, a displacement measuring system 32 arranged on the bottom side, and the proportional valve 21, pressure limiting valve 22 and the pressure transmitter 23 arranged in the discharge line 24 the check valves 27 and 29 located in the supply line 30, the piston accumulator 28 and a pump 26 with a valve for pressure limiting 31.
  • the hydraulic cylinder 12 forms a first drive.
  • An electric drive 14, which forms a second drive includes a rotor 15 configured as a hollow shaft and optionally a spring-pressure safety brake 16.
  • a transmission for converting the rotational movement of the rotor 15 into a lifting and lowering movement of the piston rod 12 is a ball screw consisting of hollow Spindle 18 which is positively connected to the piston rod 12 and the spindle nut 17 which is fixedly connected to the rotor 15. About the collar 19 of the piston rod 12, the spindle 18 is in its downward movement with its collar 55 positively connected to the piston rod 12 in connection.
  • An anti-rotation device 20 connected to the housing of the hollow shaft or torque motor 14 fixes the piston rod 13 via the splined shaft profile and thus allows the translation of a rotational movement in a translational movement.
  • the pump 26 fills the piston accumulator 28 via a check valve 27 with hydraulic oil to a pressure value which corresponds to the sum of maximum possible mass and flow forces and the required force for lifting the drawn part 10 from the contour of the lower tool 5.
  • Excess pressure oil is z. B. returned to the tank via a pressure relief valve 31.
  • a check valve 29 connects the piston accumulator 28 with the supply line 30 of the cylinder 11 and prevents backflow from the cylinder. The thereby acting on the piston 12 pressure raises the piston rod 13 and presses it against its collar 19 against the spindle 18 of the ball screw.
  • the electric drive is driven such that the piston rod can be moved to the desired position.
  • An arranged on the cylinder bottom displacement measuring system 32 detects the movement of the piston rod directly and supplies the actual value to the controller.
  • the hydraulic drive supplies the required energy.
  • the position is generally determined by the electric drive.
  • the proportional valve 21 remains closed.
  • the electric drive provides the kinetic energy and positions the piston rod as long as the plunger has not come into contact with the board holder. In this case, the proportional valve 21 must release the outflow from the cylinder.
  • the pressure in the cylinder is regulated to a value above the accumulator pressure.
  • the pressure transducer 23 provides the required actual pressure value.
  • the control of the predetermined pressure value for the drawing process takes place.
  • the placement of the plunger is detected by comparing the positions of plunger and piston rods of the die cushion modules. It is also possible at higher differential speeds to detect the placement of the plunger by a pressure increase in the cylinder.
  • a safety-oriented locking of movements of the die cushion device in the upward direction is possible by means of the spring-pressure safety brake 16.
  • the braking torque is applied by spring force to the rotor 15 of the engine.
  • rapid lowering movements can be prevented by using safety-related valves in the outflow line 24 of the cylinder.
  • the proportional valve 21 can be designed as a fail-safe valve.
  • FIG. 3 describes a complete cycle of motion of the hybrid-type die cushion device.
  • the electric drive assumes the positioning of the die cushion device. This preferably takes place synchronously with the movement of the plunger, in that corresponding to the torque motor or the hollow shaft motor corresponding position desired values are predefined as a function of the crank angle of the press drive.
  • the electric drive of the piston rod runs, which is driven in this section by the plunger. This can be done by limiting the motor current or the torque to stay in contact with the piston rod with little force or by using another displacement measuring system which detects the position of the spindle. By comparing both position values, the spindle can be tracked without contact at a small distance.
  • the electric drive takes over the leadership of the pillow movements and raises z.
  • the pressure cheek of the die cushion device delays to the plunger movement by a certain amount to allow transfer devices to remove the drawn part and then brings the die cushion device back to the starting position.
  • the padding operation is a special case, wherein the first portion of the run-up movement of the die cushion device takes place in contact with the plunger until the beginning of the braking phase.
  • the piston rods can create with the force of the hydraulic system against the board holder and plunger, the electric drive is performed with respect to the displacement measuring system of the plunger with a small distance above the collar 19 until the braking phase begins.
  • the die cushion module 101 essentially consists of two parts, namely the electric drive 102, which is also generally referred to as the second drive, and a spring 103, which is generally referred to as the first drive.
  • the spring 103 is preferably designed as a nitrogen cylinder, wherein the spring force of the spring 103 counteracts the pressing force.
  • the spring force of the nitrogen cylinder 103 can be regulated by filling or discharging nitrogen with a nitrogen supply unit 104.
  • This nitrogen supply unit 104 consists of a low-pressure accumulator 105, in which excess nitrogen can be discharged, a high-pressure accumulator 106, from which the nitrogen cylinder 3 can be filled with additional nitrogen, a pressure interrupter 107 connected therebetween and corresponding valve technology.
  • the nitrogen supply unit 104 can be arranged both directly on the nitrogen cylinder 103, as well as outside the press as a separate supply station.
  • the transmission for converting the rotational movement into a lifting and lowering movement of the piston rod 109 is a ball screw 110, consisting of a hollow spindle 18 which is positively connected to the piston rod 109 and a spindle nut 17, which is fixedly connected to a rotor 15 of the hollow shaft motor 108.
  • the Figures 5 and 6 show detailed representations of in the FIG. 3 shown die cushion module 9, which is essentially formed by a hybrid drive 52, in different positions of the piston rod 12 and the hollow spindle 18.
  • the hybrid drive is used in particular the generation and control of a board holding force, with which a drawn part or a board of at least one board holder during of the drawing operation is pressed against the upper tool.
  • the piston rod 12 in the FIG. 5 with a lowering L dropped in an arrow direction y '.
  • Such a lowering movement L of the piston rod 12, which is also generally referred to as component 12, results, for example, in the course of a drawing operation by a downward movement of the upper tool, which also acts indirectly on the piston rod 12.
  • the lowering movement L of the piston rod 12 along its axis a is independent of a position of the hollow spindle 18 of the electric drive 14.
  • a relative movement between the hollow spindle 18 and the spline 13 of the piston rod 12 is unimpeded, since the hollow spindle 18 on the spline 13th the piston rod 12 in the direction of the axis a can slide up and down unchecked.
  • the hollow spindle 18 is driven by the spindle nut 17 on the spline shaft 13 of the piston rod 12 in the y or y 'direction freely movable, but not with respect to the piston rod 12 about the longitudinal axis a rotatable.
  • the formed on the piston rod 12 collar 19 is particularly good recognizable.
  • the piston rod 12, as in the Figures 3 and 6 The electric or second drive 14 forms with its spindle 18 a height-adjustable stop 54 for the first drive or for the piston rod 12 of the cylinder 11.
  • the in the FIG. 5 shown position in which the piston rod 12 has dropped relative to the hollow spindle 18 of the second drive 14
  • the formed on the piston rod 12 collar 19 is particularly good recognizable.
  • the piston rod 12 as in the Figures 3 and 6
  • the electric or second drive 14 forms with its spindle 18 a height-adjustable stop 54 for the first drive or for the piston rod 12 of the cylinder 11.
  • the piston rod 12 can sink at any time in the y 'direction, without burdening the electric drive 14 when sinking.
  • the piston rod 12, which is a component 56 of the cylinder 11 which forms the first drive is also used for the direct or indirect actuation of the board holder by the electric drive 14, which forms the second drive.
  • a common nitrogen pressure chamber can be used for several cushion modules, wherein a plurality of die cushion modules are connected to the common pressure chamber.
  • This common nitrogen pressure chamber can also be a pressure-tight cavity in the sliding table, this pressure chamber being provided in particular for a supply of several die cushion modules.
  • the invention also provides for arranging the nitrogen supply unit outside the press as set-up station. The invention also provides to control the amount of nitrogen in the nitrogen cylinder.
  • the amount of nitrogen in the nitrogen cylinder 103 can not only be changed as a set-up process, but also be regulated during operation.
  • FIG. 1 illustrated pressure cheek 7 split executed.
  • the die cushion modules 9 of the invention do not act on a common pressure cheek 7, but on individual pressure cheek segments. These segments in turn act on the board holder 4 via one or more pressure bolts 6.
  • the piston rods of the die cushion modules 9 according to the invention then act either directly or via pressure bolts 6 on the board holder 4.
  • the board holder 4 can be designed both as a conventional, and as a segment elastic circuit board holder.
  • the die cushion modules 9 are integrated in the mobile sliding table. That is, the die cushion modules 9 and the associated movement or force transmission means are accommodated in the sliding table body and extended or retracted during a tool change with the sliding table.
  • the invention further provides for the board holder (4) to be designed as a segment-elastic board holder. It is also envisaged to integrate the die cushion modules in one or more sliding tables. Furthermore, the invention provides to realize the electric drive functions of several die cushion modules via suitable motion transmission means of a common drive. It is also envisaged to realize the hydraulic drive functions of a plurality of die cushion modules via suitable motion transmission means of a common drive. Furthermore, the invention provides to control or regulate the electric drive functions of several die cushion modules individually and / or jointly. According to the invention, it is also provided to control or regulate the hydraulic drive functions of several die cushion modules individually and / or jointly. To increase safety, it is provided to allow by means of a spring-pressure safety brake locking the die cushion device in the upward direction. Finally, it is provided to prevent by means of safety-oriented valves in the discharge line of the cylinder rapid lowering movements of the die cushion device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Coupling Device And Connection With Printed Circuit (AREA)
  • Percussion Or Vibration Massage (AREA)

Claims (15)

  1. Dispositif de coussin de serre-flan (50) de presse de transformation (51) pour générer la force de maintien d'une platine (F53) entre un outil inférieur (5) et un outil supérieur (3),
    - le dispositif de coussin de serre-flan (50) ayant au moins un moyen d'entraînement hybride (52),
    - le moyen d'entraînement hybride (52) agissant sur au moins un support de platine (4) de l'outil inférieur (5),
    - le moyen d'entraînement hybride (52) étant formé par au moins un premier moyen d'entraînement (11, 103) et au moins un second moyen d'entraînement (14, 102),
    caractérisé en ce que
    - le premier moyen d'entraînement (11, 103) et le seconde moyen d'entraînement (14, 102) forment un module de coussin de serre-flan (9),
    - le module de coussin de serre-flan (9) comprend une pièce (12, 109) à l'aide de laquelle, le support de platine (4) est déplacé par au moins l'un des moyens d'entraînement (11, 14) suivant une course de montée (H) ou une course de descente (L),
    - une poussée exercée au cours d'une opération d'étirage par l'outil supérieur (3), transmise à la pièce (12, 109), dirigée vers le bas, et produisant un mouvement de descente, ne peut être bloquée ou freinée que par le premier moyen d'entraînement (11, 103), et pour éviter de surcharger le second moyen d'entraînement (14, 102),
    - pour le mouvement de descente, la pièce (12, 109) est découplée du second moyen d'entraînement (14, 102).
  2. Dispositif de coussin de serre-flan selon la revendication 1,
    caractérisé en ce que
    - la course de soulèvement (H) générée par le premier moyen d'entraînement (11, 103) est commandée ou réglée en direction de l'outil supérieur (3) par le second moyen d'entraînement (14, 102), et
    - notamment, le second moyen d'entraînement (14, 102) forme une butée (54) de hauteur réglable par rapport à la pièce (12, 109), et
    - notamment, la course de soulèvement de la pièce (12, 109) est ajustable de manière fine par le second moyen d'entraînement (14, 102).
  3. Dispositif de coussin de serre-flan selon la revendication 1 ou 2,
    caractérisé en ce que
    - dans le cas de la course de soulèvement (H), la pièce (12, 109) est entraînée seulement par le premier moyen d'entraînement (11, 103),
    - et notamment, la pièce (12, 109) constitue un composant (56) du premier moyen d'entraînement (11, 103), et elle est notamment réalisée sous la forme d'une tige de piston (12, 109).
  4. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    les moyens d'entraînement (11, 14; 103, 102) qui forment l'entraînement hybride (52), ont des caractéristiques différentes en particulier, pour le mode d'entraînement et/ou la force d'entraînement.
  5. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    la pièce (12, 109) est abaissée par le second moyen d'entraînement (14, 102), notamment contre une force antagoniste réduite, exercée par le premier moyen d'entraînement (11, 103).
  6. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    - l'application de la pression et le mouvement du support de platine (4), sont assurés par un ou plusieurs modules de coussin de serre-flan (9),
    - les modules de coussin de serre-flan (9) comportent au moins deux moyens d'entraînement (11, 14; 103, 102) dont la direction de la force et la direction du mouvement, se situent sur un axe (a),
    - notamment, les modules de coussin de serre-flan (9) se composent d'un moyen d'entraînement électrique (14) et d'un moyen d'entraînement hydraulique (11), ou
    - les modules de coussin de serre-flan (101) se composent d'un moyen d'entraînement électrique (102) et d'un ressort (103),
    - le ressort (103) étant notamment un vérin à azote, et
    - notamment, le vérin à azote (103) a une chambre de pression, fermée,
    - la quantité d'azote étant variable, et
    - en particulier, le vérin à azote (103) peut être relié à un accumulateur basse pression (5) et/ou à un accumulateur haute pression (106).
  7. Dispositif de coussin de serre-flan selon la revendication 6,
    caractérisé en ce que
    - les modules de coussin de serre-flan (9, 101) se composent d'un moyen d'entraînement électrique (102) et d'un ressort (103),
    - le ressort (103) étant notamment un ressort mécanique.
  8. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    - pendant l'opération de transformation, entre le second moyen d'entraînement (14, 102), notamment réalisé sous forme de moyen d'entraînement électrique (14, 102) et la tige de piston (12, 109), il n'y a pas de liaison par la forme dans la direction de déplacement opposée à celle du poussoir (2),
    - de préférence l'entraînement électrique (14, 102) agit sur une collerette (19) de la tige de piston (12) du vérin (11, 103), notamment d'un vérin hydraulique (11), d'un vérin à azote (103) ou d'un vérin à ressort mécanique.
  9. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    le second moyen d'entraînement (14, 102), notamment réalisé comme entraînement électrique (14, 102) agit par l'intermédiaire d'une transmission à billes ou à poulies (17, 18, 110) sur la collerette (19) de la tige de piston (12) ou le second moyen d'entraînement (14, 102), notamment réalisé sous la forme d'un entraînement électrique (14, 102), est notamment un moteur à arbre creux ou en particulier un moteur-couple.
  10. Dispositif de coussin de serre-flan selon l'une des revendications 3 à 9,
    caractérisé en ce que
    la tige de piston (12, 109) comporte un profil cannelé (13) qui évite la rotation de la tige de piston (12, 109), autour de son axe longitudinal (a) par l'intermédiaire d'un moyen antirotation (20, 111).
  11. Dispositif de coussin de serre-flan selon l'une des revendications 6 à 9,
    caractérisé en ce que
    - les modules de coussin de serre-flan (9) agissent par l'intermédiaire d'un balancier (7) commun et par des poussoirs (6) sur le support de platine (4), ou
    - de préférence, les modules de coussin de serre-flan (9) agissent sur le support de platine (4) par l'intermédiaire d'au moins deux segments de balancier et des poussoirs (6), ou
    - de préférence les modules de coussin de serre-flan (9) agissent sur le support de platine (4) par des poussoirs (6), ou
    - de préférence les modules de coussin de serre-flan (9) agissent directement sur le support de platine (4),
    - et notamment, le support de platine (4) est réalisé sous la forme d'un support de platine à élasticité par segments.
  12. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    - les module de coussin de serre-flan (9) sont intégrés dans une ou plusieurs tables d'étirage,
    - et notamment, les fonctions d'entraînement électriques de plusieurs modules de coussin de serre-flan (9), sont réalisées par un moyen d'entraînement commun passant par des moyens de transmission de mouvements appropriés, et
    - en particulier, les fonctions d'entraînement hydrauliques de plusieurs modules de coussin de serre-flan (9) sont réalisées par un moyen de transmission de mouvements appropriés à partir d'un moyen d'entraînement commun.
  13. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    les fonctions d'entraînement électriques de plusieurs modules de coussin de serre-flan (9) sont commandées ou régulées séparément et/ou en commun et/ou de préférence les fonctions hydrauliques d'entraînement de plusieurs modules de coussin de serre-flan (9), sont commandées ou régulées séparément et/ou en commun.
  14. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    les modules de coussin de serre-flan (9), permettent un verrouillage du dispositif de coussin de module de serre-flan dans le sens de la montée par l'intermédiaire d'un frein de sécurité de pression de freinage (16).
  15. Dispositif de coussin de serre-flan selon l'une des revendications précédentes,
    caractérisé en ce que
    des soupapes de sécurité, directionnelles, dans la conduite de sortie (24) du cylindre (11, 103), évitent des mouvements d'abaissement rapides du dispositif de coussin de serre-flan.
EP07856049A 2006-11-30 2007-11-30 Dispositif de coussin hydraulique à entraînement hybride modulaire Not-in-force EP2104578B1 (fr)

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DE102006057053 2006-11-30
DE102007016359 2007-04-03
PCT/DE2007/002167 WO2008064669A2 (fr) 2006-11-30 2007-11-30 Dispositif de coussin hydraulique à entraînement hybride

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EP2104578A2 EP2104578A2 (fr) 2009-09-30
EP2104578B1 true EP2104578B1 (fr) 2010-04-28

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CN (1) CN101594946B (fr)
AT (1) ATE465826T1 (fr)
DE (1) DE502007003635D1 (fr)
ES (1) ES2343700T3 (fr)
WO (1) WO2008064669A2 (fr)

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CN105057432A (zh) * 2015-08-31 2015-11-18 西安交通大学 一种交流伺服同步电机驱动行星滚柱丝杠的液压拉伸垫

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CN102166595A (zh) * 2010-12-30 2011-08-31 一重集团大连设计研究院有限公司 可用于压力机拉伸气垫的下限位装置
WO2016054731A1 (fr) * 2014-10-06 2016-04-14 Magna International Inc. Adaptateur pour support de matrice de presse d'estampage conçu pour s'adapter à différents motifs de goupilles de bloqueur de matrice
CN104454783A (zh) * 2014-12-24 2015-03-25 济南二机床集团有限公司 压力机单顶冠单主缸纯气式拉伸垫结构
JP6059291B2 (ja) * 2015-06-03 2017-01-11 アイダエンジニアリング株式会社 プレス機械のダイクッション装置
TWI625176B (zh) * 2017-07-28 2018-06-01 連傑油壓工業股份有限公司 節能液壓成形設備
CN107366656B (zh) * 2017-09-02 2018-11-16 建湖县恒昌液压机械有限公司 一种无级闭锁结构及其闭锁柱的制作方法
CN107671164A (zh) * 2017-10-30 2018-02-09 天津普越金属制品有限公司 冲压机反冲底座及其制造工艺
EP3736061B1 (fr) * 2019-05-06 2024-08-07 Lapmaster Wolters GmbH Système de découpage fin et son procédé de fonctionnement
JP2022112954A (ja) * 2021-01-22 2022-08-03 本田技研工業株式会社 ダイクッション装置

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DE4100716A1 (de) * 1991-01-14 1992-07-16 Erfurt Umformtechnik Gmbh Einrichtung zum blechhalten in einfachwirkenden pressen
CN100377866C (zh) * 2003-11-11 2008-04-02 一重集团大连设计研究院 多连杆机械压力机
JP4516785B2 (ja) * 2004-06-18 2010-08-04 株式会社小松製作所 ダイクッション装置
DE102004030678B4 (de) * 2004-06-24 2006-03-30 Müller Weingarten AG Ziehkissen-Vorrichtung mit Hybrid-Antrieb
DE102006010648A1 (de) * 2005-03-07 2006-09-14 Müller Weingarten AG Ziehkissen-Vorrichtung mit NC-Antrieb und hydraulischem Polster
JP5129731B2 (ja) * 2005-03-07 2013-01-30 ミューラー ワインガルテン アーゲー Ｎｃ駆動装置と液圧パッドを装備したダイクッション
JP4820564B2 (ja) * 2005-03-16 2011-11-24 株式会社小松製作所 ダイクッション制御装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105057432A (zh) * 2015-08-31 2015-11-18 西安交通大学 一种交流伺服同步电机驱动行星滚柱丝杠的液压拉伸垫
CN105057432B (zh) * 2015-08-31 2017-01-25 西安交通大学 一种交流伺服同步电机驱动行星滚柱丝杠的液压拉伸垫

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WO2008064669A3 (fr) 2008-08-14
DE502007003635D1 (de) 2010-06-10
ATE465826T1 (de) 2010-05-15
CN101594946A (zh) 2009-12-02
CN101594946B (zh) 2013-05-01
ES2343700T3 (es) 2010-08-06
WO2008064669A2 (fr) 2008-06-05
EP2104578A2 (fr) 2009-09-30

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