EP2995446B1 - Presse et procede pour déformer des pièces métalliques - Google Patents

Presse et procede pour déformer des pièces métalliques Download PDF

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Publication number
EP2995446B1
EP2995446B1 EP15184429.7A EP15184429A EP2995446B1 EP 2995446 B1 EP2995446 B1 EP 2995446B1 EP 15184429 A EP15184429 A EP 15184429A EP 2995446 B1 EP2995446 B1 EP 2995446B1
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EP
European Patent Office
Prior art keywords
press
core pin
mould
axis
movement element
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EP15184429.7A
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German (de)
English (en)
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EP2995446A1 (fr
Inventor
Giuliano Baglioni
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Automazioni Industriali Srl
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Automazioni Industriali Srl
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Publication of EP2995446A1 publication Critical patent/EP2995446A1/fr
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    • 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
    • B30B1/103—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 screw means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/02—Special design or construction
    • B21J9/027—Special design or construction with punches moving along auxiliary lateral directions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B7/00—Presses characterised by a particular arrangement of the pressing members
    • B30B7/04—Presses characterised by a particular arrangement of the pressing members wherein pressing is effected in different directions simultaneously or in turn

Definitions

  • the present invention relates to the field of presses, and in particular the field of hot presses of metal pieces such as billets and the like, for making elements having one or more surface deformations, or holes with variable depth and possibly passing through the whole piece.
  • Such core pins are known to be hydraulically controlled, preferably through a cylinder/piston arrangement, since this arrangement is deemed the more suitable to ensure powers needed to carry out the piece deformation.
  • toggle-lever presses (knuckle joint presses) are known, wherein a piston acts on the hinge point between connecting rod and crank of a respective connecting rod and crank arrangement, and wherein such a piston is hydraulically driven, for example through a hydraulic jack, the connecting rod controls the core pin movement and the crank is hinged to the machine frame.
  • thermodynamic characteristics of the oil, or in general of the liquid employed for operating the hydraulic press can vary with time, for example even within a single day. Therefore, in view of the preceding, in response to the same command, the press movement can show variations over time, and thus errors, in component displacement.
  • the devices of the known art do not ensure a precise repetition of operations for deforming the billet in subsequent cycles, whereby the resulting pieces do not feature mutually homogeneous characteristics, with apparent drawbacks.
  • toggle-lever presses of the known art frequently operate with several toggle arrangements and respective core pin or punch per every single mould, so that to make several holes or surface deformations at the same time on every piece.
  • means of the known art for simultaneously controlling the movement of several core pins through hydraulic drives are thus even more complex, in addition to have remarkable weight and bulk.
  • JP H07-195197 discloses a toggle-lever machine for punching, bending and cutting a sheet.
  • Object of the present invention is the implementation of a press for making surface deformations or holes on a billet or similar metal semifinished product, that overcomes the problems of the known art.
  • object of the present invention is the implementation of a press of the afore mentioned type that is cheap and allows at the same time a high level accuracy machining.
  • a press for deforming, and in particular for surface deforming and/or boring, metal pieces having the shape of billets or similar semifinished products comprises at least one mould for the metal piece, and at least one deforming core pin, or punch, that can be reversibly and at least partially inserted into the mould to deform the metal piece.
  • the core pin is arranged on a ram movable along a first axis, and such a ram is connected through a connecting rod to a movement element reciprocating at least axially along a second axis incident to the first axis.
  • the second movement element is electrically driven. Thanks to the present invention, a simple and accurate control of the core pin position can be carried out through a system being moreover compact.
  • the described system further allows an effective power transmission to the core pin (or pins), that therefore is able to carry out the deformation of the metal piece so that to make an opening, surface deformation or hole, on the same.
  • the electric drive allows exerting high level control over the position of the movement element and thus of the core pin, so that homogeneous pieces in subsequent machine operating cycles can be shaped.
  • the mould lubrication system can operate more effectively, being able to work correctly and with constant behavior in different and subsequent operations of the press.
  • the mould lubrication system is electrically driven and controlled.
  • the timing and amount in which the lubricant has to be fed to the mould during the operations of material deformation inside the latter can be controlled, preferably by a closed-loop control, depending on the position of the core pin and/or the second axis.
  • the Proprietor found that the moulds of the presses according to the present invention have a service life up to 6 - 8 times longer than the moulds of the known art.
  • a crank connects the movement element and the connecting rod, through a shared hinging constraint, to a bearing whose position can be adjusted, so that to substantially implement a toggle.
  • the bearing is movable, preferably along at least one third axis, to allow the ram kinematics and dynamics to be precisely adjusted. Such a movement is preferably further obtained through an electric drive.
  • the main movement operations of the press can be carried out by the first movement element whereas, through the operation of the adjustable bearing, precise adjustment operations of the travel of the ram carrying the core pin or punch can be carried out.
  • every single core pin can be adjusted precisely and independently so that to make a correct deformation on the piece inside the mould, typically a perforation or surface deformation, in a repeatable way over time.
  • the speed profile with which the core pin operates can be accurately controlled, i.e. the core pin speed can be adjusted instant by instant during the path towards the mould and inside the same.
  • the movable bearing has a first tilted surface
  • an electric motor controls the movement of at least one second tilted and sliding surface, which is engaged with the first tilted surface, so that to precisely, and with small displacements, adjust the position of the movable bearing and thus, due to the described kinematic system, the position of the core pin.
  • the core pin displacement can be controlled upon preset programs.
  • one or more sensors can detect the position of one or more elements such as the ram, the movable bearing, etc., in order to perform a closed-loop control on the core pin position.
  • a press 1 for deforming metal pieces typically the so called billets or similar semifinished products, comprises one or more moulds 3 inside which the metal pieces are shaped, for example engraved or bored pieces.
  • the mould 3 typically comprises two portions 3a, 3b, at least one of which movable to selectively open and close the mould.
  • the press has a fixed lower portion 3a of the mould 3 and a movable portion 3b integral with a carriage 15 axially movable along guides 16 in a direction towards/away from the lower portion 3a of the mould. Also the drive of the carriage 15 is electrically controlled.
  • the press 1 there are one or more core pins, or punches 2, to be forcedly inserted into the mould 3, partially or wholly, in order to plastically deform the billet, thereby making respective surface deformations or bores, for example through bores, into the same.
  • a core pin, or punch 2 is visible as integrally mounted on a ram 4 whose motion is generally a translation along a first axis A1.
  • a first axis A1 especially visible in figure 1
  • the press 1 is arranged in an operative configuration, such an axis A1 (especially visible in figure 1 ) is arranged horizontally, albeit the possibility of mounting the press 1 so that the aforesaid axis A1 is vertical or oriented according to any direction selected upon the operative needs the press 1 has to meet, is not excluded.
  • Such a ram 4 is therefore an element of the press 1 slidingly mounted in a respective seat or on a specificguide that is operated in reciprocating translatory motion in order to insert and release the core pin 2 in the mould 3, the core pin 2 being integrally constrained, as mentioned, typically at one end thereof in a single piece or through proper constraints to said ram 4.
  • a first typology of ram 4 mounting a single core pin 2 i.e. the typology of ram shown in detail in figures 1 - 3
  • a second typology of ram 4a carrying two core pins 2a, 2b can be observed.
  • the press 1 has a movement element 5, typically a slider, generally moving with reciprocating rectilinear motion along a second axis A2 tilted with respect to the axis A1, and thus incident thereto.
  • a movement element 5 typically a slider, generally moving with reciprocating rectilinear motion along a second axis A2 tilted with respect to the axis A1, and thus incident thereto.
  • the tilt of such an axis A2 is equal to about 90 degrees, albeit other tilts are obviously possible.
  • the tilt of the axis A2, with respect to the axis A1 slightly changes over time in operative condition, so as to allow the movement element 5 complying with the movement of the core pin along the axis A1, and in particular of the hinge 9, and avoiding jams.
  • the axis A2, along which the movement of the movement element 5 occurs in operative condition is slightly swinging, in a controlled way.
  • the movement element 5 can be made through any tool known in the art that is able to give a predefined force along at least one rectilinear axis A2.
  • the movement element 5, as it will be better defined in the following, is indeed driven through a convenient actuator in order to provide, albeit indirectly, a thrust to the ram 4 and thus to allow the latter to apply a predefined force along the afore mentioned axis A1.
  • a connecting rod 6 i.e. a substantially rod-shaped component designed to be subjected to a roto-translation during the operation of the press 1, operatively connects the movement element 5 to the ram 4.
  • the connecting rod 6 is hinged at the ends thereof to the ram 4 and to the movement element 5, respectively.
  • connecting rod 6 could be constrained to the ram 4, and/or to the movement element 5, according to at least one rotation constraint with a possible translation component due to possible clearances made among the pieces.
  • the connecting rod 6 constrains, or at least operatively connects, the movement element 5 to the ram 4 so that a movement of the ram 4 along the first axis A1 corresponds to a movement of the movement element 5 along the second axis A2 and, thus, a force applied to the movement element 5 along the axis A2 is transmitted to the ram 4 and therefore to the core pin 2, along the first axis A1.
  • the movement element 5 is electrically controlled in its own reciprocating movement thanks to an electric drive preferably comprising an electric motor, for example of brushless type, for example of the typology known in the art such as torque motors, albeit other electric drives can be used as well.
  • the movement element 5, in the form of a slider translatable along the axis A2 in a preferably swinging way as mentioned above, is integral to a worm 7 screwing along a seat 14 that is made as a threaded sleeve or hole (nut screw) at least partially surrounding the worm 7, and rotated by a first electric motor M1.
  • the rotation of the seat 14 causes a translation along the second axis A2 of the worm 7 and the first movement element 5 connected thereto.
  • the press 1 also has a crank 8 to operatively and functionally connect the core pin 2 to a bearing 10 whose position, as it will be seen, is preferably and advantageously adjustable along at least one third axis A3 of the press 1.
  • crank 8 in the present invention herein shown, is at least rotatably constrained at one end thereof to the afore mentioned bearing 10 and is also at least rotatably constrained at its other end to the same constraint, in this case the latter being in common and present between the movement element 5 and the connecting rod 6.
  • the crank 8 is hinged at one end thereof to the hinge 9, that in turn constrains the connecting rod 6 and the movement element 5 one to another. It has to be noted that such constraints between the crank 8, the connecting rod 6 and the movement element 5 can have clearances in order to allow just very little translations among such components.
  • the bearing 10 could be integral with the press 1, so that to serve as an additional guide for the ram 4 and limit the stresses imposed to the afore described kinematic system, so that to implement a conventional toggle.
  • the position of the bearing 10 can be adjusted, i.e. it is movable, preferably with a reduced degree of freedom so that, in addition to the afore mentioned structural function, it can allow a further adjustment of kinematics and dynamics of the respective core pin 2.
  • the bearing 10 is preferably movable in a controlled way along at least one third axis A3, this axis being defined by a suitable seat or guide of the frame of the press 1 and being preferably rectilinear and coincident with, or at least parallel to, the first axis A1.
  • the position adjustment of the movable bearing 10 is aimed to allow accurate adjustments of the applied force and the travel run by the core pin 2, and that such an adjustment can be carried out before or during translationally driving the core pin 2, since the respective movement element 5 is driven, that causes the plastic deformation of the billet in the mould 3.
  • the position of the bearing 10 of the crank 8 is adjustable via a movable bearing 10 electrically controlled in its own movement, i.e. through an electric actuator for example constituted by a brushless electric motor of torque type, and by a respective kinematic system for transmitting the motion from the motor drive shaft to the bearing 10 itself.
  • the drive responsible for the adjusted movement of the bearing 10 comprises a worm 11 rotatable thanks to the action of a second electric motor M2.
  • the worm 11 reciprocatingly controls, depending on its rotation way, the translation of at least one first wedge-shaped body provided with a tilted surface 12a, having a sleeve-like portion in turn threaded (nut screw) and at least partially surrounding the worm 11.
  • the thread of the sleeve of the body provided with the first tilted surface 12a couples (meshes) with the thread of such a worm 11, so that such tilted surface 12a axially translates along the axis of the worm 11.
  • Such a first tilted surface 12a further couples by interference and reciprocally slides with a second tilted surface 10a belonging to the movable bearing 10 and being tilted in a way opposed to the tilt of the tilted surface 12a.
  • the first surface 12a slides with respect to the second surface 10a so that, according to known principles of the tilted plane, an axial translation of the movable bearing 10, in a direction typically perpendicular to the axis of the worm 11, corresponds to a relative sliding between the surfaces 12a and 10a along the aforesaid third axis A3.
  • the constraint between the two surfaces 12a and 10a can be of simple rest. However, such a solution allows the displacement of the movable bearing 10 in a single direction, i.e. the thrust direction of the first surface 12a with the second surface 10a.
  • the first surface 12a and the second surface 10a are coupled through a carriage-track system.
  • the first surface 12a has a groove not shown in the figures inside which a projection 13, integral to the second tilted surface 10a, can be coupled in a constrained way so as to slide along a single direction.
  • the second surface 10a could have a groove and the first surface a projection.
  • wheels on one of the two surfaces could be constrained so as to slide along a path defined on the other surface, etc.
  • such an angle ⁇ is preferably comprised between 45° and 90°, and even more preferably between 60° and 90°. In the embodiment of the present invention shown in the figures, the angle ⁇ is equal to about 78 degrees.
  • the travel of the movable bearing 10 is shorter than the travel of the first tilted surface 12a with respect to the worm 11, thus making easier to carry out small displacements of the mentioned movable bearing 10 and thus obtain a precise adjustment of kinematic and dynamic conditions upon which the ram 4, and thus the core pin 2, act.
  • a movable body is equipped with a pair of first surfaces 12a and 12b and the movable bearing 10 is provided with a respective pair of second surfaces 10a and 10b.
  • the first surfaces 12a and 12b can be reciprocally moved closer or away one another, so that to act on the respective second tilted surfaces 10a and 10b and thus cause a translation of the movable bearing 10 in the direction denoted as A3.
  • the worm 11 has two thread typologies 11a and 11b being counterwise one another.
  • the thread 11a can for example be a right-handed thread, whereas the thread 11b can consequently be a left-handed thread (or vice versa).
  • the two thread typologies 11a and 11b each couple with a respective tilted surface 12a or 12b, so that a displacement of the tilted surfaces 12a and 12b in a way opposite one to another corresponds to a rotation of the worm 11 in a single way.
  • the electric motor M1 controls the translation displacement of the movement element 5.
  • the electric motor M1 controls the rotation of the seat 14 and thus, by means of the coupling of the respective threads, the translation of the screw 7 carrying integrally the movement element 5 along the axis A2.
  • the electric motor M1 can be programmed so that the speed profile is deemed optimal for every single core pin 2 that has to interact with the given metal piece contained inside the mould 3.
  • the second electric motor M2 can precisely adjust the position of the core pin 2, simultaneously with the action of the first electric motor M1 or, preferably, when the motor M1 is not operative for moving the movement element 5.
  • the electric motor M2 controls the rotation of the worm 11, so as to move the first tilted surfaces 12a, 12b closer or away one another. Due to the afore described constraint, thanks to the opposed tilted surfaces 10a, 10b the bearing 10 is provided with, a movement of the movable bearing 10 along the axis A3 corresponds to such a motion.
  • Such a motion causes, due to the constraint imposed by the crank 8, a displacement even if reduced of the movement element 5 along the second axis A2 that, in turn and due to the connecting rod 6, displaces the ram 4 and correspondingly the core pin 2 connected thereto.
  • the operation of the electric motors M1 and M2 can be controlled by an automatic controller known in the art, depending on preset programs.
  • sensors can detect the position of one or more elements such as the ram 4, the movable bearing 10, the movement element 5, the screw 7, etc.
  • the position of the core pin 2 can be controlled depending on data detected by the mentioned sensors.
  • the electric drive of the core pins 2 allows phase shifting the movement of the core pins, specifically delaying or advancing the movement of one core pin with respect to another.
  • the electric motor M2 and in general an electric drive in charge for the movement of the movable bearing 10 of the crank 8, has proven to be particularly effective in carrying out an accurate adjustment of the position, and especially of kinematic and dynamic conditions, of the core pin 2, whereby the Proprietor believes that there can be considerable advantages also in innovative embodiments of a toggle-lever press in which the electric motor M2, or any other electric drive, is in charge for the adjustment of the position of the movable bearing 10 of the crank 8 of the same toggle, also in a conventional toggle-lever press having non-electric main drive (i.e. equivalent to the motor M1), but for example hydraulic or pneumatic.
  • non-electric main drive i.e. equivalent to the motor M1
  • the ratio between the travel of the body provided with the afore said first surface 12a and the travel of the movable bearing 10 can be adjusted.
  • errors in positioning the latter become negligible errors of the movable bearing.
  • the first tilted surface has an angle of 85°
  • an error of 1 cm in positioning the first tilted surface 12a along the respective screw with respect to the intended position becomes a positioning error of the core pin of 1 cm / tan (85°), i.e. lower than one millimeter.
  • a second non-electric motor M2 for example a hydraulic one, although subjected to positioning errors, can carry out a sufficiently precise adjustment of the position of the bearing 10 and, thus ultimately, of the core pin 2, thanks to the described system that allows reducing the positioning error.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Claims (9)

  1. Presse (1) pour déformer au moins une pièce métallique ayant initialement la forme d'une billette ou d'un produit semi-fini similaire, comprenant au moins un moule (3) pour ladite pièce métallique et au moins une broche centrale déformante (2) qui peut être insérée dans ledit moule (3) de manière réversible et au moins en partie pour déformer de manière plastique ladite pièce métallique, ladite broche centrale (2) étant agencée sur un plongeur (4) mobile le long d'un premier axe, ledit plongeur (4) étant raccordé via une tige de liaison (6) à un élément de déplacement (5) effectuant un mouvement de va-et-vient au moins axialement le long d'un deuxième axe incident audit premier axe, ledit élément de déplacement (5) étant entraîné par voie électrique, dans laquelle une manivelle (8), encastrée à une extrémité dans un palier respectif (10), est encastrée pour tourner au moins librement à son autre extrémité sur ledit élément de déplacement (5) et ladite tige de liaison (6), sous la contrainte entre ledit élément de déplacement (5) et ladite tige de liaison (6), afin de définir un agencement à genouillère, dans laquelle la position dudit palier (10) de la manivelle (8) est réglable via un entraînement électrique de manière à effectuer au moins une translation de manière contrôlée le long d'un troisième axe, dans laquelle ledit palier de manivelle (10) comprend un couple de secondes surfaces inclinées (10a, 10b) et un moteur électrique commande le déplacement d'un couple de premières surfaces inclinées (12a, 12b) qui sont engagées en mode coulissant avec ledit couple de secondes surfaces inclinées (10a, 10b), caractérisée en ce que deux corps en forme de cales pourvus desdites premières surfaces inclinées (12a, 12b) ayant une partie en forme de douille taraudée et entourant au moins en partie une vis sans fin (11) sont fournies et entraînées par ladite vis sans fin rotative (11) ayant un premier et un second filet (11a, 11b), lesdits premiers et seconds filets (11a, 11b) étant en sens contraire l'un de l'autre et pouvant se coupler tous deux avec une première surface inclinée (12a, 12b) dudit couple desdites premières surfaces inclinées de sorte que la rotation de ladite vis sans fin (11) fasse que lesdites premières surfaces inclinées (12a, 12b) se rapprochent ou s'écartent l'une de l'autre.
  2. Presse (1) selon la revendication 1, dans laquelle ledit troisième axe est parallèle audit premier axe ou coïncide avec celui-ci.
  3. Presse (1) selon l'une quelconque des revendications précédentes, dans laquelle ledit élément de déplacement (5) comprend un coulisseau se déplaçant avec un mouvement rectiligne de va-et-vient et qui est articulé à une extrémité de la tige de liaison (6) et ladite presse (1) est une presse à levier à genouillère.
  4. Presse (1) selon l'une quelconque des revendications précédentes, dans laquelle ledit élément de déplacement (5) comprend un filet qui peut être couplé en service à un élément rotatif fileté de manière complémentaire et qui peut être actionné par un moteur à entraînement électrique.
  5. Presse (1) selon la revendication 4, dans laquelle ledit filet dudit élément de déplacement (5) est un filet carré.
  6. Presse (1) selon l'une quelconque des revendications précédentes, comprenant un circuit de lubrification comportant au moins un canal de lubrification en communication fluidique avec ledit moule (3) et au moins des moyens de pression électriques pour un liquide de lubrification.
  7. Procédé de fabrication d'une pièce métallique à partir de billettes ou de produits semi-finis similaires via une presse (1) selon une ou plusieurs des revendications précédentes, comprenant l'étape consistant à :
    a) mouler extérieurement ladite billette dans ledit moule (3) ;
    b) déformer de manière plastique ladite billette via l'insertion réversible de ladite broche centrale (2) dans ledit moule (3) ;
    dans lequel le trajet de ladite broche centrale (2) vers ledit moule (3) et à l'intérieur dudit moule est commandé par un entraînement électrique opérant sur ledit élément de déplacement (5) qui, à son tour, actionne ladite broche centrale via une tige de liaison (6), dans lequel ladite étape (a) comprend à son tour les étapes consistant à :
    a1) effectuer un positionnement générique de ladite broche centrale via un premier moteur électrique ;
    a2) démarrer un second moteur électrique de manière à effectuer un réglage précis de la position de ladite broche centrale (2).
  8. Procédé selon la revendication 7, dans lequel ladite étape b) comprend le réglage de manière contrôlée du moment de départ de déplacement d'une première broche centrale (2) par rapport au moment de départ de déplacement décalé en phase d'une broche centrale supplémentaire et différente (2).
  9. Procédé selon la revendication 7 ou 8, dans lequel, avant et/ou après ladite étape a) et/ou avant et/ou après ladite étape b), la presse (1) effectue l'étape supplémentaire consistant à :
    c) lubrifier ledit moule (3) via un circuit de lubrification comprenant au moins un canal de lubrification en communication fluidique avec ledit moule (3) et au moins des moyens de pression électriques pour un liquide lubrifiant en fonction de la position de ladite broche centrale (2) le long dudit axe A1 et/ou en fonction de l'ouverture du moule.
EP15184429.7A 2014-09-09 2015-09-09 Presse et procede pour déformer des pièces métalliques Active EP2995446B1 (fr)

Applications Claiming Priority (1)

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ITMI20141558 2014-09-09

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EP2995446A1 EP2995446A1 (fr) 2016-03-16
EP2995446B1 true EP2995446B1 (fr) 2018-12-05

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106925704B (zh) * 2017-05-05 2019-01-11 桐乡市凯盛精密机械有限公司 冷锻冲床
WO2023031767A1 (fr) * 2021-08-30 2023-03-09 Thorside S.R.L. Presse pour forgeage à chaud de composants métalliques

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2039644A1 (de) * 1970-08-10 1972-03-23 Schuler Gmbh L Vorrichtung zum Einstellen des Abstandes zwischen dem Oberwerkzeug und dem Stoessel einer Presse

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2458796A1 (de) * 1974-12-12 1976-06-16 Wilhelm Platz Presse, vorzugsweise rollen-spindelpresse
JPH07195197A (ja) * 1993-12-29 1995-08-01 Chichibu Fuji:Kk 薄板加工装置
DE102006034201A1 (de) * 2006-07-24 2008-02-07 Siemens Ag Presse

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2039644A1 (de) * 1970-08-10 1972-03-23 Schuler Gmbh L Vorrichtung zum Einstellen des Abstandes zwischen dem Oberwerkzeug und dem Stoessel einer Presse

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EP2995446A1 (fr) 2016-03-16

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