EP1252010B1 - Presse - Google Patents

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Publication number
EP1252010B1
EP1252010B1 EP01905662A EP01905662A EP1252010B1 EP 1252010 B1 EP1252010 B1 EP 1252010B1 EP 01905662 A EP01905662 A EP 01905662A EP 01905662 A EP01905662 A EP 01905662A EP 1252010 B1 EP1252010 B1 EP 1252010B1
Authority
EP
European Patent Office
Prior art keywords
press according
tappet
machine
cylinder unit
fixed
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.)
Expired - Lifetime
Application number
EP01905662A
Other languages
German (de)
English (en)
Other versions
EP1252010A1 (fr
Inventor
Hans-Rudolf Gubler
Johannes Haack
Ernst Rytz
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.)
Feintool International Holding AG
Original Assignee
Feintool International Holding AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Feintool International Holding AG filed Critical Feintool International Holding AG
Publication of EP1252010A1 publication Critical patent/EP1252010A1/fr
Application granted granted Critical
Publication of EP1252010B1 publication Critical patent/EP1252010B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8824—With provision for dynamic balance
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8858—Fluid pressure actuated
    • Y10T83/8864—Plural cylinders

Definitions

  • the invention relates to a fine blanking press for producing fine cutting parts of a metal strip or for preforming a part by means of a tool, one part of which is attached to an upper platen and another part to a lower platen, wherein one of the platen is associated with a ram, the is supported by at least one plunger drive piston unit against a machine-fixed element, which is connected via at least two guide columns fixed to an opposite, also machine-fixed element on which the other platen is arranged, wherein the plunger is displaceable along the guide columns and wherein the opposite machine-fixed element is a ring-cylinder unit assigned.
  • a fineblanking press with hydraulically coupled ring prongs and counter-holding cylinder is known.
  • a stand is provided in which columns are arranged. These pillars penetrate an upper crosshead of the stand and are there fixedly connected to a crossbar, wherein in the traverse a double acting ring-shaped cylinder is integrated.
  • a plunger is movably arranged along the columns.
  • a press of the o. G. Art is known from US-A 3,802,310.
  • the present invention is based on the object to provide a fine blanking press, wherein the stiffness forming elements of the press and the leadership of the plunger are at least partially decoupled and the effect of shear forces or moments is reduced to the leadership.
  • the one machine-fixed element is fixedly connected to the opposite machine-fixed element via machine frame plates, wherein the one machine-fixed element, the opposite machine-fixed element and the machine frame plates form an outer fixed frame which takes over the static and dynamic forces of the system.
  • two synchronously operating ram drive piston units are provided, through which the four movements "quick closing, buttons, cutting / forming, rapid return” are performed. These are clamped, double-acting cylinders. Rapid traction cylinders, as used in known presses, are no longer necessary.
  • the ram guide is preferably effected with two to four guide columns in the corner regions of the press.
  • the guide columns serve primarily the ram guide and take only tilting moments from the tool stress. In the border areas of the press load, the guide columns take over tie rod function if necessary.
  • the actual press body is formed by an upper and lower yoke and by machine frame plates, which are usually provided four machine frame plates, each having openings for a StanzstMailzu- - and removal, tool room operation and Generaleabtransport or mounting holes. This creates a compact press, in which the press body, the control of the static and dynamic stresses and the guide columns are associated with the ram guide tasks.
  • the ram guide itself takes place via at least two spaced guide bushings.
  • the walls of the ram are preferably pulled laterally so that the actual working area of the tool is between the two guide bushes. This ensures that in the working area of the tool, a motion-neutral zone is formed, so that tilting of the plunger have no negative impact on the active elements of the tool.
  • This ring cylinder unit is usually located in or on top of the upper yoke, which in turn is a double-acting cylinder with a purge.
  • the pressure force acting on a corresponding piston is transmitted via pressure bolts and pressure plates which also sit in the yoke in the tool room.
  • pressure fluid is displaced from the corresponding pressure chamber of the ring-toothed cylinder unit by means of the pressure pin and the pressure plate.
  • This pressurized fluid is transferred to preferably four compensating pistons, which stand on the lower yoke and whose piston rods act on the underside of the ram.
  • the ram drive power is supported and the displacement work of the serration function is compensated and no longer has to be subtracted from the total force as in the known presses. Presses of this design thus have about 30% higher usable press force with the same size.
  • the displacer volume of the ring cylinder unit corresponds to the volume of the compensation piston.
  • the plunger itself is associated with a Schmidthaltekraftzylinderü, which in turn is a double-acting cylinder with flushing.
  • the counter holding power cylinder unit or its cylinder sit in or under the plunger. Again, the force of the piston is transmitted via pressure pins and pressure plates by the plunger in the tool room.
  • the displaced pressure fluid is preferably fed to two to three compensation piston in an analogous manner as in the ring cylinder unit, which are preferably integrated in the cylinder of the counter holding power cylinder unit and the piston rods are supported against the lower yoke.
  • the displacement work of the counter-holding function is compensated and supports the plunger drive force.
  • the displacement volume corresponds approximately to the volume of the compensation piston.
  • the displacement work of the counter-holding function must therefore not be subtracted from the total force of the press in this application. Presses of this design thus have a total of about 40% higher usable press force than presses of known type.
  • the ring-cylinder unit and the counter-force cylinder unit both in terms of pressure and thus the force, as well as with respect to the way to be independently adjustable.
  • This also ensures a freely selectable, controlled and / or regulated plunger speed at each operating point and thus guarantees optimum part quality while at the same time optimizing the life of the active elements of the tools.
  • the inventive press P has a rigid upper yoke 1 and a rigid lower yoke 2.
  • Upper yoke 1 and lower yoke 2 are fixed outwardly by machine frame plates 3.1 and 3.2 and form the press stand.
  • the upper yoke 1 and the lower yoke 2 are connected to each other via guide columns 4.1 and 4.2, wherein preferably four guide columns are provided in the corner regions of the press.
  • the connection with the guide columns 4.1 and 4.2 can be fixed or articulated as tie rods.
  • a plunger 5 is guided, said plunger 5 per guide column having two spaced guide bushings 6.1 and 6.2.
  • parts 7 of the plunger 5 are also formed extended, so that a greater spacing of the guide bushings 6.1 and 6.2 is ensured.
  • the plunger 5 is driven by a ram drive piston unit 8.
  • a ram drive piston unit 8 Preferably, two ram drive piston units 8 are provided, which engage the ram 5 as symmetrically as possible. In the embodiment, however, only one ram drive piston unit 8 is shown.
  • the ram drive piston unit 8 is a double-acting pretensioned cylinder 9 with rinsing, in which a piston 10 separates two pressure chambers 11 and 12 from one another. From the cylinder 9 performs a piston rod 13, which is connected to the plunger 5.
  • the plunger 5 is also assigned a counter holding force cylinder unit 20.
  • the Gegenhaltekraftzylinderussi 20 has a cylinder 21 which rests on a bottom 22 of the plunger 5.
  • a piston 23 separates two pressure chambers 24 and 25 from each other, while from the piston 20 a piston rod 26 leads out of the cylinder 21 and via pressure plates 27 with pressure bolts 28.1 and 28.2 is in communication.
  • These pressure bolts 28.1 and 28.2 pass through the plunger 5 and also a tool clamping plate 29 and engage in a not shown in detail lower tool, where they support a counter-holder, as he is known in a fine blanking tool.
  • the Gegenhaltekraftzylinderussi 20 is connected via a fluid connection not shown in detail with a compensation piston 14 in connection. Its piston 15 is seated in the cylinder 21 and here again separates two pressure chambers 17 and 18 from each other. The integration in the cylinder 21 can be dispensed with hose connections.
  • a push rod 19 is connected, which supports the cylinder 21 of the Gegenhaltekraftzylinderü 20 and is supported against the lower yoke 2.
  • a piston 32 separates two working spaces 33 and 34 from each other.
  • a piston rod 35 leads to a pressure plate 36, which in turn via pressure pins 37.1, 37.2 and 37.3 after passing through a tool clamping plate 38 with a serrated plate of a tool not shown in detail, as is also known from the prior art.
  • the ring-cylinder unit 30 is in fluid communication with at least one further compensation piston 39, which is seated on the lower yoke 2 with a corresponding cylinder housing 40.
  • a piston 41 in turn separates two working chambers 42 and 43, wherein a piston rod 44 connected to the piston 41 leads out of the cylinder 40 and is connected to the underside 22 of the plunger 5.
  • a tool as shown for example in "fineblanking" Manual for Practice, 2nd edition, 1977, page 85 ff., Essentially consists of an upper tool part and a lower tool part.
  • the upper tool part has a retrograde annular serrated plate with a serration surrounding a fixed cutting die. Opposite the cutting punch is a compliant ejector in the lower tool part Assigned (counter-holder), which in turn is surrounded by a fixed cutting plate.
  • the ring prong penetrates into the material of a punching strip and surrounds the part to be cut out.
  • the workpiece to be cut out is clamped between punch and ejector (counterholder).
  • the ram force now begins to cut out the workpiece, at the same time the annular serrated plate is displaced back against the ring-tooth force, and the ejector is displaced against the counter-holding force by the material thickness of the workpiece in the die.
  • Such a tool is preferably assembled outside the press on tool change plates 29, 38 and inserted via cantilever in the machine. This is shown for example in WO97 / 35710.
  • the cantilever beams are usually part of the machine.
  • the tool change plates 29, 38 are positioned by means of hydraulically operated centering pins and clamped hydraulically via tension or pivoting tensioning clamps. This process can semi-automatic or fully automatic via the press control are set in motion.
  • the semi or fully automatic punching operation After inserting the tool package and the semi or fully automatic input of all tool and workpiece-dependent process parameters, the semi or fully automatic punching operation can be recorded.
  • the pressure chambers 11, 12 are at the beginning of a tappet stroke; 17, 18; 24, 25; 33, 34; 42, 43 under a process-related working pressure.
  • the closing movement of the plunger 5 is now initiated in the sense that, for example, the valve is opened to the pressure chamber 11.
  • the pressure chamber 12 is still under the process-related working pressure, immediately sets the closing movement.
  • any desired path / time or speed diagram can be run within the installed capacity via the valve positions to the pressure chambers 11 and 12.
  • the pressure medium is not brought to the required pressure for the required ram movement and the required ram force, but rather the pressure chamber (eg 11) is deliberately relieved and the pressure medium is flushed into the pressure chamber 12 as a useful pressure medium.
  • the plunger 5, guided on the guide columns 4.1, 4.2 moves upwards as shown.
  • the annular tooth is pressed into the stamped strip material.
  • the annular serrated plate runs back and displaces the pressure pins 37.1 to 37.3 and the pressure plate 36 upwards.
  • the piston 32 is also pushed upward, and the pressure medium in the pressure chamber 33 is displaced pressure constant.
  • the displacement of the pressure medium from the pressure chamber 33 takes place in the pressure chamber 42 of the compensation piston 39, so that the piston rod 44 is pressed against the underside 22 of the plunger 5 and supports the plunger drive force.
  • the pressure pin 28.1 and 28.2 and the pressure plate 27 are pressed by the material thickness down, also the piston 23 of the Gegenhaltekraftzylinderussi 20.
  • This pressure medium from the pressure chamber 25 is pressure constant in the Pressure chamber 18 of the compensation piston 14 displaced, so that the push rod 19 presses against the lower yoke 2 and also supports the plunger drive force.
  • the displacer volume of the ring-gear cylinder unit and the counterforce cylinder 20 corresponds to the volume of the respective compensation pistons 14 and 39, respectively.
  • a press P according to the invention can thus fine-cut an analog workpiece with about 40% of the power.
  • the machine is equipped with all sorts of automation components, such as inlet feed and outlet feed for a punching strip, lubricator, parts feeder, parts transfer device, waste-removal device, etc ..

Claims (18)

  1. Presse de découpage fin pour la réalisation de pièces de découpage fin à partir d'une bande de métal ou pour le préfaçonnage d'une pièce au moyen d'un outil dont une partie est fixée à une plaque serre-outil supérieure (38) et une autre partie est fixée à une plaque serre-outil inférieure (29), à l'une des plaques serre-outil (29) étant associé un pousseur (5) qui s'appuie, par l'intermédiaire d'au moins une unité de piston d'entraînement de pousseur (8), contre un élément (2) fixé à la machine qui est rendu solidaire, par l'intermédiaire d'au moins deux colonnes de guidage (4.1, 4.2), d'un élément opposé, également fixé à la machine (1), sur lequel est disposée l'autre plaque serre-outil (38), le pousseur (5) étant déplaçable le long des colonnes de guidage (4.1, 4.2) et à l'élément fixé à la machine opposé (1) étant associée une unité de cylindre à dents annulaires (30),
    caractérisée par le fait que
    l'un des éléments fixés à la machine (2) est rendu solidaire, par l'intermédiaire de plaques de rampe de machine (3.1, 3.2), à l'élément fixé à la machine opposé (1), l'élément fixé à la machine (2), l'élément fixé à la machine opposé (1) et les plaques de rampe de machine (3,1, .3,2) formant un cadre de presse extérieur qui absorbe les forces statiques et dynamiques du système.
  2. Presse selon la revendication 1, caractérisée par le fait que l'unité de cylindre à dents annulaires (30) est placée sur l'élément fixé à la machine opposé.
  3. Presse selon la revendication 1 ou 2, caractérisée par le fait que le pousseur (5) est supporté par au moins un piston de compensation (39).
  4. Presse selon la revendication 3, caractérisée par le fait qu'il est prévu quatre pistons de compensation (39) qui se trouvent sur l'un élément fixé à la machine (2) et s'appuient sur le pousseur (5).
  5. Presse selon la revendication 3 ou 4, caractérisée par le fait que le ou les pistons de compensation (39) sont en communication de fluide avec l'unité de cylindre à dents annulaires (30).
  6. Presse selon la revendication 5, caractérisée par le fait que le volume de refoulement de l'unité de cylindre à dents annulaires (30) correspond au volume des pistons de compensation (39).
  7. Presse selon au moins l'une des revendications 1 à 6, caractérisée par le fait qu'au pousseur (5) est associée au moins une unité de cylindre à force d'opposition (20).
  8. Presse selon la revendication 7, caractérisée par le fait que l'unité de cylindre à force d'opposition (20) est disposée sur le pousseur (5) du même côté que celui auquel aboutent également une unité de piston d'entraînement de pousseur (8) et les pistons de compensation (39).
  9. Presse selon la revendication 6, caractérisée par le fait que l'unité de cylindre à force d'opposition (20) s'appuie, par l'intermédiaire d'au moins un piston de compensation (14), contre l'un élément fixé à la machine (2).
  10. Presse selon la revendication 9, caractérisée par le fait que l'unité de cylindre à force d'opposition (20) est en communication de fluide avec le ou les pistons de compensation (14).
  11. Presse selon la revendication 10, caractérisée par le fait que le volume de refoulement de l'unité de cylindre à force d'opposition (20) correspond au volume des pistons de compensation (14).
  12. Presse selon la revendication 10 ou 11, caractérisée par le fait que le travail de refoulement des unités à dents annulaires et à force d'opposition est utilisée dans des cylindres de compensation comme force utile pour le découpage des pièces de découpage fin.
  13. Presse selon au moins l'une des revendications 1 à 12, caractérisée par le fait que l'unité de cylindre à dents annulaires (30) et l'unité de cylindre à force d'opposition (20) sont réglables indépendamment l'une de l'autre en pression et, de ce fait, en force et, de préférence, également en course.
  14. Presse selon au moins l'une des revendications 1 à 13, caractérisée par le fait que les unités de piston d'entraînement de pousseur (8) sont réalisées sous forme d'unités de cylindre à double effet à circulation du fluide de pression.
  15. Presse selon au moins l'une des revendications 1 à 14, caractérisée par le fait que le fonctionnement synchrone d'une ou de plusieurs unités de piston d'entraînement de pousseur (8) est assuré par le fait que les circuits de régulation hydromécaniques des amplificateurs hydrauliques des unités de piston d'entraînement de pousseur (8) sont entraînés, par l'intermédiaire d'une connexion fixe en rotation, par un servomoteur commun.
  16. Presse selon la revendication 15, caractérisée par le fait que par les circuits de régulation hydromécaniques des amplificateurs hydrauliques des unités de piston d'entraînement de pousseur (8) est assuré, également en cas de force et de vitesse variables, un déplacement régulé en position du pousseur (5).
  17. Presse selon la revendication 15 ou 16, caractérisée par le fait que par les circuits de régulation hydromécaniques des amplificateurs hydrauliques des unités de piston d'entraînement de pousseur (8) peuvent être omis des systèmes électroniques de mesure de course absolue supplémentaires.
  18. Presse selon au moins l'une des revendications 1 à 17, caractérisée par le fait que les forces transversales et les couples de sollicitations excentriques sont absorbés par les plaques de cadre de machine (3.1, 3.2) et que la déformation des colonnes de guidage (4.1, 4.2) par les forces transversales et les couples peut être largement évitée.
EP01905662A 2000-02-04 2001-01-11 Presse Expired - Lifetime EP1252010B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10005023 2000-02-04
DE10005023A DE10005023C2 (de) 2000-02-04 2000-02-04 Feinschneidpresse
PCT/EP2001/000256 WO2001056776A1 (fr) 2000-02-04 2001-01-11 Presse

Publications (2)

Publication Number Publication Date
EP1252010A1 EP1252010A1 (fr) 2002-10-30
EP1252010B1 true EP1252010B1 (fr) 2006-03-29

Family

ID=7629889

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01905662A Expired - Lifetime EP1252010B1 (fr) 2000-02-04 2001-01-11 Presse

Country Status (8)

Country Link
US (1) US6964225B2 (fr)
EP (1) EP1252010B1 (fr)
JP (1) JP2003521379A (fr)
AT (1) ATE321649T1 (fr)
DE (2) DE10005023C2 (fr)
ES (1) ES2261378T3 (fr)
RU (1) RU2266204C2 (fr)
WO (1) WO2001056776A1 (fr)

Families Citing this family (10)

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Publication number Priority date Publication date Assignee Title
DE10327455A1 (de) * 2003-06-18 2005-01-05 Emitec Gesellschaft Für Emissionstechnologie Mbh Verfahren und Vorrichtung zur Herstellung eines strukturierten Blechbandes
WO2007014294A2 (fr) * 2005-07-26 2007-02-01 Amberwave Systems Corporation Solutions permettant d'integrer des materiaux alternatifs dans des circuits integres
DE102005053350A1 (de) * 2005-11-07 2007-05-10 Schuler Pressen Gmbh & Co. Kg Presse mit Schnittschlagdämpfung
DE102007017595B3 (de) 2007-04-13 2009-01-02 Horst Baltschun Feinschneidpresse
AT505724B1 (de) * 2007-09-12 2010-06-15 Trumpf Maschinen Austria Gmbh Antriebsvorrichtung für eine biegepresse
DE102009017626B3 (de) * 2009-04-16 2010-12-16 Horst Baltschun Feinschneidpresse
JP5631669B2 (ja) * 2010-09-03 2014-11-26 小島プレス工業株式会社 多重プレス成形装置
ES2839073T3 (es) * 2015-07-06 2021-07-05 Feintool Int Holding Ag Dispositivo y procedimiento para el control del accionamiento principal de una prensa troqueladora de precisión
EP3831590A1 (fr) * 2019-12-05 2021-06-09 Lapmaster Wolters GmbH Coulisseau de presse pour presse de découpage fin
DE102021118550A1 (de) 2021-07-19 2023-01-19 CellForm IP GmbH & Co. KG Vorrichtung zum Bearbeiten eines Werkstücks

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DE1704183A1 (de) * 1967-12-07 1971-04-22 Lendle & Co Kg Erich Maschinen mit an Fuehrungsstangen gefuehrten heb- und senkbaren Teilen
CH551812A (de) * 1972-03-03 1974-07-31 Hydrel Ag Feinstanzpresse.
DE2653279A1 (de) * 1976-11-24 1978-06-01 Smg Sueddeutsche Maschinenbau Vorrichtung zum schutz eines werkzeugsatzes in einer hydraulischen presse
DE2739340A1 (de) * 1977-09-01 1979-03-15 Smg Sueddeutsche Maschinenbau Hydraulisch angetriebene presse
CH669748A5 (fr) * 1984-11-28 1989-04-14 Feintool Int Holding
CH668224A5 (de) * 1985-05-01 1988-12-15 Feintool Int Holding Presse mit einer oberen und einer unteren platte zum aufspannen eines werkzeugpaketes.
DE3728418A1 (de) * 1987-08-26 1989-03-09 Horst Baltschun Dynamisch vorgespannte druckmittelbetaetigte presse
US5749279A (en) * 1996-03-20 1998-05-12 General Motors Corporation Hydraulic punch actuator with centering apparatus
DE19612242A1 (de) * 1996-03-27 1997-10-02 Feintool Int Holding Presse
DE19642635A1 (de) * 1996-03-28 1997-10-02 Horst Baltschun Feinschneidpresse mit hydraulisch gekoppeltem Ringzacken- und Gegenhalterzylinder
WO1998022238A1 (fr) * 1996-11-18 1998-05-28 Sanyo Machine Works, Ltd. Structure de montage de cylindres guides de presse de bordure
DE19929163C1 (de) * 1999-06-25 2001-01-18 Feintool Internat Holding Ag L Vorrichtung zum Feinschneiden von Werkstücken aus einem Blech

Also Published As

Publication number Publication date
US6964225B2 (en) 2005-11-15
DE50109381D1 (de) 2006-05-18
ES2261378T3 (es) 2006-11-16
EP1252010A1 (fr) 2002-10-30
ATE321649T1 (de) 2006-04-15
US20030015017A1 (en) 2003-01-23
RU2266204C2 (ru) 2005-12-20
DE10005023A1 (de) 2001-08-16
JP2003521379A (ja) 2003-07-15
DE10005023C2 (de) 2002-11-21
WO2001056776A1 (fr) 2001-08-09

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