EP0696960B1 - Press-driven tool module, in particular press-driven cross-punching or bending unit - Google Patents

Press-driven tool module, in particular press-driven cross-punching or bending unit Download PDF

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Publication number
EP0696960B1
EP0696960B1 EP19930908821 EP93908821A EP0696960B1 EP 0696960 B1 EP0696960 B1 EP 0696960B1 EP 19930908821 EP19930908821 EP 19930908821 EP 93908821 A EP93908821 A EP 93908821A EP 0696960 B1 EP0696960 B1 EP 0696960B1
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EP
European Patent Office
Prior art keywords
working
cylinder
tool module
module according
tool
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
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EP19930908821
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German (de)
French (fr)
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EP0696960A1 (en
Inventor
Wolfgang Katz
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Danly Corp
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Danly Corp
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, 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
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00Shaping by press-cutting; Perforating
    • B21D28/002Drive of the tools
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, 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
    • B30B1/007Presses, 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 using a fluid connection between the drive means and the press ram
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, 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
    • B30B1/32Presses, 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 plungers under fluid pressure
    • YGENERAL 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
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00Cutting
    • Y10T83/869Means to drive or to guide tool
    • Y10T83/8776Constantly urged tool or tool support [e.g., spring biased]
    • Y10T83/8785Through return [noncutting] stroke

Definitions

  • the invention relates to a press-driven tool module, in particular a press-driven transverse punching or bending unit according to the preamble of claim 1.
  • Comparable tool modules are known, for example, from the "MILFAB” brochure from Danly Deutschland GmbH. They have a plunger to which a tool, for example a punching or bending tool, can be attached.
  • the tappet is slidably mounted in a guide bush of a base body. The direction of movement is through the The arrangement of the guide bush is predetermined and runs horizontally.
  • a helical spring is attached either inside or outside of the base body and coupled to the plunger in such a way that it counteracts the displacement of the plunger and serves as a return spring.
  • the plunger is actuated by a rocker arm on its end facing away from the tool. This is pivotally mounted in the base body and is acted upon vertically by a press ram.
  • the rocker arm Due to the downward movement of the press ram during the working stroke, the rocker arm swivels about its axis and presses the ram carrying the tool forward in the horizontal direction. After the punching or bending process has ended, the return stroke of the press ram and the return movement of the ram carrying the tool take place as a result of the action of the return spring.
  • the return spring is necessary because the press ram is not firmly connected to the rocker arm. Rather, the press ram generally has no contact with the rocker arm in the area of its top dead center position.
  • Such tool modules have been widely used because they can be used universally in all common presses. They will be fixed there at the desired location. For this purpose, various mounting options, such as. B. holes, feather keys or shoulders arranged.
  • the rocker arm which acts as a force-deflecting element, is subject to very heavy wear, because the pivot axis has to absorb the transmitted high forces.
  • This further relates to the sliding surfaces of the rocker arm which are in contact with the press ram and the ram carrying the tool.
  • Such tool modules also offer in terms of Their arrangement possibility in the case of a required multiple arrangement little flexibility, since usually only one rocker arm can be actuated by the press ram. Therefore, complex designs are often required in order to operate several tools simultaneously using a central rocker arm. Once a geometric configuration has been preselected, it must generally be retained; even minor modifications in the geometry require the special production of a new tool module.
  • the invention was therefore based on the problem of further developing a press-driven tool module, in particular a press-driven transverse punching or bending unit of the type mentioned at the outset, in such a way that the problems described no longer occur.
  • the energy introduced by the press should be optimally implemented with the least possible technical outlay and adapted to the deformation process.
  • the invention is based on the idea of using the kinetic energy of the press ram to put the hydraulic medium under high pressure only briefly in each case, so that the desired punching and bending process can be carried out. Otherwise, the hydraulic medium is essentially depressurized.
  • a reservoir for the hydraulic medium is provided in the power cylinder, which has a connection to the displacement chamber in the top dead center position of the piston, but otherwise, d. H. at a position of the piston which deviates from the top dead center position, is sealed against high pressure with respect to the displacement space.
  • the tool module according to the invention offers the possibility of attaching the work unit carrying the tool and the force unit that pressurizes the hydraulic medium in a spatial separation from one another, the two subunits being connected by a high-pressure line. In this way it is possible to actuate several work units simultaneously by a single common force unit.
  • the position of each work unit can be changed without any significant effort.
  • the direction of machining can also be realized not only purely horizontally, but deviating therefrom in any angular position.
  • a gas spring element is integrated in the working unit as a return spring, which is integrated within the cylinder space as well as optionally within the piston and the piston rod without taking up additional space.
  • a coil spring can also be provided as an inexpensive alternative will.
  • the tool module consists of two sub-units, namely a working cylinder A and a power cylinder K.
  • the working cylinder A has a base body 33 with a cylindrical bore.
  • a working piston 10 is slidably disposed in the cylindrical bore.
  • a piston rod 9 is attached, which carries a tool 18 in the form of a stamp on the end face.
  • the piston rod 9 is also slidably guided in a bearing bush 11 which closes off the base body 33.
  • the guide bush 11 is screwed to the base body 33.
  • the guide bush 11 projects with a shoulder web 34 into the interior of the cylinder bore of the base body 33.
  • a sealing ring 35 is attached, the function of which is explained in more detail below.
  • the displacement of the working piston 10 is limited, on the one hand, by the abutment against the base 33 and, on the other hand, by the abutment on the shoulder 34 of the bearing bush 11.
  • the distance between these two end positions is the stroke H A of the working piston 10 and thus corresponds to the amount of the maximum displacement of the Tool 18.
  • the working space 22 is hereby defined as the axial section of the cylinder bore of the base body 33.
  • the working piston 10 is provided with a high-pressure seal 5, so that the working space 22 is sealed at a high pressure at this point between the working piston 10 and the cylinder bore of the base body 33.
  • the power cylinder K has a base block 1, on which a guide block 2 is placed and screwed tightly to it.
  • the guide block 2 has a through hole into which the slide bush 27 is inserted.
  • the sliding bush 27 takes over the guidance of a piston rod 3, which is attached to a plunger 23.
  • the bore receiving the piston rod 3 merges in the interior of the guide block 2 into a cylindrical bore of larger diameter, which is provided with an internal thread 36.
  • the internal thread 36 is in engagement with an external thread 37 which an upwardly facing heel ring 38 of the base block 1 is attached.
  • a cylinder bore is provided in the base block, which essentially represents the displacement space 24 and merges upwards into the cylinder bore of the guide block 2.
  • the diameter of the cylinder bore of the guide block 2 is larger than the outer diameter of the plunger 23, so that an annular space 26 remains between the plunger 23 and the guide block 2.
  • the diameter of the cylinder bore is matched to the diameter of the plunger 23.
  • the diameter of the cylinder bore in the base block 1 increases slightly in the manner of a recess. From here a bore 25 goes off, which connects the displacement space 24 with the working space 22 of the working cylinder A.
  • the displacement space 24, the bore 25, the working space 22 and parts of the annular space 23 are filled with hydraulic medium M. It is a medium viscosity oil.
  • the annular space 26 has a connection with the displacement space 24, so that a continuous liquid column is created from the displacement space 24 to the annular space 26.
  • hydraulic medium M can be supplemented via the filler valve 10, which is not shown here.
  • a vent hole 30 opening into the working space 22 is provided, which can be sealed with a vent screw 12.
  • the liquid level in the power cylinder rises until finally the entire annular space 26 is filled and thus the function of a storage space for the hydraulic medium M.
  • the storage space 26 is separated from the displacer space 24. This is ensured by a high-pressure ring seal 4, which is mounted in the heel ring 38 of the base block 1 and tightly encloses the plunger 23.
  • a gas spring element is integrated in the working cylinder A.
  • the annular space is used, which lies in the radial direction between the piston rod 9 and the cylinder bore of the working cylinder A and in the axial direction between the working piston 10 and the bearing bush 11.
  • This area is made gas-tight in that the working piston 10 is provided with a gas seal 6 and the bearing bush 11 with the gas seal 7, which seals the transition from the piston rod 9 to the bearing bush 11.
  • the seal 35 mentioned above seals the transition from the base body 33 to the bearing bush 11.
  • the annular space 31 is filled with nitrogen gas under high pressure. Moving the working cylinder 10 out of the starting position shown in FIG. 1 to the right reduces the volume of the annular space 31, and the gas therein is compressed.
  • the gas relaxes and presses the working piston 10 back into its starting position.
  • the interior of the piston 10 and the piston rod 9 are largely drilled out, so that a common cavity 32 results which has a connection 16 to the annular space 31.
  • the cavity 32 and the bore 16 are also filled with gas.
  • the desired spring characteristic can be achieved by appropriate dimensioning of the cavity. This enables an extremely compact design, since the gas spring element is completely inside the working cylinder A is integrated.
  • the gas filling can be introduced through a gas valve 8 (not shown in detail) or can be supplemented if necessary.
  • FIG. 1 The starting point as the start of a machining cycle is shown in FIG. 1. This is a punching process in which a hole is to be punched in a workpiece 20.
  • the workpiece 20 is held by a die 21, which in turn is attached to a support plate 19.
  • a press ram 17 of a press is in its top dead center position.
  • the tool 18 is in the retracted position, the working piston 10 abutting on the end face inside the cylinder bore of the base body 33 due to the action of the gas spring element.
  • the displacer 23 is held against the shoulder of the guide block 2 via the hydraulic medium M.
  • the displacement piston 23 has no contact with the high-pressure ring seal 4, so that a continuous liquid column has formed in the displacement space 24 and in the storage space 26.
  • the press ram 17 begins its downward movement and hits the piston rod 3. Due to the further downward movement of the press ram 17, the displacer 23 is forced vertically downward via the piston rod 3. It comes into contact with the high-pressure ring seal 4 after a short distance, so that from then on the displacement space 24 is sealed off from the storage space 26. Through the further downward movement of the plunger 23 increases the pressure of the hydraulic medium M, which is located in the displacement chamber 24 and in the bore 25. When the pressure rises further, the working piston 10 is first shifted to the right against the action of the gas suspension element (in the illustration according to FIGS. 1 and 2). The pressure build-up in the hydraulic medium M initially moves in the low-pressure range, since only the working piston 10 carries out a displacement movement and the tool 18 is thus delivered.
  • the press ram 17 has reached its lowest position, bottom dead center (UT) and is about to reverse its direction of movement and move upward. This enables the displacement piston 23 to return to its starting position. Since the piston rod 3 is not connected to the press ram 17, the return stroke of the plunger 23 is effected by the return stroke of the working piston 10. This is ensured by the integrated gas spring element, which was compressed as a result of the displacement of the working cylinder 10 and can now expand again. As a result of the expansion, the working piston 10 becomes contact with the cylinder bore in the base body 33 on the end face brought so that the position indicated in Figure 1 is reached again.
  • a height-adjustable mechanical stop 15 is attached to the end of the guide block 2 and serves as a stroke limitation for the press ram 17 and thus for the displacement piston 23. It is intended to prevent the plunger 23 from accidentally penetrating too deeply into the displacement chamber 24 and thereby causing the pressure in the hydraulic medium M to rise to an impermissibly high value. This virtually eliminates operating errors.
  • a burst protection device can be provided in areas leading hydraulic medium (M), for example in the area of the bore 25.
  • the low-pressure valve 13 ensures pressure equalization if the overpressure or underpressure generated as a result of the displacement movement of the plunger 23 exceeds predetermined limits. It also prevents overfilling with hydraulic medium M.
  • a spatially separate arrangement of the power cylinder K and the working cylinder A is also possible without loss of function, the bore 25 being replaced by a high-pressure line.
  • a plurality of working cylinders A can also be connected to the power cylinder K, the high pressure lines of which are coupled to the power cylinder either individually or via a multiple coupling. Especially when using a flexible line as a high-pressure line, a completely variable and freely configurable configuration can be realized.

Abstract

In a press-driven tool module, in particular press-driven cross-punching or bending unit, a tool (18) mountable on a slide (9) is movable in any direction against the action of a restoring, integrated pneumatic spring, and the tool (18) carrying slide (9) may be actuated by a vertically movable press slide (17). For that purpose, a vertically guided plunger (23) arranged in a power cylinder (K) may be actuated by the press slide (17) by means of a piston rod (3) and acts upon a hydraulic medium (M) in an underlying displacement chamber (24). The displacement chamber (24) is connected by a high pressure pipe (25) to the work chamber (22) of a working cylinder (A) whose piston rod (9) bears the tool. In a preferred embodiment, the power cylinder (K) and the working cylinder (A) may be mounted apart from each other and linked to each other by a flexible high pressure pipe.

Description

Die Erfindung betrifft ein pressengetriebenes Werkzeugmodul, insbesondere eine pressengetriebene Querstanz- oder Biegeeinheit gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a press-driven tool module, in particular a press-driven transverse punching or bending unit according to the preamble of claim 1.

Vergleichbare Werkzeugmodule sind beispielsweise aus dem Prospektblatt "MILFAB" der Danly Deutschland GmbH bekannt. Sie besitzen einen Stößel, an dem ein Werkzeug, beispielsweise ein Stanz- oder Biegewerkzeug anbringbar ist. Der Stößel ist in einer Führungsbuchse eines Grundkörpers verschiebbar gelagert. Die Verschieberichtung ist durch die Anordnung der Führungsbuchse vorgegeben und verläuft horizontal. Parallel zum Stößel ist entweder innerhalb oder außerhalb des Grundkörpers eine Schraubenfeder angebracht und mit dem Stößel derart gekoppelt, daß sie der Verschiebung des Stößels entgegenwirkt und als Rückstellfeder dient. Der Stößel wird an seiner dem Werkzeug abgewandten Stirnseite von einem Kipphebel betätigt. Dieser ist schwenkbar im Grundkörper gelagert und wird von einem Pressenstößel vertikal beaufschlagt. Durch die Abwärtsbewegung des Pressenstößels beim Arbeitshub schwenkt der Kipphebel um seine Achse und drückt dabei den das Werkzeug tragenden Stößel in horizontaler Richtung nach vorne. Nach Beendigung des Stanz- oder Biegevorgangs erfolgen der Rückhub des Pressenstößels sowie die Rückstellbewegung des das Werkzeug tragenden Stößels infolge der Wirkung der Rückholfeder. Die Rückholfeder ist deshalb erforderlich, weil der Pressenstößel nicht mit dem Kipphebel fest verbunden ist. Vielmehr hat im allgemeinen der Pressenstößel im Bereich seiner oberen Totpunktlage keine Berührung mit dem Kipphebel.Comparable tool modules are known, for example, from the "MILFAB" brochure from Danly Deutschland GmbH. They have a plunger to which a tool, for example a punching or bending tool, can be attached. The tappet is slidably mounted in a guide bush of a base body. The direction of movement is through the The arrangement of the guide bush is predetermined and runs horizontally. Parallel to the plunger, a helical spring is attached either inside or outside of the base body and coupled to the plunger in such a way that it counteracts the displacement of the plunger and serves as a return spring. The plunger is actuated by a rocker arm on its end facing away from the tool. This is pivotally mounted in the base body and is acted upon vertically by a press ram. Due to the downward movement of the press ram during the working stroke, the rocker arm swivels about its axis and presses the ram carrying the tool forward in the horizontal direction. After the punching or bending process has ended, the return stroke of the press ram and the return movement of the ram carrying the tool take place as a result of the action of the return spring. The return spring is necessary because the press ram is not firmly connected to the rocker arm. Rather, the press ram generally has no contact with the rocker arm in the area of its top dead center position.

Derartige Werkzeugmodule haben eine weite Verbreitung gefunden, da sie universell in allen gängigen Pressen einsetzbar sind. Sie werden dort an der gewünschten Stelle fixiert. Hierzu sind am Grundkörper verschiedene Befestigungsmöglichkeiten, wie z. B. Bohrungen, Paßfedernuten oder Absätze angeordnet.Such tool modules have been widely used because they can be used universally in all common presses. They will be fixed there at the desired location. For this purpose, various mounting options, such as. B. holes, feather keys or shoulders arranged.

Dennoch weisen sie eine Reihe von Nachteilen auf. So unterliegt der als kraftumlenkendes Organ wirkende Kipphebel einem sehr starken Verschleiß, weil die Schwenkachse die übertragenen hohen Kräfte aufnehmen muß. Dies betrifft weiterhin die mit dem Pressenstößel und dem das Werkzeug tragenden Stößel in Berührung stehenden Gleitflächen des Kipphebels. Auch bieten derartige Werkzeugmodule hinsichtlich ihrer Anordnungsmöglichkeit im Falle einer erforderlichen Mehrfachanordnung wenig Flexibilität, da in der Regel jeweils nur ein Kipphebel durch den Pressenstößel betätigbar ist. Deshalb sind häufig aufwendige Konstruktionen erforderlich, um gleichzeitig mehrere Werkzeuge durch einen zentralen Kipphebel zu betätigen. Eine einmal vorgewählte geometrische Konfiguration muß in der Regel beibehalten werden, selbst geringfügige Modifikationen in der Geometrie erfordern die Sonderanfertigung eines neuen Werkzeugmoduls.Nevertheless, they have a number of disadvantages. For example, the rocker arm, which acts as a force-deflecting element, is subject to very heavy wear, because the pivot axis has to absorb the transmitted high forces. This further relates to the sliding surfaces of the rocker arm which are in contact with the press ram and the ram carrying the tool. Such tool modules also offer in terms of Their arrangement possibility in the case of a required multiple arrangement little flexibility, since usually only one rocker arm can be actuated by the press ram. Therefore, complex designs are often required in order to operate several tools simultaneously using a central rocker arm. Once a geometric configuration has been preselected, it must generally be retained; even minor modifications in the geometry require the special production of a new tool module.

Dem Grunde nach ist es auch schon bekannt geworden, beispielsweise aus der DE 26 00 948 B2, einen Hydraulikzylinder zur Formgebung zu benutzen, wobei ein im Zylinder verschiebbarer Arbeitskolben mit einer Kolbenstange ein Werkzeug trägt. Zum Antrieb wird eine Hydraulikflüssigkeit verwendet, die von einem separaten Hydraulikaggregat unter Druck gesetzt wird. Derartige Hydraulikaggregate sind jedoch nicht von einer Presse antreibbar, sondern besitzen in der Regel Elektromotoren. Um den für einen Stanz- oder Biegevorgang aufzubringenden Druck statisch aufzubringen, ist es erforderlich, eine sehr hohe Leistung zu installieren. Dies ist unökonomisch, da der für die Bearbeitung erforderliche Maximaldruck lediglich kurzfristig, d. h. impulsartig benötigt wird. In der genannten Druckschrift wird deshalb eine aufwendige Konstruktion vorgeschlagen, bei der über einen Hilfskolben gesteuert eine schlagartige, hohe Krafteinwirkung durch Freigabe einer gespeicherten Energie bewirkt wird. Abgesehen von dem hierzu erforderlichen technischen Aufwand läßt sich eine derartige Konstruktion nicht mit einer vorhandenen Presse betreiben, sondern erfordert eine komplette Umkonfiguration der Bearbeitungsstation mit Hydraulikaggregaten.Basically, it has also become known, for example from DE 26 00 948 B2, to use a hydraulic cylinder for shaping, a working piston which is displaceable in the cylinder carrying a tool with a piston rod. A hydraulic fluid is used for the drive, which is pressurized by a separate hydraulic unit. However, hydraulic units of this type cannot be driven by a press, but generally have electric motors. In order to statically apply the pressure to be applied for a punching or bending process, it is necessary to install a very high output. This is uneconomical, since the maximum pressure required for processing is only required for a short time, ie in a pulsed manner. In the cited publication, therefore, a complex construction is proposed, in which an abrupt, high force is caused by the release of a stored energy, controlled by an auxiliary piston. Apart from the technical effort required for this, such a construction cannot be operated with an existing press, but rather requires a complete reconfiguration of the processing station with hydraulic units.

Schließlich ist es aus der EP 0 251 794 A2, von der die Erfindung ausgeht, bekannt, bei einem pressengetriebenen Werkzeugmodul die Kraftumlenkung hydraulisch zu realisieren. Hierzu ist ein Kraftzylinder vorgesehen, dessen Kolben über eine nach außen geführte Kolbenstange vom Pressenstößel beaufschlagt wird. Weiterhin ist ein Arbeitszylinder vorgesehen, in welchem ein Arbeitskolben verschiebbar gelagert ist. Zwischen dem Kraftzylinder und dem Arbeitszylinder ist eine hydraulische Verbindung vorgesehen, so daß zwischen dem im Kraftzylinder gebildeten Verdrängerraum und dem im Arbeitszylinder gebildeten Arbeitsraum eine kommunizierende Verbindung besteht. Das darin befindliche, weitgehend inkompressible Hydraulikmedium erlaubt deshalb eine Kraftübertragung vom Kraftzylinder auf den Arbeitszylinder. Nachteilig ist auch hierbei, daß der zeitliche Verlauf des Druckaufbaus nicht mit dem für den Bearbeitungsvorgang erforderlichen Kraftbedarf korrespondiert.Finally, it is known from EP 0 251 794 A2, from which the invention is based, to implement the force deflection hydraulically in a press-driven tool module. For this purpose, a power cylinder is provided, the piston of which is pressed by the press ram via an outwardly directed piston rod. Furthermore, a working cylinder is provided, in which a working piston is slidably mounted. A hydraulic connection is provided between the power cylinder and the working cylinder, so that there is a communicating connection between the displacement space formed in the power cylinder and the working space formed in the working cylinder. The largely incompressible hydraulic medium contained therein therefore allows power to be transferred from the power cylinder to the working cylinder. It is also disadvantageous here that the chronological course of the pressure build-up does not correspond to the force required for the machining process.

Der Erfindung lag daher das Problem zugrunde, ein pressengetriebenes Werkzeugmodul, insbesondere eine pressengetriebene Querstanz- oder Biegeeinheit der eingangs genannten Art derart weiterzuentwickeln, daß die geschilderten Probleme nicht mehr auftreten. Insbesondere soll die durch die Presse eingeleitete Energie mit möglichst geringem technischen Aufwand optimal umgesetzt und auf den Verformungsvorgang abgestimmt werden.The invention was therefore based on the problem of further developing a press-driven tool module, in particular a press-driven transverse punching or bending unit of the type mentioned at the outset, in such a way that the problems described no longer occur. In particular, the energy introduced by the press should be optimally implemented with the least possible technical outlay and adapted to the deformation process.

Das Problem wird durch ein pressengetriebenes Werkzeugmodul gelöst, welches die Merkmale des Anspruchs 1 aufweist.The problem is solved by a press-driven tool module, which has the features of claim 1.

Vorteilhafte Weiterbildungen der Erfindung sind durch die Merkmale der Unteransprüche angegeben.Advantageous developments of the invention are specified by the features of the subclaims.

Der Erfindung liegt die Idee zugrunde, die kinetische Energie des Pressenstößels dazu zu benutzten, das Hydraulikmedium jeweils nur kurzzeitig unter Hochdruck zu setzen, so daß der gewünschte Stanz- und Biegevorgang ausgeführt werden kann. Im übrigen ist das Hydraulikmedium im wesentlichen drucklos.The invention is based on the idea of using the kinetic energy of the press ram to put the hydraulic medium under high pressure only briefly in each case, so that the desired punching and bending process can be carried out. Otherwise, the hydraulic medium is essentially depressurized.

Konkret wird dies dadurch erreicht, daß im Kraftzylinder ein Vorratsraum für das Hydraulikmedium vorgesehen ist, der in der oberen Totpunktlage des Kolbens zum Verdrängerraum hin Verbindung hat, im übrigen aber, d. h. bei einer von der oberen Totpunktlage abweichenden Position des Kolbens, gegenüber dem Verdrängerraum hochdruckabgedichtet ist.Specifically, this is achieved in that a reservoir for the hydraulic medium is provided in the power cylinder, which has a connection to the displacement chamber in the top dead center position of the piston, but otherwise, d. H. at a position of the piston which deviates from the top dead center position, is sealed against high pressure with respect to the displacement space.

Insbesondere bietet das erfindungsgemäße Werkzeugmodul gemäß einer bevorzugten Ausführungsform die Möglichkeit, die das Werkzeug tragende Arbeitseinheit und die das Hydraulikmedium unter Druck setzende Krafteinheit in räumlicher Trennung voneinander anzubringen wobei beide Teileinheiten durch eine Hochdruckleitung verbunden werden. Auf diese Weise ist es möglich, gleichzeitig mehrere Arbeitseinheiten durch eine einzige gemeinsame Krafteinheit zu betätigen. Ohne nennenswerten Aufwand kann die Position jeder Arbeitseinheit verändert werden. Insbesondere läßt sich auch die Richtung der Bearbeitung nicht nur rein horizontal, sondern hiervon abweichend in jeder beliebigen Winkellage realisieren.In particular, according to a preferred embodiment, the tool module according to the invention offers the possibility of attaching the work unit carrying the tool and the force unit that pressurizes the hydraulic medium in a spatial separation from one another, the two subunits being connected by a high-pressure line. In this way it is possible to actuate several work units simultaneously by a single common force unit. The position of each work unit can be changed without any significant effort. In particular, the direction of machining can also be realized not only purely horizontally, but deviating therefrom in any angular position.

In einer besonders bevorzugten Ausführungsform der Erfindung ist in der Arbeitseinheit ein Gasfederelement als Rückstellfeder integriert, welches ohne zusätzlichen Platzbedarf innerhalb des Zylinderraums sowie gegebenenfalls innerhalb des Kolbens und der Kolbenstange integriert ist. Bei Anwendungsfällen mit relativ geringen Rückstellkräften kann auch eine Schraubenfeder als preisgünstige Alternative vorgesehen werden.In a particularly preferred embodiment of the invention, a gas spring element is integrated in the working unit as a return spring, which is integrated within the cylinder space as well as optionally within the piston and the piston rod without taking up additional space. In applications with relatively low restoring forces, a coil spring can also be provided as an inexpensive alternative will.

Die Erfindung wird nachstehend anhand des in den Figuren schematisch dargestellten Ausführungsbeispiels nähert erläutert. Dort werden auch weitere Vorteile im Detail erläutert. Es zeigen

Figur 1 -
Schnittdarstellung des Werkzeugmoduls, Pressenstößel im oberen Totpunkt und
Figur 2 -
Schnittdarstellung des Werkzeugmoduls, Pressenstößel im unteren Totpunkt.
The invention is explained in more detail below with reference to the exemplary embodiment shown schematically in the figures. Further advantages are also explained in detail there. Show it
Figure 1 -
Sectional view of the tool module, press ram at top dead center and
Figure 2 -
Sectional view of the tool module, press ram at bottom dead center.

Das Werkzeugmodul besteht aus zwei Teileinheiten, nämlich einem Arbeitszylinder A und einem Kraftzylinder K.The tool module consists of two sub-units, namely a working cylinder A and a power cylinder K.

Der Arbeitszylinder A weist einen Grundkörper 33 mit einer zylindrischen Bohrung auf. In der zylindrischen Bohrung ist ein Arbeitskolben 10 verschiebbar angeordnet. Am Arbeitskolben 10 ist eine Kolbenstange 9 angebracht, welche stirnseitig ein Werkzeug 18 in Form eines Stempels trägt. Die Kolbenstange 9 ist ebenfalls verschieblich in einer Lagerbuchse 11 geführt, die den Grundkörper 33 abschließt. Die Führungsbuchse 11 ist mit dem Grundkörper 33 verschraubt. Die Führungsbuchse 11 ragt mit einem Absatzsteg 34 in das Innere der Zylinderbohrung des Grundkörpers 33 hinein. Im Überlappungsbereich zwischen dem Grundkörper 33 und der Lagerbuchse 11 ist ein Dichtring 35 angebracht, dessen Funktion nachstehend näher erläutert wird. Der Verschiebeweg des Arbeitskolbens 10 wird einerseits begrenzt durch das stirnseitige Anliegen am Grundkörper 33 und andererseits durch das Anliegen am Absatzsteg 34 der Lagerbuchse 11. Der Abstand zwischen diesen beiden Endlagen ist der Hub HA des Arbeitskolbens 10 und entspricht damit dem Betrag der maximalen Verschiebung des Werkzeugs 18. Gleichzeitig wird hierdurch der Arbeitsraum 22 als Axialabschnitt der Zylinderbohrung des Grundkörpers 33 definiert.The working cylinder A has a base body 33 with a cylindrical bore. A working piston 10 is slidably disposed in the cylindrical bore. On the working piston 10, a piston rod 9 is attached, which carries a tool 18 in the form of a stamp on the end face. The piston rod 9 is also slidably guided in a bearing bush 11 which closes off the base body 33. The guide bush 11 is screwed to the base body 33. The guide bush 11 projects with a shoulder web 34 into the interior of the cylinder bore of the base body 33. In the area of overlap between the base body 33 and the bearing bush 11, a sealing ring 35 is attached, the function of which is explained in more detail below. The displacement of the working piston 10 is limited, on the one hand, by the abutment against the base 33 and, on the other hand, by the abutment on the shoulder 34 of the bearing bush 11. The distance between these two end positions is the stroke H A of the working piston 10 and thus corresponds to the amount of the maximum displacement of the Tool 18. At the same time, the working space 22 is hereby defined as the axial section of the cylinder bore of the base body 33.

Der Arbeitskolben 10 ist mit einer Hochdruckdichtung 5 versehen, so daß der Arbeitsraum 22 an dieser Stelle zwischen dem Arbeitskolben 10 und der Zylinderbohrung des Grundkörpers 33 hochdruckabgedichtet ist.The working piston 10 is provided with a high-pressure seal 5, so that the working space 22 is sealed at a high pressure at this point between the working piston 10 and the cylinder bore of the base body 33.

Der Kraftzylinder K weist einen Basisblock 1 auf, auf dem ein Führungsblock 2 aufgesetzt und mit diesem dicht verschraubt ist. Der Führungsblock 2 besitzt eine Durchgangsbohrung, in die die Gleitbuchse 27 eingesetzt ist. Die Gleitbuchse 27 übernimmt die Führung einer Kolbenstange 3, die an einem Tauchkolben 23 befestigt ist. Die die Kolbenstange 3 aufnehmende Bohrung geht im Inneren des Führungsblocks 2 in eine zylindrische Bohrung größeren Durchmessers über, die mit einem Innengewinde 36 versehen ist. Das Innengewinde 36 ist im Eingriff mit einem Außengewinde 37, das an einem nach oben weisenden Absatzring 38 des Basisblocks 1 angebracht ist.The power cylinder K has a base block 1, on which a guide block 2 is placed and screwed tightly to it. The guide block 2 has a through hole into which the slide bush 27 is inserted. The sliding bush 27 takes over the guidance of a piston rod 3, which is attached to a plunger 23. The bore receiving the piston rod 3 merges in the interior of the guide block 2 into a cylindrical bore of larger diameter, which is provided with an internal thread 36. The internal thread 36 is in engagement with an external thread 37 which an upwardly facing heel ring 38 of the base block 1 is attached.

Im Basisblock ist eine Zylinderbohrung angebracht, die im wesentlichen den Verdrängerraum 24 darstellt und nach oben hin in die Zylinderbohrung des Führungsblocks 2 übergeht. Der Durchmesser der Zylinderbohrung des Führungsblocks 2 ist größer als der Außendurchmesser des Tauchkolbens 23, so daß zwischen dem Tauchkolben 23 und dem Führungsblock 2 ein Ringraum 26 verbleibt. Im Bereich des Absatzrings 38 ist der Durchmesser der Zylinderbohrung auf den Durchmesser des Tauchkolbens 23 abgestimmt.A cylinder bore is provided in the base block, which essentially represents the displacement space 24 and merges upwards into the cylinder bore of the guide block 2. The diameter of the cylinder bore of the guide block 2 is larger than the outer diameter of the plunger 23, so that an annular space 26 remains between the plunger 23 and the guide block 2. In the area of the shoulder ring 38, the diameter of the cylinder bore is matched to the diameter of the plunger 23.

Nach unten hin nimmt der Durchmesser der Zylinderbohrung im Basisblock 1 geringfügig nach Art eines Einstichs zu. Von hier aus geht eine Bohrung 25 ab, die den Verdrängerraum 24 mit dem Arbeitsraum 22 des Arbeitszylinders A verbindet. Der Verdrängerraum 24, die Bohrung 25, der Arbeitsraum 22 sowie Teile des Ringraums 23 sind mit Hydraulikmedium M gefüllt. Es handelt sich hierbei um ein Öl mittlerer Viskosität.At the bottom, the diameter of the cylinder bore in the base block 1 increases slightly in the manner of a recess. From here a bore 25 goes off, which connects the displacement space 24 with the working space 22 of the working cylinder A. The displacement space 24, the bore 25, the working space 22 and parts of the annular space 23 are filled with hydraulic medium M. It is a medium viscosity oil.

In der in Figur 1 skizzierten Stellung des Tauchkolbens 23 hat der Ringraum 26 Verbindung mit dem Verdrängerraum 24, so daß sich eine durchgehende Flüssigkeitssäule vom Verdrängerraum 24 zum Ringraum 26 einstellt. In dieser Position kann über das hier nicht näher dargestellte Einfüllventil 10 Hydraulikmedium M ergänzt werden. Zur Erleichterung des Einfüllvorgangs ist eine in den Arbeitsraum 22 mündende Entlüftungsbohrung 30 vorgesehen, die mit einer Entlüftungsschraube 12 dicht verschließbar ist. Durch das Befüllen steigt der Flüssigkeitspegel im Kraftzylinder nach oben, bis schließlich der gesamte Ringraum 26 gefüllt ist und damit die Funktion eines Vorratsraums für das Hydraulikmedium M hat. In einer hiervon abweichenden Position des Verdrängerkolbens 23, wie sie beispielsweise durch Figur 2 charakterisiert ist, ist der Vorratsraum 26 vom Verdrängerraum 24 getrennt. Hierfür sorgt eine Hochdruck-Ringdichtung 4, die im Absatzring 38 des Basisblocks 1 gelagert ist und den Tauchkolben 23 dicht umschließt.In the position of the plunger 23 outlined in FIG. 1, the annular space 26 has a connection with the displacement space 24, so that a continuous liquid column is created from the displacement space 24 to the annular space 26. In this position, hydraulic medium M can be supplemented via the filler valve 10, which is not shown here. To facilitate the filling process, a vent hole 30 opening into the working space 22 is provided, which can be sealed with a vent screw 12. As a result of the filling, the liquid level in the power cylinder rises until finally the entire annular space 26 is filled and thus the function of a storage space for the hydraulic medium M. Has. In a different position of the displacer piston 23, as is characterized, for example, by FIG. 2, the storage space 26 is separated from the displacer space 24. This is ensured by a high-pressure ring seal 4, which is mounted in the heel ring 38 of the base block 1 and tightly encloses the plunger 23.

Im Arbeitszylinder A ist ein Gasfederelement integriert. Hierzu wird der Ringraum benutzt, der in radialer Richtung zwischen der Kolbenstange 9 und der Zylinderbohrung des Arbeitszylinders A und in axialer Richtung zwischen dem Arbeitskolben 10 und der Lagerbuchse 11 liegt. Dieser Bereich wird gasdicht dadurch gestaltet, daß der Arbeitskolben 10 mit einer Gasdichtung 6 und die Lagerbuchse 11 mit der Gasdichtung 7 versehen ist, welche den Übergang von der Kolbenstange 9 zur Lagerbuchse 11 abdichtet. Weiterhin dichtet die oben erwähnte Dichtung 35 den Übergang vom Grundkörper 33 zur Lagerbuchse 11. Der Ringraum 31 ist mit Stickstoffgas unter hohem Druck gefüllt. Eine Verschiebung des Arbeitszylinders 10 aus der in Figur 1 dargestellten Ausgangsposition heraus nach rechts verkleinert das Volumen des Ringraums 31, das darin befindliche Gas wird komprimiert. Bei einer Entlastung des Arbeitskolbens 10 entspannt sich das Gas und drückt den Arbeitskolben 10 in seine Ausgangsposition zurück. Um den Druckanstieg infolge der Verschiebebewegung im Ringraum 31 zu begrenzen, werden das Innere des Kolbens 10 und der Kolbenstange 9 weitgehend aufgebohrt, so daß sich ein gemeinsamer Hohlraum 32 ergibt, der über eine Bohrung 16 zum Ringraum 31 Verbindung hat. Somit sind der Hohlraum 32 und die Bohrung 16 ebenfalls mit Gas gefüllt. Durch eine entsprechende Dimensionierung des Hohlraums läßt sich die gewünschte Federcharakteristik erzielen. Dies ermöglicht eine äußerst kompakte Bauweise, da das Gasfederelement vollständig im Inneren des Arbeitszylinders A integriert ist.A gas spring element is integrated in the working cylinder A. For this purpose, the annular space is used, which lies in the radial direction between the piston rod 9 and the cylinder bore of the working cylinder A and in the axial direction between the working piston 10 and the bearing bush 11. This area is made gas-tight in that the working piston 10 is provided with a gas seal 6 and the bearing bush 11 with the gas seal 7, which seals the transition from the piston rod 9 to the bearing bush 11. Furthermore, the seal 35 mentioned above seals the transition from the base body 33 to the bearing bush 11. The annular space 31 is filled with nitrogen gas under high pressure. Moving the working cylinder 10 out of the starting position shown in FIG. 1 to the right reduces the volume of the annular space 31, and the gas therein is compressed. When the working piston 10 is relieved of pressure, the gas relaxes and presses the working piston 10 back into its starting position. In order to limit the pressure increase due to the displacement movement in the annular space 31, the interior of the piston 10 and the piston rod 9 are largely drilled out, so that a common cavity 32 results which has a connection 16 to the annular space 31. Thus, the cavity 32 and the bore 16 are also filled with gas. The desired spring characteristic can be achieved by appropriate dimensioning of the cavity. This enables an extremely compact design, since the gas spring element is completely inside the working cylinder A is integrated.

Die Gasfüllung kann durch ein nicht näher dagestelltes Gasventil 8 eingebracht bzw. bei Bedarf ergänzt werden.The gas filling can be introduced through a gas valve 8 (not shown in detail) or can be supplemented if necessary.

Die Funktionsweise des Werkzeugmoduls wird nachstehend im Detail erläutert:The functionality of the tool module is explained in detail below:

Der Ausgangspunkt als Beginn eines Bearbeitungszykluses ist in Figur 1 dargestellt. Es handelt sich hierbei um einen Stanzvorgang, bei dem ein Loch in ein Werkstück 20 gestanzt werden soll. Das Werkstück 20 ist von einer Matrize 21 gehalten, die ihrerseits an einer Stützplatte 19 befestigt ist.The starting point as the start of a machining cycle is shown in FIG. 1. This is a punching process in which a hole is to be punched in a workpiece 20. The workpiece 20 is held by a die 21, which in turn is attached to a support plate 19.

Ein Pressenstößel 17 einer hier nicht dargestellten Presse befindet sich in seiner oberen Totpunktlage. Das Werkzeug 18 befindet sich in zurückgezogener Position, wobei der Arbeitskolben 10 infolge der Wirkung des Gasfederelements stirnseitig im Inneren der Zylinderbohrung des Grundkörpers 33 anliegt. Hierdurch wird über das Hydraulikmedium M der Verdrängerkolben 23 gegen die Schulter des Führungsblocks 2 gedrückt gehalten. Der Verdrängerkolben 23 hat keine Berührung mit der Hochdruck-Ringdichtung 4, so daß sich eine durchgehende Flüssigkeitssäule im Verdrängerraum 24 und im Vorratsraum 26 ausgebildet hat.A press ram 17 of a press, not shown here, is in its top dead center position. The tool 18 is in the retracted position, the working piston 10 abutting on the end face inside the cylinder bore of the base body 33 due to the action of the gas spring element. As a result, the displacer 23 is held against the shoulder of the guide block 2 via the hydraulic medium M. The displacement piston 23 has no contact with the high-pressure ring seal 4, so that a continuous liquid column has formed in the displacement space 24 and in the storage space 26.

Nunmehr beginnt der Pressenstößel 17 seine Abwärtsbewegung und trifft auf die Kolbenstange 3 auf. Durch die weitere Abwärtsbewegung des Pressenstößels 17 wird über die Kolbenstange 3 der Verdrängerkolben 23 vertikal nach unten gezwungen. Er gerät dabei nach kurzer Wegstrecke in Kontakt mit der Hochdruck-Ringdichtung 4, so daß von da ab der Verdrängerraum 24 zum Vorratsraum 26 hin abgedichtet ist. Durch die weitere Abwärtsbewegung des Tauchkolbens 23 erhöht sich der Druck des Hydraulikmediums M, das sich im Verdrängerraum 24 und in der Bohrung 25 befindet. Beim weiteren Druckanstieg wird zunächst der Arbeitskolben 10 gegen die Wirkung des Gasfederungselements (in der Darstellung gemäß Figur 1 und 2) nach rechts verschoben. Der Druckaufbau in dem Hydraulikmedium M bewegt sich zunächst im Niederdruckbereich, da lediglich der Arbeitskolben 10 eine Verschiebebewegung vollführt und damit das Werkzeug 18 zustellt.Now the press ram 17 begins its downward movement and hits the piston rod 3. Due to the further downward movement of the press ram 17, the displacer 23 is forced vertically downward via the piston rod 3. It comes into contact with the high-pressure ring seal 4 after a short distance, so that from then on the displacement space 24 is sealed off from the storage space 26. Through the further downward movement of the plunger 23 increases the pressure of the hydraulic medium M, which is located in the displacement chamber 24 and in the bore 25. When the pressure rises further, the working piston 10 is first shifted to the right against the action of the gas suspension element (in the illustration according to FIGS. 1 and 2). The pressure build-up in the hydraulic medium M initially moves in the low-pressure range, since only the working piston 10 carries out a displacement movement and the tool 18 is thus delivered.

Beim Auftreffen des Werkzeugs 18 auf das Werkstück 20 steigt der Druck im Hydraulikmedium M schlagartig an, da der Tauchkolben 23 durch den Pressenstößel 17 weiter nach unten gezwungen wird, der Arbeitskolben 10 jedoch infolge des Anliegens des Werkzeugs 18 am Werkstück 20 in seiner Position verharrt. Der Druck steigt weiter so lange an, bis die zum Stanzen erforderliche Kraft aufgebaut ist und das Werkzeug schlagartig in die Matrize eindringt. Das Eindringen in die Matrize wird durch das Anliegen des Arbeitskolbens am Absatzsteg 34 der Lagerbuchse 11 begrenzt. Dies entspricht der in Figur 2 dargestellten Position.When the tool 18 strikes the workpiece 20, the pressure in the hydraulic medium M suddenly increases because the plunger 23 is forced further down by the press ram 17, but the working piston 10 remains in its position due to the tool 18 resting on the workpiece 20. The pressure continues to rise until the force required for punching is built up and the tool suddenly penetrates the die. The penetration into the die is limited by the abutment of the working piston on the shoulder web 34 of the bearing bush 11. This corresponds to the position shown in Figure 2.

Der Pressenstößel 17 hat seine unterste Position, den unteren Totpunkt (U.T.) erreicht und ist im Begriff, seine Bewegungsrichtung umzukehren und sich nach oben zu bewegen. Hierdurch wird dem Verdrängerkolben 23 ermöglicht, in seine Ausgangsposition zurückzukehren. Da die Kolbenstange 3 nicht mit dem Pressenstößel 17 verbunden ist, wird der Rückhub des Tauchkolbens 23 durch den Rückhub des Arbeitskolbens 10 bewirkt. Hierfür sorgt das integrierte Gasfederelement, welches infolge der Verschiebung des Arbeitszylinders 10 komprimiert wurde und nunmehr wieder expandieren kann. Infolge der Expansion wird der Arbeitskolben 10 stirnseitig zur Anlage an der Zylinderbohrung in dem Grundkörper 33 gebracht, so daß erneut die in Figur 1 angedeutete Position erreicht wird.The press ram 17 has reached its lowest position, bottom dead center (UT) and is about to reverse its direction of movement and move upward. This enables the displacement piston 23 to return to its starting position. Since the piston rod 3 is not connected to the press ram 17, the return stroke of the plunger 23 is effected by the return stroke of the working piston 10. This is ensured by the integrated gas spring element, which was compressed as a result of the displacement of the working cylinder 10 and can now expand again. As a result of the expansion, the working piston 10 becomes contact with the cylinder bore in the base body 33 on the end face brought so that the position indicated in Figure 1 is reached again.

Stirnseitig am Führungsblock 2 ist ein höhenjustierbarer mechanischer Anschlag 15 angebracht, der als Hubbegrenzung für den Pressenstößel 17 und damit für den Verdrängerkolben 23 dient. Er soll verhindern, daß der Tauchkolben 23 versehentlich zu tief in den Verdrängerraum 24 eindringt und dadurch den Druck im Hydraulikmedium M auf einen unzulässig hohen Wert ansteigen läßt. Damit sind Bedienungsfehler praktisch ausgeschlossen. Zusätzlich kann in Hydraulikmedium (M) führenden Bereichen, beispielsweise im Bereich der Bohrung 25, eine hier nicht dargestellte Berstsicherung vorgesehen werden.A height-adjustable mechanical stop 15 is attached to the end of the guide block 2 and serves as a stroke limitation for the press ram 17 and thus for the displacement piston 23. It is intended to prevent the plunger 23 from accidentally penetrating too deeply into the displacement chamber 24 and thereby causing the pressure in the hydraulic medium M to rise to an impermissibly high value. This virtually eliminates operating errors. In addition, a burst protection device, not shown here, can be provided in areas leading hydraulic medium (M), for example in the area of the bore 25.

Von oben mündet in den Vorratsraum 26 eine Druckausgleichsbohrung 29, die mit einem Niederdruckventil 13 verschlossen ist. Das Niederdruckventil 13 sorgt für einen Druckausgleich, sofern der infolge der Verschiebebewegung des Tauchkolbens 23 erzeugte Über- oder Unterdruck vorbestimmte Grenzen übersteigt. Auch verhindert es ein Überfüllen mit Hydraulikmedium M.A pressure compensation bore 29, which is closed with a low pressure valve 13, opens into the storage space 26 from above. The low-pressure valve 13 ensures pressure equalization if the overpressure or underpressure generated as a result of the displacement movement of the plunger 23 exceeds predetermined limits. It also prevents overfilling with hydraulic medium M.

Ohne Funktionseinbuße ist auch eine räumlich getrennte Anordnung von Kraftzylinder K und Arbeitszylinder A möglich, wobei die Bohrung 25 durch eine Hochdruckleitung zu ersetzen ist. Auch kann an dem Kraftzylinder K eine Vielzahl von Arbeitszylindern A angeschlossen werden, deren Hochdruckleitungen entweder einzeln oder über eine Mehrfachkupplung mit dem Kraftzylinder gekoppelt werden. Insbesondere bei Verwendung einer flexiblen Leitung als Hochdruckleitung läßt sich eine völlig variable und freizügig zu gestaltende Konfiguration verwirklichen.A spatially separate arrangement of the power cylinder K and the working cylinder A is also possible without loss of function, the bore 25 being replaced by a high-pressure line. A plurality of working cylinders A can also be connected to the power cylinder K, the high pressure lines of which are coupled to the power cylinder either individually or via a multiple coupling. Especially when using a flexible line as a high-pressure line, a completely variable and freely configurable configuration can be realized.

In einem konkreten Fall wurden die folgenden Druck- und Größenverhältnisse bestimmt.The following pressure and size ratios were determined in a specific case.

In der in Figur 1 dargestellten Position befindet sich Öl mittlerer Viskosität unter Umgebungsbedingungen im Verdrängerraum 24 und im Vorratsraum 26. Im Gasfederelement befindet sich Stickstoffgas unter einem Druck von 100 bar. Während des Bearbeitungsvorgangs steigt der Öldruck auf maximal 400 bar an, der Druck im Gasfederungselement erreicht etwa 140 bar.In the position shown in FIG. 1 there is oil of medium viscosity under ambient conditions in the displacement chamber 24 and in the storage chamber 26. In the gas spring element there is nitrogen gas under a pressure of 100 bar. During the machining process, the oil pressure rises to a maximum of 400 bar, the pressure in the gas suspension element reaches approximately 140 bar.

FIGURENLEGENDEFIGURE LEGEND

11
BasisblockBase block
22nd
FührungsblockGuide block
33rd
KolbenstangePiston rod
44th
Hochdruck-RingdichtungHigh pressure ring seal
55
HochdruckdichtungHigh pressure seal
66
GasdichtungGas seal
77
GasdichtungGas seal
88th
GasventilGas valve
99
KolbenstangePiston rod
1010th
ArbeitskolbenPiston
1111
LagerbuchseBearing bush
1212th
EntlüftungsschraubeBleed screw
1313
NiederdruckventilLow pressure valve
1414
EinfüllventilFilling valve
1515
Anschlagattack
1616
Bohrungdrilling
1717th
PressenstößelPress ram
1818th
WerkzeugTool
1919th
StützträgerSupport beam
2020th
Werkstückworkpiece
2121
Matrizedie
2222
Arbeitsraumworking space
2323
TauchkolbenPlunger
2424th
VerdrängerraumDisplacement room
2525th
Bohrung, HochdruckleitungBore, high pressure line
2626
VorratsraumPantry
2727
GleitbuchseSliding bush
2828
StirnflächeFace
2929
DruckausgleichsbohrungPressure equalization hole
3030th
EntlüftungsbohrungVent hole
3131
RingraumAnnulus
3232
Hohlraumcavity
3333
GrundkörperBasic body
3434
AbsatzstegHeel
3535
DichtringSealing ring
3636
Innengewindeinner thread
3737
AußengewindeExternal thread
3838
AbsatzringHeel ring
AA
ArbeitszylinderWorking cylinder
KK
KraftzylinderPower cylinder
MM
HydraulikmediumHydraulic medium
HA H A
Hub des ArbeitskolbensStroke of the working piston
HK H K
Hub des TauchkolbensStroke of the plunger

Claims (16)

  1. Press-driven tool module, in particular press-driven cross-punching or bending unit, having a tool (18), in particular a punching or bending tool, mountable on a ram (9), which is mounted so as to be displaceable in a main body (33) in a direction deviating from the vertical, in particular in the horizontal direction, against the action of a restoring spring element,
    - wherein the ram carrying the tool (18) is designed as piston rod (9) of a working piston (10) which can be acted on by a hydraulic medium (M) and which is mounted so as to be displaceable in a working space (22) of a working cylinder (A),
    - wherein the hydraulic medium (M) contained in a displacement space (24) of a power cylinder (K) is displaceable by a piston (23) mounted vertically in the power cylinder (K), which can itself be actuated by means of a piston rod (3) of the press ram (17), and
    - wherein a hydraulic connection in the form of a high-pressure line (25) for the hydraulic medium (M) is provided between the displacement space (24) of the power cylinder (K) and the working space (22) of the working cylinder (A),
    characterized in that a reservoir space (26) for the hydraulic medium (M) is provided in the power cylinder (K), which is connected to the displacement space (24) of the power cylinder (K) in the top dead-centre position (T.D.C.) of the piston (23), and is otherwise high-pressure-sealed with respect to the displacement space (24).
  2. Tool module according to Claim 1, characterized in that the piston (23) is designed as immersion piston and in that the power cylinder (K) has a base block (1) and a guide block (2) joined to the base block (1), wherein a cylinder bore is provided in the base block (1), which essentially forms the displacement space (24) and carries, in its upper region, a high-pressure ring seal (4), which is brought into radial contact with the immersion piston (23) when the latter is in a position deviating from the top dead-centre position (T.D.C.), and wherein further a cylinder bore is present in the guide block (2), whose diameter is greater than that of the cylinder bore in the base block (1) so that the reservoir space (26) for the hydraulic medium (M) is formed above the displacement space (24) and merges into the latter.
  3. Tool module according to Claim 2, characterized in that the guide block (2) has a slide bush (27) for guiding the piston rod (3).
  4. Tool module according to one of the preceding claims, characterized in that the power cylinder (K) has, at its guide face (28) adjacent to the press ram (17), a height-adjustable mechanical stop (15) for limiting the travel of the press ram (17).
  5. Tool module according to one of the preceding claims, characterized in that a pressure equalization bore (29) provided with a low-pressure valve (13) opens into the reservoir space (26) from above.
  6. Tool module according to one of the preceding claims, characterized in that a venting bore (30) which can be tightly sealed with a venting screw (12) opens into the working space (22) from above.
  7. Tool module according to one of the preceding claims, characterized in that the cylinder bore of the working cylinder (A) is sealed on the tool side by a bearing bush (11) in which the piston rod (9) is mounted.
  8. Tool module according to one of the preceding claims, characterized in that the restoring spring element is a helical spring.
  9. Tool module according to one of Claims 1 to 7, characterized in that the restoring spring element is a gas spring element.
  10. Tool module according to Claim 9, characterized in that at least one annular space (31) filled with gas (G) serves as gas spring element, which is disposed in the radial direction between the piston rod (9) and the cylinder bore of the working cylinder (A) and in the axial direction between the working piston (10) and the bearing bush (11).
  11. Tool module according to Claim 10, characterized in that the annular space (31) is connected to a common cavity (32) provided in the interior of the working piston (10) and the piston rod (9) by means of a bore (16) present in the working piston (10) or in the piston rod (9).
  12. Tool module according to one of the preceding claims, characterized in that the power cylinder (K) and the working cylinder (A) form an inseparable unit.
  13. Tool module according to one of Claims 1 to 11, characterized in that the power cylinder (K) and the working cylinder (A) are each independently manipulable subunits, which can be joined to one another by means of a separate high-pressure line.
  14. Tool module according to Claim 13, characterized in that the separate high-pressure line is designed as flexible hose.
  15. Tool module according to one of Claims 12 to 14, characterized in that the power cylinder (K) is simultaneously coupled to a plurality of working cylinders (A).
  16. Tool module according to one of the preceding claims, characterized in that the piston rod (9) is provided with a rapid replacement device for receiving the tool (18).
EP19930908821 1993-04-26 1993-04-26 Press-driven tool module, in particular press-driven cross-punching or bending unit Expired - Lifetime EP0696960B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE1993/000370 WO1994025260A1 (en) 1993-04-26 1993-04-26 Press-driven tool module, in particular press-driven cross-punching or bending unit

Publications (2)

Publication Number Publication Date
EP0696960A1 EP0696960A1 (en) 1996-02-21
EP0696960B1 true EP0696960B1 (en) 1997-03-26

Family

ID=6888083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930908821 Expired - Lifetime EP0696960B1 (en) 1993-04-26 1993-04-26 Press-driven tool module, in particular press-driven cross-punching or bending unit

Country Status (8)

Country Link
US (1) US5606910A (en)
EP (1) EP0696960B1 (en)
JP (1) JPH08508681A (en)
KR (1) KR960701740A (en)
DE (2) DE59306000D1 (en)
ES (1) ES2100530T3 (en)
FR (1) FR2704478B3 (en)
WO (1) WO1994025260A1 (en)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
AT505160B1 (en) * 2007-05-30 2008-11-15 Bogner Fritz Mag HYDRAULIC SYSTEM
AT505440B1 (en) * 2007-05-30 2009-03-15 Bogner Fritz Mag HYDRAULIC SYSTEM

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JPH09308994A (en) * 1996-05-21 1997-12-02 Janome Sewing Mach Co Ltd Portable type motor-driven press
PT833061E (en) * 1996-09-26 2002-04-29 Simone Bordignon HYDRAULIC PRESS WITH OIL AUTOMATIC COMPENSATION
US6295813B1 (en) * 1997-11-24 2001-10-02 Diebolt International, Inc. Press driven tool actuator module
US5927178A (en) * 1997-11-24 1999-07-27 Diebolt International, Inc. Press driven tool actuator module
DE19830825B4 (en) * 1998-07-09 2006-10-12 Schnupp Gmbh & Co Hydraulik Kg forming tool
US8211359B2 (en) * 1999-07-29 2012-07-03 Beane Glenn L Method, system, and computer program for controlling a hydraulic press
DE102011014769B4 (en) * 2011-03-23 2016-06-09 Form Technology Gmbh Press with plunger and machining tool
DE102013105150A1 (en) * 2012-06-06 2013-12-12 Bundesrepublik Deutschland, vertreten durch das Bundesministerium für Wirtschaft und Technologie, dieses vertreten durch den Präsidenten der BAM, Bundesanstalt für Materialforschung und -prüfung Improved device for applying a directed pressure force to a plurality of samples
US10532481B2 (en) * 2015-11-25 2020-01-14 Ridge Tool Company Punch tool system
EP3181343B1 (en) * 2015-12-14 2018-09-05 Nitrogas, S.A.U. Hydraulic actuating device for a press
CN107138603B (en) * 2017-06-29 2019-12-03 奇瑞汽车股份有限公司 Hydraulic side blow aperture apparatus
DE102020000238B4 (en) 2020-01-16 2022-08-04 Fritz Stepper GmbH & Co. KG. core station
CN112275903A (en) * 2020-10-15 2021-01-29 深圳数码模汽车技术有限公司 Multi-angle side punching die and method for automobile framework part

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FR2348051A1 (en) * 1976-04-12 1977-11-10 Polymatic Sa Hydraulically operated sheet metal piercing tool - has intermediate chamber between pressure multiplier head and double acting piercing cylinder
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Publication number Priority date Publication date Assignee Title
AT505160B1 (en) * 2007-05-30 2008-11-15 Bogner Fritz Mag HYDRAULIC SYSTEM
AT505440B1 (en) * 2007-05-30 2009-03-15 Bogner Fritz Mag HYDRAULIC SYSTEM

Also Published As

Publication number Publication date
FR2704478B3 (en) 1995-03-24
EP0696960A1 (en) 1996-02-21
ES2100530T3 (en) 1997-06-16
KR960701740A (en) 1996-03-28
FR2704478A3 (en) 1994-11-04
JPH08508681A (en) 1996-09-17
DE9405764U1 (en) 1994-06-01
US5606910A (en) 1997-03-04
WO1994025260A1 (en) 1994-11-10
DE59306000D1 (en) 1997-04-30

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