EP0650780B1 - Transfer mechanism, especially for a transfer press - Google Patents

Transfer mechanism, especially for a transfer press Download PDF

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Publication number
EP0650780B1
EP0650780B1 EP94115058A EP94115058A EP0650780B1 EP 0650780 B1 EP0650780 B1 EP 0650780B1 EP 94115058 A EP94115058 A EP 94115058A EP 94115058 A EP94115058 A EP 94115058A EP 0650780 B1 EP0650780 B1 EP 0650780B1
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EP
European Patent Office
Prior art keywords
drive
forward feed
feed mechanism
press
housing
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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
EP94115058A
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German (de)
French (fr)
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EP0650780A1 (en
Inventor
Erich Harsch
Rainer Reichenbach
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Mueller Weingarten AG
Original Assignee
Maschinenfabrik Mueller Weingarten AG
Mueller Weingarten AG
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Publication of EP0650780A1 publication Critical patent/EP0650780A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/05—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work specially adapted for multi-stage presses

Definitions

  • the invention relates to a transfer drive according to the preamble of claim 1.
  • the transport device for transporting parts in a transfer press consists of gripper rails which, in addition to the longitudinal and lifting movement, carry out an additional transverse movement, gripper elements being provided on the gripper rails themselves.
  • the basic idea of such systems is that the workpieces or parts have to be transported from stage to stage of the press without the transport elements being in the tool room during the actual machining process. With the three-dimensional transfer system, the gripper rails must be moved laterally out of the tool room.
  • each gripper rail is articulated by means of a push rod on a slide which can be displaced transversely, the slide being able to be displaced transversely into a fixed starting position in order to adapt to the respective workpiece size.
  • the respective closing movement of the gripper rail then takes place as a lateral pivoting movement or transverse movement on a carriage which is fixed in the transverse direction by means of corresponding ball joints.
  • the cross-slidable slides themselves are attached to a cross-beam, which are connected to the gear housing of a press drive via conventional drive levers.
  • the gearboxes are stationary in the front area or entrance area of the step press and contain the usual cam disks that are driven by rollers to carry out the advancing, tensioning and lifting movement of the mounting rails, the gearbox being driven from the press head.
  • a basic illustration of such a drive for a pair of gripper rails is given in EP 0 210 745 A2 (FIG. 4).
  • the invention has for its object to reduce the amount of moving masses as much as possible in order to obtain a simplification of the construction and thus savings in manufacturing costs and operating costs. A significant reduction in transfer drive power is also contemplated.
  • the main idea of the drive device according to the invention is that the individual movements of the gripper rail are analyzed and corresponding movement sequences are optimized with regard to movable masses. For example, if one starts from the subject of DE 38 42 182 C1, the sequence of movements of the transverse movement or closing movement of the gripper rails is divided into the usual transverse pendulum movement of the gripper rail between a fixed slide and the gripper rail via a push rod that can be pivoted back and forth.
  • the further movement of each gripper rail relates to an adjustability (width adjustment) of the starting position of the slide on a crossbar, to a basic setting of the slide depending on the workpiece size or type adjust.
  • the slide for mounting a push rod for each gripper rail can accordingly be set on a crossbar in a position that is at the maximum outside or at the inside from where the respective closing movement of the respective gripper rail is carried out.
  • this adjustability of the set-up axes requires the structural effort of the crossbar with the associated drive for the slides assigned to the gripper rails.
  • the mass of the crossbar must also be moved with each working stroke.
  • the invention provides for decoupling these motion sequences in order to save masses that are unnecessarily moved.
  • the invention is based on the main idea that the adjustability of the gripper rail in its respective workpiece-dependent starting position is achieved by technical means that are not involved in the current work cycle. This is done according to the invention by shifting the required lateral adjustment movement into the drive housing of the drive gear. If the entire gear is consequently moved into the required, workpiece-dependent middle position, the drive lever protruding from the drive gear and pivotable in the longitudinal direction can be connected directly to the respective gripper rail via an associated push rod. The push rod articulated between the drive lever and the gripper rail then enables the usual gripping or closing movement of the gripper rail. As a result, all intermediate elements contained in known devices, such as. B. the driver crossbar to carry out the adjustment of the set-up axis.
  • the adjustment of the transmission housing as a whole has the advantage that considerably less moving masses have to be moved during operation of the gripper rails due to the lack of components. This gives a high saving of Manufacturing and operating costs. Since the transfer systems also require considerable acceleration and deceleration values, a significant reduction in the transfer drive power is also possible by reducing the moving masses.
  • the drive gear with corresponding cams, eccentrics and / or gears or direct coupling can be driven in an advantageous development of the invention by the central drive of the press itself or by its own drive motor.
  • the latter decouples the ram drive of the press from the drive system of the gripper rail.
  • a powerful electrical or electronic control for electrical coupling or for synchronizing the press with the transfer drive is then required.
  • the first exemplary embodiment shown in FIGS. 1 to 3 comprises a large-part step press with a plurality of processing stations 2 arranged one behind the other, each of which is assigned a lower tool 4 arranged on a table 3 and an upper tool 5 fastened to a press ram 6.
  • the press rams 6 are connected to associated head pieces 7 of the press, which are supported by lateral press stands 8.
  • each gripper rail 9, 10 serves to transport the workpieces to be deposited in the processing stations, pass through the press stages.
  • each gripper rail 9, 10 performs a horizontal longitudinal movement (arrow 15) forwards and backwards by means of an associated advancing mechanism 11, 12.
  • a lifting mechanism 13 for carrying out a vertical or lifting movement (arrow 16) of each gripper rail and a tensioning or closing mechanism 14 for carrying out a transverse movement or closing movement of each gripper rail (arrow 17) are provided.
  • the gripper rail can thus carry out a three-dimensional transport movement, that is to say the two gripper rails 9, 10 move synchronously into the tool space after the machining process has been completed and the tool space is open (clamping or closing movement), grasp the workpiece and lift it from the lower tool by means of the lifting movement.
  • a subsequent longitudinal movement of the Gripper rails transports the lifted workpiece to the subsequent processing station or an intermediate stage, where it is placed on a lower tool, for example.
  • the subsequent transverse movement of the two gripper rails outwards leads out of the press chamber so that the ram with the upper tool can move down onto the lower tool without being disturbed.
  • the stroke movement of the press ram 6 must be precisely coordinated with the workpiece transport via the gripper rails 9, 10. Accordingly, in the exemplary embodiment according to FIGS. 1 to 3, the advancement, lifting and tensioning mechanisms 11 to 14 are driven via the drive of the press, in particular an eccentric wheel 18, which simultaneously serves to drive the press rams 6.
  • the drive arranged in the head piece 7 of the press thus represents a forced synchronization with the advance, the lifting and the tensioning mechanisms 11 to 14 together.
  • the countershaft transmission 20 which can be seen in particular in FIGS. 1 and 2, consists of a first gearwheel 21 driven by the additional transmission 19, from which two horizontally extending countershafts 22, 22 'laterally lead into the drive housing 23, 23' of the two advancement mechanisms 11, 12 and there with a second gear 24, 24 'are connected.
  • the two advancement mechanisms 11, 12 within the respective drive housings 23, 23 ' are constructed in mirror image, however, so that the advancement mechanism 11 is described below.
  • the second gearwheel 24 connected to the countershaft 22 is connected within the transmission of the advancement mechanism to a third gearwheel 25 which is connected to a central one Shaft 26 is mounted.
  • Various cam disks 27, 28 are located on the shaft 26 and are picked up by associated rollers 29, 30.
  • a shaft 31, which is also mounted in the drive housing, is used to mount a drive lever 32, the pivoting movement of which in a vertical plane 33 is controlled by an angle ⁇ by the cams 27, 28.
  • the structure of the advance mechanism 11, 12, i.e. H. the gear arrangement within the drive housing 23, 23 'with drive gears or complementary curves corresponds to the usual state of the art.
  • the lifting mechanism 13 arranged on the side of the drive housing 23 ' is driven by the countershaft 22' which is guided through and extended through the drive housing 13, the gear arrangement 34 being designed within the gear housing 35 of the lifting mechanism in a manner known per se.
  • a mechanical lever connection 36 leads from the transmission housing 35 to the lifting and closing box 37, which carries out the combined lifting and closing movement of the gripper rails 9, 10.
  • the tensioning and closing mechanism 14 arranged on the right of the drive housing 23 in FIG. 1 is likewise driven via the countershaft 22 extended by the drive housing 23.
  • the gear arrangement 39 arranged within the gear housing 38 is in turn connected to the combined lifting and closing box 37 via a lever connection 40.
  • the particularity of the arrangement is, in particular, as shown in FIG. 1, that the entire housing 23, 23 'of the respective advancing mechanism 11, 12 can be shifted laterally by an amount l 1 , so that the vertical plane 33 of the drive lever 32, 32 'into position 33' shown in dashed lines in Fig. 1.
  • This The entire housing 23, 23 ' is displaced by means of a displacement drive 41 as is shown in more detail in FIG. 1.
  • the displacement drive 41 comprises a hydraulic or preferably electric drive motor 42 which acts via a deflection gear 43 on two drive shafts 45 arranged in the vertical plane of symmetry 44.
  • a deflection gear 43 on two drive shafts 45 arranged in the vertical plane of symmetry 44.
  • At a distance l 2 are at the lower end of the drive shaft 45 and at the upper end of the drive shaft 45 'each a further deflection gear 46, 46' from which two drive shafts 47, 47 'in the lower area and 48, 48' in the upper area Branch the area to the side.
  • the shafts 47, 47 'and 48, 48' also lie in a vertical plane 49 (see FIG. 2) which is perpendicular to the symmetry vertical plane 44.
  • the drive shafts 47, 47 'and 48, 48' are formed at least over an adjustment range corresponding to the distance l 1 as a threaded spindle, which each cooperate with a spindle nut 50 on the side walls 51 of the drive housing 23, 23 '. 1, the spindle nuts 50 interacting with the lower drive shafts 47, 47 'can be seen in the housing wall 51.
  • the spindle nuts interacting with the upper drive shafts 48, 48 ' are covered by the central shaft 26 of the respective gear arrangements, but are equally present.
  • the slopes of the threaded spindles 47, 47 'and 48, 48' are designed in opposite directions. Accordingly, if the drive 42 is actuated, the threaded spindles 47, 47 'and 48, 48' rotate in the same direction, so that the drive housing 23, 23 'in the direction of the closing movement (arrow 17) inwards or outwards in opposite directions Direction can be shifted. The lateral housing wall 51 then comes into the dot-dash position 51 'in the innermost or to be in the retracted position of the drive housing 23, 23 '. Likewise, the drive lever 32, 32 'moves into the position of its vertical plane indicated by 33'.
  • the upper countershafts 22, 22 'shown in FIG. 1 are designed as spline shafts on which the respective drive housing 23, 23' can shift laterally by the amount l 1 .
  • the two outer drive housings 13, 14 remain stationary in their position for the lifting mechanism or the tensioning or closing mechanism.
  • the drive lever 32, 32 ' is connected to the gripper rails 9, 10 via a push rod 52, 52' only shown in FIG. 1 and shown in FIGS. 2 and 3.
  • each gripper rail 9, 10 can then perform the lateral closing movement shown in FIGS. 1 and 3, the respective push rod 52, 52 'being pivoted by the angle ⁇ (see FIG. 3). 3, therefore, the closing movement of the gripper rail 9 into position 9 ', the closing movement of the gripper rail 10 into position 10'.
  • the respective drive lever 32, 32 'thus remains in its initial position when the set-up axis is set, so that it can be connected directly to the respective gripper rail 9, 10 via the respective push rod 52, 52'.
  • FIGS. 4 to 6 differs from the first embodiment of the invention according to FIGS. 1 to 3 essentially only in that the drive for the advance mechanism 11, 12 via a separate motor drive 54, 55 for the two associated gripper rails 9, 10 takes place. Otherwise, the same parts are identified by the same reference numerals as are described in the first exemplary embodiment.
  • the drive for the advancing mechanism is also shown here as an example.
  • the separate motor drives 54, 55 result in an independent drive for the three-dimensional movements of the two gripper rails 9, 10.
  • the electrical drives 54, 55 act directly on a gear 57 via their drive pinions 56, that performs the pivoting movement of the associated drive lever 32, 32 'about the axis 31, 31' by the angle ⁇ .
  • the gear 57 can also be designed as a gear segment in order to effect the pivoting movement of the drive lever 32, 32 '.
  • the drive lever 32, 32 ' is in turn connected to the respective gripper rail 9, 10 via a push rod 52, 52'.
  • FIG. 6 Another construction variant is shown in FIG. 6, where the drive motors 54, 55 for the advancing mechanism are connected directly to the axis 31, 31 '.
  • each drive housing 23, 23 ' is fastened to a guide rail 58, 58' arranged on the end face of the press, which is perpendicular to the longitudinal axis of the press in a vertical plane.
  • Each drive housing 23, 23 ' has a guide carriage 59 which allows the drive housing 23, 23' to be displaced transversely with the drive 54, 55 flanged on. 5 shows an upper and lower slide guide 59, 59 'for the respective drive housing.
  • the lateral displaceability in the transverse direction again takes place by means of a central electric drive motor 42 'located on the vertical center plane of symmetry, which acts via a deflection gear 43' on two laterally projecting drive shafts 60, 60 ', which lead as threaded spindles to the two drive housings 23, 23' and there are engaged with associated spindle nuts 50. Due to the opposite slope of the threaded spindles 60, 60 ', the drive housings 23, 23' are laterally shifted by the amount l 1 into the dashed position shown in FIG. 4, the respective drive motor 54, 55 being in the position 54 'or 55' wanders.

Description

Die Erfindung betrifft einen Transferantrieb nach dem Oberbegriff des Anspruchs 1.The invention relates to a transfer drive according to the preamble of claim 1.

Stand der Technik:State of the art:

Die Transporteinrichtung zum Transportieren von Teilen in einer Transferpresse besteht aus Greiferschienen, die neben der Längs- und Hubbewegung eine zusätzliche Querbewegung durchführen, wobei Greiferelemente an den Greiferschienen selbst vorgesehen sind. Der Grundgedanke derartiger Systeme liegt darin, daß die Werkstücke oder -teile von Stufe zu Stufe der Presse transportiert werden müssen, ohne daß sich die Transportelemente beim eigentlichen Bearbeitungsvorgang im Werkzeugraum befinden. Die Greiferschienen müssen beim dreidimensionalen Transfersystem aus dem Werkzeugraum seitlich wieder herausgefahren werden.The transport device for transporting parts in a transfer press consists of gripper rails which, in addition to the longitudinal and lifting movement, carry out an additional transverse movement, gripper elements being provided on the gripper rails themselves. The basic idea of such systems is that the workpieces or parts have to be transported from stage to stage of the press without the transport elements being in the tool room during the actual machining process. With the three-dimensional transfer system, the gripper rails must be moved laterally out of the tool room.

Aus der DE 38 42 182 C1 ist ein Greiferschienenantrieb für Stufenpressen nach der Gattung des Anspruchs 1 bekanntgeworden, bei welchem die Greiferschienen eine dreidimensionale Fahrbewegung ausführen. Insbesondere ist neben der üblichen Längsbewegung und Hubbewegung der beiden parallel verlaufenden Greiferschienen eine zusätzliche Querbewegung als Schließbewegung zum Greifen bzw. Spannen der Werkstücke vorgesehen. Hierfür ist jede Greiferschiene über eine Schubstange gelenkig an einem querverschiebbaren Schlitten gelagert, wobei der Schlitten zur Anpassung an die jeweilige Werkstückgröße in eine feste Ausgangsposition querverschiebbar ist. Die jeweilige Schließbewegung der Greiferschiene erfolgt dann als seitliche Schwenkbewegung oder Querbewegung an einem in Querrichtung feststehenden Schlitten mittels entsprechender Kugelgelenke. Die querverschiebbaren Schlitten selbst sind an einer Quertraverse befestigt, die über übliche Antriebshebel mit dem Getriebegehäuse eines Pressenantriebs verbunden sind. Die Getriebegehäuse sind stationär im vorderen Bereich oder Eingangsbereich der Stufenpresse angeordnet und beinhalten die üblichen von Rollen abgefahrenen Kurvenscheiben zur Durchführung der Vorrück-, Spann- und Hubbewegung der Tragschienen, wobei der Antrieb des Getriebes vom Pressenkopf aus erfolgt. Eine prinzipielle Darstellung eines solchen Antriebs eines Greiferschienenpaars ist in der EP 0 210 745 A2 (Fig. 4) wiedergegeben.DE 38 42 182 C1 is a gripper rail drive for Step presses according to the preamble of claim 1 become known, in which the gripper rails perform a three-dimensional movement. In particular, in addition to the usual longitudinal movement and lifting movement of the two parallel gripper rails, an additional transverse movement is provided as a closing movement for gripping or clamping the workpieces. For this purpose, each gripper rail is articulated by means of a push rod on a slide which can be displaced transversely, the slide being able to be displaced transversely into a fixed starting position in order to adapt to the respective workpiece size. The respective closing movement of the gripper rail then takes place as a lateral pivoting movement or transverse movement on a carriage which is fixed in the transverse direction by means of corresponding ball joints. The cross-slidable slides themselves are attached to a cross-beam, which are connected to the gear housing of a press drive via conventional drive levers. The gearboxes are stationary in the front area or entrance area of the step press and contain the usual cam disks that are driven by rollers to carry out the advancing, tensioning and lifting movement of the mounting rails, the gearbox being driven from the press head. A basic illustration of such a drive for a pair of gripper rails is given in EP 0 210 745 A2 (FIG. 4).

Nachteilig an einer solchen Anordnung ist die Bewegung von großen Massen zur Durchführung der dreidimensionalen Antriebsbewegung. Insbesondere sind auch solche Massen mitzubewegen, die jeweils für die Querverstellung der beiden Greiferschienen erforderlich sind.The disadvantage of such an arrangement is the movement of large masses for carrying out the three-dimensional drive movement. In particular, such masses are also to be moved, which are required in each case for the transverse adjustment of the two gripper rails.

Um eine Entkopplung vom Antrieb des Pressenstößels selbst zu erhalten, ist es aus der DE 33 29 900 C2 bekanntgeworden, eine dreidimensionale Bewegung der Greiferschienen durch jeweils voneinander getrennte Antriebe durchzuführen. Die Verstellbewegung erfolgt dabei im wesentlichen über Zahnstangengetriebe, die nur ungenau arbeiten und einen hohen baulichen Aufwand darstellen.In order to obtain a decoupling from the drive of the press ram itself, it has become known from DE 33 29 900 C2 to carry out a three-dimensional movement of the gripper rails by drives which are each separated from one another. The Adjustment movement takes place essentially via rack and pinion gearboxes, which work only inaccurately and represent a high structural outlay.

Aufgabe und Vorteile der Erfindung:Object and advantages of the invention:

Der Erfindung liegt die Aufgabe zugrunde, den Umfang an beweglichen Massen möglichst stark zu reduzieren, um eine Vereinfachung der Konstruktion und damit Einsparung von Herstellungskosten und Betriebskosten zu erhalten. Weiterhin ist eine wesentliche Verringerung der Transferantriebsleistung beabsichtigt.The invention has for its object to reduce the amount of moving masses as much as possible in order to obtain a simplification of the construction and thus savings in manufacturing costs and operating costs. A significant reduction in transfer drive power is also contemplated.

Diese Aufgabe wird ausgehend von einem Antrieb nach dem Oberbegriff des Anspruchs 1 durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This object is achieved on the basis of a drive according to the preamble of claim 1 by the characterizing features of claim 1.

In den Unteransprüchen sind vorteilhafte und zweckmäßige Weiterbildungen des erfindungsgemäßen Antriebssystems angegeben.Advantageous and expedient developments of the drive system according to the invention are specified in the subclaims.

Der erfindungsgemäßen Antriebseinrichtung liegt der Kerngedanke zugrunde, daß die einzelnen Bewegungen der Greiferschiene analysiert und entsprechende Bewegungsabläufe hinsichtlich beweglicher Massen optimiert werden. Geht man beispielsweise vom Gegenstand der einleitend genannten DE 38 42 182 C1 aus, so gliedert sich der Bewegungsablauf der Querbewegung oder Schließbewegung der Greiferschienen zum einen in die übliche querverlaufende Pendelbewegung der Greiferschiene zwischen einem feststehenden Schlitten und der Greiferschiene über eine hin und her schwenkbare Schubstange. Die weitere Bewegung jeder Greiferschiene bezieht sich auf eine Verstellbarkeit (Weiteneinstellung) der Ausgangslage des Schlittens an einer Quertraverse, um eine Grundeinstellung des Schlittens je nach Werkstückgröße oder Werkstückart einzustellen. Der Schlitten zur Lagerung einer Schubstange für jede Greiferschiene kann demnach an einer Quertraverse in einer maximal außenliegenden oder maximal innenliegenden Position eingestellt werden, von wo aus die jeweilige Schließbewegung der jeweiligen Greiferschiene ausgeführt wird. Diese Verstellbarkeit der Rüstachsen erfordert jedoch den baulichen Aufwand der Quertraverse mit zugehörigem Antrieb für die jeweils den Greiferschienen zugeordneten Schlitten. Weiterhin muß auch die Masse der Quertraverse bei jedem Arbeitshub mitbewegt werden.The main idea of the drive device according to the invention is that the individual movements of the gripper rail are analyzed and corresponding movement sequences are optimized with regard to movable masses. For example, if one starts from the subject of DE 38 42 182 C1, the sequence of movements of the transverse movement or closing movement of the gripper rails is divided into the usual transverse pendulum movement of the gripper rail between a fixed slide and the gripper rail via a push rod that can be pivoted back and forth. The further movement of each gripper rail relates to an adjustability (width adjustment) of the starting position of the slide on a crossbar, to a basic setting of the slide depending on the workpiece size or type adjust. The slide for mounting a push rod for each gripper rail can accordingly be set on a crossbar in a position that is at the maximum outside or at the inside from where the respective closing movement of the respective gripper rail is carried out. However, this adjustability of the set-up axes requires the structural effort of the crossbar with the associated drive for the slides assigned to the gripper rails. Furthermore, the mass of the crossbar must also be moved with each working stroke.

Demgegenüber sieht die Erfindung vor, diese Bewegungsabläufe zu entkoppeln, um eine Einsparung von unnötig zu bewegenden Massen zu erhalten. Dabei liegt der Erfindung der Kerngedanke zugrunde, daß die Verstellbarkeit der Greiferschiene in ihrer jeweiligen, werkstückabhängigen Ausgangsposition durch technische Mittel erfolgt, die nicht am laufenden Arbeitstakt beteiligt sind. Dies geschieht erfindungsgemäß durch eine Verlagerung der erforderlichen seitlichen Verstellbewegung in das Antriebsgehäuse des Antriebsgetriebes. Wird demzufolge das gesamte Getriebe in die erforderliche, werkstückabhängige Mittelposition verfahren, so kann der aus dem Antriebsgetriebe herausragende, in Längsrichtung verschwenkbare Antriebshebel direkt über eine zugehörige Schubstange mit der jeweiligen Greiferschiene verbunden werden. Die zwischen Antriebshebel und Greiferschiene gelenkig gelagerte Schubstange ermöglicht dann die übliche Spann- oder Schließbewegung der Greiferschiene. Hierdurch können alle, bei bekannten Einrichtungen enthaltenen Zwischenglieder, wie z. B. die Mitnehmertraverse zur Durchführung der Verstellung der Rüstachse entfallen.In contrast, the invention provides for decoupling these motion sequences in order to save masses that are unnecessarily moved. The invention is based on the main idea that the adjustability of the gripper rail in its respective workpiece-dependent starting position is achieved by technical means that are not involved in the current work cycle. This is done according to the invention by shifting the required lateral adjustment movement into the drive housing of the drive gear. If the entire gear is consequently moved into the required, workpiece-dependent middle position, the drive lever protruding from the drive gear and pivotable in the longitudinal direction can be connected directly to the respective gripper rail via an associated push rod. The push rod articulated between the drive lever and the gripper rail then enables the usual gripping or closing movement of the gripper rail. As a result, all intermediate elements contained in known devices, such as. B. the driver crossbar to carry out the adjustment of the set-up axis.

Die Verstellung des Getriebegehäuses insgesamt hat demzufolge den Vorteil, daß erheblich weniger bewegliche Massen aufgrund fehlender Bauteile während des Betriebs der Greiferschienen bewegt werden müssen. Dies gibt eine hohe Einsparung von Herstellungs- und Betriebskosten. Da bei den Transfersystemen auch beträchtliche Beschleunigungs- und Verzögerungswerte gefordert werden, ist durch die Verringerung der beweglichen Massen auch eine wesentliche Reduzierung der Transferantriebsleistung möglich.The adjustment of the transmission housing as a whole has the advantage that considerably less moving masses have to be moved during operation of the gripper rails due to the lack of components. This gives a high saving of Manufacturing and operating costs. Since the transfer systems also require considerable acceleration and deceleration values, a significant reduction in the transfer drive power is also possible by reducing the moving masses.

Das Antriebsgetriebe mit entsprechenden Kurvenscheiben, Exzentern und/oder Zahnrädern oder Direktkoppelung kann in vorteilhafter Weiterbildung der Erfindung vom Zentralantrieb der Presse selbst oder durch einen eigenen Antriebsmotor angetrieben werden. Letzteres bewirkt eine Entkopplung des Stößelantriebs der Presse vom Antriebssystem der Greiferschiene. Jedoch ist dann eine leistungsfähige elektrische bzw. elektronische Steuerung zur elektrischen Kopplung bzw. zur Synchronisierung der Presse mit dem Transferantrieb erforderlich.The drive gear with corresponding cams, eccentrics and / or gears or direct coupling can be driven in an advantageous development of the invention by the central drive of the press itself or by its own drive motor. The latter decouples the ram drive of the press from the drive system of the gripper rail. However, a powerful electrical or electronic control for electrical coupling or for synchronizing the press with the transfer drive is then required.

Weitere Einzelheiten und Vorteile ergeben sich aus der nachfolgenden Beschreibung von Ausführungsbeispielen im Zusammenhang mit der Figurenbeschreibung.Further details and advantages result from the following description of exemplary embodiments in connection with the description of the figures.

Es zeigen

Fig. 1 bis 3
ein erstes Ausführungsbeispiel einer Greiferschienenantriebsvorrichtung, wobei Fig. 1 eine Stirnansicht auf die Presse, Fig. 2 eine Seitenansicht der Darstellung nach Fig. 1 und Fig. 3 eine Draufsicht nach Fig. 2 mit jeweils erforderlichen Details zeigt,
Fig. 4
eine Draufsicht einer Ausführungsvariante mit eigenem Antrieb,
Fig. 5
eine Seitenansicht der Darstellung nach Fig. 4 und
Fig. 6
eine Seitenansicht der Darstellung nach Fig. 4 jedoch mit geändertem Antriebsprinzip.
Show it
1 to 3
1 shows a first exemplary embodiment of a gripper rail drive device, FIG. 1 showing an end view of the press, FIG. 2 showing a side view of the illustration according to FIG. 1 and FIG. 3 showing a top view according to FIG.
Fig. 4
a plan view of a variant with its own drive,
Fig. 5
a side view of the illustration of FIGS. 4 and
Fig. 6
a side view of the illustration of FIG. 4 but with a modified drive principle.

Beschreibung von Ausführungsbeispielen:Description of exemplary embodiments:

Das in den Figuren 1 bis 3 dargestellte erste Ausführungsbeispiel umfaßt eine Großteil-Stufenpresse mit einer Vielzahl hintereinander angeordneten Bearbeitungsstationen 2, denen jeweils ein auf einem Tisch 3 angeordnetes Unterwerkzeug 4 sowie ein an einem Pressenstößel 6 befestigtes Oberwerkzeug 5 zugeordnet ist. Die Pressenstößel 6 sind mit zugehörigen Kopfstücken 7 der Presse verbunden, die von seitlichen Pressenständern 8 getragen sind.The first exemplary embodiment shown in FIGS. 1 to 3 comprises a large-part step press with a plurality of processing stations 2 arranged one behind the other, each of which is assigned a lower tool 4 arranged on a table 3 and an upper tool 5 fastened to a press ram 6. The press rams 6 are connected to associated head pieces 7 of the press, which are supported by lateral press stands 8.

Durch die Pressenstufen führen zwei seitlich, parallel zueinander angeordnete Greiferschienen 9, 10, die zum Transport der in den Bearbeitungsstationen abzulegenden Werkstücke dienen. Hierfür führt jede Greiferschiene 9, 10 mittels eines zugehörigen Vorrückmechanismus 11, 12 eine horizontale Längsbewegung (Pfeil 15) vor und zurück durch.Two laterally parallel gripper rails 9, 10, which serve to transport the workpieces to be deposited in the processing stations, pass through the press stages. For this purpose, each gripper rail 9, 10 performs a horizontal longitudinal movement (arrow 15) forwards and backwards by means of an associated advancing mechanism 11, 12.

Weiterhin ist ein Hubmechanismus 13 zur Durchführung einer Vertikal- oder Hubbewegung (Pfeil 16) jeder Greiferschiene und ein Spann- bzw. Schließmechanismus 14 zur Durchführung einer Querbewegung oder Schließbewegung jeder Greiferschiene (Pfeil 17) vorgesehen. Damit kann die Greiferschiene eine dreidimensionale Transportbewegung durchführen, d. h. die beiden Greiferschienen 9, 10 fahren nach vollzogenem Bearbeitungsvorgang bei geöffnetem Werkzeugraum synchron in den Werkzeugraum hinein (Spann- bzw. Schließbewegung), ergreifen das Werkstück und heben es mittels der Hubbewegung vom Unterwerkzeug ab. Eine nachfolgende Längsbewegung der Greiferschienen transportiert das abgehobene Werkstück in die nachfolgende Bearbeitungsstation oder einer Zwischenstufe und legt dieses dort beispielsweise wiederum auf ein Unterwerkzeug ab. Die nachfolgende Querbewegung der beiden Greiferschienen nach außen führen aus dem Pressenraum heraus, damit der Stößel mit dem Oberwerkzeug ungestört nach unten auf das Unterwerkzeug fahren kann.Furthermore, a lifting mechanism 13 for carrying out a vertical or lifting movement (arrow 16) of each gripper rail and a tensioning or closing mechanism 14 for carrying out a transverse movement or closing movement of each gripper rail (arrow 17) are provided. The gripper rail can thus carry out a three-dimensional transport movement, that is to say the two gripper rails 9, 10 move synchronously into the tool space after the machining process has been completed and the tool space is open (clamping or closing movement), grasp the workpiece and lift it from the lower tool by means of the lifting movement. A subsequent longitudinal movement of the Gripper rails transports the lifted workpiece to the subsequent processing station or an intermediate stage, where it is placed on a lower tool, for example. The subsequent transverse movement of the two gripper rails outwards leads out of the press chamber so that the ram with the upper tool can move down onto the lower tool without being disturbed.

Aus dieser Darstellung eines Arbeitshubes wird ersichtlich, daß die Hubbewegung des Pressenstößels 6 genauestens mit dem Werkstücktransport über die Greiferschienen 9, 10 abgestimmt sein muß. Demzufolge erfolgt beim Ausführungsbeispiel nach den Figuren 1 bis 3 der Antrieb von Vorrück-, Hub- und Spannmechanismus 11 bis 14 über den Antrieb der Presse, insbesondere ein Exzenterrad 18, welcher gleichzeitig zum Antrieb der Pressenstößel 6 dient. Der im Kopfstück 7 der Presse angeordnete Antrieb stellt somit eine Zwangssynchronisation mit den Vorrück-, den Hub- und den Spannmechanismus 11 bis 14 gemeinsam dar.From this representation of a working stroke it can be seen that the stroke movement of the press ram 6 must be precisely coordinated with the workpiece transport via the gripper rails 9, 10. Accordingly, in the exemplary embodiment according to FIGS. 1 to 3, the advancement, lifting and tensioning mechanisms 11 to 14 are driven via the drive of the press, in particular an eccentric wheel 18, which simultaneously serves to drive the press rams 6. The drive arranged in the head piece 7 of the press thus represents a forced synchronization with the advance, the lifting and the tensioning mechanisms 11 to 14 together.

Das insbesondere aus den Figuren 1 und 2 ersichtliche Vorlegegetriebe 20 besteht aus einem vom Zusatzgetriebe 19 angetriebenen ersten Zahnrad 21, von welchem seitlich zwei horizontal verlaufende Vorlegewellen 22, 22' in die Antriebsgehäuse 23, 23' der beiden Vorrückmechanismen 11, 12 führen und dort mit einem zweiten Zahnrad 24, 24' verbunden sind.The countershaft transmission 20, which can be seen in particular in FIGS. 1 and 2, consists of a first gearwheel 21 driven by the additional transmission 19, from which two horizontally extending countershafts 22, 22 'laterally lead into the drive housing 23, 23' of the two advancement mechanisms 11, 12 and there with a second gear 24, 24 'are connected.

Die beiden Vorrückmechanismen 11, 12 innerhalb der jeweiligen Antriebsgehäuse 23, 23' sind gleich jedoch spiegelbildlich aufgebaut, so daß im weiteren der Vorrückmechanismus 11 beschrieben wird.The two advancement mechanisms 11, 12 within the respective drive housings 23, 23 'are constructed in mirror image, however, so that the advancement mechanism 11 is described below.

Das mit der Vorlegewelle 22 verbundene zweite Zahnrad 24 ist innerhalb des Getriebes des Vorrückmechanismus mit einem dritten Zahnrad 25 verbunden, welches an einer zentralen Welle 26 gelagert ist. Auf der Welle 26 befinden sich verschiedene Kurvenscheiben 27, 28, die von zugehörigen Rollen 29, 30 abgegriffen werden. Eine im Antriebsgehäuse weiterhin gelagerte Welle 31 dient zur Lagerung eines Antriebshebels 32, dessen Schwenkbewegung in einer Vertikalebene 33 um einen Winkel α durch die Kurvenscheiben 27, 28 gesteuert wird.The second gearwheel 24 connected to the countershaft 22 is connected within the transmission of the advancement mechanism to a third gearwheel 25 which is connected to a central one Shaft 26 is mounted. Various cam disks 27, 28 are located on the shaft 26 and are picked up by associated rollers 29, 30. A shaft 31, which is also mounted in the drive housing, is used to mount a drive lever 32, the pivoting movement of which in a vertical plane 33 is controlled by an angle α by the cams 27, 28.

Der Aufbau des Vorrückmechanismus 11, 12, d. h. die Getriebeanordnung innerhalb des Antriebsgehäuses 23, 23' mit Antriebszahnräder bzw. Komplementärkurven entspricht dem üblichen Stand der Technik. Gleichermaßen wird der seitlich des Antriebsgehäuses 23' angeordnete Hubmechanismus 13 durch die durch das Antriebsgehäuse 13 hindurchgeführte und verlängerte Vorlegewelle 22' angetrieben, wobei die Getriebeanordnung 34 innerhalb des Getriebegehäuses 35 des Hubmechanismus in an sich bekannter Weise ausgestaltet ist. Eine nur gestrichelt angedeutete mechanische Hebelverbindung 36 führt vom Getriebegehäuse 35 zum Hub- und Schließkasten 37, der die kombinierte Hub- und Schließbewegung der Greiferschienen 9, 10 durchführt.The structure of the advance mechanism 11, 12, i.e. H. the gear arrangement within the drive housing 23, 23 'with drive gears or complementary curves corresponds to the usual state of the art. Likewise, the lifting mechanism 13 arranged on the side of the drive housing 23 'is driven by the countershaft 22' which is guided through and extended through the drive housing 13, the gear arrangement 34 being designed within the gear housing 35 of the lifting mechanism in a manner known per se. A mechanical lever connection 36, indicated only by dashed lines, leads from the transmission housing 35 to the lifting and closing box 37, which carries out the combined lifting and closing movement of the gripper rails 9, 10.

Auch der in Fig. 1 rechts des Antriebsgehäuses 23 angeordnete Spann- und Schließmechanismus 14 wird gleichermaßen über die durch das Antriebsgehäuse 23 verlängerte Vorlegewelle 22 angetrieben. Die innerhalb des Getriebegehäuses 38 angeordnete Getriebeanordnung 39 ist wiederum über eine Hebelverbindung 40 mit dem kombinierten Hub- und Schließkasten 37 verbunden.The tensioning and closing mechanism 14 arranged on the right of the drive housing 23 in FIG. 1 is likewise driven via the countershaft 22 extended by the drive housing 23. The gear arrangement 39 arranged within the gear housing 38 is in turn connected to the combined lifting and closing box 37 via a lever connection 40.

Die Besonderheit der Anordnung liegt nun insbesondere gemäß der Darstellung in Fig. 1 darin, daß das gesamte Gehäuse 23, 23' des jeweiligen Vorrückmechanismus 11, 12 seitlich um einen Betrag l1 verschoben werden kann, so daß die Vertikalebene 33 des Antriebshebels 32, 32' in die in Fig. 1 gestrichelte Position 33' verschiebbar ist. Diese Verschiebung des kompletten Gehäuses 23, 23' geschieht mittels eines Verschiebeantriebs 41 wie er in Fig. 1 näher dargestellt ist.The particularity of the arrangement is, in particular, as shown in FIG. 1, that the entire housing 23, 23 'of the respective advancing mechanism 11, 12 can be shifted laterally by an amount l 1 , so that the vertical plane 33 of the drive lever 32, 32 'into position 33' shown in dashed lines in Fig. 1. This The entire housing 23, 23 'is displaced by means of a displacement drive 41 as is shown in more detail in FIG. 1.

Der Verschiebeantrieb 41 umfaßt einen hydraulischen oder vorzugsweise elektrischen Antriebsmotor 42 der über ein Umlenkgetriebe 43 auf zwei in der vertikalen Symmetrieebene 44 angeordnete Antriebswellen 45 einwirkt. In einem Abstand l2 befinden sich am unteren Ende der Antriebswelle 45 bzw. am oberen Ende der Antriebswelle 45' jeweils ein weiteres Umlenkgetriebe 46, 46' von welchem aus jeweils zwei Antriebswellen 47, 47' im unteren Bereich sowie 48, 48' im oberen Bereich seitlich abzweigen. Die Wellen 47, 47' bzw. 48, 48' liegen ebenfalls in einer Vertikalebene 49 (siehe Fig. 2), die senkrecht zur Symmetrievertikalebene 44 steht.The displacement drive 41 comprises a hydraulic or preferably electric drive motor 42 which acts via a deflection gear 43 on two drive shafts 45 arranged in the vertical plane of symmetry 44. At a distance l 2 are at the lower end of the drive shaft 45 and at the upper end of the drive shaft 45 'each a further deflection gear 46, 46' from which two drive shafts 47, 47 'in the lower area and 48, 48' in the upper area Branch the area to the side. The shafts 47, 47 'and 48, 48' also lie in a vertical plane 49 (see FIG. 2) which is perpendicular to the symmetry vertical plane 44.

Die Antriebswellen 47, 47' bzw. 48, 48' sind wenigstens über einen dem Abstand l1 entsprechenden Verstellbereich als Gewindespindel ausgebildet, die jeweils mit einer Spindelmutter 50 an den Seitenwandungen 51 der Antriebsgehäuse 23, 23' zusammenwirken. In der Fig. 1 sind die mit den unteren Antriebswellen 47, 47' zusammenwirkenden Spindelmuttern 50 in der Gehäusewandung 51 erkennbar. Die mit den oberen Antriebswellen 48, 48' zusammenwirkenden Spindelmuttern sind durch die zentrale Welle 26 der jeweiligen Getriebeanordnungen verdeckt, jedoch gleichermaßen vorhanden.The drive shafts 47, 47 'and 48, 48' are formed at least over an adjustment range corresponding to the distance l 1 as a threaded spindle, which each cooperate with a spindle nut 50 on the side walls 51 of the drive housing 23, 23 '. 1, the spindle nuts 50 interacting with the lower drive shafts 47, 47 'can be seen in the housing wall 51. The spindle nuts interacting with the upper drive shafts 48, 48 'are covered by the central shaft 26 of the respective gear arrangements, but are equally present.

Die Steigungen der Gewindespindeln 47, 47' bzw. 48, 48' sind gegenläufig ausgebildet. Wird demzufolge der Antrieb 42 betätigt, so drehen sich die Gewindespindeln 47, 47' und 48, 48' in jeweils gleicher Richtung, so daß die Antriebsgehäuse 23, 23' in Richtung der Schließbewegung (Pfeil 17) nach innen oder nach außen in jeweils entgegengesetzter Richtung verschoben werden können. Die seitliche Gehäusewandung 51 kommt dann in die strichpunktierte Lage 51' in innerster oder zusammengefahrener Stellung der Antriebsgehäuse 23, 23' zu liegen. Gleichermaßen wandert der Antriebshebel 32, 32' in die mit 33' angegebene Lage seiner Vertikalebene.The slopes of the threaded spindles 47, 47 'and 48, 48' are designed in opposite directions. Accordingly, if the drive 42 is actuated, the threaded spindles 47, 47 'and 48, 48' rotate in the same direction, so that the drive housing 23, 23 'in the direction of the closing movement (arrow 17) inwards or outwards in opposite directions Direction can be shifted. The lateral housing wall 51 then comes into the dot-dash position 51 'in the innermost or to be in the retracted position of the drive housing 23, 23 '. Likewise, the drive lever 32, 32 'moves into the position of its vertical plane indicated by 33'.

Um diese Verschiebbarkeit zu ermöglichen, sind die in Fig. 1 dargestellten oberen Vorlegewellen 22, 22' als Keilwellen ausgebildet, auf denen sich das jeweilige Antriebsgehäuse 23, 23' seitlich um den Betrag l1 verschieben kann. Dabei bleiben die beiden äußeren Antriebsgehäuse 13, 14 für den Hubmechanismus bzw. den Spann- bzw. Schließmechanismus in ihrer Lage stationär.In order to enable this displaceability, the upper countershafts 22, 22 'shown in FIG. 1 are designed as spline shafts on which the respective drive housing 23, 23' can shift laterally by the amount l 1 . The two outer drive housings 13, 14 remain stationary in their position for the lifting mechanism or the tensioning or closing mechanism.

Aufgrund der seitlichen Verschiebbarkeit der gesamten Getriebeanordnung in den Antriebsgehäusen 23, 23' ergibt sich die Verschiebbarkeit des jeweiligen Antriebshebels 32, 32'. Der Antriebshebel 32, 32' ist über eine in Fig. 1 nur angedeutete, in Fig. 2 und 3 dargestellte Schubstange 52, 52' mit den Greiferschienen 9, 10 verbunden. Dabei ermöglichen Kugelgelenke 53 an den Enden der Schubstangen 52, 52' eine seitliche Verschwenkbarkeit der Schubstangen.The displaceability of the respective drive lever 32, 32 'results from the lateral displaceability of the entire gear arrangement in the drive housings 23, 23'. The drive lever 32, 32 'is connected to the gripper rails 9, 10 via a push rod 52, 52' only shown in FIG. 1 and shown in FIGS. 2 and 3. Ball joints 53 at the ends of the push rods 52, 52 'enable the push rods to be pivoted sideways.

Wie einleitend beschrieben, erfolgt die Positionierung der Antriebsgehäuse 23, 23' in Abhängigkeit des in der Presse zu bearbeitenden Werkstücks. Mittels des Verschiebeantriebs 41 werden die beiden Antriebshebel 32, 32' seitlich solange verschoben, daß die Vertikalmittelebene 33 in einer mittigen Ausgangslage angeordnet ist, wie dies in den Fig. 1 und 3 in der äußeren Getriebeanordnung sowie gestrichelt in der inneren Getriebeanordnung gezeigt ist. Von dieser fest eingestellten Rüstachse kann dann jede Greiferschiene 9, 10, die in den Figuren 1 und 3 dargestellte seitliche Schließbewegung durchführen, wobei die jeweilige Schubstange 52, 52' um den Winkel β verschwenkt wird (siehe Fig. 3). In der Anordnung nach Fig. 3 erfolgt deshalb die Schließbewegung der Greiferschiene 9 in die Position 9', die Schließbewegung der Greiferschiene 10 in die Position 10'. Mit 9'' bzw. 10'' ist die maximal mögliche innerste Position der beiden Greiferschienen nach Verschiebung des Antriebsgehäuses um den Betrag l1 in die innerste Position angegeben. Die zugehörige äußere Schwenkposition der beiden Greiferschienen 9, 10 ist zur Beibehaltung der Übersichtlichkeit der Zeichnungen nicht mehr dargestellt, sondern lediglich mit der zugehörigen Schwenkwinkelverstellung β gezeigt.As described in the introduction, the drive housings 23, 23 'are positioned as a function of the workpiece to be machined in the press. By means of the displacement drive 41, the two drive levers 32, 32 'are laterally displaced until the vertical center plane 33 is arranged in a central starting position, as shown in FIGS. 1 and 3 in the outer gear arrangement and in dashed lines in the inner gear arrangement. From this set setting axis each gripper rail 9, 10 can then perform the lateral closing movement shown in FIGS. 1 and 3, the respective push rod 52, 52 'being pivoted by the angle β (see FIG. 3). 3, therefore, the closing movement of the gripper rail 9 into position 9 ', the closing movement of the gripper rail 10 into position 10'. With 9 '' or 10 '' the maximum possible innermost position of the two gripper rails after moving the drive housing by the amount l 1 into the innermost position is specified. The associated outer pivot position of the two gripper rails 9, 10 is no longer shown to maintain the clarity of the drawings, but is only shown with the associated pivot angle adjustment β.

Während des Bearbeitungsvorgangs bleibt demnach bei eingestellter Rüstachse der jeweilige Antriebshebel 32, 32' in seiner eingerichteten Ausgangslage stehen, so daß dieser über die jeweilige Schubstange 52, 52' direkt mit der jeweiligen Greiferschiene 9, 10 verbunden werden kann.During the machining process, the respective drive lever 32, 32 'thus remains in its initial position when the set-up axis is set, so that it can be connected directly to the respective gripper rail 9, 10 via the respective push rod 52, 52'.

Das weitere Ausführungsbeispiel der Erfindung nach Fig. 4 bis 6 unterscheidet sich vom ersten Ausführungsbeispiel der Erfindung nach Fig. 1 bis 3 im wesentlichen nur dadurch, daß der Antrieb für Vorrückmechanismus 11, 12 über einen jeweils separaten Motorantrieb 54, 55 für die beiden zugehörigen Greiferschienen 9, 10 erfolgt. Im übrigen sind gleiche Teile mit gleichen Bezugszeichen gekennzeichnet, wie sie im ersten Ausführungsbeispiel beschrieben sind. Exemplarisch ist auch hier der Antrieb für den Vorrückmechanismus dargestellt.The further embodiment of the invention according to FIGS. 4 to 6 differs from the first embodiment of the invention according to FIGS. 1 to 3 essentially only in that the drive for the advance mechanism 11, 12 via a separate motor drive 54, 55 for the two associated gripper rails 9, 10 takes place. Otherwise, the same parts are identified by the same reference numerals as are described in the first exemplary embodiment. The drive for the advancing mechanism is also shown here as an example.

Durch die separaten Motorantriebe 54, 55 ergibt sich ein eigenständiger Antrieb für die dreidimensionalen Bewegungen der beiden Greiferschienen 9, 10. Wie in Fig. 4 und 5 angedeutet, wirken die elektrischen Antriebe 54, 55 über ihre Antriebsritzel 56 unmittelbar auf ein Getriebe 57 ein, das die Schwenkbewegung des jeweils zugehörigen Antriebshebels 32, 32' um die Achse 31, 31' um den Winkel α durchführt. Das Getriebe 57 kann auch als Zahnradsegment ausgebildet sein, um die Schwenkbewegung des Antriebshebels 32, 32' zu bewirken. Der Antriebshebel 32, 32' ist, wie zuvor beschrieben, wiederum über eine Schubstange 52, 52' mit der jeweiligen Greiferschiene 9, 10 verbunden.The separate motor drives 54, 55 result in an independent drive for the three-dimensional movements of the two gripper rails 9, 10. As indicated in FIGS. 4 and 5, the electrical drives 54, 55 act directly on a gear 57 via their drive pinions 56, that performs the pivoting movement of the associated drive lever 32, 32 'about the axis 31, 31' by the angle α. The gear 57 can also be designed as a gear segment in order to effect the pivoting movement of the drive lever 32, 32 '. As previously described, the drive lever 32, 32 'is in turn connected to the respective gripper rail 9, 10 via a push rod 52, 52'.

Eine weitere Konstruktionsvariante zeigt Fig. 6, wo die Antriebsmotore 54, 55 für den Vorrückmechanismus direkt mit der Achse 31, 31' verbunden sind.Another construction variant is shown in FIG. 6, where the drive motors 54, 55 for the advancing mechanism are connected directly to the axis 31, 31 '.

Die Verstellung der Antriebsgehäuse 23, 23' für den Vorrückmechanismus 11, 12 erfolgt wiederum in analoger Weise wie zuvor beschrieben. Hierfür ist das jeweilige Gehäuse 23, 23' an einer stirnseitig der Presse angeordneten Führungsschiene 58, 58' befestigt, die in einer Vertikalebene quer zur Pressenlängsachse steht. Jedes Antriebsgehäuse 23, 23' weist einen Führungsschlitten 59 auf, der eine Querverschiebbarkeit der Antriebsgehäuse 23, 23' mit angeflanschtem Antrieb 54, 55 erlaubt. Aus Fig. 5 ergibt sich eine obere und untere Schlittenführung 59, 59' für das jeweilige Antriebsgehäuse. Die seitliche Verschiebbarkeit in Querrichtung erfolgt wiederum mittels eines auf der vertikalen Symmetriemittelebene liegenden zentralen elektrischen Antriebsmotors 42' der über ein Umlenkgetriebe 43' auf zwei seitlich auskragende Antriebswellen 60, 60' einwirkt, die als Gewindespindeln zu den beiden Antriebsgehäusen 23, 23' führen und dort mit zugehörigen Spindelmuttern 50 in Eingriff stehen. Durch die gegenläufige Steigung der Gewindespindeln 60, 60' werden die Antriebsgehäuse 23, 23' seitlich um den Betrag l1 in die in Fig. 4 dargestellte gestrichelte Position verschoben, wobei der jeweilige Antriebsmotor 54, 55 in die Position 54' bzw. 55' wandert.The adjustment of the drive housing 23, 23 'for the advancing mechanism 11, 12 is again carried out in an analogous manner to that previously described. For this purpose, the respective housing 23, 23 'is fastened to a guide rail 58, 58' arranged on the end face of the press, which is perpendicular to the longitudinal axis of the press in a vertical plane. Each drive housing 23, 23 'has a guide carriage 59 which allows the drive housing 23, 23' to be displaced transversely with the drive 54, 55 flanged on. 5 shows an upper and lower slide guide 59, 59 'for the respective drive housing. The lateral displaceability in the transverse direction again takes place by means of a central electric drive motor 42 'located on the vertical center plane of symmetry, which acts via a deflection gear 43' on two laterally projecting drive shafts 60, 60 ', which lead as threaded spindles to the two drive housings 23, 23' and there are engaged with associated spindle nuts 50. Due to the opposite slope of the threaded spindles 60, 60 ', the drive housings 23, 23' are laterally shifted by the amount l 1 into the dashed position shown in FIG. 4, the respective drive motor 54, 55 being in the position 54 'or 55' wanders.

In Fig. 4 sind lediglich die beiden Antriebsgehäuse 23, 23' für den zugehörigen Vorrückmechanismus 11, 12 dargestellt. Ein separater Antrieb und eine entsprechende Anordnung kann für den Hubmechanismus 13 bzw. den Spann- und Schließmechanismus 14 in analoger Weise, jedoch stationär angeordnet vorgesehen sein.4, only the two drive housings 23, 23 'for the associated advancing mechanism 11, 12 are shown. A separate drive and a corresponding arrangement can be provided for the lifting mechanism 13 or the tensioning and closing mechanism 14 in an analogous manner, but arranged in a stationary manner.

Selbstverständlich müssen die unabhängigen Einzelantriebe in ihrem Bewegungsablauf untereinander sowie mit der Bewegung der Presse synchronisiert werden.Of course, the movement of the independent individual drives must be synchronized with each other and with the movement of the press.

Die Erfindung ist nicht auf das dargestellte und beschriebene Ausführungsbeispiel beschränkt. Sie umfaßt auch vielmehr alle fachmännischen Weiterbildungen innerhalb des durch die Patentansprüche definierten Schutzbereichs.The invention is not restricted to the exemplary embodiment shown and described. Rather, it also includes all professional developments within the scope of protection defined by the claims.

Claims (10)

  1. A transfer drive for a press, with a device for the triaxial transport of workpieces through machining stations of the press, with, disposed parallel with each other, two carrier or gripper rails (9, 10) which, by means of a forward feed mechanism (11, 12), perform a horizontal longitudinal movement and, by means of a lifting mechanism (13), a vertical movement and also, by means of a clamping or closing mechanism (14), a transverse movement, whereby the starting position of the gripper rail drive for the forward feed mechanism (11, 12) is, as a workpiece dependent mounting axis (33, 33') variable in the transverse direction of the press arrangement, whereby the forward feed mechanism (11, 12) comprises a drive lever (32, 32') pivotable in the longitudinal direction of the press and a push rod (52, 52') connected to the respective gripper rail (9, 10), characterised in that the drive lever (32, 32') is connected directly via the push rod (52, 52') to the respective gripper rail (9, 10) and in that in order to vary the spacing of the forward feed mechanism (11, 12), a displacement drive (41, 41) is provided which displaces the forward feed mechanism (11, 12) with the associated drive lever (32, 32') as a whole crosswise to the direction of transport.
  2. A drive according to claim 1, characterised in that the forward feed mechanism (11, 12) is disposed in a drive housing (23, 23') with a gear arrangement and in that the displacement drive (41, 41') which produces a transverse displacement of the drive housing (23, 23') including the forward feed mechanism (11, 12).
  3. A drive according to claim 2, characterised in that the lateral spacing of the drive housing (23, 23') for the forward feed mechanism (11, 12) is in each case achieved via at least one driveable screw threaded rod (47, 47' or 48, 48' or 60, 60') co-operating with an associated spindle nut (50) on the drive housing (23, 23').
  4. A drive according to claim 3, characterised in that a central displacement drive (41, 41') for adjusting the spacing of the drive housing (23, 23') including the forward feed mechanism (11, 12) is provided whereby via a first deflecting gear mechanism (23), it is possible to drive two aligned drive shafts (45, 45') which at their ends respectively drive a second deflecting gear mechanism (46) for driving the screw threaded spindles (47, 47' and 48, 48').
  5. A drive according to one of claims 2 to 4, characterised in that two pairs of screw threaded spindles (47, 47' and 48, 48') disposed parallel with each other are associated with each drive housing (23, 23').
  6. A drive according to one of the preceding claims, characterised in that the drive for the forward feed mechanism (11, 12) and/or the lifting mechanism (13) and/or the clamping or closing mechanism (14) is effected via the central drive (18, 19) of the gang press.
  7. A drive according to one of the preceding claims 1 to 5, characterised in that the drive for the forward feed mechanism (11, 12) and/or the lifting mechanism (13) and/or the clamping or closing mechanism (14) is effected via in each case a separate drive.
  8. A drive according to claim 7, characterised in that the drive for the forward feed mechanism (11, 12) is effected via means of a separate drive |(54, 55) independently of the other drive system of the gripper rails (9, 10) whereby a central displacement drive (41') is provided to perform a transverse movement of the associated drive housing (23, 23').
  9. A drive according to claim 7 or 8, characterised in that the displacement drive (41') comprises a drive motor (42') which, via a deflecting gear transmission (43') acts on two drive shafts (60, 60') constructed as screw threaded spindles and which engage spindle nuts (50) on the drive housing (23, 23') to produce their lateral displacement.
  10. A drive according to one of claims 7 to 9, characterised in that the individual movements are synchronised with one another and with the movement of the press.
EP94115058A 1993-10-28 1994-09-23 Transfer mechanism, especially for a transfer press Expired - Lifetime EP0650780B1 (en)

Applications Claiming Priority (2)

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DE4336853A DE4336853A1 (en) 1993-10-28 1993-10-28 Transfer drive, especially for a transfer press
DE4336853 1993-10-28

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EP0650780A1 EP0650780A1 (en) 1995-05-03
EP0650780B1 true EP0650780B1 (en) 1997-08-06

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DE202007004720U1 (en) * 2007-03-30 2008-05-21 Settele, Wilhelm Cam mechanism with two take-off rollers, as well as punch-bending machine with such a cam mechanism
DE102007015467B4 (en) 2007-03-30 2015-02-05 Wilhelm Settele Cam mechanism with two take-off rollers, method for producing such a cam gear, program for performing the steps of the method, and punch-bending machine with such a cam mechanism

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3426255A1 (en) * 1984-07-17 1986-01-23 L. Schuler GmbH, 7320 Göppingen Device for changing the position of the closing/opening stroke of the feed bars of a multi-stage press
JPS6221434A (en) * 1985-07-19 1987-01-29 Toyota Motor Corp Device for feeding and ejecting work to and out of press machine
DE3842182C1 (en) * 1988-12-15 1989-09-28 Maschinenfabrik Mueller-Weingarten Ag, 7987 Weingarten, De

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EP0650780A1 (en) 1995-05-03
DE59403629D1 (en) 1997-09-11
DE4336853A1 (en) 1995-05-04
ES2105456T3 (en) 1997-10-16

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