EP0206186B1 - Automatic transfer device for work pieces in a multistation forming machine - Google Patents

Automatic transfer device for work pieces in a multistation forming machine Download PDF

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Publication number
EP0206186B1
EP0206186B1 EP86108162A EP86108162A EP0206186B1 EP 0206186 B1 EP0206186 B1 EP 0206186B1 EP 86108162 A EP86108162 A EP 86108162A EP 86108162 A EP86108162 A EP 86108162A EP 0206186 B1 EP0206186 B1 EP 0206186B1
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EP
European Patent Office
Prior art keywords
supporting tube
gripper
supporting
accordance
yoke
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
Application number
EP86108162A
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German (de)
French (fr)
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EP0206186A1 (en
Inventor
Ulrich Steinhauser
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Hatebur Umformmaschinen AG
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Hatebur Umformmaschinen AG
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Priority to AT86108162T priority Critical patent/ATE39633T1/en
Publication of EP0206186A1 publication Critical patent/EP0206186A1/en
Application granted granted Critical
Publication of EP0206186B1 publication Critical patent/EP0206186B1/en
Expired legal-status Critical Current

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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
    • B21D43/055—Devices comprising a pair of longitudinally and laterally movable parallel transfer bars
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K27/00—Handling devices, e.g. for feeding, aligning, discharging, Cutting-off means; Arrangement thereof
    • B21K27/02—Feeding devices for rods, wire, or strips
    • B21K27/04—Feeding devices for rods, wire, or strips allowing successive working steps

Definitions

  • the invention relates to a device for the automatic transport of workpieces on a multi-stage forming machine according to the preamble of claim 1.
  • drive shafts are arranged in the support tubes in the form of a longitudinally displaceable and rotatably mounted camshaft, which are set in a periodically oscillating pivoting movement by means of a drive device and thereby transfer levers in the form of angle levers both with the control cams of the camshaft as well as with the pliers jaws, swivel accordingly, these transmission levers transfer their swivel displacement to pliers jaws running in straight guides.
  • the periodically oscillating drive shafts can also be adjusted within certain limits, such an adjustment is only possible for all transmission levers that are actuated by a common drive shaft, so that usually only one pair of pliers optimally adapted to the workpiece and the Forming tools certain holding and transport functions can be set.
  • additional measures must therefore be provided, such as. B. particularly long retaining pins and long punch to be able to compensate for the impairments occurring in connection with the transverse transport within certain limits on the part of the respective forming station.
  • the known device is also severely restricted with regard to a certain independence in the setting of the opening and closing movements of the pliers jaws, since one and the same cam section always remains effective for both movement sequences.
  • the object of the invention is, in particular, to design the drive for the transmission levers in a device of the type mentioned at the outset, avoiding the disadvantages of the known, such that the temporal function sequence for each pair of pliers of an associated forming station in relation to the corresponding sequence at an adjacent or at Additional peripheral stations can be set selectively independently of one another, such an adjustability should be able to be carried out in a simple and reliable manner with the shortest interruption in production.
  • the solution to this problem according to the invention is defined by the features and measures characterized in claim 1.
  • This solution according to the invention uses instead of periodically oscillating drive shafts in the support tubes rotatably mounted rotatingly driven camshafts, whereby it is achieved that each transmission lever is given a continuous pivoting movement corresponding to the cam control surface.
  • the solution according to the invention characterizes a mutual adjustability of the individual cam members on the camshaft forming the drive shaft with respect to the camshaft axis of rotation and relative to one another. This adjustability makes it possible to individually adjust a pair of pliers or each individual pliers with regard to a very specific opening and closing function that can be specified at each forming station.
  • a further particular advantage results from the use of revolvingly driven camshafts in that the design of the cam member to be selected can take place within relatively wide limits, since the control function of each cam member is no longer only limited, as is known, for the control function of each cam member, but each one complete shaft revolution, which overall achieves a conceptually more favorable separation between the tong opening and closing movement sequences and thereby creates more scope in the actual tong control.
  • cam members on the camshaft are detachable and adjustable serrated lock washers which are provided with corresponding markings for setting predetermined rotational angle positions with respect to the camshaft rotational axis.
  • serrated lock washers By using such serrated lock washers, a camshaft with adjustable cam links is created, the rotation angle positions of which can be selected quickly and easily for optimal drive of the respective transmission levers and thus of the pairs of pliers using the markings provided with the camshafts removed from the support tubes.
  • another aspect of the device according to the invention includes the accommodation of a camshaft composed of serrated lock washers, when using support tubes which are as light as possible, inter alia for reasons of mass acceleration, and the narrow space conditions in the interior of the support tube.
  • a bearing arrangement is provided in which, depending on the loads to be mastered in some or all of the camshaft sections that lie between adjacent serrated lock washers and, if appropriate, also next to the respective serrated lock washers of a camshaft, a corresponding number of Rolling bearings are provided whose outer bearing rings have a smaller diameter than the inner diameter of the respective support tube.
  • a plurality of support pins projecting through the wall of the support tube into the interior of the support tube are provided over the outer ring in question, which, for example, rest at three points on the outer ring circumference and hold it, and thus the roller bearing, in the manner of a steady rest.
  • Such support of the rolling bearings and thus the camshafts within the support tubes offers considerable advantages in terms of production, since the outer tube diameter of the respective support tube can be manufactured with known, comparatively simple measures to close tolerances and the support pins, correspondingly precisely machined, according to the outer circumferential surface of the respective support tube to center the respective rolling bearing, with an optionally adjustable supporting force, can be aligned.
  • the bearing arrangement is to be provided in particular within the longitudinal extent of each pliers box, the inner surface of a clamped fastening section of the pliers box which is in contact with the outer circumferential surface of each support tube can advantageously be used for simple and at the same time functionally reliable fixing of the support pins in the radial direction of the support tube.
  • an axial bearing is also provided on each camshaft on a section facing the yoke, which is fixedly connected to the camshaft and can be coupled to the surrounding support tube via a detachable locking arrangement engaging thereon, so that it is common when the device is ready for operation is displaceable in the axial direction with the support tube.
  • each camshaft can be removed from the associated support tube and replaced by a preset replacement shaft. Precisely in view of the quick convertibility, which contributes significantly to increasing the economy of the entire machine, the functional interaction of the features of the device according to the invention detailed above should be understood.
  • the transmission levers which are each supported within a pliers box on the upper support tube with respect to the forming area, are designed as so-called two-armed levers, that is to say that the shaft-drive-side lever section of the transmission lever lies on one side of the articulation axis of this lever, while a tong-drive-side lever section lies on the other side of said pivot axis is provided.
  • the pliers box provided on the lower support tube with respect to the forming area is designed with a transmission lever in the form of a one-armed lever. ie that the shaft drive-side and the tong drive-side lever section are provided on a common lever arm which is assigned to the transverse transport area with respect to the pivot axis of the transmission lever.
  • the two parallel support tubes can be arranged offset from one another, so that the lower support tube is at a smaller distance from the workpiece transport plane than the upper one.
  • This different design of the pliers boxes and arrangement of the support tubes allows that when swiveling up the pliers box held on the upper support tube, the space necessary for vertically moving out the dies can be exposed, while the compact design of the lower pliers box leaves enough space to to provide a drop channel for the workpieces from the forming station in a structurally particularly advantageous manner close behind the lower pliers box.
  • the connection between the yoke and in particular the upper support tube with respect to the forming area is mediated by a device which can be expanded via a fluid pressure arrangement
  • the upper pliers box can be pivoted upwards together with the support tube when the fluid pressure is removed.
  • the interior of the pliers box remains completely sealed off from the surroundings, so that scale, cooling water or other contaminants, such as those found in the work area of a hot press, can never get into the pliers box and impair the reliable function of the machine elements in it.
  • the upper pliers box for the pivoting of which a corresponding actuating device can advantageously be provided, can be driven with the pliers raised, so that the drive between the pliers and the forming machine does not need to be decoupled.
  • two support tubes 2a, 2b are each rotatably and axially displaceably mounted in two slide bearings 50, 51 and shown in their left end position in FIG. 1.
  • Four forming stations U1 to U4 of the forming machine are located between the support tubes 2a, 2b, wherein a workpiece W can be transported from one forming station to the next by a pair of pliers jaws 11, 11 shown schematically.
  • the jaws 11 are slidably mounted in a row next to each other in an upper jaw box 3a and a lower jaw box 3b in straight guides.
  • the pliers boxes 3a, 3b are connected to the support tubes 2a, 2b in a rotationally fixed connection during the workpiece transport and, as shown schematically in FIG. 3, are clamped onto the outer peripheral surface 2d of the support tube 2b.
  • the support tubes 2a and 2b are connected via a yoke 17 to a unit which is slidable in the workpiece transport direction and are coupled to a drive mechanism (not shown) via an articulation point 18 of the yoke.
  • the support tubes 2a and 2b are arranged offset from one another while maintaining the parallel extension visible in FIG. 1, such that the lower support tube 2b with respect to the forming region has a smaller distance from the workpiece transport plane than the upper support tube 2a.
  • the pliers box 3a assigned to this support tube 2a also has an elongated shape with respect to the pliers box 3b, which contains the lower support tube 2b, and receives a transmission lever 6a, which is assigned to a respective pliers jaw 11 and which is pivotably mounted in the form of a two-armed lever on a fixed pin 8 .
  • the corresponding transmission lever 6b in the lower pliers box 3b is in the form of a one-armed lever likewise articulated around a fixed pin 8, and both transmission levers 6a and 6b engage the pliers jaws 11 with pliers-side lever sections 56, on which there is a ball 10, around these to move within their tong holder 12.
  • camshaft 4a and 4b which serve as drive shafts for a swivel displacement of the respective transmission levers and, for this purpose, have cam members 5 in the form of adjustable serrated lock washers 5a, 5b, on the serrated lock washer control surfaces 53 of which there is a shaft drive section 52 of the transmission lever 6a or 6b.
  • a scanning roller 9 is rotatably guided on a pin 16 on the shaft drive-side section 52 of the transmission lever.
  • Schematically illustrated spring assemblies 7 load respective transmission levers 6a and 6b accordingly and thereby press the scanning rollers 9 onto the control surfaces 53 of the Serrated lock washers 5a, 5b. From Fig. 2 it can be seen that with one rotation of the camshafts 4a and 4b each jaw 11 is moved by the transmission levers 6a and 6b within the tong carrier 12. In Fig. 2, the closed position of the tooth jaws 11 is shown schematically. In Fig. 2 fluid cylinders 22 are shown attacking each transmission lever 6a, 6b.
  • the transmission levers can be lifted against the spring preload from the respective serrated disc control surfaces 53, which is necessary, for example, when replacing the camshafts 4a and 4b, which are mounted within the support tubes 2a and 2b .
  • the fluid cylinders 22 can be operated to prevent the jaws 11 from closing.
  • Such control of the fluid cylinder takes place, for. B. for the elimination of defective preforms, such as those that occur, for example, in the transition from one material bar to the next.
  • the first pliers are kept open via the fluid cylinder 22, so that this faulty compact is not transported further.
  • the serrated lock washers 5a, 5b are exchangeable and fastened in an adjustable manner in the circumferential direction of the camshafts. This enables each serrated lock washer to be set independently of the others on the camshaft. that a control optimally adapted to the corresponding forming process can be achieved for each pair of jaws 11.
  • a bearing arrangement 54 is used, which according to FIG. 3 comprises a roller bearing 15, the inner ring 15b of which is on the camshaft 4b is seated and the outer ring 15a has a smaller diameter than the inner diameter of the support tube 2b.
  • support pins 14 which pass through the wall of the support tube 2b are used, which are provided in the circumferential direction of the respective roller bearing 15 distributed at angular intervals and grouped around the outer ring 15a, and with their end surface 14a facing the outer ring peripheral surface 15d, the entire roller bearing 15 centrally in the manner of a steady rest support.
  • the realization of the bearing arrangement 54 only makes it necessary to manufacture the outer circumferential surface 2d to a predetermined diameter with a narrow tolerance range, and the support pins 14, which with their shank visible in FIG bores provided through the support tube wall are machined with a corresponding precision, and they with their pin end faces 14c lying on the peripheral surface 2d on an inner surface 3c clamped onto this outer peripheral surface 2d of the relevant support tube, which is part of the fastening section of the pliers box 3a or 3b to support.
  • the view of the support pin 14 according to FIG. 4 shows that its pin end face 14c, in contrast to the cylindrical pin shaft, is square and, as can be seen in FIG.
  • FIG. 5 shows the section of the yoke 17 according to FIG. 1 containing the upper support tube 2a in detail.
  • the support tube 2a is connected to the section of the yoke 17 shown via a device 37 which engages on its outer circumference. By introducing a fluid into one or more ring channels in the device 37, the device 37 is expanded, thereby making it possible to establish a non-positive connection between the support tube 2a and the yoke 17.
  • both support tubes 2a and 2b (FIG. 1) are connected to the yoke 17 to form a slidably displaceable unit.
  • a bolt arrangement 23 is screwed to the yoke 17 at a plurality of fastening points 24a, 24b (see FIGS. 6 and 7) and has bolts 23a, 23b which engage in the axial bearing 19 in the radial direction and which in their engagement position according to FIG. 5 have a connection which is rigid in the axial direction between the support tube 2a and the camshaft 4a.
  • the yoke is set in a periodically oscillating longitudinal movement in the direction of the double arrow 20, the yoke takes over the support tubes 2a and 2b the camshafts 4a and 4b accordingly.
  • the respective stroke of the transverse transport corresponds to the center distance between two adjacent forming stations U1 to U4 according to FIG. 1.
  • the latch arrangement 23 must be released so that the camshafts 4a and 4b can be pulled out of the support tubes 2a and 2b. 5, the bolts 23a and 23b are displaceably guided between bolt guide plates 26 and 27, the mutual spacing of the guide plates at the fastening points 24a, b being corresponding Spacer sleeves 34 is set. From Fig. 6 it can be seen that the bolts 23a, b can be shifted about pivot pins 25a and 25b and that at the lower end region according to FIG. 6 of the bolt arrangement 23 between the bolts 23a and 23b a spring 33 seated on a guide pin 32 and on the a fluid cylinder arrangement 31 is provided with respect to the pivot portions 25a and 25b opposite end sections of the bolts 23a and 23b.
  • the camshafts 4a and 4b are set in rotation by the main drive of the forming machine via a chain and gear drive shown schematically in the form of a box 35 in FIG. 1. This rotary movement is transmitted due to the simultaneous axial movement of the camshafts with the help of spline shafts, not shown.
  • the device As soon as the support tube 2a rotates according to the stroke of the hydraulic cylinder 38 and thus has brought the upper tong box 3a into an upper swivel position, the device is hydraulically expanded again, and the renewed press connection securely supports the tong box in its upper swivel position by the yoke 17 held.
  • the gear 41 is also moved, which is why the pinion 40 must have a width such that it can at least correspond to the transverse transport stroke plus the thickness of the gear 41 in order to pivot the upper tong box 3a in any axial position of the support tube. If these conditions are met, the pinion 40 and the gear 41 can remain constantly engaged. In order to keep the wear between the pinion and the gear as low as possible and so that no forces are exerted on the swivel arrangement during operation of the device, the backlash between the pinion 40 and gear 41 is relatively large.
  • a positioning device 42 is used for this purpose, which has a tab 43 screwed onto the support tube 2a with a milled contour, in which a positioning prism 44 is fastened.
  • a screw shown schematically in the right-hand illustration according to FIG. 8 is used for fastening.
  • a contour corresponding to the prism 44 is incorporated, so that the support tube, particularly in the last phase of pivoting back into its starting position via the positioning prism 44 and the contour in Yoke section 17a is adjusted axially and radially securely.
  • the tab 43 is swiveled into its position shown in broken lines as shown in FIG. 8.

Abstract

The proposed cross transfer device has two parallel support tubes (2a, 2b) which are displaceable in reciprocating manner in the workpiece transfer direction in the forming area and to which are fixed in each case an upper and a lower gripper box (3a, 3b). The two gripper boxes are used for the rectilinear guidance of gripper jaws (11) which interact in pairs, seize a workpiece at each forming station (U1 to U3) and can be transferred to the in each case adjacent forming station (U2 to U4) and released again. Transmission levers (6a, 6b) pivotably mounted in the gripper boxes (3a, 3b) are used for driving the gripper jaws (11), the pivoting movement of which transmission levers (6a, 6b) is controlled by a rotating camshaft (4a, 4b) which in each case is centrally mounted in one of the support tubes (2a, 2b) via antifriction bearings (15) and supporting pins ( 14). The cam members (5) of this camshaft are fan-type disks (5a, 5b) which can be adjusted in each case relative to the axis of rotation of the camshaft supporting it and relative to one another, so that each transmission lever (6a, 6b) can be individually set, independently of the further transmission levers provided, for controlling a certain gripper movement.

Description

Die Erfindung bezieht sich auf eine Einrichtung zum automatischen Transport von Werkstücken an einer mehrstufigen Umformmaschine gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a device for the automatic transport of workpieces on a multi-stage forming machine according to the preamble of claim 1.

Bei einer derartigen bekannten Umformmaschine (DE-C-2 715 966) sind in den Tragrohren Antriebswellen in Form je einer längsverschieb- und drehbar gelagerten Kurvenwelle angeordnet, die über eine Antriebsvorrichtung in periodisch oszillierende Schwenkbewegungen versetzt werden und dabei Übertragungshebel in Form von Winkelhebeln, die sowohl mit den Steuerkurven der Kurvenwelle als auch mit den Zangenbacken in Verbindung stehen, entsprechend verschwenken, wobei diese Übertragungshebel ihre Schwenkverlagerung auf in geradlinigen Führungen laufenden Zangenbacken übertragen.In such a known forming machine (DE-C-2 715 966), drive shafts are arranged in the support tubes in the form of a longitudinally displaceable and rotatably mounted camshaft, which are set in a periodically oscillating pivoting movement by means of a drive device and thereby transfer levers in the form of angle levers both with the control cams of the camshaft as well as with the pliers jaws, swivel accordingly, these transmission levers transfer their swivel displacement to pliers jaws running in straight guides.

Zwar können die periodisch oszillierenden Antriebswellen auch in gewissen Grenzen verstellt werden, jedoch ist eine derartige Verstellung jeweils nur für sämtliche Übertragungshebel, die von einer gemeinsamen Antriebswelle betätigt werden, möglich, so daß in der Regel nur ein Zangenpaar optimal auf die durch das Werkstück und die Umformwerkzeuge bestimmten Halte- und Transportfunktionen eingestellt werden kann. Bei einer vierstufigen Umformmaschine, welche drei Zangenpaare benötigt, sind daher zusätzliche Maßnahmen vorzusehen, wie z. B. besonders lange Haltestifte und lange Stanzstempel, um in gewissen Grenzen auf Seiten der jeweiligen Umformstation eine Kompensation der im Zusammenhang mit dem Quertransport auftretenden Beeinträchtigungen vornehmen zu können.Although the periodically oscillating drive shafts can also be adjusted within certain limits, such an adjustment is only possible for all transmission levers that are actuated by a common drive shaft, so that usually only one pair of pliers optimally adapted to the workpiece and the Forming tools certain holding and transport functions can be set. In a four-stage forming machine, which requires three pairs of pliers, additional measures must therefore be provided, such as. B. particularly long retaining pins and long punch to be able to compensate for the impairments occurring in connection with the transverse transport within certain limits on the part of the respective forming station.

Zusätzlich zu dem bereits angesprochenen Nachteil bei den bekannten periodisch oszillierenden Antriebswellen ist die bekannte Einrichtung auch hinsichtlich einer gewissen Unabhängigkeit in der Einstellung der Öffnungs-und Schließbewegungen der Zangenbacken stark eingeschränkt, da für beide Bewegungsabläufe stets ein und derselbe Nockenabschnitt wirksam bleibt.In addition to the already mentioned disadvantage of the known periodically oscillating drive shafts, the known device is also severely restricted with regard to a certain independence in the setting of the opening and closing movements of the pliers jaws, since one and the same cam section always remains effective for both movement sequences.

Die Aufgabe der Erfindung besteht nun darin, bei einer Einrichtung der eingangs genannten Art insbesondere den Antrieb für die Übertragungshebel unter Vermeidung der Nachteile des Bekannten so auszubilden, daß der zeitliche Funktionsablauf bei jedem Zangenpaar einer zugehörigen Umformstation im Verhältnis zum entsprechenden Ablauf an einer benachbarten oder an weiteren Umfangsstationen unabhängig voneinander selektiv eingestellt werden kann, wobei eine derartige Einstellbarkeit auf einfache Weise bei kürzester Produktionsunterbrechung funktions-und betriebssicher ausführbar sein soll.The object of the invention is, in particular, to design the drive for the transmission levers in a device of the type mentioned at the outset, avoiding the disadvantages of the known, such that the temporal function sequence for each pair of pliers of an associated forming station in relation to the corresponding sequence at an adjacent or at Additional peripheral stations can be set selectively independently of one another, such an adjustability should be able to be carried out in a simple and reliable manner with the shortest interruption in production.

Die Lösung dieser erfindungsgemäßen Aufgabe ist durch die im Patentanspruch 1 gekennzeichneten Merkmale und Maßnahmen definiert. Diese erfindungsgemäße Lösung verwendet anstelle periodisch oszillierender Antriebswellen in den Tragrohren drehbar gelagerte umlaufend angetriebene Nockenwellen, wodurch erreicht wird, daß jedem Übertragungshebel eine der Nockensteuerfläche entsprechende kontinuierliche Schwenkbewegung erteilt wird. Zudem kennzeichnet die erfindungsgemäße Lösung eine gegenseitige Verstellbarkeit der einzelnen Nockenglieder auf der die Antriebswelle bildenden Nockenwelle bezüglich der Nockenwelle-Rotationsachse und relativ zueinander. Diese Verstellbarkeit macht eine individuelle Einstellung eines Zangenpaars bzw. jeder einzelnen Zange im Hinblick auf eine ganz bestimmte, an jeder Umformstation vorgebbare Öffnungs- und Schließfunktion möglich.The solution to this problem according to the invention is defined by the features and measures characterized in claim 1. This solution according to the invention uses instead of periodically oscillating drive shafts in the support tubes rotatably mounted rotatingly driven camshafts, whereby it is achieved that each transmission lever is given a continuous pivoting movement corresponding to the cam control surface. In addition, the solution according to the invention characterizes a mutual adjustability of the individual cam members on the camshaft forming the drive shaft with respect to the camshaft axis of rotation and relative to one another. This adjustability makes it possible to individually adjust a pair of pliers or each individual pliers with regard to a very specific opening and closing function that can be specified at each forming station.

Ein weiterer besonderer Vorteil ergibt sich durch die Verwendung umlaufend angetriebener Nockenwellen dadurch, daß die Gestaltung des zu wählenden Nockenglieds in relativ weiten Grenzen erfolgen kann, da für die Steuerfunktion eines jeden Nockenglieds nicht mehr nur, wie beim Bekannten, ein beschränkter Schwenkbereich zur Verfügung steht, sondern jeweils eine ganze Wellenumdrehung, wodurch insgesamt eine konzeptionell günstigere Trennung zwischen den Zangenöffnungs- und Schließbewegungsabläufen erreicht und dadurch mehr Spielraum in der eigentlichen Zangensteuerung geschaffen wird.A further particular advantage results from the use of revolvingly driven camshafts in that the design of the cam member to be selected can take place within relatively wide limits, since the control function of each cam member is no longer only limited, as is known, for the control function of each cam member, but each one complete shaft revolution, which overall achieves a conceptually more favorable separation between the tong opening and closing movement sequences and thereby creates more scope in the actual tong control.

Eine weitere besonders vorteilhafte Realisierung der erfindungsgemäßen Einrichtung ist dann gegeben, wenn die Nockenglieder auf der Nockenwelle lös- und verstellbar angebrachte Fächerscheiben sind, die mit entsprechenden Markierungen zur Einstellung von vorbestimmten Drehwinkelpositionen bezüglich der Nockenwellen-Rotationsachse versehen sind. Durch den Einsatz derartiger Fächerscheiben wird eine Nockenwelle mit einstellbaren Nockengliedergeschaffen, deren zu wählende Drehwinkelpositionen für einen optimalen Antrieb der jeweiligen Übertragungshebel und damit der Zangenpaare anhand der vorgesehenen Markierungen bei aus den Tragrohren herausgenommenen Nockenwellen rasch und einfach erfolgen kann.A further particularly advantageous realization of the device according to the invention is given when the cam members on the camshaft are detachable and adjustable serrated lock washers which are provided with corresponding markings for setting predetermined rotational angle positions with respect to the camshaft rotational axis. By using such serrated lock washers, a camshaft with adjustable cam links is created, the rotation angle positions of which can be selected quickly and easily for optimal drive of the respective transmission levers and thus of the pairs of pliers using the markings provided with the camshafts removed from the support tubes.

Ein weiterer Aspekt der erfindungsgemäßen Einrichtung umfaßt in diesem Zusammenhang die Unterbringung einer aus Fächerscheiben zusammengesetzten Nockenwelle, bei der Verwendung von unter anderem aus Massenbeschleunigungsgründen möglichst leichten Tragrohren und den dabei engen Platzverhältnissen im Tragrohrinnenraum. Gemäß einem erfindungsgemäßen Lösungsmerkmal ist eine Lageranordnung vorgesehen, bei welcher, je nach den abstützungsmäßig zu beherrschenden Belastungen in einigen oder allen Nockenwellenabschnitten, die zwischen benachbarten Fächerscheiben liegen und gegebenenfalls auch neben den jeweils außenliegenden Fächerscheiben einer Nockenwelle, eine entsprechende Anzahl von Wälzlagern vorgesehen sind, deren Lager-Außenringe einen kleineren Durchmesser besitzen als der Innendurchmesser des jeweiligen Tragrohrs beträgt. Zur Abstützung dieser Wälzlager innerhalb der Tragrohre sind über den betreffenden Außenring verteilt mehrere durch die Wandung des Tragrohrs hindurch in den Tragrohrinnenraum hineinragende Stützzapfen vorgesehen, die beispielsweise an drei Stellen am Außenringumfang anliegen und diesen, und damit das Wälzlager, nach Art einer Lünette halten. Eine derartige Abstützung der Wälzlager und damit der Nockenwellen innerhalb der Tragrohre bietet erhebliche fertigungstechnische Vorteile, da der Rohraußendurchmesser des jeweiligen Tragrohrs mit bekannten, vergleichsweise einfachen Maßnahmen nach engen Toleranzen gefertigt werden kann und die Stützzapfen, entsprechend präzise bearbeitet, nach der äußeren Umfangsfläche des jeweiligen Tragrohrs zur Zentrierung des jeweiligen Wälzlagers, mit einer gegebenenfalls einstellbaren Abstützkraft, ausgerichtet werden können. Da die Lageranordnung insbesondere innerhalb der Längserstreckung eines jeden Zangenkastens vorzusehen ist, kann vorteilhafterweise die an der äußeren Umfangsfläche eines jeden Tragrohrs anliegende Innenfläche eines aufgeklemmten Befestigungsabschnitts des Zangenkastens zur einfachen und gleichzeitig funktionssicheren Festlegung der Stützzapfen in Radialrichtung des Tragrohrs herangezogen werden.In this context, another aspect of the device according to the invention includes the accommodation of a camshaft composed of serrated lock washers, when using support tubes which are as light as possible, inter alia for reasons of mass acceleration, and the narrow space conditions in the interior of the support tube. According to a solution feature according to the invention, a bearing arrangement is provided in which, depending on the loads to be mastered in some or all of the camshaft sections that lie between adjacent serrated lock washers and, if appropriate, also next to the respective serrated lock washers of a camshaft, a corresponding number of Rolling bearings are provided whose outer bearing rings have a smaller diameter than the inner diameter of the respective support tube. To support these roller bearings within the support tubes, a plurality of support pins projecting through the wall of the support tube into the interior of the support tube are provided over the outer ring in question, which, for example, rest at three points on the outer ring circumference and hold it, and thus the roller bearing, in the manner of a steady rest. Such support of the rolling bearings and thus the camshafts within the support tubes offers considerable advantages in terms of production, since the outer tube diameter of the respective support tube can be manufactured with known, comparatively simple measures to close tolerances and the support pins, correspondingly precisely machined, according to the outer circumferential surface of the respective support tube to center the respective rolling bearing, with an optionally adjustable supporting force, can be aligned. Since the bearing arrangement is to be provided in particular within the longitudinal extent of each pliers box, the inner surface of a clamped fastening section of the pliers box which is in contact with the outer circumferential surface of each support tube can advantageously be used for simple and at the same time functionally reliable fixing of the support pins in the radial direction of the support tube.

Bei der erfindungsgemäßen Einrichtung ist ferner an jeder Nockenwelle an einem dem Joch zugewandten Abschnitt ein Axiallager vorgesehen, das fest mit der Nockenwelle verbunden und über eine an diesem angreifende lösbare Riegelanordnung mit dem umgebenden Tragrohr gekoppelt werden kann, so daß es in betriebsbereitem Zustand der Einrichtung gemeinsam mit dem Tragrohr in axialer Richtung verlagerbar ist. Damit bei einem notwendigen Produktionsumbau ein rasches Umstellen der Zangenbewegung auf ein neues Werkstück möglich ist, kann jede Nockenwelle aus dem zugehörigen Tragrohr herausgenommen und durch eine voreingestellte Austauschwelle ersetzt werden. Gerade im Hinblick auf die rasche Umstellbarkeit, welche wesentlich zur Erhöhung der Wirtschaftlichkeit der gesamten Maschine beiträgt, sollen die vorstehend im einzelnen aufgeführten Merkmale der erfindungsgemäßen Einrichtung in ihrem funktionalen Zusammenspiel verstanden werden. Infolge der lünettenartigen Abstützung in der Lageranordnung setzt diese einem Herausziehen einer Nockenwelle aus dem jeweiligen Tragrohr keinen eine große Axialkraft notwendig machenden Widerstand entgegen, so daß jede Nockenwelle nach einem Lösen der Riegelanordnung und einem Abheben der an den Fächerscheiben anliegenden wellenantriebsseitigen Abschnitte der Übertragungshebel sowie nach dem automatischen Abkuppeln der Antriebsteile problemlos von Hand aus den Tragrohren herausgezogen werden kann. Außerhalb der Tragrohre lassen sich entweder die Fächerscheiben anhand der vorgesehenen Skalen in kurzer Zeit neu einstellen, oder es werden die Nockenwellen mit bereits eingestellten Fächerscheiben im ganzen ausgetauscht. Da bei der erfindungsgemäßen Einrichtung die Nockenwellen identisch aufgebaut und gleichsinnig drehend konzipiert sind, lassen sich die Nockenwellen bezüglich der Tragrohre nicht verwechseln, was auch eine gewisse Erleichterung bei einem notwendigen Produktionsumbau mit sich bringt.In the device according to the invention, an axial bearing is also provided on each camshaft on a section facing the yoke, which is fixedly connected to the camshaft and can be coupled to the surrounding support tube via a detachable locking arrangement engaging thereon, so that it is common when the device is ready for operation is displaceable in the axial direction with the support tube. To make it possible to quickly change the tongs movement to a new workpiece when a production change is necessary, each camshaft can be removed from the associated support tube and replaced by a preset replacement shaft. Precisely in view of the quick convertibility, which contributes significantly to increasing the economy of the entire machine, the functional interaction of the features of the device according to the invention detailed above should be understood. As a result of the bezel-like support in the bearing arrangement, this does not provide any resistance to pulling a camshaft out of the respective support tube, so that each camshaft after loosening the locking arrangement and lifting off the shaft drive-side sections of the transmission levers resting on the serrated lock washers and after automatic disconnection of the drive parts can be easily pulled out of the support tubes by hand. Outside of the support tubes, either the serrated lock washers can be reset in a short time using the provided scales, or the camshafts can be replaced with the serrated lock washers already set. Since in the device according to the invention the camshafts are constructed identically and rotate in the same direction, the camshafts cannot be confused with respect to the support tubes, which also brings some relief in the case of a necessary conversion of the production.

Weitere Merkmale und Vorteile, insbesondere zu vorleilhaften Ausführungsformen der Erfindung ergeben sich aus den weiteren Patentansprüchen, in denen die jeweils dargestellten Merkmale sowohl für sich genommen als auch in ihrer jeweils technich sinnvollen funktionalen Verknüpfung beansprucht werden.Further features and advantages, in particular with respect to advantageous embodiments of the invention, result from the further patent claims, in which the features shown in each case are taken on their own and also claimed in their technically meaningful functional link.

Zudem ist es im Zusammenhang mit der erfindungsgemäßen Einrichtung von Bedeutung, daß mittels des erfindungsgemäßen Antriebsprinzips zwei unterschiedlich aufgebaute Übertragungshebel mit einander entsprechendem Schwingungsverlauf gesteuert werden können. Bei einer bevorzugten Ausführungsform sind die Übertragungshebel, die jeweils innerhalb eines Zangenkastens am bezüglich des Umformbereichs oberen Tragrohr abgestützt sind, als sogenannte zweiarmige Hebel ausgeführt, d. h. daß der wellenantriebsseitige Hebelabschnitt des Übertragungshebels an einer Seite der Anlenkachse dieses Hebels liegt, während ein zangenantriebsseitiger Hebelabschnitt an der anderen Seite der genannten Schwenkachse vorgesehen ist. Dadurch ergibt sich eine in Längsrichtung des Übertragungshebels langgestreckte Ausführung des betreffenden Zangenkastens. Der bezüglich des Umformbereichs am unteren Tragrohr vorgesehene Zangenkasten ist hingegen mit einem Übertragungshebel in Form eines einarmigen Hebels ausgestaltet. d. h. daß der wellenantriebsseitige und der zangenantriebsseitige Hebelabschnitt an einem gemeinsamen Hebelarm, der bezüglich der Schwenkachse des Übertragungshebels dem Quertransportbereich zugeordnet ist, vorgesehen sind. Dadurch lassen sich die beiden parallelen Tragrohre zueinander versetzt anordnen, so daß das untere Tragrohr einen geringeren Abstand von der Werkstücktransportebene besitzt als das obere. Diese unterschiedliche Ausführung der Zangenkästen und Anordnung der Tragrohre gestattet es, daß bei einem Hochschwenken des am oberen Tragrohr gehaltenen Zangenkastens der zum senkrechten Herausfahren der Matrizen notwendige Raum freigelegt werden kann, während die gedrungene Bauweise des unteren Zangenkastens genügend Platz frei läßt, um einen Ausfallkanal für die Werkstücke aus der Umformstation in konstruktiv besonders günstiger Weise dicht hinter dem unteren Zangenkasten vorzusehen.In addition, it is important in connection with the device according to the invention that by means of the drive principle according to the invention two differently constructed transmission levers can be controlled with a corresponding vibration profile. In a preferred embodiment, the transmission levers, which are each supported within a pliers box on the upper support tube with respect to the forming area, are designed as so-called two-armed levers, that is to say that the shaft-drive-side lever section of the transmission lever lies on one side of the articulation axis of this lever, while a tong-drive-side lever section lies on the other side of said pivot axis is provided. This results in an elongated design of the relevant pliers box in the longitudinal direction of the transmission lever. The pliers box provided on the lower support tube with respect to the forming area, on the other hand, is designed with a transmission lever in the form of a one-armed lever. ie that the shaft drive-side and the tong drive-side lever section are provided on a common lever arm which is assigned to the transverse transport area with respect to the pivot axis of the transmission lever. As a result, the two parallel support tubes can be arranged offset from one another, so that the lower support tube is at a smaller distance from the workpiece transport plane than the upper one. This different design of the pliers boxes and arrangement of the support tubes allows that when swiveling up the pliers box held on the upper support tube, the space necessary for vertically moving out the dies can be exposed, while the compact design of the lower pliers box leaves enough space to to provide a drop channel for the workpieces from the forming station in a structurally particularly advantageous manner close behind the lower pliers box.

Da bei der erfindungsgemäßen Einrichtung die Verbindung zwischen dem Joch und insbesondere dem bezüglich des Umformbereichs oberen Tragrohr über eine Vorrichtung vermittelt wird, die über eine Fluiddruckanordnung aufweitbar ist, läßt sich bei einem weggenommenen Fluiddruck der obere Zangenkasten nach oben gemeinsam mit dem Tragrohr verschwenken. Dabei bleibt der Innenraum des Zangenkastens vollständig von der Umgebung abgeschlossen, so daß niemals Zunder, Kühlwasser oder andere verunreinigende Substanzen, wie sie im Arbeitsbereich einer Warmpresse vorkommen, in den Zangenkasten hineingelangen und die zuverlässige Funktion der in ihm befindlichen Maschinenelemente beeinträchtigen können. Außerdem läßt sich infolge der erfindungsgemäßen Ausbildung der Antriebswelle der obere Zangenkasten, zu dessen Verschwenkung vorteilhafterweise eine entsprechende Stelleinrichtung vorgesehen sein kann, mit angehobenen Zangen fahren, so daß der Antrieb zwischen den Zangen und der Umformmaschine nicht entkoppelt zu werden braucht. Auch mit diesen Maßnahmen wird das Umrüsten und Einrichten der Maschine bei angehobenen Zangen vereinfacht und erleichtert.Since, in the device according to the invention, the connection between the yoke and in particular the upper support tube with respect to the forming area is mediated by a device which can be expanded via a fluid pressure arrangement, the upper pliers box can be pivoted upwards together with the support tube when the fluid pressure is removed. The interior of the pliers box remains completely sealed off from the surroundings, so that scale, cooling water or other contaminants, such as those found in the work area of a hot press, can never get into the pliers box and impair the reliable function of the machine elements in it. In addition, due to the design of the drive shaft according to the invention, the upper pliers box, for the pivoting of which a corresponding actuating device can advantageously be provided, can be driven with the pliers raised, so that the drive between the pliers and the forming machine does not need to be decoupled. These measures also make it easier and easier to change over and set up the machine when the pliers are raised.

Ein Ausführungsbeispiel der Erfindung wird anhand von Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1 eine schematische Ansicht einer Einrichtung nach den Merkmalen der Erfindung,
  • Fig. 2 eine schematische Schnittdarstellung bei einer Schnittführung entlang der Linie A - A in Fig. 1,
  • Fig. 3 eine weitere Schnittdsrstellung bei einer Schnittführung entlang der Linie B - B in Fig. 1,
  • Fig. 4 eine Ansicht eines in Fig. 3 gezeigten Einzelteils in Richtung des Pfeils C in Fig. 3,
  • Fig. 5 eine Schnittdarstellung eines Einrichtungsabschnitts in Fig. 1 bei einer Schnittführung entlang der Pfeile D - D in Fig. 1,
  • Fig. 6 eine Querschnittansicht bei einer Schnittführung entlang der Linie C - C in Fig. 5,
  • Fig. 7 eine Ansicht auf den in Fig. 1 rechten Einrichtungsabschnitt in Richtung des Pfeils A unter Weglassung von in Fig. 1 schematisch dargestellten Axiallagern 19 und
  • Fig. 8 eine schematische Darstellung in Auf-und Seitenriß einer Positioniereinrichtung.
An embodiment of the invention is explained in more detail with reference to drawings. Show it:
  • 1 is a schematic view of a device according to the features of the invention,
  • FIG. 2 shows a schematic sectional illustration in a sectional arrangement along the line AA in FIG. 1, FIG.
  • 3 shows a further sectional view with a sectional view along the line BB in FIG. 1,
  • 4 shows a view of an individual part shown in FIG. 3 in the direction of arrow C in FIG. 3,
  • 5 shows a sectional illustration of a device section in FIG. 1 with a section along the arrows D - D in FIG. 1,
  • 6 is a cross-sectional view with a section along the line C - C in FIG. 5,
  • Fig. 7 is a view of the right portion of Fig. 1 in the direction of arrow A, omitting the axial bearings 19 and 19 shown schematically in Fig. 1
  • 8 shows a schematic illustration in elevation and side elevation of a positioning device.

An einem in Fig. 1 schematisch gezeigten Maschinenkörper 1 sind zwei Tragrohre 2a, 2b in je zwei Gleitlagern 50, 51 dreh- und axialverschiebbar gelagert und in Fig. 1 in ihrer linken Endlage dargestellt. Zwischen den Tragrohren 2a, 2b befinden sich vier Umformstationen U1 bis U4 der Umformmaschine, wobei jeweils von einem schematisch dargestellten Zangenbackenpaar 11, 11 ein Werkstück W von einer Umformstation zur nächsten transportiert werden kann. Die Zangenbacken 11 sind in einer Reihe nebeneinanderliegend in einem oberen Zangenkasten 3a und einem unteren Zangenkasten 3b in geradlinigen Führungen verschiebbar gelagert. Die Zangenkästen 3a, 3b stehen mit den Tragrohren 2a, 2b während des Werkstücktransports in drehfester Verbindung und sind, wie in Fig. 3 schematisch dargestellt, auf die äußere Umfangsfläche 2d des Tragrohrs 2b aufgeklemmt.On a machine body 1 shown schematically in FIG. 1, two support tubes 2a, 2b are each rotatably and axially displaceably mounted in two slide bearings 50, 51 and shown in their left end position in FIG. 1. Four forming stations U1 to U4 of the forming machine are located between the support tubes 2a, 2b, wherein a workpiece W can be transported from one forming station to the next by a pair of pliers jaws 11, 11 shown schematically. The jaws 11 are slidably mounted in a row next to each other in an upper jaw box 3a and a lower jaw box 3b in straight guides. The pliers boxes 3a, 3b are connected to the support tubes 2a, 2b in a rotationally fixed connection during the workpiece transport and, as shown schematically in FIG. 3, are clamped onto the outer peripheral surface 2d of the support tube 2b.

In dem in Fig. 1 rechten Abschnitt der Einrichtung sind die Tragrohre 2a und 2b über ein Joch 17 zu einer in Werkstücktransportrichtung gleitend verschiebbaren Einheit verbunden und über eine Anlenkstelle 18 des Jochs an einen nichtgezeigten Antriebsmechanismus gekoppelt.In the right-hand section of the device in FIG. 1, the support tubes 2a and 2b are connected via a yoke 17 to a unit which is slidable in the workpiece transport direction and are coupled to a drive mechanism (not shown) via an articulation point 18 of the yoke.

Bei der Schnittdarstcllung gemäß Fig. 2 sind die Tragrohre 2a und 2b unter Beibehaltung der in Fig. 1 sichtbaren parallelen Erstreckung zueinander versetzt angeordnet, derart, daß das bezüglich des Umformbereichs untere Tragrohr 2b einen geringeren Abstand von der Werkstücktransportebene besitzt als das obere Tragrohr 2a. Der diesem Tragrohr 2a zugeordnete Zangenkasten 3a besitzt zudem eine gegenüber dem Zangenkasten 3b, der das untere Tragrohr 2b enthält, langgestreckte Form und nimmt einen einer jeweiligen Zangenbacke 11 zugeordneten Übertragungshebel 6a auf, der in Form eines zweiarmigen Hebels an einem ortsfesten Zapfen 8 schwenkbar gelagert ist. Der entsprechende Übertragungshebel 6b im unteren Zangenkasten 3b besitzt die Form eines ebenfalls um einen ortsfesten Zapfen 8 angelenkten einarmigen Hebels, und beide Übertragungshebel 6a und 6b greifen mit zangenseitigen Hebelabschnitten 56,an denen sich eine Kugel 10 befindet, an den Zangenbacken 11 an, um diese innerhalb ihrer Zangenträger 12 zu verschieben.In the sectional view according to FIG. 2, the support tubes 2a and 2b are arranged offset from one another while maintaining the parallel extension visible in FIG. 1, such that the lower support tube 2b with respect to the forming region has a smaller distance from the workpiece transport plane than the upper support tube 2a. The pliers box 3a assigned to this support tube 2a also has an elongated shape with respect to the pliers box 3b, which contains the lower support tube 2b, and receives a transmission lever 6a, which is assigned to a respective pliers jaw 11 and which is pivotably mounted in the form of a two-armed lever on a fixed pin 8 . The corresponding transmission lever 6b in the lower pliers box 3b is in the form of a one-armed lever likewise articulated around a fixed pin 8, and both transmission levers 6a and 6b engage the pliers jaws 11 with pliers-side lever sections 56, on which there is a ball 10, around these to move within their tong holder 12.

Im Innenraum beider Tragrohre 2a und 2b befindet sich je eine Nockenwelle 4a und 4b, die als Antriebswellen für eine Schwenkverlagerung der jeweiligen Übertragungshebel dienen und dazu Nockenglieder 5 in Form einstellbarer Fächerscheiben 5a, 5b aufweisen, auf deren Fächerscheiben-Steuerflächen 53 jeweils ein wellentriebseitiger Abschnitt 52 des Übertragungshebels 6a bzw. 6b anliegt. Zum reibungsarmen Antrieb der Übertragungshebel 6a und 6b ist an dem wellenantriebsseitigen Abschnitt 52 des Übertragungshebels jeweils eine Abtastrolle 9 auf einem Zapfen 16 drehbar geführt. Schematisch dargestellte Federpakete 7 belastenden jeweiligen Übertragungshebel 6a und 6b entsprechend vor und drücken dadurch die Abtastrollen 9 auf die Steuerflächen 53 der Fächerscheiben 5a, 5b. Aus Fig. 2 ist ersichtlich, daß bei einer Umdrehung der Nockenwellen 4a und 4b jede Zangenbacke 11 von den Übertragungshebeln 6a und 6b innerhalb der Zangenträger 12 verschoben wird. In Fig. 2 ist schematisch die Schliesslage der Zahnbacken 11 abgebildet. In Fig. 2 sind Fluidzylinder 22 an jedem Übertragungshebel 6a, 6b angreifend dargestellt. Mittels dieser Fluidzylinder, die beispielsweise als Hydraulikzylinder ausgeführt sein können, lassen sich die Übertragungshebel gegen die Federvorbelastung von den jeweiligen Fächerscheiben-Steuerflächen 53 abheben, was beispielsweise beim Auswechseln der Nockenwellen 4a und 4b, die innerhalb der Tragrohre 2a und 2b gelagert sind, erforderlich ist. Ferner können die Fluidzylinder 22 betrieben werden, um die Zangenbacken 11 am Schließen zu hindern. Eine derartige Ansteuerung der Fluidzylinder erfolgt z. B. für ein Ausscheiden von fehlerhaften Vorformpreßlingen, wie sie beispielsweise beim Übergang von einer Materialstange zur nächsten entstehen. Dabei wird über den Fluidzylinder 22 die erste Zange offengehalten, so daß dieser fehlerhafte Preßling nicht weitertransportiert wird.In the interior of both support tubes 2a and 2b there is a camshaft 4a and 4b, which serve as drive shafts for a swivel displacement of the respective transmission levers and, for this purpose, have cam members 5 in the form of adjustable serrated lock washers 5a, 5b, on the serrated lock washer control surfaces 53 of which there is a shaft drive section 52 of the transmission lever 6a or 6b. For the low-friction drive of the transmission levers 6a and 6b, a scanning roller 9 is rotatably guided on a pin 16 on the shaft drive-side section 52 of the transmission lever. Schematically illustrated spring assemblies 7 load respective transmission levers 6a and 6b accordingly and thereby press the scanning rollers 9 onto the control surfaces 53 of the Serrated lock washers 5a, 5b. From Fig. 2 it can be seen that with one rotation of the camshafts 4a and 4b each jaw 11 is moved by the transmission levers 6a and 6b within the tong carrier 12. In Fig. 2, the closed position of the tooth jaws 11 is shown schematically. In Fig. 2 fluid cylinders 22 are shown attacking each transmission lever 6a, 6b. By means of these fluid cylinders, which can be designed as hydraulic cylinders, for example, the transmission levers can be lifted against the spring preload from the respective serrated disc control surfaces 53, which is necessary, for example, when replacing the camshafts 4a and 4b, which are mounted within the support tubes 2a and 2b . Furthermore, the fluid cylinders 22 can be operated to prevent the jaws 11 from closing. Such control of the fluid cylinder takes place, for. B. for the elimination of defective preforms, such as those that occur, for example, in the transition from one material bar to the next. In this case, the first pliers are kept open via the fluid cylinder 22, so that this faulty compact is not transported further.

Auf den Nockenwellen 4a und 4b sind die Fächerscheiben 5a, 5b auswechselbar und in Umfangsrichtung der Nockenwellen verstellbar befestigt. Dadurch kann jede Fächerscheibe unabhängig von anderen auf der Nockenwelle so eingestellt werden. daß für jedes Zangenbackenpaar 11 eine dem entsprechenden Umformvorgang optimal angepaßte Steuerung erreicht werden kann.On the camshafts 4a and 4b, the serrated lock washers 5a, 5b are exchangeable and fastened in an adjustable manner in the circumferential direction of the camshafts. This enables each serrated lock washer to be set independently of the others on the camshaft. that a control optimally adapted to the corresponding forming process can be achieved for each pair of jaws 11.

Zur Erzielung einer raschen Austauschbarkeit der Nockenwellen 4a und 4b und gleichzeitig einer präzisen Lagerung der jeweiligen Nockenwelle über eine beträchtliche axiale Erstreckung innerhalb der Tragrohre 2a, 2b dient eine Lagerungsanordnung 54, die gemäß Fig. 3 ein Wälzlager 15 umfaßt, dessen Innenring 15b auf der Nockenwelle 4b aufsitzt und dessen Außenring 15a einen kleineren Durchmesser besitzt als der Innendurchmesser des Tragrohrs 2b beträgt. Zur Überbrückung der Durchmesserdifferenz dienen durch die Wandung des Tragrohrs 2b hindurchtretende Stützzapfen 14, die in Umfangsrichtung des jeweiligen Wälzlagers 15 auf Winkelabstände verteilt um den Außenring 15a gruppiert vorgesehen sind und mit ihren der Außenringumfangsfläche 15d zugewandten Endfläche 14a das gesamte Wälzlager 15 zentrisch nach Art einer Lünette abstützen. In fertigungstechnischer Hinsicht ist es von Vorteil, daß die Realisierung der Lageranordnung 54 es lediglich erforderlich macht, die äußere Umfangsfläche 2d auf einen vorgegebenen Durchmesser mit einem engen Toleranzbereich zu fertigen, und die Stützzapfen 14, die mit ihrem in Fig. 4 sichtbaren Schaft durch in der Tragrohrwandung vorgesehene Bohrungen hindurchgeführt sind, mit einer entsprechenden Präzision zu bearbeiten, und sie mit ihren an der Umfangsfläche 2d liegenden Zapfenstirnflächen 14c an einer auf diese äußere Umfangsfläche 2d des betreffenden Tragrohrs aufgeklemmten Innenfläche 3c, die Bestandteil des Befestigungsabschnitts des Zangenkastens 3a bzw. 3b ist abzustützen. Die Ansicht des Stützzapfens 14 gemäß Fig. 4 zeigt, daß seine Zapfen-Stirnfläche 14c im Unterschied zum zylindrischen Zapfenschaft quadratisch und, wie Fig. 3 erkennen läßt, mit einer dem Radius der Innenfläche 3c des besagten Befestigungsabschnitts entsprechenden Krümmung versehen ist. Ersichtlicherweise bedingt diese spezifische Formgebung des Stützzapfens 14 bei einer entsprechend angepaßten Bearbeitung der äußeren Umfangsfläche 2d eine zuverlässige Lagerung der Wälzlager 15 im jeweiligen Tragrohr.To achieve rapid interchangeability of the camshafts 4a and 4b and at the same time a precise mounting of the respective camshaft over a considerable axial extent within the support tubes 2a, 2b, a bearing arrangement 54 is used, which according to FIG. 3 comprises a roller bearing 15, the inner ring 15b of which is on the camshaft 4b is seated and the outer ring 15a has a smaller diameter than the inner diameter of the support tube 2b. To bridge the difference in diameter, support pins 14 which pass through the wall of the support tube 2b are used, which are provided in the circumferential direction of the respective roller bearing 15 distributed at angular intervals and grouped around the outer ring 15a, and with their end surface 14a facing the outer ring peripheral surface 15d, the entire roller bearing 15 centrally in the manner of a steady rest support. From a manufacturing point of view, it is advantageous that the realization of the bearing arrangement 54 only makes it necessary to manufacture the outer circumferential surface 2d to a predetermined diameter with a narrow tolerance range, and the support pins 14, which with their shank visible in FIG bores provided through the support tube wall are machined with a corresponding precision, and they with their pin end faces 14c lying on the peripheral surface 2d on an inner surface 3c clamped onto this outer peripheral surface 2d of the relevant support tube, which is part of the fastening section of the pliers box 3a or 3b to support. The view of the support pin 14 according to FIG. 4 shows that its pin end face 14c, in contrast to the cylindrical pin shaft, is square and, as can be seen in FIG. 3, is provided with a curvature corresponding to the radius of the inner surface 3c of said fastening section. Obviously, this specific shape of the support pin 14 requires a reliable mounting of the roller bearings 15 in the respective support tube when the outer peripheral surface 2d is adapted accordingly.

In der Schnittdarstellung gemäß Fig. 5 ist der das obere Tragrohr 2a enthaltende Abschnitt des Jochs 17 gemäß Fig. 1 im einzelnen dargestellt. Das Tragrohr 2a steht mit dem gezeigten Abschnitt des Jochs 17 über eine an seinem Außenumfang angreifende Vorrichtung 37 in Verbindung. Durch Einleiten eines Fluids in einen oder mehrere Ringkanäle in der Vorrichtung 37 wird diese aufgeweitet, dadurch lässt sich eine kraftschlüssige Verbindung zwischen dem Tragrohr 2a und dem Joch 17 herstellen. Im quertransportbereiten Zustand sind beide Tragrohre 2a und 2b (Fig. 1) mit dem Joch 17 zu einer gleitend verschiebbaren Einheit verbunden. Neben dem gemäß Fig. 5 rechten Ende des Tragrohrs 2a befindet sich auf der Nockenwelle 4a ein Axiallager 19, das einen mit der Nockenwelle 4a fest verbundenen Lagerring 29 aufweist, der in seinem Außenumfangsbereich ein radial schwimmend gelagertes Kupplungsglied 28 trägt. Eine Riegelanordnung 23 ist an mehreren Befestigungsstellen 24a, 24b (vgl. Fig. 6 und 7) am Joch 17 angeschraubt und besitzt in Radialrichtung in das Axiallager 19 eingreifende Riegel 23a, 23b, welche in ihrer Eingriffsposition gemäß Fig. 5 eine in Axialrichtung starre Verbindung zwischen dem Tragrohr 2a und der Nockenwelle 4a herstellen. Wenn bei einer solchen Verbindung auf die Anlenkstelle 18 des Jochs 17 (Fig. 1) über eine nicht gezeigte Pleuelstange eines bekannten Kurven-Koppelgetriebes das Joch in eine periodisch oszillierende Längsbewegung in Richtung des Doppelpfeils 20 versetzt wird, nimmt das Joch über die Tragrohre 2a und 2b die Nockenwellen 4a und 4b entsprechend mit. Der jeweilige Hub des Quertransports entspricht dem Mittenabstand zwischen zwei benachbarten Umformstationen U1 bis U4 gemäß Fig. 1.5 shows the section of the yoke 17 according to FIG. 1 containing the upper support tube 2a in detail. The support tube 2a is connected to the section of the yoke 17 shown via a device 37 which engages on its outer circumference. By introducing a fluid into one or more ring channels in the device 37, the device 37 is expanded, thereby making it possible to establish a non-positive connection between the support tube 2a and the yoke 17. In the state ready for transverse transport, both support tubes 2a and 2b (FIG. 1) are connected to the yoke 17 to form a slidably displaceable unit. In addition to the right end of the support tube 2a according to FIG. 5, there is an axial bearing 19 on the camshaft 4a, which has a bearing ring 29 which is fixedly connected to the camshaft 4a and which carries a radially floating coupling member 28 in its outer peripheral region. A bolt arrangement 23 is screwed to the yoke 17 at a plurality of fastening points 24a, 24b (see FIGS. 6 and 7) and has bolts 23a, 23b which engage in the axial bearing 19 in the radial direction and which in their engagement position according to FIG. 5 have a connection which is rigid in the axial direction between the support tube 2a and the camshaft 4a. When such a connection to the articulation point 18 of the yoke 17 (FIG. 1) via a connecting rod, not shown, of a known cam coupling gear, the yoke is set in a periodically oscillating longitudinal movement in the direction of the double arrow 20, the yoke takes over the support tubes 2a and 2b the camshafts 4a and 4b accordingly. The respective stroke of the transverse transport corresponds to the center distance between two adjacent forming stations U1 to U4 according to FIG. 1.

Damit die Nockenwellen 4a und 4b aus den Tragrohren 2a und 2b herausgezogen werden können, muß die Riegelanordnung 23 gelöst werden. Ihre Riegel 23a und 23b sind gemäß Fig. 5 zwischen Riegelführungsplatten 26 und 27 verschiebbar geführt, wobei der gegenseitige Abstand der Führungsplatten an den Befestigungsstellen 24a, b über entsprechende Distanzhülsen 34 festgelegt ist. Aus Fig. 6 ist ersichtlich, daß die Riegel 23a, b um Schwenkzapfen 25a und 25b verlagerbar sind und daß an dem gemäß Fig. 6 unteren Endbereich der Riegelanordnung 23 zwischen den Riegeln 23a und 23b eine auf einem Führungszapfen 32 sitzende Feder 33 und an den bezüglich der Schwenkzapfen 25a und 25b gegenüberliegenden Endabschnitten der Riegel 23a und 23b eine Fluidzylinderanordnung 31 vorgesehen ist. Aus der Darstellung in Fig. 6 ist ersichtlich, daß ein Herausschwenken der Riegel 23a, 23b aus der abgebildeten Verriegelungsposition über die Feder 33 bewirkt wird, sobald der während der Verriegelung ausgeübte Fluiddruck in der Zylinderanordnung 31 weggenommen wird. Bei einem entsprechenden erneuten Anlegen des Fluiddrucks läßt sich die Riegelanordnung 23 wieder schließen. In den Fig. 5 und 6 sind lediglich das Axiallager 19 und die Riegelanordnung 23 für die gemäß Fig. 1 obere Tragrohranordnung dargestellt. Für das Tragrohr 2b und die Nockenwelle 4b ist ein entsprechender Aufbau vorgesehen. Um ein axiales Herausziehen der Nockenwellen 4a und 4b aus dem entsprechenden Tragrohr 2a und 2b (Pfeile 21) vornehmen zu können, sind zusätzlich zum Lösen der Riegelanordnung 23 die in Fig. 2 schematisch dargestellten Fluidzylinder 22 in der Weise zu betätigen, daß sie die Übertragungshebel 6a und 6b aus ihrem Eingriff mit den Fächerscheiben 5a, 5b herausnehmen.The latch arrangement 23 must be released so that the camshafts 4a and 4b can be pulled out of the support tubes 2a and 2b. 5, the bolts 23a and 23b are displaceably guided between bolt guide plates 26 and 27, the mutual spacing of the guide plates at the fastening points 24a, b being corresponding Spacer sleeves 34 is set. From Fig. 6 it can be seen that the bolts 23a, b can be shifted about pivot pins 25a and 25b and that at the lower end region according to FIG. 6 of the bolt arrangement 23 between the bolts 23a and 23b a spring 33 seated on a guide pin 32 and on the a fluid cylinder arrangement 31 is provided with respect to the pivot portions 25a and 25b opposite end sections of the bolts 23a and 23b. It can be seen from the illustration in FIG. 6 that the latches 23a, 23b are pivoted out of the locking position shown via the spring 33 as soon as the fluid pressure exerted during the locking is removed in the cylinder arrangement 31. With a corresponding renewed application of the fluid pressure, the latch arrangement 23 can be closed again. 5 and 6, only the thrust bearing 19 and the locking arrangement 23 for the upper support tube arrangement shown in FIG. 1 are shown. A corresponding structure is provided for the support tube 2b and the camshaft 4b. In order to be able to axially pull the camshafts 4a and 4b out of the corresponding support tube 2a and 2b (arrows 21), in addition to releasing the locking arrangement 23, the fluid cylinders 22 shown schematically in FIG. 2 must be actuated in such a way that they move the transmission levers Remove 6a and 6b from their engagement with the serrated lock washers 5a, 5b.

Die Nockenwellen 4a und 4b werden vom Hauptantrieb der Umformmaschine über einen in Form eines Kastens 35 in Fig. 1 schematisch dargestellten Ketten- und Zahnradantrieb in Drehung versetzt. Diese Drehbewegung wird infolge der gleichzeitig stattfindenden Axialbewegung der Nockenwellen mit Hilfe von nicht dargestellten Keilwellen übertragen.The camshafts 4a and 4b are set in rotation by the main drive of the forming machine via a chain and gear drive shown schematically in the form of a box 35 in FIG. 1. This rotary movement is transmitted due to the simultaneous axial movement of the camshafts with the help of spline shafts, not shown.

Für ein Hochschwenken des oberen Zangenkastens 3a gemeinsam mit dem Tragrohr 2a aus der in den Fig. 1 und 2 gezeigten Lage, wird die Verbindung zwischen dem Tragrohr 2a und dem Joch 17 über die hydraulisch aufgeweitete, genannte Vorrichtung 37 durch Weggnahme des Hydraulikdruckes aufgehoben. Ein Hochschwenken erfolgt durch Betätigung eines Hydraulikzylinders 38 gemäß Fig. 7, der eine Zahnstange 39 verschiebt, welche über ein Ritzel 40 ein Zahnrad 41 in Drehung versetzt, das, wie aus Fig. 5 ersichtlich, am Endabschnitt des Tragrohrs 2a über eine Verkeilung drehfest angeordnet ist. Sobald das Tragrohr 2a sich dem Hub des Hydraulikzylinders 38 entsprechend verdreht und damit den oberen Zangenkasten 3a in eine obere Schwenklage gebracht hat, erfolgt wieder das hydraulische Aufweiten der Vorrichtung, und über die erneute Pressverbindung wird der Zangenkasten in seiner oberen Schwenklage vom Joch 17 abgestützt sicher gehalten.For a swiveling up of the upper pliers box 3a together with the support tube 2a from the position shown in FIGS. 1 and 2, the connection between the support tube 2a and the yoke 17 is released via the hydraulically widened device 37 by removing the hydraulic pressure. 7, which moves a rack 39, which rotates a gearwheel 41 via a pinion 40, which, as can be seen in FIG. 5, is arranged in a rotationally fixed manner at the end section of the support tube 2a by means of a wedge is. As soon as the support tube 2a rotates according to the stroke of the hydraulic cylinder 38 and thus has brought the upper tong box 3a into an upper swivel position, the device is hydraulically expanded again, and the renewed press connection securely supports the tong box in its upper swivel position by the yoke 17 held.

Während des Quertransports des Jochs 17 wird das Zahnrad 41 mitbewegt, weshalb für eine Verschwenkbarkeit des oberen Zangenkastens 3a in jeder beliebigen Axialstellung des Tragrohrs das Ritzel 40 eine solche Breite besitzen muß, daß sie mindestens dem Quertransporthub zuzüglich der Dicke des Zahnrads 41 entspricht. Wenn diese Bedingungen erfüllt sind, können das Ritzel 40 und das Zahnrad 41 ständig im Eingriff bleiben. Um den Verschleiß zwischen dem Ritzel und dem Zahnrad möglichst gering zu halten und damit ferner während des Betriebs der Einrichtung keine Kräfte auf die Schwenkanordnung ausgeübt werden, ist das Zahnspiel zwischen Ritzel 40 und.Zahnrad 41 relativ groß bemessen.During the transverse transport of the yoke 17, the gear 41 is also moved, which is why the pinion 40 must have a width such that it can at least correspond to the transverse transport stroke plus the thickness of the gear 41 in order to pivot the upper tong box 3a in any axial position of the support tube. If these conditions are met, the pinion 40 and the gear 41 can remain constantly engaged. In order to keep the wear between the pinion and the gear as low as possible and so that no forces are exerted on the swivel arrangement during operation of the device, the backlash between the pinion 40 and gear 41 is relatively large.

Damit nach einem Hochschwenken des oberen Zangenkastens 3a eine genaue Wiederherstellung der Ausgangslage und damit eine wiederholbare lagerichtige Zusammenarbeit der oberen und unteren Zangenbacken 11 möglich ist, muß die exakte Arbeitsstellung des Tragrohrs 2a sowohl in axialer als auch in radialer Richtung genau positioniert werden. Dazu dient eine Positioniereinrichtung 42, die eine auf das Tragrohr 2a aufgeschraubte Lasche 43 mit einer eingefrästen Kontur aufweist, in der ein Positionierprisma 44 befestigt ist. Zur Befestigung dient eine in der rechten Abbildung gemäß Fig. 8 schematisch dargestellte Schraube. In einen in der Schwenkrichtung des Tragrohrs 2a dem Positionierprisma 44 gegenüberliegenden vorstehenden Jochabschnitt 17a des Jochs 17 ist eine dem Prisma 44 entsprechende Kontur eingearbeitet, so daß das Tragrohr vor allem in der letzten Phase des Rückschwenkens in seine Ausgangslage über das Positionierprisma 44 und die Kontur im Jochabschnitt 17a axial und radial sicher justiert wird. Wenn sich der Zangenkasten 3a in seiner hochgeschwenkten Position befindet, ist die Lasche 43 gemäß der linken Darstellung in Fig. 8 in ihre strichpunktiert eingezeichnete Lage verschwenkt.In order for an exact restoration of the starting position and thus a repeatable correct cooperation of the upper and lower jaws 11 is possible after swiveling up the upper pliers box 3a, the exact working position of the support tube 2a must be positioned exactly in both the axial and radial directions. A positioning device 42 is used for this purpose, which has a tab 43 screwed onto the support tube 2a with a milled contour, in which a positioning prism 44 is fastened. A screw shown schematically in the right-hand illustration according to FIG. 8 is used for fastening. In a projecting yoke section 17a of the yoke 17 opposite the positioning prism 44 in the pivoting direction of the support tube 2a, a contour corresponding to the prism 44 is incorporated, so that the support tube, particularly in the last phase of pivoting back into its starting position via the positioning prism 44 and the contour in Yoke section 17a is adjusted axially and radially securely. When the tong box 3a is in its swiveled-up position, the tab 43 is swiveled into its position shown in broken lines as shown in FIG. 8.

Claims (12)

1. Automatic transfer device for workpieces in a multi-station forming machine, for the non- cutting forming of metal parts, particularly in a forming machine used in the pre-heated state, one workpiece (w) being taken up by each pair of interacting gripper jaws (11) in a forming station (U1, U2, U3 ...), transferred to the adjacent station (U2, U3, U4 ...) and these released, with two parallel supporting tubes (2a, 2b) which are driven in phase with the forming machine and guided to and fro in fixed bearings (50, 51) in its forming range and combined by a yoke (17) to form a unit slidable in the workpiece transfer direction, and which are coupled to a driving mechanism and to which gripper boxes (3a, 3b) are affixed by which the gripper jaws movable towards each other are guided in a rectilinear direction and which also serve to support transfer levers (6a, 6b) operatively connected on the one hand to the gripper jaws and on the other to driving shafts movable in relation to one another in the supporting tubes, characterized by the fact that the driving shafts consist of cam shafts (4a, 4b) rotatably mounted in the supporting tubes (2a, 2b) and driven in rotation and having a number of cam elements (5) which are associated with each transfer lever and which are adjustable both as regards the cam shaft rotation axis and the angle in relation to one another to which they have been rotated.
2. Device in accordance with Claim 1, characterized by the fact that the cam elements (5) consist of fan-type discs (5a, 5b) provided with appropriate markings for setting preselected rotation angle positions in respect of the cam shaft rotation axis and that each transfer lever (6a, 6b) is provided, on a lever section (52) on the drive shaft side, with a scanning roller (9) running on a control surface (53) of the fan-type discs.
3. Device in accordance with Claim 2, characterized by the fact that the cam shaft (4a, 4b) equipped with the fan-type discs (5a, 5b) are combined identically, rotate in the same direction and are mounted interchangeably as a complete constructional unit, that a bearing system (54) comprises in some or all cam shafts, between adjacent fan-type discs (5a, 5b) in accordance with the way in which they are allocated to the respective transfer levers (6a, 6b) and possibly also adjacent to the outermost fan-type discs corresponding number of roller bearings (15) of which the outer bearing rings (15a) have a smaller external diameter than the internal diameter of the relevant supporting tube (2a, 2b) and that each roller bearing (15) is secured concentrically, in the manner of a steady rest, on the peripheral surface (15d) of its outer ring, by a number of supporting journals (14) distributed at angular intervals around the relevant outer ring, passing through radial borings in the wall of the supporting tube (2a, 2b) and extending into the interior of the latter as far as the outer ring, and that the depth to which the said supporting journal (14) penetrates the interior of the supporting tube is adjusted in accordance with the outer peripheral surface (2d) of the supporting tube concerned.
4. Device in accordance with Claim 3, characterized by the fact that the bearing system (54) provided within the length of a securing section of the gripper box (3a, 3b) clamped onto the outer peripheral surface (2d) of each supporting tube (2a, 2b), that the outer peripheral surface (2d) of the supporting tube is precision- worked to a preselected diameter with a narrow tolerance range and the supporting journals (14) are worked with a corresponding degree of precision, particularly in their length, and supported by their end surfaces (14c) resting on the peripheral surface (2d), on an internal surface (3c) of the securing section clamped onto the outer peripheral surface (2d).
5. Device in accordance with one of Claims 1 - 4, characterized by the fact that each cam shaft (4a, 4b) is locked, in a zone on the yoke side via an axial bearing (19) and a releasable locking system (23) acting on the said bearing, in a transversely transferable state with the corresponding supporting tube (2a, 2b), so that it can be displaced in the axial direction, and that those sections (52) of the transfer levers (6a, 6b) which are on the driving shaft side are movable by fluid cylinders (22) acting on the levers from their contact with the relevant cam shaft (4a, 4b), in such a way that the cam shaft, if the locking system (23) is additionally released, can be extracted from the supporting tube (2a, 2b) and replaced, if necessary, by a replacement shaft.
6. Device in accordance with Claim 5, characterized by the fact that the axial bearing (19) has a bearing ring (29) rigidly connected to the cam shaft (4a, 4b) bearing a radially floating coupling piece (28) in its external peripheral zone, that the locking system (23) is provided adjacent to the coupling piece, with locks (23a, 23b) pivotably mounted on the yoke (17) and having claws (30) which are disengaged from the coupling piece (28) by a spring (33) between the locks (23a, 23b) and can be caused to engage the coupling piece (28) by fluid cylinders (31) acting on the bolts in the opposite operative direction, in order to couple the relevant supporting tube (2a, 2b) to the corresponding cam shaft (4a, 4b) in such a way that they will be movable together in the axial direction.
7. Device in accordance with one of Claims 1 - 6, characterized by the fact that the cam shafts (4a, 4b) are driven in rotation in the same direction by the main drive of the forming machine via a combined chain wheel and toothed wheel gearing (35) and via spline shafts which in the course of their rotation also allow of an axial displacement of the cam shafts (4a, 4b) together with the associated supporting tubes (2a, 2b).
8. Device in accordance with one of Claims 1 - 7, characterized by the fact that the connection between the yoke (17) and in particular the supporting tube (2a) uppermost as regards the forming zone (U1 - U2) is provided by a device (37) acting on the outer peripheral surface of the supporting tube, that this device can be widened by means of a fluid pressure system thus producing the connection between the yoke and the said supporting tube, and that a swivel drive (41, 40, 39, 38) is provided to rotate the supporting tube (2a) together with the associated gripper box (3a) when the yoke has been disconnected, a positioning device being provided for accurate adjustment of the position of the supporting tube (2a) which, likewise after the release of the yoke connection, has been pivoted back into its initial position.
9. Device in accordance with Claim 8, characterized by the fact that the positioning device (42) is equipped with a strap (43) clamped onto the supporting tube (2a) and having a milled contour in which a positioning prism (44) is secured, that a contour corresponding to the prism is worked into that projecting section (17a) of the yoke which is opposite to the positioning prism (44) as viewed in the pivoting direction of the supporting tube (2a), in such a way that the supporting tube (2a), particularly in the final phase of the return pivoting movement to its initial position, is axially and radially adjusted with the positioning prism (44) and the contour in the said section of the yoke.
10. Device in accordance with one of Claims 1 - 9, characterized by the fact that of the two parallel supporting tubes (2a, 2b) with the respective cam shafts (4a, 4b) the supporting tube (2c) which is the lower as regards the forming zone (U1, U2) is at a shorter distance from the workpiece transfer plane than the upper supporting tube (2a), that the transfer lever (6b) associated with the lower supporting tube (2b) or with the corresponding cam shaft (4b) is designed as a single-arm lever with its section (52) on the shaft drive side, and its section (56) on the gripper drive side, and is positioned in a gripper box (3b) of compact construction in the longitudinal direction of the transfer lever (6b) and that a discharge channel (57) for workpieces expelled from the forming machine is provided immediately behind the said gripper box (3b).
11. Device in accordance with one of Claims 2 and 5 as well as 2 - 10, characterized by the fact that each scanning roller (9) of a transfer lever (6a, 6b) is biased towards the control surface (53) of the fan-type disc by a spring (7) and that the fluid cylinders (22) provided on each transfer lever (6a, 6b) can be controlled in opposition to the biasing direction of the said spring.
EP86108162A 1985-06-24 1986-06-14 Automatic transfer device for work pieces in a multistation forming machine Expired EP0206186B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86108162T ATE39633T1 (en) 1985-06-24 1986-06-14 DEVICE FOR AUTOMATIC TRANSPORTATION OF WORKPIECES ON A MULTI-STAGE FORMING MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2680/85 1985-06-24
CH268085 1985-06-24

Publications (2)

Publication Number Publication Date
EP0206186A1 EP0206186A1 (en) 1986-12-30
EP0206186B1 true EP0206186B1 (en) 1989-01-04

Family

ID=4239161

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86108162A Expired EP0206186B1 (en) 1985-06-24 1986-06-14 Automatic transfer device for work pieces in a multistation forming machine

Country Status (5)

Country Link
US (1) US4759208A (en)
EP (1) EP0206186B1 (en)
JP (1) JPS61296935A (en)
AT (1) ATE39633T1 (en)
DE (1) DE3661598D1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EA000551B1 (en) 1996-10-03 1999-10-28 Хатебур Умформмашинен Аг Device for the automatic conveyance of workpieces on a multiple metal-forming machine tool

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851979A (en) * 1954-06-15 1958-09-16 Henry B Chatfield Transfer device
DE1249806B (en) * 1957-12-02
DE1232097B (en) * 1961-06-29 1967-01-12 Metallwaren Und Maschinenfabri Step feed device for sheet metal presses or the like.
US3180123A (en) * 1962-10-12 1965-04-27 Ajax Mfg Co Work transfer mechanism for forging presses and the like
GB1308245A (en) * 1970-06-05 1973-02-21 Wickman Mach Tool Sales Ltd Feed mechanism
US3754667A (en) * 1972-01-07 1973-08-28 R Storch Transfer mechanism
DE2715966C3 (en) * 1977-04-09 1980-03-27 Hatebur Umformmaschinen Ag, Basel (Schweiz) Device for the automatic transport of workpieces on multi-stage cross transport presses
US4404837A (en) * 1979-07-11 1983-09-20 American Can Company Press transfer bar
US4428221A (en) * 1982-01-22 1984-01-31 Owens Roland G Transfer apparatus for straight side press

Also Published As

Publication number Publication date
DE3661598D1 (en) 1989-02-09
EP0206186A1 (en) 1986-12-30
ATE39633T1 (en) 1989-01-15
JPS61296935A (en) 1986-12-27
US4759208A (en) 1988-07-26

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