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EP0543773A1 - Hydraulic bending press - Google Patents

Hydraulic bending press Download PDF

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Publication number
EP0543773A1
EP0543773A1 EP92810803A EP92810803A EP0543773A1 EP 0543773 A1 EP0543773 A1 EP 0543773A1 EP 92810803 A EP92810803 A EP 92810803A EP 92810803 A EP92810803 A EP 92810803A EP 0543773 A1 EP0543773 A1 EP 0543773A1
Authority
EP
European Patent Office
Prior art keywords
joint
hydraulic press
press brake
brake according
butt
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.)
Ceased
Application number
EP92810803A
Other languages
German (de)
French (fr)
Inventor
Waldemar Krumholz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
M&S Brugg AG
Original Assignee
M&S Brugg AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by M&S Brugg AG filed Critical M&S Brugg AG
Publication of EP0543773A1 publication Critical patent/EP0543773A1/en
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal
    • 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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure

Definitions

  • the invention relates to a hydraulic press brake, with a bar-shaped or cheek-shaped plunger, which is articulated at both ends to the piston rod of a power cylinder, with an articulated butt connection being provided for transmitting the pressing force from the piston rod to the plunger.
  • the butt joints are designed as simple butt joints and bridged by supporting members, which are each articulated to the piston rods and the plunger. These support elements take up the ram weight when the ram is empty and hold the elements of the butt joints together. In the operation of the ram, the higher-load butt joints take over the power transmission, while the support elements with their less resilient spherical bearings are largely relieved.
  • the aim of the invention is to create a hydraulic press brake of the type mentioned, which does not have the disadvantages described and is characterized in particular by the fact that it operates with a play-free ram drive in every operating case and still enables a simpler frame structure with less machining effort and that it also allows an operational inclination of the ram with a relatively large angle of inclination.
  • butt connection is formed by a double joint consisting of two butt joints which are effectively arranged in series with equally oriented degrees of freedom.
  • Cylinder joints with joint axes or ball joints running perpendicular to the plane of movement of the plunger are suitable as butt joints.
  • the double joints allow a play-free connection between piston rods and tappet, so that an unintentional inclination of the tappet in the working stroke is avoided. Furthermore, a greater tolerance with regard to the parallelism of the force vectors is permissible, which means that with regard to the positioning of the force cylinders with respect to the parallelism of their lines of action, less high accuracy is sufficient and an expensive reworking of the mounting surfaces in question may even be dispensed with. In addition, the presence of the double joints also prevents excessively high managers.
  • an operational inclination of the ram with a relatively large angle of inclination can be achieved without a significant increase in the number of executives, and because the guides are free from play, an inclination once set in the working stroke of the ram is retained regardless of the degree of uniformity of the load.
  • each double joint is made up of a joint head connected to the piston rod or the tappet and a double-sided joint socket arranged freely movable between the two joint heads, the joint heads being made of brass, for example, and the joint sockets being made of steel, in particular cast steel consist.
  • the double joint can be designed in such a way that the joint heads and the piston rods or the plungers abut each other loosely on flat surfaces running transversely to the direction of the joint and are fixed in their mutual transverse position by means of fitting bolts.
  • a preferred embodiment consists in the fact that the center of the rod ends on the piston rods or on the tappet with the respective center of the articulated axes on the piston rods or on the tappet the supporting organs collapse. This is in contrast to the well-known simple butt joint, the center of which has no functional relationship to the joint axes of the supporting members.
  • the support members preferably have a freewheel which is effective during the press stroke of the ram in order to relieve the support members of impact forces during the operation of the ram.
  • the support members can include spring elements that are switched on in the frictional engagement thereof and dampen the force peaks acting on the support members at the beginning of the empty stroke of the ram.
  • the spring elements are also expediently dimensioned such that, under their action, the elements of the butt joints are held together loosely when the plunger is empty.
  • each support member consists of a bolt which is fixedly connected to the one articulation axis in the direction of force and which passes freely through the other articulation axis in a bore and has a support element at the end.
  • the ram can have a central swivel joint at the height of the power cylinder, which can be moved vertically in a straight guide.
  • this straight guide ensures that the ram always assumes a defined position in this regard, despite the horizontal displacement made possible by the double joints.
  • the frame of the press brake is essentially composed of two vertical side walls 1 and a yoke beam 2 connecting the side walls 1 to one another on the upper side.
  • the yoke beam is box-shaped and consists of two vertical longitudinal plates 3 and 4, which are connected to one another at the ends by a vertical transverse plate 5.
  • the side walls 1 are each formed from two upstanding plates 6 and 7, which are arranged at a distance from one another leaving a space 8 and are connected to one another on the upper side by the yoke beam 2 and on the underside by an intermediate piece 9.
  • the active parts of the press brake form a fixed lower beam 10 and an upper beam 11 forming the vertically movable ram, both of which are in the horizontal direction extend between the two side cheeks 1 of the frame into the respective intermediate space 8 thereof and to which the bending tools can be fastened in a manner not shown.
  • each intermediate piece 9 rests on a shoulder 13 of the plates 6 and 7 which is thickened by a shoulder 12 and at the same time serves as a bearing block for the lower beam 10 designed as a free-floating beam.
  • each intermediate piece 9 has two supports 14 spaced from one another, each with a semi-cylindrical pan 15 are provided.
  • a cylindrical pin 16 is anchored at both, stepped ends of the lower beam 10 which reach between the supports 14 and which rests with their projecting ends in the relevant pans 15 of the supports 14.
  • the upper cheek 11 hangs at its two remote ends on two supporting members 17, which are articulated on the one hand to the upper cheek 11 and on the other hand to the piston rod 18 of a power cylinder 19.
  • the hinge axis located on the upper cheek 11 being designated 20 and the hinge axis located on the piston rod 18 being designated 21.
  • Each power cylinder 19 is fastened to the adjacent cross plate 5 of the yoke beam 2 with a mounting flange 22.
  • an articulated butt joint in the form of a double joint 23 is provided for the transfer of the pressing force from the piston rods 18 to the upper cheek 11, an articulated butt joint in the form of a double joint 23 is provided. Details regarding the formation of the double joints 23 and the support members 17 are shown in FIGS. 3 and 4.
  • FIG. 3 shows one of the butt connections in section, the section plane running parallel to the plane of movement of the upper cheek 11.
  • the double joint 23 which forms the butt joint consists of two butt joints which are effectively arranged in series and is constructed from a joint head 24 connected to the piston rod 18, a joint head 25 connected to the upper cheek 11 and a two-sided joint socket 26 arranged between the two joint heads 24 and 25. Due to the selected position of the sectional plane, FIG. 3 applies both to cylindrical joints with joint axes running perpendicular to the plane of movement of the upper cheek 11 and to ball joints.
  • the abutting surfaces are either cylindrical or spherical.
  • the joint heads 24, 25 are preferably made of brass and the joint sockets 26 are made of steel, in particular cast steel.
  • the joint heads 24 and 25 abut on flat surfaces 27 and 28 running transversely to the direction of impact loosely on the piston rod 18 and on the upper cheek 11 and are secured against lateral displacement by means of locating bolts 29 and 30.
  • the contact surface 28 is adapted to the circumference of the joint head 25 by a thickening 31 of the upper cheek 11 provided at the connection point.
  • the centers of the butt joints fall with the associated joint axes of the support members 17 together, that is, the center of the joint head 24 and the adjoining socket side of the two-sided socket 26 coincides with the center of the joint axis 21 on the piston rod 18, and the center of the joint head 25 with the adjoining it
  • the socket side of the socket 26 coincides with the center of the joint axis 20 on the upper cheek 11. This ensures that the distance between the joint axes 20 and 21 remains constant with each adjustment of the double joint. Accordingly, when the double joint is adjusted, the supporting members 17 assigned to it are not subjected to additional tensile or compressive forces, as would be the case without the fixed distance between the joint axes.
  • FIG. 4 A first embodiment of the support members 17 bridging the butt connections is shown in FIG. 4.
  • the support member 17 is divided in the direction of force into an upper part 32 connected to the hinge axis 21 and a lower part 33 connected to the hinge axis 20.
  • the upper part 32 and the lower part 33 are loosely connected to one another by supporting bolts in the form of screws 34 which secure the push through sideways directed leg 35 of the upper part 32 in a free-running manner and are screwed into the lower part 33.
  • spring elements 37 for example plate springs, are used, which are dimensioned such that the elements 24, 25, 26 of the Hold the butt joints loosely together.
  • the free running of the support members 17 ensures that the pressing force is transmitted exclusively through the double joints 21 forming the butt connections in the working step of the ram, and consequently the support members 17 and their articulated connections are not additionally stressed by the pressing force.
  • each support member 40 consists of a bolt 41 which is fixedly connected to a sleeve 42 surrounding the hinge axis 21, e.g. is screwed and welded and which passes freely through the other joint axis 43 in a bore 44 and has a support element in the form of a nut 45 screwed onto the bolt end.
  • the spring elements 46 are arranged on the bolt 41 between the nut 45 and a part 47 of the joint axis 43 flattened at the connection point.
  • the articulated axis 43 is rotatably arranged in the upper cheek 11, while in the case of the articulated axes 20 and 21 the pivot bearing can optionally be located on the upper cheek 11 or on the support members 17 or on the bushing 42 of the support member 40.
  • the articulated connections formed by a double joint 23 and the support members 17 and 40 respectively assigned to them can be designed absolutely free of play. This ensures a high level of working accuracy for the press brake. A high manufacturing accuracy is only for these joint connections and required for the means not shown here for the parallel guidance of the upper beam 11.
  • the positioning of the power cylinders 19 does not require such a high level of accuracy, since inaccuracies in the mounting means in this regard do not necessarily affect the position of the upper beam 11, but are compensated for by the double joints 23. This considerably simplifies the structure of the frame.
  • the guide means for the upper beam 11 can be easily adjusted on the fully assembled press brake thanks to the double joints 23 until the upper beam 11 is precisely aligned with the lower beam 10.
  • the spherical design of the butt joint proves to be particularly advantageous in contrast to a likewise possible cylindrical joint design, because the plane of the upper cheek 11 can be adjusted in all directions due to the additional degree of freedom and regardless of the accuracy of the position of the power cylinder 19 by adjusting the 11 guides for the path of the upper beam can be brought into the desired operating position with high accuracy.
  • FIG. 6 shows schematically the mutual displacement of the elements 24, 25 and 26 of each double joint 23 with an inclined upper beam 11.
  • this Figure shows the moving parts with horizontal position of the upper cheek 11 with dash-dotted lines and with an inclined position thereof with solid lines, and the names of these parts refer to the inclined position.
  • a swivel joint 38 provided on the upper cheek 11, which is arranged at the height of the power cylinders 19 and can be moved vertically in a straight guide (not shown).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Automatic Assembly (AREA)
  • Braking Arrangements (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

The bending press has a bar- or beam-shaped ram (11), which is connected at both ends, in articulated fashion, to the piston rod (18) of a power cylinder (19). To transmit the press force from the piston rod to the ram (11), a hinge-like butt-joint connection is provided, this butt-joint connection being formed by a double joint (23) with two butt joints (24, 26; 25, 26) situated in series as regards their action. This measure makes possible play-free driving of the ram and, at the same time, a higher tolerance as regards the parallelism of the piston rods (18). In addition, it is also possible, under the same preconditions, to achieve tilting of the ram (11) at a relatively large angle of inclination during operation. …<IMAGE>…

Description

Die Erfindung betrifft eine hydraulische Abkantpresse, mit einem balken- oder wangenförmigen Stössel, welcher an seinen beiden Enden je mit der Kolbenstange eines Kraftzylinders gelenkig verbunden ist, wobei zur Übertragung der Presskraft von der Kolbenstange auf den Stössel eine gelenkartige Stossverbindung vorgesehen ist.The invention relates to a hydraulic press brake, with a bar-shaped or cheek-shaped plunger, which is articulated at both ends to the piston rod of a power cylinder, with an articulated butt connection being provided for transmitting the pressing force from the piston rod to the plunger.

Bei bekannten Abkantpressen dieser Art sind die Stossverbindungen als einfache Stossgelenke ausgebildet und durch Tragorgane überbrückt, welche je mit den Kolbenstangen und dem Stössel gelenkig verbunden sind. Diese Tragorgane nehmen im Leergang des Stössels das Stösselgewicht auf und halten die Elemente der Stossgelenke zusammen. Im Arbeitsgang des Stössels übernehmen die höher belastbaren Stossgelenke die Kraftübertragung, während die Tragorgane mit ihren weniger belastbaren Gelenklagern dabei weitgehend entlastet sind.In known press brakes of this type, the butt joints are designed as simple butt joints and bridged by supporting members, which are each articulated to the piston rods and the plunger. These support elements take up the ram weight when the ram is empty and hold the elements of the butt joints together. In the operation of the ram, the higher-load butt joints take over the power transmission, while the support elements with their less resilient spherical bearings are largely relieved.

Bei einer solchen Anordnung eines linear beweglichen Stössels mit zweipunktiger Krafteinleitung besteht das Problem, eine genaue Parallelität der beiden Kraftvektoren bzw. der beiden Kolbenstangenführungen zu erreichen. Ungenauigkeiten in dieser Beziehung wirken sich beim Arbeitsgang des Stössels in übermässig hohen Führungskräften in den Führungslagern sowie an den Elementen der Stossgelenke aus, welche die Lebensdauer dieser Teile herabsetzen und z.B. zum Verklemmen der Kolbenstangen führen können. Zur Vermeidung solcher betrieblicher Mängel ist eine sehr hohe Massgenauigkeit der zusammenwirkenden Teile und insbesondere auch der Montageflächen für die Kraftzylinder erforderlich. Gerade die genaue Bearbeitung dieser Montageflächen ist jedoch mit einem sehr hohen Aufwand verbunden. Insbesondere bei grossen Abkantpressen mit mehrere Meter breitem Durchgang ist es hingegen praktisch nicht möglich, mit wirtschaftlich tragbarem Bearbeitungsaufwand die erwünschte hohe Genauigkeit der Parallelität hinsichtlich der Kraftwirkung zu erreichen. Man hat deshalb versucht, die genannten Ungenauigkeiten wenigstens in gewissen Grenzen zu halten und durch ein entsprechend grosses Spiel in den Gelenkverbindungen zwischen Kolbenstangen und Stössel und in den Kolbenstangenführungen auszugleichen. Diese Massnahme hat jedoch den Nachteil, dass aufgrund der spielbehafteten Verbindungen und Führungen sich der Stössel bei ungleichmässiger Belastung im Arbeitsgang schrägstellen kann, wodurch nicht tolerierbare Ungenauigkeiten am bearbeiteten Werkstück auftreten können. Zudem besteht die Gefahr, dass bei einer Schrägstellung des Stössels im Arbeitsgang die Führungskräfte nach Aufhebung des Spiels wiederum zu stark ansteigen.With such an arrangement of a linearly movable ram with two-point force introduction, there is the problem of an exact parallelism of the two force vectors or the two To reach piston rod guides. Inaccuracies in this regard affect the operation of the ram in excessively high managers in the guide bearings and on the elements of the butt joints, which reduce the life of these parts and can lead to jamming of the piston rods, for example. To avoid such operational defects, a very high dimensional accuracy of the interacting parts and in particular also the mounting surfaces for the power cylinders is required. However, the precise machining of these assembly surfaces is associated with a very high outlay. In particular, in the case of large press brakes with a passage of several meters in width, it is practically not possible to achieve the desired high accuracy of parallelism with regard to the force effect with economically acceptable machining effort. Attempts have therefore been made to keep the inaccuracies mentioned at least within certain limits and to compensate for them by a correspondingly large amount of play in the articulated connections between the piston rods and tappet and in the piston rod guides. However, this measure has the disadvantage that, due to the playful connections and guides, the ram can tilt when the load is uneven in the work step, which means that intolerable inaccuracies can occur on the machined workpiece. There is also the risk that if the ram is tilted in the work step, the managers will rise too much after lifting the game.

Andererseits besteht das Bedürfnis, für gewisse Arbeitsgänge die Möglichkeit einer bestimmten Schräglage des Stössels vorzusehen. Durch spielbehaftete Verbindungen zwischen Kolbenstangen und Stössel wäre zwar diese Möglichkeit grundsätzlich gegeben. Der unter solchen Umständen erzielbare Winkel der Schrägstellung ist jedoch meist ungenügend gross. Ausserdem müsste man dabei die mit dem Spiel verbundenen, oben erwähnten Nachteile in Kauf nehmen.On the other hand, there is a need to provide the possibility of a certain inclined position of the ram for certain work steps. This possibility would be given in principle by connections with play between piston rods and tappet. However, the angle of inclination that can be achieved under such circumstances is usually insufficient. In addition, one would have to accept the disadvantages associated with the game, mentioned above.

Das Ziel der Erfindung besteht nun darin, eine hydraulische Abkantpresse der eingangs genannten Art zu schaffen, welche die beschriebenen Nachteile nicht aufweist und sich insbesondere dadurch auszeichnet, dass sie in jedem Betriebsfall mit spielfreiem Stösselantrieb arbeitet und trotzdem sogar einen einfacheren Gestellaufbau mit geringerem Bearbeitungsaufwand ermöglicht und dass sie zudem eine betriebsmässige Schrägstellung des Stössels mit verhältnismässig grossem Neigungswinkel erlaubt.The aim of the invention is to create a hydraulic press brake of the type mentioned, which does not have the disadvantages described and is characterized in particular by the fact that it operates with a play-free ram drive in every operating case and still enables a simpler frame structure with less machining effort and that it also allows an operational inclination of the ram with a relatively large angle of inclination.

Dieses Ziel lässt sich gemäss der Erfindung dadurch erreichen, dass die Stossverbindung durch ein Doppelgelenk aus zwei wirkungsmässig in Reihe liegenden Stossgelenken mit gleichorientierten Freiheitsgraden gebildet ist. Als Stossgelenke kommen Zylindergelenke mit senkrecht zur Bewegungsebene des Stössels verlaufenden Gelenkachsen oder Kugelgelenke in Frage.This goal can be achieved according to the invention in that the butt connection is formed by a double joint consisting of two butt joints which are effectively arranged in series with equally oriented degrees of freedom. Cylinder joints with joint axes or ball joints running perpendicular to the plane of movement of the plunger are suitable as butt joints.

Die Doppelgelenke lassen im Gegensatz zu einfachen gelenkartigen Stossverbindungen eine spielfreie Verbindung zwischen Kolbenstangen und Stössel zu, so dass eine ungewollte Schrägstellung des Stössels im Arbeitshub vermieden wird. Ferner ist eine grössere Toleranz in bezug auf die Parallelität der Kraftvektoren zulässig, was bedeutet, dass in Bezug auf die Positionierung der Kraftzylinder hinsichtlich der Parallelität ihrer Wirkungslinien eine weniger hohe Genauigkeit ausreicht und auf eine teure Nachbearbeitung der betreffenden Montageflächen unter Umständen sogar verzichtet werden kann. Ausserdem werden durch das Vorhandensein der Doppelgelenke auch übermässig hohe Führungskräfte vermieden. Schliesslich lässt sich eine betriebliche Schrägstellung des Stössels mit verhältnismässig grossem Neigungswinkel ohne wesentliche Erhöhung der Führungskräfte erzielen, wobei aufgrund der Spielfreiheit der Führungen eine einmal eingestellte Schrägstellung im Arbeitshub des Stössels unabhängig vom Gleichmässigkeitsgrad der Belastung erhalten bleibt.In contrast to simple articulated butt joints, the double joints allow a play-free connection between piston rods and tappet, so that an unintentional inclination of the tappet in the working stroke is avoided. Furthermore, a greater tolerance with regard to the parallelism of the force vectors is permissible, which means that with regard to the positioning of the force cylinders with respect to the parallelism of their lines of action, less high accuracy is sufficient and an expensive reworking of the mounting surfaces in question may even be dispensed with. In addition, the presence of the double joints also prevents excessively high managers. Finally, an operational inclination of the ram with a relatively large angle of inclination can be achieved without a significant increase in the number of executives, and because the guides are free from play, an inclination once set in the working stroke of the ram is retained regardless of the degree of uniformity of the load.

Gemäss einer bevorzugten Ausführungsform ist jedes Doppelgelenk aus je einem mit der Kolbenstange bzw. mit dem Stössel verbundenen Gelenkkopf und einer zwischen den beiden Gelenkköpfen frei beweglich angeordneten, zweiseitigen Gelenkpfanne aufgebaut, wobei die Gelenkköpfe z.B. aus Messing und die Gelenkpfannen z.B. aus Stahl, insbesondere aus Stahlguss bestehen.According to a preferred embodiment, each double joint is made up of a joint head connected to the piston rod or the tappet and a double-sided joint socket arranged freely movable between the two joint heads, the joint heads being made of brass, for example, and the joint sockets being made of steel, in particular cast steel consist.

Im weiteren kann das Doppelgelenk so gestaltet sein, dass die Gelenkköpfe und die Kolbenstangen bzw. die Stössel an quer zur Stossrichtung verlaufenden ebenen Flächen lose aneinanderstossen und durch Passbolzen in ihrer gegenseitigen Querlage fixiert sind.Furthermore, the double joint can be designed in such a way that the joint heads and the piston rods or the plungers abut each other loosely on flat surfaces running transversely to the direction of the joint and are fixed in their mutual transverse position by means of fitting bolts.

Wenn die Stossverbindungen in an sich bekannter Weise durch an Kolbenstange und Stössel angelenkte Tragorgane überbrückt sind, besteht eine bevorzugte Ausführungsform darin, dass das Zentrum der Gelenkköpfe an den Kolbenstangen bzw. am Stössel mit dem jeweiligen Zentrum der an den Kolbenstangen bzw. am Stössel befindlichen Gelenkachsen der Tragorgane zusammenfällt. Dies im Gegensatz zu dem bekannten einfachen Stossgelenk, dessen Zentrum zu den Gelenkachsen der Tragorgane in keiner funktionellen Beziehung steht.If the butt connections are bridged in a manner known per se by supporting members articulated on the piston rod and tappet, a preferred embodiment consists in the fact that the center of the rod ends on the piston rods or on the tappet with the respective center of the articulated axes on the piston rods or on the tappet the supporting organs collapse. This is in contrast to the well-known simple butt joint, the center of which has no functional relationship to the joint axes of the supporting members.

Vorzugsweise weisen die Tragorgane einen beim Presshub des Stössels wirksamen Freilauf auf, um die Tragorgane beim Arbeitsgang des Stössels von Stosskräften zu entlasten. Ferner können die Tragorgane in den Kraftschluss derselben eingeschaltete Federelemente enthalten, welche die zu Beginn des Leerhubs des Stössels auf die Tragorgane einwirkenden Kraftspitzen dämpfen. Dabei sind die Federelemente zweckmässigerweise ausserdem so dimensioniert, dass unter deren Wirkung die Elemente der Stossgelenke im Leergang des Stössels lose zusammengehalten werden.The support members preferably have a freewheel which is effective during the press stroke of the ram in order to relieve the support members of impact forces during the operation of the ram. Furthermore, the support members can include spring elements that are switched on in the frictional engagement thereof and dampen the force peaks acting on the support members at the beginning of the empty stroke of the ram. The spring elements are also expediently dimensioned such that, under their action, the elements of the butt joints are held together loosely when the plunger is empty.

Gemäss einer ersten praktischen Ausführung sind die Tragorgane in Kraftrichtung unterteilt und die Teile durch Tragbolzen lose miteinander verbunden. Eine andere Ausführung kann beispielsweise darin bestehen, dass jedes Tragorgan aus einem Bolzen besteht, welcher mit der einen Gelenkachse in Kraftrichtung fest verbunden ist und welcher die andere Gelenkachse in einer Bohrung freilaufend durchsetzt und endseitig ein Tragelement aufweist.According to a first practical embodiment, the support members are divided in the direction of force and the parts are loosely connected to one another by support bolts. Another embodiment can consist, for example, in that each support member consists of a bolt which is fixedly connected to the one articulation axis in the direction of force and which passes freely through the other articulation axis in a bore and has a support element at the end.

Damit bei der Schrägstellung des Stössels die seitliche Auslenkung desselben im Raum zwischen den beiden Kraftzylindern möglichst gering ist und sich auf beide Seiten gleichmässig verteilt, kann der Stössel auf der Höhe der Kraftzylinder ein zentrales Drehgelenk aufweisen, welches in einer Geradführung vertikal bewegbar ist. Ausserdem wird durch diese Geradführung erreicht, dass der Stössel trotz der durch die Doppelgelenke an sich ermöglichten Horizontalverschiebung diesbezüglich stets eine definierte Lage einnimmt.So that the lateral deflection of the ram in the space between the two power cylinders is as small as possible and is evenly distributed on both sides when the ram is tilted, the ram can have a central swivel joint at the height of the power cylinder, which can be moved vertically in a straight guide. In addition, this straight guide ensures that the ram always assumes a defined position in this regard, despite the horizontal displacement made possible by the double joints.

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung dargestellt, und zwar zeigen:

Fig. 1
eine Seitenansicht der erfindungsgemässen Abkantpresse;
Fig. 2
eine auf die beiden Seitenenden beschränkte Frontansicht der Abkantpresse nach Fig. 1;
Fig. 3
Ansicht eines Doppelgelenkes in grösserem Massstab, im Schnitt;
Fig. 4
Ansicht einer ersten Ausführung des Tragorgans in grösserem Massstab;
Fig. 5
Ansicht einer zweiten Ausführung des Tragorgans in grösserem Massstab; und
Fig. 6
schematische Darstellung der Abkantpresse mit schräggestelltem Stössel.
An exemplary embodiment of the invention is shown in the drawing, namely:
Fig. 1
a side view of the press brake according to the invention;
Fig. 2
a front view limited to the two side ends of the press brake according to Fig. 1;
Fig. 3
View of a double joint on a larger scale, in section;
Fig. 4
View of a first embodiment of the support member on a larger scale;
Fig. 5
View of a second embodiment of the support member on a larger scale; and
Fig. 6
schematic representation of the press brake with inclined ram.

Gemäss den Fig. 1 und 2 ist das Gestell der Abkantpresse im wesentlichen aus zwei vertikalen Seitenwangen 1 und einem die Seitenwangen 1 oberseitig miteinander verbindenden Jochbalken 2 aufgebaut. Der Jochbalken ist kastenförmig ausgebildet und besteht aus zwei vertikalen Längsplatten 3 und 4, welche endseitig durch je eine vertikale Querplatte 5 miteinander verbunden sind. Die Seitenwangen 1 sind aus je zwei hochstehenden Platten 6 und 7 gebildet, welche mit einem einen Zwischenraum 8 freilassenden Abstand voneinander angeordnet sind und oberseitig durch den Jochbalken 2 und unterseitig je durch ein Zwischenstück 9 miteinander verbunden sind.1 and 2, the frame of the press brake is essentially composed of two vertical side walls 1 and a yoke beam 2 connecting the side walls 1 to one another on the upper side. The yoke beam is box-shaped and consists of two vertical longitudinal plates 3 and 4, which are connected to one another at the ends by a vertical transverse plate 5. The side walls 1 are each formed from two upstanding plates 6 and 7, which are arranged at a distance from one another leaving a space 8 and are connected to one another on the upper side by the yoke beam 2 and on the underside by an intermediate piece 9.

Die aktiven Teile der Abkantpresse bilden eine feststehende Unterwange 10 und eine den vertikal beweglichen Stössel bildende Oberwange 11, welche beide sich in horizontaler Richtung zwischen den beiden Seitenwangen 1 des Gestells bis in den jeweiligen Zwischenraum 8 derselben erstrecken und an denen die Abkantwerkzeuge in nicht dargestellter Weise befestigbar sind.The active parts of the press brake form a fixed lower beam 10 and an upper beam 11 forming the vertically movable ram, both of which are in the horizontal direction extend between the two side cheeks 1 of the frame into the respective intermediate space 8 thereof and to which the bending tools can be fastened in a manner not shown.

Das Zwischenstück 9 ruht je auf einer durch einen Ansatz 12 verdickten Schulter 13 der Platten 6 und 7 und dient zugleich als Lagerbock für die als freiaufliegender Balken konzipierte Unterwange 10. Zu diesem Zweck weist jedes Zwischenstück 9 zwei voneinander distanzierte Stützen 14 auf, welche je mit einer halbzylindrischen Pfanne 15 versehen sind. An beiden, jeweils zwischen die Stützen 14 reichenden, abgesetzten Enden der Unterwange 10 ist ein zylindrischer Zapfen 16 verankert, welcher mit seinen vorstehenden Enden in den betreffenden Pfannen 15 der Stützen 14 ruht.The intermediate piece 9 rests on a shoulder 13 of the plates 6 and 7 which is thickened by a shoulder 12 and at the same time serves as a bearing block for the lower beam 10 designed as a free-floating beam. For this purpose, each intermediate piece 9 has two supports 14 spaced from one another, each with a semi-cylindrical pan 15 are provided. A cylindrical pin 16 is anchored at both, stepped ends of the lower beam 10 which reach between the supports 14 and which rests with their projecting ends in the relevant pans 15 of the supports 14.

Die Oberwange 11 hängt an ihren beiden abgesetzten Enden je an zwei Tragorganen 17, welche einerseits mit der Oberwange 11 und andererseits mit der Kolbenstange 18 eines Kraftzylinders 19 gelenkig verbunden sind. wobei die an der Oberwange 11 befindliche Gelenkachse mit 20 und die an.der Kolbenstange 18 befindliche Gelenkachse mit 21 bezeichnet ist. Jeder Kraftzylinder 19 ist mit einem Montageflansch 22 an der benachbarten Querplatte 5 des Jochbalkens 2 befestigt. Zur Übertragung der Presskraft von den Kolbenstangen 18 auf die Oberwange 11 ist je eine gelenkartige Stossverbindung in Form eines Doppelgelenkes 23 vorgesehen. Einzelheiten in bezug auf die Ausbildung der Doppelgelenke 23 und der Tragorgane 17 gehen aus den Fig. 3 und 4 hervor.The upper cheek 11 hangs at its two remote ends on two supporting members 17, which are articulated on the one hand to the upper cheek 11 and on the other hand to the piston rod 18 of a power cylinder 19. the hinge axis located on the upper cheek 11 being designated 20 and the hinge axis located on the piston rod 18 being designated 21. Each power cylinder 19 is fastened to the adjacent cross plate 5 of the yoke beam 2 with a mounting flange 22. For the transfer of the pressing force from the piston rods 18 to the upper cheek 11, an articulated butt joint in the form of a double joint 23 is provided. Details regarding the formation of the double joints 23 and the support members 17 are shown in FIGS. 3 and 4.

Die Fig. 3 zeigt eine der Stossverbindungen im Schnitt, wobei die Schnittebene parallel zur Bewegungsebene der Oberwange 11 verläuft. Das die Stossverbindung bildende Doppelgelenk 23 besteht aus zwei wirkungsmässig in Reihe liegenden Stossgelenken und ist aus einem mit der Kolbenstange 18 verbundenen Gelenkkopf 24, einem mit der Oberwange 11 verbundenen Gelenkkopf 25 und einer zwischen den beiden Gelenkköpfen 24 und 25 angeordneten, zweiseitigen Gelenkpfanne 26 aufgebaut. Aufgrund der gewählten Lage der Schnittebene gilt die Fig. 3 sowohl für Zylindergelenke mit senkrecht zur Bewegungsebene der Oberwange 11 verlaufenden Gelenkachsen als auch für Kugelgelenke. Die Stossflächen sind also entweder zylinderfömig oder kugelförmig ausgebildet. In einer bevorzugten Ausführung der Doppelgelenke 23 bestehen die Gelenkköpfe 24, 25 vorzugsweise aus Messing und die Gelenkpfannen 26 aus Stahl, insbesondere aus Stahlguss. Die Gelenkköpfe 24 und 25 stossen an quer zur Stossrichtung verlaufenden ebenen Flächen 27 bzw. 28 lose an der Kolbenstange 18 bzw. an der Oberwange 11 an und sind durch Passbolzen 29 bzw. 30 gegen seitliche Verschiebung gesichert.FIG. 3 shows one of the butt connections in section, the section plane running parallel to the plane of movement of the upper cheek 11. The double joint 23 which forms the butt joint consists of two butt joints which are effectively arranged in series and is constructed from a joint head 24 connected to the piston rod 18, a joint head 25 connected to the upper cheek 11 and a two-sided joint socket 26 arranged between the two joint heads 24 and 25. Due to the selected position of the sectional plane, FIG. 3 applies both to cylindrical joints with joint axes running perpendicular to the plane of movement of the upper cheek 11 and to ball joints. The abutting surfaces are either cylindrical or spherical. In a preferred embodiment of the double joints 23, the joint heads 24, 25 are preferably made of brass and the joint sockets 26 are made of steel, in particular cast steel. The joint heads 24 and 25 abut on flat surfaces 27 and 28 running transversely to the direction of impact loosely on the piston rod 18 and on the upper cheek 11 and are secured against lateral displacement by means of locating bolts 29 and 30.

Die Anlagefläche 28 ist durch eine an der Verbindungsstelle vorgesehene Verdickung 31 der Oberwange 11 dem Umfang des Gelenkkopfs 25 angepasst. Die Zentren der Stossgelenke fallen mit den jeweils zugeordneten Gelenkachsen der Tragorgane 17 zusammen, d.h. das Zentrum des Gelenkkopfs 24 und der an dieser anliegenden Pfannenseite der zweiseitigen Gelenkpfanne 26 fällt mit dem Zentrum der Gelenkachse 21 an der Kolbenstange 18 zusammen, und das Zentrum der Gelenkkopfs 25 mit der an dieser anliegenden Pfannenseite der Gelenkpfanne 26 fällt mit dem Zentrum der Gelenkachse 20 an der Oberwange 11 zusammen. Dadurch wird erreicht, dass der Abstand zwischen den Gelenkachsen 20 und 21 bei jeder Verstellung des Doppelgelenkes konstant bleibt. Demzufolge werden bei einer Verstellung des Doppelgelenkes die demselben zugeordneten Tragorgane 17 nicht zusätzlichen Zug- oder Druckkräften ausgesetzt, wie dies ohne den festen Abstand der Gelenkachsen der Fall wäre.The contact surface 28 is adapted to the circumference of the joint head 25 by a thickening 31 of the upper cheek 11 provided at the connection point. The centers of the butt joints fall with the associated joint axes of the support members 17 together, that is, the center of the joint head 24 and the adjoining socket side of the two-sided socket 26 coincides with the center of the joint axis 21 on the piston rod 18, and the center of the joint head 25 with the adjoining it The socket side of the socket 26 coincides with the center of the joint axis 20 on the upper cheek 11. This ensures that the distance between the joint axes 20 and 21 remains constant with each adjustment of the double joint. Accordingly, when the double joint is adjusted, the supporting members 17 assigned to it are not subjected to additional tensile or compressive forces, as would be the case without the fixed distance between the joint axes.

Eine erste Ausführung der die Stossverbindungen überbrückenden Tragorgane 17 ist in Fig. 4 dargestellt. Gemäss dieser Ausführung ist das Tragorgan 17 in Kraftrichtung unterteilt in einen mit der Gelenkachse 21 verbundenen Oberteil 32 und einen mit der Gelenkachse 20 verbundenen Unterteil 33. Der Oberteil 32 und der Unterteil 33 sind durch Tragbolzen in Form von Schrauben 34 lose miteinander verbunden, welche die seitwärts gerichteten Schenkel 35 des Oberteils 32 freilaufend durchsetzen und in den Unterteil 33 eingeschraubt sind. Zwischen den Schraubenköpfen 36 und den Schenkeln 35 des Oberteils 32 sind Federelemente 37, z.B. Tellerfedern, eingesetzt, welche so dimensioniert sind, dass im Leergang des Stössels, d.h. der Oberwange 11, die Elemente 24, 25, 26 der Stossgelenke lose zusammenhalten. Durch den Freilauf der Tragorgane 17 wird erreicht, dass im Arbeitsgang des Stössels die Presskraft ausschliesslich durch die die Stossverbindungen bildenden Doppelgelenke 21 übertragen wird und infolgedessen die Tragorgane 17 und deren Gelenkverbindungen durch die Presskraft nicht zusätzlich beansprucht werden.A first embodiment of the support members 17 bridging the butt connections is shown in FIG. 4. According to this embodiment, the support member 17 is divided in the direction of force into an upper part 32 connected to the hinge axis 21 and a lower part 33 connected to the hinge axis 20. The upper part 32 and the lower part 33 are loosely connected to one another by supporting bolts in the form of screws 34 which secure the push through sideways directed leg 35 of the upper part 32 in a free-running manner and are screwed into the lower part 33. Between the screw heads 36 and the legs 35 of the upper part 32, spring elements 37, for example plate springs, are used, which are dimensioned such that the elements 24, 25, 26 of the Hold the butt joints loosely together. The free running of the support members 17 ensures that the pressing force is transmitted exclusively through the double joints 21 forming the butt connections in the working step of the ram, and consequently the support members 17 and their articulated connections are not additionally stressed by the pressing force.

Gemäss einer anderen Ausführung nach Fig. 5 besteht jedes Tragorgan 40 aus einem Bolzen 41, welcher mit einer die Gelenkachse 21 umschliessenden Muffe 42 fest verbunden, z.B. verschraubt und verschweisst ist und welcher die andere Gelenkachse 43 in einer Bohrung 44 freilaufend durchsetzt und endseitig ein Tragelement in Form einer auf das Bolzenende aufgeschraubten Mutter 45 aufweist. Die Federelemente 46 sind auf dem Bolzen 41 zwischen der Mutter 45 und einem an der Verbindungsstelle abgeflachten Teil 47 der Gelenkachse 43 angeordnet. Bei dieser Ausführung ist die Gelenkachse 43 in der Oberwange 11 drehbar angeordnet, während sich bei den Gelenkachsen 20 und 21 das Drehlager wahlweise an der Oberwange 11 oder an den Tragorganen 17 bzw. an der Buchse 42 des Tragorgans 40 befinden kann.According to another embodiment according to Fig. 5, each support member 40 consists of a bolt 41 which is fixedly connected to a sleeve 42 surrounding the hinge axis 21, e.g. is screwed and welded and which passes freely through the other joint axis 43 in a bore 44 and has a support element in the form of a nut 45 screwed onto the bolt end. The spring elements 46 are arranged on the bolt 41 between the nut 45 and a part 47 of the joint axis 43 flattened at the connection point. In this embodiment, the articulated axis 43 is rotatably arranged in the upper cheek 11, while in the case of the articulated axes 20 and 21 the pivot bearing can optionally be located on the upper cheek 11 or on the support members 17 or on the bushing 42 of the support member 40.

Die durch je ein Doppelgelenk 23 und die diesen jeweils zugeordneten Tragorgane 17 bzw. 40 gebildeten Gelenkverbindungen lassen sich absolut spielfrei gestalten. Dadurch wird eine hohe Arbeitsgenauigkeit der Abkantpresse erreicht. Dabei ist eine hohe Herstellungsgenauigkeit nur für diese Gelenkverbindungen und für die hier nicht dargestellten Mittel für die Parallelführung der Oberwange 11 erforderlich. Für die Positionierung der Kraftzylinder 19 ist dagegen keine so hohe Genauigkeit notwendig, da diesbezügliche Ungenauigkeiten der Montagemittel sich nicht zwangsläufig auf die Lage der Oberwange 11 auswirken, sondern von den Doppelgelenken 23 ausgeglichen werden. Dadurch wird der Gestellaufbau erheblich vereinfacht. Die Führungsmittel für die Oberwange 11 lassen sich an der fertig montierten Abkantpresse dank der Doppelgelenke 23 problemlos verstellen, bis die Oberwange 11 auf die Unterwange 10 genau ausgerichtet ist. In dieser Beziehung erweist sich die sphärische Ausbildung der Stossverbindung im Gegensatz zu einer ebenfalls möglichen zylindrischen Gelenkausführung besonders vorteilhaft, weil dadurch die Ebene der Oberwange 11 aufgrund des zusätzlichen Freiheitsgrades in allen Richtungen verstellbar ist und unabhängig von der Genauigkeit der Lage der Kraftzylinder 19 durch Justierung der für die Bahn der Oberwange 11 massgebenden Führungen mit hoher Genauigkeit in die gewünschte Betriebslage gebracht werden kann.The articulated connections formed by a double joint 23 and the support members 17 and 40 respectively assigned to them can be designed absolutely free of play. This ensures a high level of working accuracy for the press brake. A high manufacturing accuracy is only for these joint connections and required for the means not shown here for the parallel guidance of the upper beam 11. In contrast, the positioning of the power cylinders 19 does not require such a high level of accuracy, since inaccuracies in the mounting means in this regard do not necessarily affect the position of the upper beam 11, but are compensated for by the double joints 23. This considerably simplifies the structure of the frame. The guide means for the upper beam 11 can be easily adjusted on the fully assembled press brake thanks to the double joints 23 until the upper beam 11 is precisely aligned with the lower beam 10. In this regard, the spherical design of the butt joint proves to be particularly advantageous in contrast to a likewise possible cylindrical joint design, because the plane of the upper cheek 11 can be adjusted in all directions due to the additional degree of freedom and regardless of the accuracy of the position of the power cylinder 19 by adjusting the 11 guides for the path of the upper beam can be brought into the desired operating position with high accuracy.

Ferner ist aufgrund der Doppelgelenke 23 unter Wahrung der Spielfreiheit in den Gelenkverbindungen eine betriebsmässige Schrägstellung der Oberwange 11 in grösserem Umfang möglich. An einem Prototyp konnte die Oberwange 11 bis zu einem Winkel von 15° geneigt werden. Die Fig. 6 zeigt schematisch die gegenseitige Verschiebung der Elemente 24, 25 und 26 jedes Doppelgelenks 23 bei schräggestellter Oberwange 11. In dieser Figur sind die beweglichen Teile bei Horizontallage der Oberwange 11 mit strichpunktierten und bei Schräglage derselben mit ausgezogenen Linien dargestellt, und die Bezeichnungen dieser Teile beziehen sich auf die Schräglage. In Fig. 6 ist ausserdem ein an der Oberwange 11 vorgesehenes Drehgelenk 38 angedeutet, welches auf der Hohe der Kraftzylinder 19 angeordnet und in einer nicht dargestellten Geradführung vertikal bewegbar ist. Mit dieser Massnahme wird eine von den Doppelgelenken 23 an sich ermöglichte Horizontalverschiebung der Oberwange 11 längs der Unterwange 10 vermieden, so dass die Oberwange 11 sowohl in ihrer Horizontallage als auch in jeder Neigungslage diesbezüglich eine definierte Stellung einnimmt. Im übrigen wird durch die Geradführung die seitliche Auslenkung der schräggestellten Oberwange 11 im Raum zwischen den beiden Kraftzylindern 19 in Grenzen gehalten und auf beide Seiten gleichmässig verteilt.Furthermore, due to the double joints 23 while maintaining freedom from play in the joint connections, an operational inclination of the upper cheek 11 is possible to a greater extent. On a prototype, the upper beam 11 could be tilted up to an angle of 15 °. Fig. 6 shows schematically the mutual displacement of the elements 24, 25 and 26 of each double joint 23 with an inclined upper beam 11. In this Figure shows the moving parts with horizontal position of the upper cheek 11 with dash-dotted lines and with an inclined position thereof with solid lines, and the names of these parts refer to the inclined position. In FIG. 6 there is also indicated a swivel joint 38 provided on the upper cheek 11, which is arranged at the height of the power cylinders 19 and can be moved vertically in a straight guide (not shown). With this measure, a horizontal displacement of the upper beam 11 along the lower beam 10, which is made possible by the double joints 23, is avoided, so that the upper beam 11 assumes a defined position in this regard both in its horizontal position and in any inclined position. In addition, the linear deflection of the inclined upper cheek 11 in the space between the two power cylinders 19 is kept within limits and evenly distributed on both sides.

Claims (14)

Hydraulische Abkantpresse, mit einem balken- oder wangenförmigen Stössel (11), welcher an seinen beiden Enden je mit der Kolbenstange (18) eines Kraftzylinders (19) gelenkig verbunden ist, wobei zur Übertragung der Stosskraft von der Kolbenstange (18) auf den Stössel (11) eine gelenkartige Stossverbindung vorgesehen ist, dadurch gekennzeichnet, dass die Stossverbindung durch ein Doppelgelenk (23) aus zwei wirkungsmässig in Reihe liegenden Stossgelenken (24, 26; 25, 26) mit gleichorientierten Freiheitsgraden gebildet ist.Hydraulic press brake, with a bar-shaped or cheek-shaped plunger (11), which is articulated at both ends to the piston rod (18) of a power cylinder (19), whereby the transmission of the impact force from the piston rod (18) to the plunger ( 11) an articulated butt joint is provided, characterized in that the butt joint is formed by a double joint (23) consisting of two butt joints (24, 26; 25, 26) which are effectively arranged in series with equally oriented degrees of freedom. Hydraulische Abkantpresse nach Anspruch 1, dadurch gekennzeichnet, dass jedes Doppelgelenk (23) aus je einem mit der Kolbenstange (18) bzw. mit dem Stössel (11) verbundenen Gelenkkopf (24, 25) und einer zwischen den beiden Gelenkköpfen frei beweglich angeordneten, zweiseitigen Gelenkpfanne (26) aufgebaut ist.Hydraulic press brake according to Claim 1, characterized in that each double joint (23) consists of a joint head (24, 25) connected to the piston rod (18) or the plunger (11) and a double-sided one which is freely movable between the two joint heads Joint socket (26) is constructed. Hydraulische Abkantpresse nach Anspruch 2, dadurch gekennzeichnet, dass die Gelenkköpfe (24, 25) aus Messing und die Gelenkpfannen aus Stahl, insbesondere aus Stahlguss, bestehen.Hydraulic press brake according to claim 2, characterized in that the joint heads (24, 25) consist of brass and the joint socket made of steel, in particular cast steel. Hydraulische Abkantpresse nach Anspruch 2, dadurch gekennzeichnet, dass die Gelenkköpfe (24, 25) und die Kolbenstangen (18) bzw. der Stössel (11) an quer zur Stossrichtung verlaufenden ebenen Flächen (27, 28) lose aneinanderstossen und durch Passbolzen (29, 30) in ihrer gegenseitigen Querlage fixiert sind.Hydraulic press brake according to claim 2, characterized in that the rod ends (24, 25) and the piston rods (18) or the plunger (11) abut loosely on flat surfaces (27, 28) running transversely to the direction of impact and by means of locating bolts (29, 30) are fixed in their mutual transverse position. Hydraulische Abkantpresse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Stossgelenke Zylindergelenke mit senkrecht zur Bewegungsebene des Stössels verlaufenden Gelenkachsen sind.Hydraulic press brake according to one of the preceding claims, characterized in that the butt joints are cylindrical joints with joint axes running perpendicular to the plane of movement of the ram. Hydraulische Abkantpresse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Stossgelenke Kugelgelenke sind.Hydraulic press brake according to one of the preceding claims, characterized in that the butt joints are ball joints. Hydraulische Abkantpresse nach Anspruch 1, dadurch gekennzeichnet, dass jede Stossverbindung durch Tragorgane (17; 40) überbrückt ist, welche mit der Kolbenstange (18) und dem Stössel (11) gelenkig verbunden sind.Hydraulic press brake according to claim 1, characterized in that each butt connection is bridged by supporting members (17; 40) which are connected in an articulated manner to the piston rod (18) and the tappet (11). Hydraulische Abkantpresse nach den Ansprüchen 2 und 7, dadurch gekennzeichnet, dass das Zentrum der Gelenkköpfe (24, 25) an den Kolbenstangen (18) bzw. am Stössel (11) mit dem jeweiligen Zentrum der an den Kolbenstangen (18) bzw. am Stössel (11) befindlichen Gelenkachsen (21, 20) der Tragorgane (17; 40) zusammenfällt.Hydraulic press brake according to claims 2 and 7, characterized in that the center of the rod ends (24, 25) on the piston rods (18) or on the plunger (11) with the respective center of the on the piston rods (18) or on the plunger (11) located joint axes (21, 20) of the support members (17; 40) coincides. Hydraulische Abkantpresse nach einem der Ansprüche 7 und 8, dadurch gekennzeichnet, dass die Tragorgane (17; 40) einen beim Presshub des Stössels (11) wirksamen Freilauf aufweisen.Hydraulic press brake according to one of claims 7 and 8, characterized in that the support members (17; 40) have a freewheel which is effective during the press stroke of the ram (11). Hydraulische Abkantpresse nach Anspruch 9, dadurch gekennzeichnet, dass die Tragorgane (17; 40) in den Kraftschluss derselben eingeschaltete Federelemente (37; 46) enthalten.Hydraulic press brake according to Claim 9, characterized in that the supporting members (17; 40) contain spring elements (37; 46) which are switched into the force-locking connection thereof. Hydraulische Abkantpresse nach Anspruch 10, dadurch gekennzeichnet, dass die Federelemente (37; 46) so dimensioniert sind, dass unter deren Wirkung die Elemente (24, 25, 26) der Stossverbindungen im Leergang des Stössels (11) lose zusammengehalten werden.Hydraulic press brake according to claim 10, characterized in that the spring elements (37; 46) are dimensioned such that under their action the elements (24, 25, 26) of the butt joints are held together loosely in the empty passage of the ram (11). Hydraulische Abkantpresse nach einem der Ansprüche 9 und 10, dadurch gekennzeichnet, dass die Tragorgane (23) in Kraftrichtung unterteilt und die Teile (32, 33) durch Tragbolzen (34) lose miteinander verbunden sind.Hydraulic press brake according to one of Claims 9 and 10, characterized in that the support members (23) are divided in the direction of force and the parts (32, 33) are loosely connected to one another by support bolts (34). Hydraulische Abkantpresse nach Anspruch 10, dadurch gekennzeichnet, dass jedes Tragorgan aus einem Bolzen (41) besteht, welcher mit der einen Gelenkachse (21) in Kraftrichtung fest verbunden ist und welcher die andere Gelenkachse (20) in einer Bohrung (43) freilaufend durchsetzt und endseitig ein Tragelement (45) aufweist.Hydraulic press brake according to claim 10, characterized in that each support member consists of a bolt (41) which is fixedly connected to one hinge axis (21) in the direction of force and which passes freely through the other hinge axis (20) in a bore (43) and has a support element (45) at the end. Hydraulische Abkantpresse nach Anspruch 1, dadurch gekennzeichnet, dass der Stössel (11) auf der Höhe der Kraftzylinder (19) ein zentrales Drehgelenk (38) aufweist, welches in einer Geradführung vertikal bewegbar ist.Hydraulic press brake according to claim 1, characterized in that the plunger (11) at the level of the power cylinder (19) has a central swivel joint (38) which is vertically movable in a straight guide.
EP92810803A 1991-11-21 1992-10-20 Hydraulic bending press Ceased EP0543773A1 (en)

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DE4138285 1991-11-21

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CN107695140A (en) * 2017-11-13 2018-02-16 北京天立成信机械电子设备有限公司 A kind of U-shaped workpiece hydraulic forming device

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WO1995004643A1 (en) * 1993-08-11 1995-02-16 Engel Maschinenbau Gesellschaft M.B.H. Injection moulding machine
US5556656A (en) * 1993-08-11 1996-09-17 Engel Maschinenbau Gesellschaft Gmbh Injection moulding machine
EP2581144A1 (en) * 2011-10-12 2013-04-17 Weinbrenner Maschinenbau GmbH Bending machine
ITMI20120052A1 (en) * 2012-01-19 2013-07-20 Unimec S R L ELECTRIC ACTUATOR, PARTICULARLY FOR FOLDING AND SIMILAR PRESSES.

Also Published As

Publication number Publication date
US5272904A (en) 1993-12-28
CN1072357A (en) 1993-05-26
DE4138285C2 (en) 1994-04-07
JPH05212444A (en) 1993-08-24
DE4138285A1 (en) 1993-05-27

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