EP2228203B1 - Mechanical forming press - Google Patents

Mechanical forming press Download PDF

Info

Publication number
EP2228203B1
EP2228203B1 EP10001331.7A EP10001331A EP2228203B1 EP 2228203 B1 EP2228203 B1 EP 2228203B1 EP 10001331 A EP10001331 A EP 10001331A EP 2228203 B1 EP2228203 B1 EP 2228203B1
Authority
EP
European Patent Office
Prior art keywords
press
gear
drive
eccentric
ram
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.)
Active
Application number
EP10001331.7A
Other languages
German (de)
French (fr)
Other versions
EP2228203A2 (en
EP2228203A3 (en
Inventor
Stefan Dipl.-Wi.-Ing. Kaiser (FH)
Ingolf Dr. Pappe
Andreas Dipl.-Ing. Walther
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.)
Andritz Technology and Asset Management GmbH
Original Assignee
Andritz Technology and Asset Management GmbH
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 Andritz Technology and Asset Management GmbH filed Critical Andritz Technology and Asset Management GmbH
Priority to SI201031074T priority Critical patent/SI2228203T1/en
Priority to PL10001331T priority patent/PL2228203T3/en
Publication of EP2228203A2 publication Critical patent/EP2228203A2/en
Publication of EP2228203A3 publication Critical patent/EP2228203A3/en
Application granted granted Critical
Publication of EP2228203B1 publication Critical patent/EP2228203B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis

Definitions

  • the invention relates to a mechanical forming press with a press gear, via which a press ram is mechanically coupled to a drive, wherein the drive comprises at least one electric servomotor.
  • Such a forming press is for example from the document DE 10 2004 009 256 B4 known.
  • WO-A-2006104000 discloses a mechanical forming press having the features of the preamble of claim 1.
  • Such a forming press has a complex structure with many components.
  • the invention has for its object to provide a mechanical forming press of the type mentioned above, which has a particularly simple structure with the lowest possible number of components.
  • the invention provides the mechanical forming press according to claim 1, which is equipped with a press gear, via which a press ram is mechanically coupled to a drive, wherein the drive comprises at least one electric servomotor and the press gear between a drive shaft of the servomotor and an output shaft for the press ram has a continuously varying transmission ratio.
  • the output shaft driving the press ram can be made to have a varying angular velocity when a drive shaft of the servomotor rotates at a substantially constant angular velocity.
  • the powerful electric servomotor is characterized by high torque and can be used as the main drive.
  • the rotational movement of the servo motor is transformed by means of the press gear in a translational movement of the press ram.
  • the servomotor can be operated particularly efficiently in continuous operation at a substantially constant angular velocity, wherein power losses, the z. B. result by repeated acceleration and deceleration of the engine and the entire press gear, can be avoided. Due to the infinitely variable transmission ratio of the press gear can be achieved that the press ram is slowed down just in the forming area of the mechanical forming press, so that lower impact speeds, lower noise emissions and longer tool life can be achieved.
  • the mechanical forming press of the type mentioned has a particularly simple structure with an extremely small number of components, so that the object underlying the invention is achieved.
  • the press gear has a multi-crank gear. Due to the multi-crank gear, a continuously variable transmission ratio of the press gear can be accomplished in a simple manner.
  • the press gear on a drag crank gear According to the invention, the press gear on a drag crank gear.
  • the continuously varying transmission ratio of the press gear can be accomplished in a very small space.
  • the drag crank gear comprises the output shaft for the press ram and a counter gear wherein the output shaft is arranged eccentrically to the counter gear and coupled via a drag crank with the counter gear.
  • the output shaft is designed as an eccentric shaft.
  • the eccentric shaft accomplishes the basic translation of the press gear.
  • the basic ratio of the press gear can be multiplied in a simple manner with the continuously varying transmission ratio of the towing gear, wherein the overall gear ratio of the press gear is adjustable depending on the desired course on the ram stroke.
  • the transmission ratio of the press gear is increased in the region of the forming of the forming press.
  • the press ram is slowed down in the forming area, whereby a slowed down pulling speed and an increased working travel can be achieved before the bottom dead center.
  • the press ram is coupled clutch-free with the drive.
  • a continuous drive of the press ram can be realized across the entire ram stroke.
  • the number of components can be further reduced if a clutch is dispensed with.
  • a connecting rod driving the press ram is arranged with the interposition of an eccentric disc adjustably on the eccentric of the eccentric shaft.
  • the counter gear is located centrally between the two eccentrics.
  • the drive follows on one side laterally next to the eccentrics.
  • the torque to be transmitted causes a torsion of the eccentric shaft.
  • This torsion has different degrees of rotation of the eccentric result.
  • the differently sized twist angle cause an inclination of the press ram.
  • a drive between the two eccentrics avoids this effect.
  • the countershaft transmission can be arranged centrally between the eccentrics. Then arise at both eccentrics angle of rotation of the same size and direction. A tilting of the press ram can be effectively avoided.
  • At least one transmission stage is arranged between the drive and the counter gear.
  • the torque acting on the counter gear can be precisely matched to the respective requirements, so that optimum operating results can be achieved.
  • the drive shaft of the servomotor rotates at a higher speed than the counter gear and / or the output shaft for the press ram. With a correspondingly powerful drive, it is also possible to couple the drive directly to the counter gear.
  • the translation stage is engaged with the drive and / or with the counter gear. As a result, a slip-free translation can be accomplished.
  • the translation stage is formed by preferably a single-stage spur gear. Such a transmission is particularly easy to produce.
  • a preferred aspect of the invention relates to a method of actuating a mechanical forming press according to any one of the preceding embodiments, wherein the electric servomotor is operated at substantially the same speed over the entire ram stroke. As a result, energy-intensive speed changes are avoided and the servo motor can be operated very efficiently in continuous operation.
  • FIG. 1 shows a perspective view of the press drive according to the invention.
  • the invention relates to a mechanical forming press with a continuous or clutch-free press gear, via which a press ram is mechanically coupled to a drive.
  • the drive comprises at least one electric servomotor with a drive shaft, wherein the press gear between a drive shaft of the servomotor and an output shaft for the press ram has a continuously variable transmission ratio, so that the output shaft has a varying angular velocity when the drive shaft of the servomotor with a substantially constant angular velocity turns.
  • the forming press has a housing which has a gear housing and a press head.
  • the press housing which provides the bearings for the gear parts, and the press ram are not shown for clarity.
  • FIG. 1 shows a perspective view of the press gear 1 of the invention for a mechanical forming press.
  • the press drive in the present case comprises two electric servomotors 2 each having a drive shaft 20 and a drive pinion 21.
  • the drive pinions 21 of the electric servomotors 2 are coupled to the press gear 1.
  • the press transmission 1 comprises a countershaft, a drag crank gear 3 and a slider crank gear.
  • the countershaft comprises a gear stage 4 designed as a spur gear with a large sprocket 41 and a small sprocket 42.
  • the large sprocket 41 is engaged with the drive sprockets 21 of the electric servomotors 2 and the small sprocket 42 is connected to the counter gear 31 of the towing crank gear 3 engaged.
  • the towing gear 3 includes an output shaft 30 for the ram (s) 31 and the counter gear 31.
  • the output shaft 30 is eccentric to the counter gear 31 and continuously coupled to the counter gear 31 via a drag crank (not shown) such that the output shaft 30 has a varying angular velocity when the counter gear 31 rotates at a substantially constant angular velocity.
  • the output shaft 30, which is designed as an eccentric shaft, forms a slider-crank mechanism and comprises two eccentrics 32, on which connecting rods 34 are rotatably mounted with the interposition of eccentric discs 33.
  • the connecting rods 34 are connected in a known manner with a press die, not shown, which is guided vertically slidably movable in Pressenkopf Faculty of the housing.
  • the eccentric discs 33 are preferably adjustable relative to the eccentric shaft 30.
  • the counter gear 31 is arranged centrally between the two eccentrics 32.
  • the drive shafts 20 of the servomotors 2, the gear ratio 4, the counter gear 31 and the eccentric shaft 30 are preferably arranged substantially parallel to each other, wherein the transmission stage 4, the counter gear 31 and the eccentric shaft 30 are fixedly mounted and rotatably supported in respective bearings in the housing of the forming press are.
  • the drive takes place via the electric servomotors 2, which rotate in the same direction of rotation at a substantially constant angular velocity.
  • the power of the electric servomotors 2 is over the translation stage 4 is applied to the counter gear 31, which is coupled via a towing crank with infinitely variable transmission ratio with the eccentric shaft 30.
  • the drag crank causes the eccentric shaft 30 to have a varying angular velocity as the counter gear 31 rotates at a substantially constant angular velocity, thereby increasing the gear ratio in the area of forming the forming press 1.
  • the power of the electric servomotors 2 is applied to the eccentric 32, which then transmit the power respectively to the associated connecting rods 34.
  • the invention is based on the idea that high-performance servomotors 2 are used as the main drive, so that by controlling the servomotor a flexibilization of the ram stroke is possible.
  • the rotational movement of the servo motors 2 is transformed by means of the continuous press gear 1 with continuously variable transmission ratio in a translational movement of the press ram.
  • the gear ratio is increased in the forming press according to the invention in the field of forming.
  • the ratio of the thrust crank gear (eccentric shaft) as a basic translation of the press drive is multiplied by the varying over the crank angle gear ratio of the towing crank mechanism.
  • the flexibility of the stroke of the press ram is achieved by the direct control of the servomotors, which act as main motors.
  • the gear ratio is increased by the drag crank gear. This ensures that the Nennpresskraftweg the press at given torques of the servomotors increased.
  • the nominal force of travel of a 6300 kN press in conventional eccentric drive is 7.6 mm and in the case of a servo press with integrated drag crank mechanism 10.5 mm before bottom dead center.
  • a higher nominal working capacity is provided when using the same servomotors.

Description

Die Erfindung betrifft eine mechanische Umformpresse mit einem Pressengetriebe, über welches ein Pressenstößel mit einem Antrieb mechanisch gekoppelt ist, wobei der Antrieb zumindest einen elektrischen Servomotor umfasst.The invention relates to a mechanical forming press with a press gear, via which a press ram is mechanically coupled to a drive, wherein the drive comprises at least one electric servomotor.

Eine derartige Umformpresse ist beispielsweise aus der Druckschrift DE 10 2004 009 256 B4 bekannt.Such a forming press is for example from the document DE 10 2004 009 256 B4 known.

Das Dokument WO-A-2006104000 offenbart eine mechanische Umformpresse mit dem Merkmalen des Oberbegriffs des Anspruchs 1.The document WO-A-2006104000 discloses a mechanical forming press having the features of the preamble of claim 1.

Eine solche Umformpresse weist einen komplexen Aufbau mit vielen Bauteilen auf.Such a forming press has a complex structure with many components.

Der Erfindung liegt die Aufgabe zugrunde, eine mechanische Umformpresse der eingangs genannten Art bereit zu stellen, die einen besonders einfachen Aufbau mit einer möglichst geringen Anzahl an Bauteilen aufweist.The invention has for its object to provide a mechanical forming press of the type mentioned above, which has a particularly simple structure with the lowest possible number of components.

Um die der Erfindung zugrunde liegende Aufgabe zu lösen, stellt die Erfindung die mechanische Umformpresse nach Anspruch 1 bereit, die mit einem Pressengetriebe ausgestattet ist, über welches ein Pressenstößel mit einem Antrieb mechanisch gekoppelt ist, wobei der Antrieb zumindest einen elektrischen Servomotor umfasst und das Pressengetriebe zwischen einer Antriebswelle des Servomotors und einer Abtriebswelle für den Pressenstößel ein stufenlos variierendes Übersetzungsverhältnis aufweist. Im Ergebnis kann erreicht werden, dass die den Pressenstößel treibende Abtriebswelle eine variierende Winkelgeschwindigkeit aufweist, wenn sich eine Antriebswelle des Servomotors mit einer im wesentlichen konstanten Winkelgeschwindigkeit dreht. Durch Ansteuerung und Betätigung des Servomotors mit im wesentlichen konstanter Drehzahl ist so eine Flexibilisierung des Stößelhubes möglich. Der leistungsstarke elektrische Servomotor zeichnet sich durch ein hohes Drehmoment aus und kann als Hauptantrieb eingesetzt werden. Diese Flexibilisierung des Stößelhubes ermöglicht neue technologische Möglichkeiten im Bereich des Umformen, Stanzens und Prägens. Die Drehbewegung des Servomotors wird mit Hilfe des Pressengetriebes in eine translatorische Bewegung des Pressenstößels transformiert. Der Servomotor kann bei einer im wesentlichen konstanten Winkelgeschwindigkeit besonders effizient im Dauerbetrieb betrieben werden, wobei Verlustleistungen, die sich z. B. durch wiederholtes Beschleunigen und Abbremsen des Motors und des gesamten Pressengetriebes ergeben, vermieden werden. Durch das stufenlos variierende Übersetzungsverhältnis des Pressengetriebes kann erreicht werden, dass der Pressenstößel gerade im Umformbereich der mechanischen Umformpresse verlangsamt wird, so dass geringere Auftreffgeschwindigkeiten, geringere Schallemissionen und höhere Werkzeugstandzeiten erzielt werden können. Im Ergebnis weist die mechanische Umformpresse der eingangs genannten Art einen besonders einfachen Aufbau mit einer äußerst geringen Anzahl an Bauteilen auf, so dass die der Erfindung zugrunde liegende Aufgabe gelöst wird.To solve the problem underlying the invention, the invention provides the mechanical forming press according to claim 1, which is equipped with a press gear, via which a press ram is mechanically coupled to a drive, wherein the drive comprises at least one electric servomotor and the press gear between a drive shaft of the servomotor and an output shaft for the press ram has a continuously varying transmission ratio. As a result, the output shaft driving the press ram can be made to have a varying angular velocity when a drive shaft of the servomotor rotates at a substantially constant angular velocity. By controlling and operating the servo motor with a substantially constant speed as a flexibilization of the ram stroke is possible. The powerful electric servomotor is characterized by high torque and can be used as the main drive. This flexibility of the ram stroke enables new technological possibilities in the area of forming, stamping and embossing. The rotational movement of the servo motor is transformed by means of the press gear in a translational movement of the press ram. The servomotor can be operated particularly efficiently in continuous operation at a substantially constant angular velocity, wherein power losses, the z. B. result by repeated acceleration and deceleration of the engine and the entire press gear, can be avoided. Due to the infinitely variable transmission ratio of the press gear can be achieved that the press ram is slowed down just in the forming area of the mechanical forming press, so that lower impact speeds, lower noise emissions and longer tool life can be achieved. As a result, the mechanical forming press of the type mentioned has a particularly simple structure with an extremely small number of components, so that the object underlying the invention is achieved.

Es kann sich als vorteilhaft erweisen, wenn das Pressengetriebe ein Mehrkurbelgetriebe aufweist. Durch das Mehrkurbelgetriebe kann ein stufenlos variierendes Übersetzungsverhältnis des Pressengetriebes auf einfache Weise bewerkstelligt werden.It may prove advantageous if the press gear has a multi-crank gear. Due to the multi-crank gear, a continuously variable transmission ratio of the press gear can be accomplished in a simple manner.

Erfindungsgemäss weist das Pressengetriebe ein Schleppkurbelgetriebe auf. Bei dieser Ausführung kann das stufenlos variierendes Übersetzungsverhältnis des Pressengetriebes auf sehr geringem Bauraum bewerkstelligt werden.According to the invention, the press gear on a drag crank gear. In this embodiment, the continuously varying transmission ratio of the press gear can be accomplished in a very small space.

Erfindungsgemäss umfasst das Schleppkurbelgetriebe die Abtriebswelle für den Pressenstößel und ein Vorgelegerad wobei die Abtriebswelle exzentrisch zum Vorgelegerad angeordnet und über eine Schleppkurbel mit dem Vorgelegerad gekoppelt ist.According to the invention, the drag crank gear comprises the output shaft for the press ram and a counter gear wherein the output shaft is arranged eccentrically to the counter gear and coupled via a drag crank with the counter gear.

Dadurch lässt sich ein Schleppkurbelgetriebe in sehr kompakter Bauform und auf besonders einfache Weise realisieren.This makes it possible to realize a drag crank mechanism in a very compact design and in a particularly simple manner.

Erfindungsgemäss ist die Abtriebswelle als Exzenterwelle ausgebildet. Die Exzenterwelle bewerkstelligt die Grundübersetzung des Pressengetriebes.According to the invention, the output shaft is designed as an eccentric shaft. The eccentric shaft accomplishes the basic translation of the press gear.

Da die Schleppkurbel direkt auf die Exzenterwelle als Abtriebswelle wirkt, kann die Grundübersetzung des Pressengetriebes auf einfache Weise mit dem stufenlos variierenden Übersetzungsverhältnis des Schleppkurbelgetriebes multipliziert werden, wobei das Gesamtübersetzungsverhältnis des Pressengetriebes je nach dem gewünschten Verlauf über den Stößelhub einstellbar ist.Since the towing crank acts directly on the eccentric shaft as the output shaft, the basic ratio of the press gear can be multiplied in a simple manner with the continuously varying transmission ratio of the towing gear, wherein the overall gear ratio of the press gear is adjustable depending on the desired course on the ram stroke.

Es kann sich als günstig erweisen, wenn das Übersetzungsverhältnis des Pressengetriebes im Bereich der Umformung der Umformpresse vergrößert wird. Dadurch wird der Pressenstößel im Umformbereich verlangsamt, wobei eine verlangsamte Ziehgeschwindigkeit und ein erhöhter Arbeitsweg vor dem unteren Totpunkt erzielt werden kann.It may prove to be advantageous if the transmission ratio of the press gear is increased in the region of the forming of the forming press. As a result, the press ram is slowed down in the forming area, whereby a slowed down pulling speed and an increased working travel can be achieved before the bottom dead center.

In einer vorteilhaften Weiterbildung der Erfindung ist der Pressenstößel kupplungsfrei mit dem Antrieb gekoppelt. So kann über den gesamten Stößelhub hinweg ein kontinuierlicher Antrieb des Pressenstößels realisiert werden. Zudem kann die Anzahl der Bauteile weiter reduziert werden, wenn auf eine Kupplung verzichtet wird.In an advantageous development of the invention, the press ram is coupled clutch-free with the drive. Thus, a continuous drive of the press ram can be realized across the entire ram stroke. In addition, the number of components can be further reduced if a clutch is dispensed with.

Erfindungsgemäss ist ein den Pressenstößel antreibender Pleuel unter Zwischenschaltung einer Exzenterscheibe verstellbar auf dem Exzenter der Exzenterwelle angeordnet. Dadurch kann Gesamtübersetzungsverhältnis des Pressengetriebes auf einfache Weise verstellt werden.According to the invention, a connecting rod driving the press ram is arranged with the interposition of an eccentric disc adjustably on the eccentric of the eccentric shaft. As a result, the overall transmission ratio of the press gear can be adjusted in a simple manner.

Es kann sich als nützlich erweisen, wenn das Vorgelegerad, mittig, zwischen den beiden Exzentern angeordnet ist. Dadurch entsteht ein sogenannter Mittelantrieb, bei dem die Antriebsleistung vom Vorgelegegetriebe von der Pressenmitte her über die Exzenterwellen auf die Exzenter übertragen wird. Bei einem Seitenantrieb folgt der Antrieb einseitig seitlich neben den Exzentern. Das zu übertragende Drehmoment bewirkt eine Torsion der Exzenterwelle. Diese Torsion hat unterschiedlich große Verdrehwinkel der Exzenter zur Folge. Die unterschiedlich großen Verdrehwinkel bewirken eine Schrägstellung des Pressenstößels. Durch einen Antrieb zwischen den beiden Exzentern lässt sich dieser Effekt vermeiden. In einer vorteilhaften Weiterbildung der Erfindung kann das Vorgelegegetriebe mittig zwischen den Exzentern angeordnet sein. Dann ergeben sich an beiden Exzentern Verdrehwinkel gleicher Größe und Richtung. Ein Schrägstellen des Pressenstößels kann dadurch wirkungsvoll vermieden werden.It may be useful if the counter gear is located centrally between the two eccentrics. This creates a so-called center drive, in which the drive power is transmitted from the countershaft gear from the center of the press forth on the eccentric shafts on the eccentric. With a side drive, the drive follows on one side laterally next to the eccentrics. The torque to be transmitted causes a torsion of the eccentric shaft. This torsion has different degrees of rotation of the eccentric result. The differently sized twist angle cause an inclination of the press ram. A drive between the two eccentrics avoids this effect. In an advantageous development of the invention, the countershaft transmission can be arranged centrally between the eccentrics. Then arise at both eccentrics angle of rotation of the same size and direction. A tilting of the press ram can be effectively avoided.

Erfindungsgemäss ist zumindest eine Übersetzungsstufe zwischen dem Antrieb und dem Vorgelegerad angeordnet.According to the invention, at least one transmission stage is arranged between the drive and the counter gear.

Dadurch kann das auf das Vorgelegerad einwirkende Drehmoment genau auf die jeweiligen Bedürfnisse abgestimmt werden, so dass optimale Betriebsergebnisse erzielbar sind. In einer bevorzugten Ausführung dreht sich die Antriebswelle des Servomotors mit höherer Drehzahl als das Vorgelegerad und/oder die Abtriebswelle für den Pressenstößel. Bei einem entsprechend leistungsstarken Antrieb ist es auch möglich, den Antrieb unmittelbar mit dem Vorgelegerad zu koppeln.As a result, the torque acting on the counter gear can be precisely matched to the respective requirements, so that optimum operating results can be achieved. In a preferred embodiment, the drive shaft of the servomotor rotates at a higher speed than the counter gear and / or the output shaft for the press ram. With a correspondingly powerful drive, it is also possible to couple the drive directly to the counter gear.

Erfindungsgemäss befindet sich die Übersetzungsstufe mit dem Antrieb und/oder mit dem Vorgelegerad in Eingriff. Dadurch kann eine schlupffreie Übersetzung bewerkstelligt werden.According to the invention, the translation stage is engaged with the drive and / or with the counter gear. As a result, a slip-free translation can be accomplished.

Es kann sich als vorteilhaft erweisen, wenn die Übersetzungsstufe durch vorzugsweise ein einstufiges Stirnradgetriebe gebildet wird. So ein Getriebe lässt sich besonders einfach herstellen.It may prove advantageous if the translation stage is formed by preferably a single-stage spur gear. Such a transmission is particularly easy to produce.

Es kann sich als hilfreich erweisen, wenn der elektrische Servomotor über den gesamten Stößelhub im gleichen Drehsinn betätigt wird. Dadurch wird der elektrische Servomotor wenig beansprucht und kann mit geringer Leistung betrieben werden.It can be helpful if the electric servomotor is operated in the same direction of rotation over the entire stroke. As a result, the electric servomotor is little stressed and can be operated with low power.

Ein bevorzugter Aspekt der Erfindung betrifft ein Verfahren zur Betätigung einer mechanischen Umformpresse nach einer der vorangegangenen Ausführungen, wobei der elektrische Servomotor über den gesamten Stößelhub mit im wesentlichen gleicher Drehzahl betätigt wird. Dadurch werden energieaufwändige Drehzahländerungen vermieden und der Servomotor kann besonders effizient im Dauerbetrieb betrieben werden.A preferred aspect of the invention relates to a method of actuating a mechanical forming press according to any one of the preceding embodiments, wherein the electric servomotor is operated at substantially the same speed over the entire ram stroke. As a result, energy-intensive speed changes are avoided and the servo motor can be operated very efficiently in continuous operation.

Die bevorzugte Ausführung und Anwendung der Erfindung wird nachstehend mit Bezug auf die Zeichnungen im Detail beschrieben.The preferred embodiment and application of the invention will be described below in detail with reference to the drawings.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Figur 1 zeigt eine perspektivische Darstellung des erfindungsgemäßen Pressenantriebs. FIG. 1 shows a perspective view of the press drive according to the invention.

Detaillierte Beschreibung des bevorzugten AusführungsbeispielsDetailed Description of the Preferred Embodiment

Die Erfindung betrifft eine mechanische Umformpresse mit einem kontinuierlichen bzw. kupplungsfreien Pressengetriebe, über welches ein Pressenstößel mit einem Antrieb mechanisch gekoppelt ist. Der Antrieb umfasst zumindest einen elektrischen Servomotor mit einer Antriebswelle, wobei das Pressengetriebe zwischen einer Antriebswelle des Servomotors und einer Abtriebswelle für den Pressenstößel ein stufenlos variables Übersetzungsverhältnis aufweist, so dass die Abtriebswelle eine variierende Winkelgeschwindigkeit aufweist, wenn sich die Antriebswelle des Servomotors mit einer im wesentlichen konstanten Winkelgeschwindigkeit dreht.The invention relates to a mechanical forming press with a continuous or clutch-free press gear, via which a press ram is mechanically coupled to a drive. The drive comprises at least one electric servomotor with a drive shaft, wherein the press gear between a drive shaft of the servomotor and an output shaft for the press ram has a continuously variable transmission ratio, so that the output shaft has a varying angular velocity when the drive shaft of the servomotor with a substantially constant angular velocity turns.

Die Umformpresse verfügt über ein Gehäuse, das ein Getriebegehäuse und ein Pressenkopfstück aufweist. Das Pressengehäuse, welches die Lagerstellen für die Getriebeteile bereitstellt, und die Pressenstößel sind der besseren Übersicht halber nicht dargestellt.The forming press has a housing which has a gear housing and a press head. The press housing, which provides the bearings for the gear parts, and the press ram are not shown for clarity.

Figur 1 zeigt eine perspektivische Darstellung des erfindungsgemäßen Pressengetriebes 1 für eine mechanische Umformpresse. FIG. 1 shows a perspective view of the press gear 1 of the invention for a mechanical forming press.

Der Pressenantrieb umfasst im vorliegenden Fall zwei elektrische Servomotoren 2 mit je einer Antriebswelle 20 und einem Antriebsritzel 21. Die Antriebsritzel 21 der elektrischen Servomotoren 2 sind mit dem Pressengetriebe 1 gekoppelt.The press drive in the present case comprises two electric servomotors 2 each having a drive shaft 20 and a drive pinion 21. The drive pinions 21 of the electric servomotors 2 are coupled to the press gear 1.

Das Pressengetriebe 1 umfasst ein Vorgelege, ein Schleppkurbelgetriebe 3 und ein Schubkurbelgetriebe. Das Vorgelege umfasst eine als Stirnradgetriebe ausgebildete Übersetzungsstufe 4 mit einem großen Zahnkranz 41 und einem kleinen Zahnkranz 42. Der große Zahnkranz 41 befindet sich mit den Antriebsritzeln 21 der elektrischen Servomotoren 2 in Eingriff und der kleine Zahnkranz 42 befindet sich mit dem Vorgelegerad 31 des Schleppkurbelgetriebes 3 in Eingriff.The press transmission 1 comprises a countershaft, a drag crank gear 3 and a slider crank gear. The countershaft comprises a gear stage 4 designed as a spur gear with a large sprocket 41 and a small sprocket 42. The large sprocket 41 is engaged with the drive sprockets 21 of the electric servomotors 2 and the small sprocket 42 is connected to the counter gear 31 of the towing crank gear 3 engaged.

Das Schleppkurbelgetriebe 3 umfasst eine Abtriebswelle 30 für den/die Pressenstößel und das Vorgelegerad 31. Die Abtriebswelle 30 ist exzentrisch zum Vorgelegerad 31 angeordnet und über eine Schleppkurbel (nicht dargestellt) kontinuierlich mit dem Vorgelegerad 31 gekoppelt wobei, so dass die Abtriebswelle 30 eine variierende Winkelgeschwindigkeit aufweist, wenn sich das Vorgelegerad 31 mit einer im wesentlichen konstanten Winkelgeschwindigkeit dreht.The towing gear 3 includes an output shaft 30 for the ram (s) 31 and the counter gear 31. The output shaft 30 is eccentric to the counter gear 31 and continuously coupled to the counter gear 31 via a drag crank (not shown) such that the output shaft 30 has a varying angular velocity when the counter gear 31 rotates at a substantially constant angular velocity.

Die Abtriebswelle 30, die als Exzenterwelle ausgebildet ist, bildet ein Schubkurbelgetriebe und umfasst zwei Exzenter 32, auf welchen Pleuel 34 unter Zwischenschaltung von Exzenterscheiben 33 drehbar gelagert sind. Die Pleuel 34 sind in bekannter Weise mit einem nicht dargestellten Pressstempel verbunden, der im Pressenkopfstück des Gehäuses vertikal gleitend beweglich geführt ist. Die Exzenterscheiben 33 sind vorzugsweise gegenüber der Exzenterwelle 30 verstellbar. Das Vorgelegerad 31 ist mittig zwischen den beiden Exzentern 32 angeordnet.The output shaft 30, which is designed as an eccentric shaft, forms a slider-crank mechanism and comprises two eccentrics 32, on which connecting rods 34 are rotatably mounted with the interposition of eccentric discs 33. The connecting rods 34 are connected in a known manner with a press die, not shown, which is guided vertically slidably movable in Pressenkopfstück of the housing. The eccentric discs 33 are preferably adjustable relative to the eccentric shaft 30. The counter gear 31 is arranged centrally between the two eccentrics 32.

Die Antriebswellen 20 der Servomotoren 2, die Übersetzungsstufe 4, das Vorgelegerad 31 und die Exzenterwelle 30 sind vorzugsweise im Wesentlichen parallel zueinander angeordnet, wobei die Übersetzungsstufe 4, das Vorgelegerad 31 und die Exzenterwelle 30 in jeweiligen Lagerstellen im Gehäuse der Umformpresse ortsfest angeordnet und drehbar gelagert sind.The drive shafts 20 of the servomotors 2, the gear ratio 4, the counter gear 31 and the eccentric shaft 30 are preferably arranged substantially parallel to each other, wherein the transmission stage 4, the counter gear 31 and the eccentric shaft 30 are fixedly mounted and rotatably supported in respective bearings in the housing of the forming press are.

Nachfolgend wird die Wirkungs- und Funktionsweise der Erfindung näher erläutert.The operation and operation of the invention will be explained in more detail.

Beim Betrieb der erfindungsgemäßen Umformpresse 1 erfolgt der Antrieb über die elektrischen Servomotoren 2, die sich mit einer im wesentlichen konstanten Winkelgeschwindigkeit in gleichem Drehsinn drehen. Die Leistung der elektrischen Servomotoren 2 wird über die Übersetzungsstufe 4 auf das Vorgelegerad 31 aufgebracht, das über eine Schleppkurbel mit stufenlos variierendem Übersetzungsverhältnis mit der Exzenterwelle 30 gekoppelt ist. Die Schleppkurbel bewirkt, dass die Exzenterwelle 30 eine variierende Winkelgeschwindigkeit aufweist, wenn sich das Vorgelegerad 31 mit einer im wesentlichen konstanten Winkelgeschwindigkeit dreht, wobei das Übersetzungsverhältnis im Bereich der Umformung der Umformpresse 1 vergrößert wird. Durch die Drehung der Exzenterwelle 30 wird die Leistung der elektrischen Servomotoren 2 auf die Exzenter 32 aufgebracht, welche die Leistung dann jeweils auf die zugeordneten Pleuel 34 übertragen. Über die Pleuel 34 erfolgt dann der Antrieb des nicht dargestellten Pressenstössels. Durch den mittigen Antrieb der Exzenterwelle 30 ist der Verdrehwinkel für die beiden Exzenter 34 gegenüber dem Vorgelegerad 31 im wesentlichen gleich, so dass eine Schiefstellung des nicht dargestellten Pressenstößels verhindert wird.During operation of the forming press 1 according to the invention, the drive takes place via the electric servomotors 2, which rotate in the same direction of rotation at a substantially constant angular velocity. The power of the electric servomotors 2 is over the translation stage 4 is applied to the counter gear 31, which is coupled via a towing crank with infinitely variable transmission ratio with the eccentric shaft 30. The drag crank causes the eccentric shaft 30 to have a varying angular velocity as the counter gear 31 rotates at a substantially constant angular velocity, thereby increasing the gear ratio in the area of forming the forming press 1. By the rotation of the eccentric shaft 30, the power of the electric servomotors 2 is applied to the eccentric 32, which then transmit the power respectively to the associated connecting rods 34. About the connecting rod 34 then takes the drive of the press ram, not shown. Due to the central drive of the eccentric shaft 30, the angle of rotation for the two eccentrics 34 with respect to the counter gear 31 is substantially equal, so that a misalignment of the press ram, not shown, is prevented.

Die Erfindung beruht auf dem Gedanken, dass leistungsstarke Servomotoren 2 als Hauptantrieb eingesetzt werden, so dass durch Ansteuerung des Servomotors eine Flexibilisierung des Stößelhubes möglich ist. Die Drehbewegung der Servomotoren 2 wird mit Hilfe des kontinuierlichen Pressengetriebes 1 mit stufenlos variierendem Übersetzungsverhältnis in eine translatorische Bewegung des Pressenstößels transformiert.The invention is based on the idea that high-performance servomotors 2 are used as the main drive, so that by controlling the servomotor a flexibilization of the ram stroke is possible. The rotational movement of the servo motors 2 is transformed by means of the continuous press gear 1 with continuously variable transmission ratio in a translational movement of the press ram.

Im Gegensatz zu Servo-Pressen mit Exzentergetrieben, bei welchen aufgrund des konstanten Übersetzungsverhältnisses keine optimale Umsetzung des vorhandenen Motormoments in die benötigte Umformkraft bzw. Arbeitsvermögen der Presse vorhanden ist, wird das Übersetzungsverhältnis bei der erfindungsgemäßen Umformpresse im Bereich der Umformung vergrößert.In contrast to servo presses with eccentric gears, in which due to the constant gear ratio no optimal conversion of the existing engine torque in the required forming force or working capacity of the press is present, the gear ratio is increased in the forming press according to the invention in the field of forming.

Die folgenden Vorteile ergeben sich durch die Erfindung:The following advantages result from the invention:

Das Übersetzungsverhältnis des Schubkurbelgetriebes (Exzenterwelle) als Grundübersetzung des Pressenantriebes wird mit dem über dem Kurbelwinkel variierenden Übersetzungsverhältnis des Schleppkurbelgetriebes multipliziert.The ratio of the thrust crank gear (eccentric shaft) as a basic translation of the press drive is multiplied by the varying over the crank angle gear ratio of the towing crank mechanism.

Die Flexibilisierung des Hubes des Pressenstößels erfolgt durch die direkte Ansteuerung der Servomotoren, die als Hauptmotoren fungieren.The flexibility of the stroke of the press ram is achieved by the direct control of the servomotors, which act as main motors.

Im Kurbelwinkelbereich von 120-180°, also im Bereich der Umformung, wird das Übersetzungsverhältnis durch das Schleppkurbelgetriebe vergrößert. Dadurch wird erreicht, dass sich der Nennpresskraftweg der Presse bei gegebenen Drehmomenten der Servomotoren vergrößert. So beträgt der Nennpresskraftweg einer 6300 kN-Presse bei herkömmlichem Exzenterantrieb 7,6 mm und bei einer Servo-Presse mit integriertem Schleppkurbelgetriebe 10,5 mm vor dem unteren Totpunkt. Für den technologischen Umformprozess wird beim Einsatz gleicher Servomotoren ein höheres Nennarbeitsvermögen zur Verfügung gestellt.In the crank angle range of 120-180 °, ie in the area of forming, the gear ratio is increased by the drag crank gear. This ensures that the Nennpresskraftweg the press at given torques of the servomotors increased. For example, the nominal force of travel of a 6300 kN press in conventional eccentric drive is 7.6 mm and in the case of a servo press with integrated drag crank mechanism 10.5 mm before bottom dead center. For the technological forming process, a higher nominal working capacity is provided when using the same servomotors.

Es liegen keine zusätzlichen spielbehaftete Gelenke im Kraftfluss der Presse vor, wodurch die gleiche Steifigkeit der Antriebskonfiguration wie bei Exzenterpressen erreicht werden kann.There are no additional backlash joints in the force flow of the press, whereby the same rigidity of the drive configuration as in eccentric presses can be achieved.

Über den gesamten Stößelhub ist ein kontinuierlicher Antrieb realisierbar. Ein reversiver Betrieb im Pressenantrieb ist nicht erforderlich.Over the entire ram stroke a continuous drive can be realized. A reversible operation in the press drive is not required.

Im Ergebnis wird Gesamtenergiebilanz des Pressenantriebs deutlich verbessert und die Anzahl der Bauteile wird deutlich verringert.As a result, the overall energy balance of the press drive is significantly improved and the number of components is significantly reduced.

Claims (8)

  1. Mechanical forming press with a press gear mechanism (1) via which a press ram is connected mechanically to a drive (2), wherein the drive (2) comprises at least one electric servomotor, wherein the press gear mechanism (1) has an infinitely variable transmission ratio between a drive shaft (20) of the servomotor and an output shaft (30) for the press ram, the press gear mechanism (1) having a drag link assembly (3), comprising the output shaft (30) for the press ram, which is designed as an eccentric shaft (30), and a counter gear (31), wherein the output shaft (30) is arranged eccentrically to the counter gear (31) and connected to the counter gear (31) via a drag link, and wherein at least one transmission stage (4) is arranged between the drive (2) and the counter gear (31), characterised in that the eccentric shaft (30) comprises two eccentric wheels (32) and the counter gear (31) being arranged between the two eccentric wheels (32), wherein a connecting rod (34) that drives the press ram is provided in an adjustable arrangement by interposition of an eccentric disc (33) on the eccentric wheel (32) of the eccentric shaft (30), and wherein the transmission stage (4) engages the drive (2) and the counter gear (31).
  2. Mechanical forming press according to claim 1, characterised in that the press gear mechanism (1) comprises a multi-crank gear (3).
  3. Mechanical forming press according to one of the preceding claims, characterised in that the transmission ratio of the press gear mechanism (1) is increased in the forming zone of the forming press (1).
  4. Mechanical forming press according to one of the preceding claims, characterised in that the press ram is linked to the drive (2) free of any coupling.
  5. Mechanical forming press according to one of the preceding claims, characterised in that the counter gear (31) is arranged in the middle between the two eccentric wheels (32).
  6. Mechanical forming press according to one of the preceding claims, characterised in that the transmission stage (4) is formed preferably by a single-stage spur gear.
  7. Mechanical forming press according to one of the preceding claims, characterised in that the electric servomotor (2) is operated in the same sense of rotation over the entire ram stroke.
  8. Method for operating a mechanical forming press according to one of the preceding claims, characterised in that the electric servomotor (2) is operated at largely the same speed over the entire ram stroke.
EP10001331.7A 2009-03-06 2010-02-09 Mechanical forming press Active EP2228203B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SI201031074T SI2228203T1 (en) 2009-03-06 2010-02-09 Mechanical forming press
PL10001331T PL2228203T3 (en) 2009-03-06 2010-02-09 Mechanical forming press

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009012111.0A DE102009012111B4 (en) 2009-03-06 2009-03-06 Mechanical forming press and method for actuating this forming press

Publications (3)

Publication Number Publication Date
EP2228203A2 EP2228203A2 (en) 2010-09-15
EP2228203A3 EP2228203A3 (en) 2013-05-15
EP2228203B1 true EP2228203B1 (en) 2015-09-09

Family

ID=42237236

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10001331.7A Active EP2228203B1 (en) 2009-03-06 2010-02-09 Mechanical forming press

Country Status (11)

Country Link
EP (1) EP2228203B1 (en)
CN (1) CN101823345B (en)
DE (1) DE102009012111B4 (en)
DK (1) DK2228203T3 (en)
EA (1) EA016473B1 (en)
ES (1) ES2553853T3 (en)
HU (1) HUE025845T2 (en)
PL (1) PL2228203T3 (en)
PT (1) PT2228203E (en)
SI (1) SI2228203T1 (en)
UA (1) UA98663C2 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT511135B1 (en) * 2011-03-11 2015-09-15 Andritz Tech & Asset Man Gmbh DRIVE UNIT FOR A PUNCH AUTOMATOR OR A PRESS
EP2529922B1 (en) * 2011-05-31 2019-03-27 Haulick + Roos GmbH Drive device for a press, die cutter or moulding machine
ITVE20120010U1 (en) * 2012-04-02 2013-10-03 Dallan Spa PUNCH DRIVE DEVICE FOR PUNCHING HEADS.-
CN104553013A (en) * 2014-12-29 2015-04-29 一重集团大连设计研究院有限公司 Main drive structure for high-speed servo press
CN105351484A (en) * 2015-12-22 2016-02-24 扬州捷迈锻压机械有限公司 Eccentric gear
CN112496090B (en) * 2020-11-26 2023-08-01 安徽金阳金属结构工程有限公司 Deviation correcting device for H-shaped steel production and working method thereof
CN113070435A (en) * 2021-03-19 2021-07-06 沃得精机(中国)有限公司 Servo motor transmission structure
CN113400701B (en) * 2021-08-17 2021-10-29 江苏专创轻合金科技有限公司 Automatic press machine with adjustable power and use method thereof

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3421184C2 (en) * 1984-06-07 1986-11-20 Unidor GmbH, 7534 Birkenfeld Procedure for adjusting the stroke on eccentric presses
SU1355498A1 (en) * 1985-12-30 1987-11-30 Рязанское производственное объединение "Тяжпрессмаш" Crank press
JPS62275599A (en) * 1986-05-06 1987-11-30 Aida Eng Ltd Production of press machine
EP0250871B1 (en) * 1986-06-30 1990-08-08 Aida Engineering Ltd. Slide stroke variable device for a press
SU1505796A1 (en) * 1988-01-04 1989-09-07 Предприятие П/Я Г-4585 Device for controlling stroke length of crank press crosshead
JPH0832375B2 (en) * 1990-01-17 1996-03-29 アイダエンジニアリング株式会社 Press crank drive mechanism
DE69301361T2 (en) * 1992-03-16 1996-09-05 Ishikawajima Harima Heavy Ind Drive device for a mechanical press
RU2047497C1 (en) * 1992-08-26 1995-11-10 Лев Николаевич Зарубин Screw extruder
RU2091643C1 (en) * 1995-07-13 1997-09-27 Виталий Валентинович Кулешов Gear-and-lever variable-speed drive
DE19645464B4 (en) * 1995-11-13 2006-12-07 The Minster Machine Co., Minster Mechanical press
JP3803445B2 (en) * 1997-02-14 2006-08-02 株式会社アマダ Press machine drive unit
JPH10328891A (en) * 1997-05-30 1998-12-15 Amada Eng Center:Kk Press
DE19810406A1 (en) * 1998-03-11 1999-09-16 Schuler Pressen Gmbh & Co Eccentric press with variable slide movement
JP2002137099A (en) * 2000-11-01 2002-05-14 Amada Eng Center Co Ltd Press drive method and its device
DE102004009256B4 (en) * 2004-02-26 2008-04-03 Schuler Pressen Gmbh & Co. Kg Mechanical multi-servo press
WO2005109013A2 (en) * 2004-05-06 2005-11-17 Alcatel Optical Networks Israel Ltd. Efficient protection mechanisms in a ring topology network utilizing label switching protocols
JP2006192494A (en) * 2005-01-17 2006-07-27 Komatsu Ltd Press machine
JP2006263806A (en) * 2005-03-25 2006-10-05 Komatsu Ltd Method for manufacturing servo press, and servo press
ES2508791T3 (en) * 2005-08-16 2014-10-16 Schuler Pressen Gmbh Press drive module and procedure for the preparation of a constructive series of presses
DE102006019207B4 (en) * 2006-04-21 2008-07-24 Müller Weingarten AG Drive system of a multi-tappet forming press
DE102007026727B4 (en) * 2006-06-08 2014-12-31 Müller Weingarten AG Drive system of a forming press
CN2923286Y (en) * 2006-06-09 2007-07-18 扬州锻压机床集团有限公司 Servo driving press of low inertness
JP4370623B2 (en) * 2006-10-30 2009-11-25 株式会社Ｉｈｉ Servo motor driven tandem press line
DE102006056520A1 (en) * 2006-11-30 2008-06-05 Schuler Pressen Gmbh & Co. Kg Press e.g. transverse flux press, for deformation of workpiece, has plunger drive with drive source connected to tappet and executing continuous drive motion, and another drive source connected to stilt end and performing drive movement
BRPI0721808A2 (en) * 2007-06-06 2013-01-22 Abb Research Ltd drive motor upgrade kit, handwheel-driven mechanical press and method for adapting a mechanical press to an auxiliary press

Also Published As

Publication number Publication date
EA016473B1 (en) 2012-05-30
UA98663C2 (en) 2012-06-11
CN101823345B (en) 2013-07-24
PL2228203T3 (en) 2016-03-31
DE102009012111B4 (en) 2014-10-02
SI2228203T1 (en) 2016-01-29
EP2228203A2 (en) 2010-09-15
DK2228203T3 (en) 2015-12-14
DE102009012111A1 (en) 2010-09-16
ES2553853T3 (en) 2015-12-14
EA201000305A1 (en) 2010-10-29
PT2228203E (en) 2015-12-31
HUE025845T2 (en) 2016-04-28
EP2228203A3 (en) 2013-05-15
CN101823345A (en) 2010-09-08

Similar Documents

Publication Publication Date Title
EP2228203B1 (en) Mechanical forming press
EP0615077B1 (en) Power transmission with two hydraulic engines
DE102014201254B4 (en) Transmission arrangement and drive train for a hybrid vehicle and hybrid vehicle
WO2005061861A1 (en) Adjusting device for a camshaft of an internal combustion engine
EP1734286B1 (en) Power-splitting hydromechanical transmission with superimposing transmission means
EP1930149A1 (en) drive for eccenter press
DE4243267B4 (en) steering gear
DE10357729B4 (en) Steering actuator of a "steer-by-wire system"
DE69916861T2 (en) POWER GEAR WITH MULTIPLE PLANETARY WHEEL DRIVES
WO2010066520A1 (en) Internal combustion engine having a secondary auxiliaries drive
EP1800850A2 (en) Drive device for a forming machine, in particular press drive, and forming machine
DE19962630B4 (en) Drive device for a forming machine
DE102020101918A1 (en) Gearbox for an electric drive of a motor vehicle
EP2327539B1 (en) Press or punching press with switchable planetary gear
EP1075931B1 (en) Eccentric press
DE19959394C2 (en) Drive device for a forming machine
EP1415892A1 (en) Hydraulic system for a servo steering of a motor vehicle
DE2317759C3 (en) Control device for a continuously variable transmission for vehicles
WO2012163382A1 (en) Transmission device and adjusting device having such a transmission device
DE2927768C2 (en) Infinitely variable mechanical speed change transmission - incorporates crankpin with eccentric drive to control alternately operated clutches to rotate output spindle
EP1370411B1 (en) Drive device, particularly for a mechanical press or stamping press
DE19734474A1 (en) Gear transmission group for coupling two concentric shafts with a single drive shaft
DE10247439B4 (en) Transmission for windscreen wiper device and windscreen wiper device, which is provided with such a transmission
DE1627971A1 (en) Creep drive for presses
EP1636515B1 (en) Electric motor for an automatic manual transmission

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

RIC1 Information provided on ipc code assigned before grant

Ipc: B30B 1/26 20060101AFI20130405BHEP

17P Request for examination filed

Effective date: 20131106

RBV Designated contracting states (corrected)

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

17Q First examination report despatched

Effective date: 20140805

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150331

RBV Designated contracting states (corrected)

Designated state(s): AT BE BG CH CY CZ DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: DE

Ref legal event code: R108

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 747775

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150915

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: RO

Ref legal event code: EPE

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: KIRKER AND CIE S.A., CH

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2553853

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20151214

Ref country code: DK

Ref legal event code: T3

Effective date: 20151207

REG Reference to a national code

Ref country code: PT

Ref legal event code: SC4A

Free format text: AVAILABILITY OF NATIONAL TRANSLATION

Effective date: 20151203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151210

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20150909

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E025845

Country of ref document: HU

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160109

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: SK

Ref legal event code: T3

Ref document number: E 19944

Country of ref document: SK

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20160610

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160209

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160209

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20230216

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: RO

Payment date: 20230131

Year of fee payment: 14

Ref country code: NO

Payment date: 20230220

Year of fee payment: 14

Ref country code: FR

Payment date: 20230220

Year of fee payment: 14

Ref country code: FI

Payment date: 20230224

Year of fee payment: 14

Ref country code: DK

Payment date: 20230220

Year of fee payment: 14

Ref country code: CZ

Payment date: 20230130

Year of fee payment: 14

Ref country code: CH

Payment date: 20230307

Year of fee payment: 14

Ref country code: BG

Payment date: 20230216

Year of fee payment: 14

Ref country code: AT

Payment date: 20230217

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20230208

Year of fee payment: 14

Ref country code: SK

Payment date: 20230127

Year of fee payment: 14

Ref country code: SI

Payment date: 20230126

Year of fee payment: 14

Ref country code: PT

Payment date: 20230126

Year of fee payment: 14

Ref country code: PL

Payment date: 20230127

Year of fee payment: 14

Ref country code: IT

Payment date: 20230223

Year of fee payment: 14

Ref country code: HU

Payment date: 20230220

Year of fee payment: 14

Ref country code: GB

Payment date: 20230220

Year of fee payment: 14

Ref country code: BE

Payment date: 20230216

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20230424

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20240219

Year of fee payment: 15

Ref country code: ES

Payment date: 20240325

Year of fee payment: 15