EP2867009B1 - Machine press - Google Patents

Machine press Download PDF

Info

Publication number
EP2867009B1
EP2867009B1 EP13728967.4A EP13728967A EP2867009B1 EP 2867009 B1 EP2867009 B1 EP 2867009B1 EP 13728967 A EP13728967 A EP 13728967A EP 2867009 B1 EP2867009 B1 EP 2867009B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
piston unit
machine press
press according
chamber
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
EP13728967.4A
Other languages
German (de)
French (fr)
Other versions
EP2867009A1 (en
Inventor
Manfred Kurz
Andreas SOCHER
Stefan GUTH
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.)
Hoerbiger Automatisierungstechnik Holding GmbH
Original Assignee
Hoerbiger Automatisierungstechnik Holding 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 Hoerbiger Automatisierungstechnik Holding GmbH filed Critical Hoerbiger Automatisierungstechnik Holding GmbH
Publication of EP2867009A1 publication Critical patent/EP2867009A1/en
Application granted granted Critical
Publication of EP2867009B1 publication Critical patent/EP2867009B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B15/00Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16Control arrangements for fluid-driven presses
    • B30B15/163Control arrangements for fluid-driven presses for accumulator-driven presses
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B15/00Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16Control arrangements for fluid-driven presses
    • B30B15/165Control arrangements for fluid-driven presses for pneumatically-hydraulically driven presses
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26Supply reservoir or sump assemblies
    • F15B1/265Supply reservoir or sump assemblies with pressurised main reservoir
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205Systems with pumps
    • F15B2211/20507Type of prime mover
    • F15B2211/20515Electric motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205Systems with pumps
    • F15B2211/2053Type of pump
    • F15B2211/20569Type of pump capable of working as pump and motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/625Accumulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051Linear output members
    • F15B2211/7055Linear output members having more than two chambers

Definitions

  • the present invention relates to a machine press, in particular a press brake, having a machine structure, a fixed in a spatial relationship to the machine structure lower tool carrier, an upper tool carrier which is relative to the lower tool carrier linearly moved up and down by a power stroke, and one on the upper tool carrier acting, the downward movement of the upper tool carrier causing closed hydraulic drive system comprising at least one hydraulic drive unit, which in turn comprises at least one hydraulic cylinder-piston unit and at least one of these acting, supplied from a reservoir hydraulic unit, wherein in the reservoir constantly above the ambient pressure lying base pressure prevails
  • Such machine presses are known in various designs and configurations and in use.
  • the DE 102009052531 A1 a machine press of the generic type.
  • a hydraulic system dedicated to a press such as a baler, in which a press ram is associated with a main press cylinder having a primary side for generating pressing force and means for returning the press ram are.
  • the device for returning the press ram is operated from a (second) open hydraulic circuit, from which also a pressure booster is operated, by means of which with the primary side of the main pressure cylinder in communication (first) closed hydraulic circuit kept under constant pressure becomes.
  • US Pat. No. 3,669,151-A1 describes a hydraulic system with a cylinder reservoir in which there is a base pressure above the ambient pressure.
  • the voriegende invention is directed to provide optimized in terms of essential practical aspects machine press of the generic type, which is so far in particular by aspects of the size and structural complexity - and thus the production costs - goes.
  • high-pressure gas storage can make do with a fraction of that size, which according to the DE 102009052531 A1 having provided pressure accumulator. Even the space required for the cylinder memory and the high-pressure gas storage combined is still significantly less than the space required for the pressure accumulator of the generic machine press, being added as a further advantage that by the possible in the present invention, spatial separation of cylinder storage and high-pressure gas storage increased flexibility in terms of use of space with the option of particularly compact executed hydraulic drive systems consists.
  • a hydraulic drive unit with a change volume in the order of 101 are kept constantly below a base pressure between 2 and 3 bar, said Such a case typically the Effective area of the hydraulic space on the piston unit by a factor between 50 and 150, more typically by a factor between 75 and 100 is greater than the effective area of the high-pressure gas storage on the piston unit.
  • a first preferred embodiment of the present invention is characterized in that the pressure fluid chamber - preferably centrally - is disposed within the piston unit, in such a way that it with respect to the cylindrical outer surface of him more or less deeply penetrating immersion tube with the high-pressure gas storage is in communication, is sealed.
  • the hydraulic space can be limited in particular by the complete end face of the piston unit.
  • the pressure fluid space (as a cylindrical cavity) may be provided within a projection provided on the piston unit which projects into the hydraulic space, the pressure fluid space being delimited by a piston element sealingly guided in said cylindrical cavity.
  • the pressure fluid space can optionally be designed annular.
  • the gas compressed in the high-pressure gas reservoir acts either directly on the piston unit can, or - by interposition of a liquid active medium - indirectly.
  • the gas of the high-pressure gas reservoir can be in the pressure fluid chamber of the cylinder reservoir, or a liquid pressure fluid which serves to transmit the pressure prevailing in the high-pressure gas reservoir to the pressurized fluid chamber and the corresponding pressurization of the piston unit.
  • the high pressure gas storage operates Yet another function of the machine press according to the invention, namely by being identical to a spring gas storage, which acts on a return stroke working space of the associated drive unit.
  • the drawing dispenses with the machine press as a whole, and is limited to the reproduction of the relevant for the present invention, on the respective drive system related aspects.
  • the closed hydraulic drive system acting on the upper tool carrier of the machine press to effect its downward movement comprises at least one hydraulic drive unit 1.
  • the respective drive system of each machine press comprises two of the illustrated drive units, so that will be described in the following description ,
  • Each of the two drive units 1 in turn comprises a hydraulic cylinder-piston unit 2 - it may optionally be provided more cylinder-piston units 2 - with a cylinder 3 and a guided therein piston 4, the piston rod 5 with the upper tool carrier of Machine press is firmly connected, and a hydraulic cylinder-piston unit 2 acted upon hydraulic unit 6 with a by a (reversible with respect to the direction of rotation) electric motor 7, designed as a reversible hydraulic pump eighth
  • the upper tool carrier is biased by means of a spring device in its upper end position.
  • the spring device is integrated into the hydraulic cylinder-piston units 2 of the two drive units 1 such that each of the piston rod working space 9 of the hydraulic cylinder-piston units 2 is hydraulically connected to an associated, under a gas bias external pressure accumulator 10.
  • the hydraulic drive of the machine press can be switched between a rapid traverse and a press pass.
  • the valve 18 is switched over, so that the hydraulic unit 6 acts in parallel on the piston working chamber 17 and the auxiliary working space 15.
  • the delivery of the hydraulic unit 6 is shut down and stopped, so that the upper tool carrier stops.
  • the tool then stops for a short time before the so-called “decompression stroke” begins, ie the slow, controlled lifting of the upper tool and opening of the press over a small stroke (eg 2-3 mm) by reversing the conveying direction of the hydraulic unit.
  • the valve 18 and the Nachsaugventil 19 are reversed, so that the piston 4 retracts under the action of the spring means.
  • the retraction of the piston 4 takes place in the Rapid traverse controlled (braked) by the auxiliary working space 15 is controlled and controlled emptied via the further operated with respect to the closing of the press reverse flow direction hydraulic unit 6.
  • the delivery rate of the hydraulic unit 6 can be changed over and adjusted.
  • a reservoir 20 is provided for the hydraulic fluid, which comprises a volume-variable hydraulic chamber (reservoir) 21, wherein the maximum volume difference of the reservoir 21 is tuned to the change volume of the hydraulic cylinder-piston unit 2.
  • the hydraulic fluid is clamped in the hydraulic system in such a way that it constantly and everywhere - and thus in particular in the reservoir 21 - at least one above ambient pressure base pressure prevails.
  • the reservoir 20 as a cylinder memory 22 with a by a cylinder 23 and a piston unit 24 slidably guided therein guided reservoir (hydraulic chamber) 21 executed.
  • the piston unit 24 is acted upon by a pressure fluid space 25 on its side which is functionally opposite the hydraulic space 21. This is in turn connected to a high-pressure gas storage 26 in conjunction.
  • the active surface 27 the pressure fluid space 25 on the piston unit 24 is small compared to the effective area 28 of the hydraulic space 21 on the piston unit 24.
  • the pressure fluid space 25 is arranged centrally within the piston unit 24. It is sealed against the cylindrical outer surface 29 of a more or less deeply penetrating immersion tube 30, which is in communication with the high-pressure gas storage 26.
  • the high-pressure gas storage 26 is designed as a hydraulic accumulator whose oil side is connected to the pressure fluid space 25.
  • On the back of the piston unit 24 prevails - via a corresponding ventilation opening 43 - ambient pressure.
  • the hydraulic space 21 is limited by the complete end face 28 of the piston unit 24.
  • Fig. 2 is the in Fig. 1 illustrated, described above hydraulic drive unit 1 modified such that a single high-pressure gas storage 31 is provided, the functions of the two according to the embodiment according to Fig. 1 provided high-pressure gas storage 10 and 26 combined in itself.
  • the high-pressure gas accumulator 31 is thus not only functionally assigned to the reservoir 20, but also part of the - hydropneumatically executed - spring device by also the piston rod working space (return stroke working space) 9 applied.
  • Fig. 3 is the in Fig. 2 illustrated above, the hydraulic drive unit 1 with respect to the reservoir 20 modified such that the pressure fluid chamber 25 is arranged as a cavity within a provided on the piston unit 24, this extending projection 32.
  • the projection 32 protrudes into the hydraulic chamber 21, which in turn has a corresponding extension into it.
  • the pressure fluid space 25 is delimited by a sealing piston 33 sealingly guided in said cavity.
  • the sealing piston 33 is here arranged on the front side of a dip tube 34, which passes through the (for this reason annular) pressure fluid chamber 25 and opposite the cylindrical outer surface 35 of the projection 32 of the piston unit 24 is sealed.
  • the high-pressure gas accumulator 31 is connected to the dip tube 34 and acted on this the pressure fluid space 25th
  • Fig. 4 is the in Fig. 1 illustrated, described above hydraulic drive unit 1 with respect to the reservoir 20 such that the high-pressure gas accumulator 36, due to the pressure bias the hydraulic system is constantly impressed at least above the ambient pressure base pressure, within the cylinder reservoir 22, namely disposed within the piston unit 24 ,
  • the pressurized fluid space 25 and the gas space of the high-pressure gas reservoir 36 thus merge into one another, ie they form - as one arranged in the piston unit 24 Cavity - a spatially and functionally inseparable unit.
  • An immersion pin 37 fixedly connected to the cylinder of the reservoir 20 protrudes more or less deeply into the cavity, depending on the position of the piston unit, which is sealed off from the cylindrical outer surface 38 of the immersion tap 37.
  • the active surface of the high-pressure gas reservoir 36 on the piston unit 24 corresponds in this embodiment to the end face 39 of the dip pin 37 opposite proportion of the cavity bounding end wall 40 of the piston unit.
  • a filling channel 41 is provided with a check valve 42 in order to compensate for a possible leakage of the pressure gas clamped in the cavity can.
  • the upper tool carrier of the machine press can be lowered at all at two different speeds, ie in an input and a press gear, and if so, that a combined hydraulic cylinder according to the illustrated construction is used for this purpose.
  • Various other known embodiments, which allow a two-stage lowering movement of the upper tool carrier, can also be used in the context of the present invention.

Description

Die vorliegende Erfindung betrifft eine Maschinenpresse, insbesondere Abkantpresse, mit einer Maschinenstruktur, einem in fester räumlicher Beziehung zu der Maschinenstruktur angeordneten unteren Werkzeugträger, einem oberen Werkzeugträger, der relativ zu dem unteren Werkzeugträger um einen Betriebshub linear auf und ab verfahrbar ist, und einem auf den oberen Werkzeugträger wirkenden, die abwärts gerichtete Bewegung des oberen Werkzeugträgers bewirkenden geschlossenen hydraulischen Antriebssystem, welches mindestens eine hydraulische Antriebseinheit aufweist, welche ihrerseits mindestens eine hydraulische Zylinder-Kolben-Einheit und mindestens ein diese beaufschlagendes, aus einem Vorratsbehälter versorgtes Hydraulikaggregat umfasst, wobei in dem Vorratsbehälter ständig ein über dem Umgebungsdruck liegender Basisdruck herrschtThe present invention relates to a machine press, in particular a press brake, having a machine structure, a fixed in a spatial relationship to the machine structure lower tool carrier, an upper tool carrier which is relative to the lower tool carrier linearly moved up and down by a power stroke, and one on the upper tool carrier acting, the downward movement of the upper tool carrier causing closed hydraulic drive system comprising at least one hydraulic drive unit, which in turn comprises at least one hydraulic cylinder-piston unit and at least one of these acting, supplied from a reservoir hydraulic unit, wherein in the reservoir constantly above the ambient pressure lying base pressure prevails

Derartige Maschinenpressen sind in diversen Ausführungen und Ausgestaltungen bekannt und im Einsatz. Beispielsweise offenbart die DE 102009052531 A1 eine Maschinenpresse der gattungsgemäßen Art.Such machine presses are known in various designs and configurations and in use. For example, the DE 102009052531 A1 a machine press of the generic type.

Bekannt ist darüber hinaus, nämlich aus der DE 698 29 318 T2 , ein für eine Presse wie beispielsweise eine Ballenpresse bestimmtes hydraulisches System, bei dem einem Pressenstößel ein Haupt-Presszylinder mit einer Primärseite zum Erzeugen von Presskraft und eine Einrichtung zum Zurückführen des Pressenstößels zugeordnet sind. Die Einrichtung zum Zurückführen des Pressenstößels wird dabei aus einem (zweiten) offenen hydraulischen Kreislauf betrieben, aus welchem auch ein Druckverstärker betrieben wird, mittels dessen der mit der Primärseite des Haupt-Presszylinders in Verbindung stehende (erste) geschlossene hydraulische Kreislauf ständig unter einem Überdruck gehalten wird.It is known, moreover, namely from the DE 698 29 318 T2 , a hydraulic system dedicated to a press such as a baler, in which a press ram is associated with a main press cylinder having a primary side for generating pressing force and means for returning the press ram are. The device for returning the press ram is operated from a (second) open hydraulic circuit, from which also a pressure booster is operated, by means of which with the primary side of the main pressure cylinder in communication (first) closed hydraulic circuit kept under constant pressure becomes.

US 3 669 151-A1 beschreibt einen Hydrauliksystem mit einem Zylinderspeicher, in dem ein über dem Umgebungsdruckliegender Basisdruck herrscht. US Pat. No. 3,669,151-A1 describes a hydraulic system with a cylinder reservoir in which there is a base pressure above the ambient pressure.

Die vor iegende Erfindung ist darauf gerichtet, eine hinsichtlich wesentlicher praxisrelevanter Aspekte optimierte Maschinenpresse der gattungsgemäßen Art bereitzustellen, wobei es insoweit namentlich um Aspekte der Baugröße und des baulichen Aufwands - und somit auch der Herstellungskosten - geht.The voriegende invention is directed to provide optimized in terms of essential practical aspects machine press of the generic type, which is so far in particular by aspects of the size and structural complexity - and thus the production costs - goes.

Gelöst wird die vorstehend bezeichnete Aufgabenstellung gemäß der vorliegenden Erfindung bei einer Maschinenpresse mit den Merkmalen des Anspruchs 1. Namentlich bei besonderes großen und leistungsfähigen Maschinenpressen lassen sich auf dieses Weise gegenüber dem Stand der Technik signifikante Vorteile erreichen; denn selbst bei Maschinenpressen mit einem vergleichsweise großen benötigten Wechselvolumen, welches bei erfindungsgemäßen Maschinenpressen durch die Differenz zwischen dem maximalen und dem minimalen Volumen des Hydraulikraums des Zylinderspeichers definiert ist, lässt sich mit einem vergleichsweise kleinen Hochdruck-Gasspeicher sicherstellen, dass in der mindestens einen hydraulischen Antriebseinheit ständig, d.h. über sämtliche Betriebsphasen der Maschinenpresse zuverlässig ein über dem Umgebungsdruck liegender Basisdruck herrscht. In diesem Sinne kann der nach der vorliegenden Erfindung vorgesehene Hochdruck-Gasspeicher mit einem Bruchteil jener Baugröße auskommen, die der gemäß der DE 102009052531 A1 vorgesehene Druckspeicher aufweist. Selbst der Platzbedarf für den Zylinderspeicher und den Hochdruck-Gasspeicher zusammengenommen ist noch immer deutlich geringer als der Platzbedarf für den Druckspeicher der gattungsgemäßen Maschinenpresse, wobei als weiterer Vorteil hinzukommt, dass durch die im Rahmen der vorliegenden Erfindung mögliche räumliche Trennung von Zylinderspeicher und Hochdruck-Gasspeicher eine erhöhte Flexibilität hinsichtlich der Raumnutzung mit der Option besonders kompakt ausgeführter hydraulischer Antriebssysteme besteht. In konkreter Umsetzung der vorliegenden Erfindung kann beispielsweise mit einem Hochdruck-Gasspeicher mit einem Volumen von etwa 0,3 - 0,51 eine hydraulische Antriebseinheit mit einem Wechselvolumen in der Größenordnung von 101 ständig unter einem Basisdruck zwischen 2 und 3 bar gehalten werden, wobei in einem solchen Falle typischerweise die Wirkfläche des Hydraulikraumes an der Kolbeneinheit um einen Faktor zwischen 50 und 150, besonders typischerweise um einen Faktor zwischen 75 und 100 größer ist als die Wirkfläche des Hochdruck-Gasspeichers an der Kolbeneinheit.The above-mentioned object is achieved according to the present invention in a machine press with the features of claim 1. Namely, in particular large and powerful machine presses can be achieved in this way compared to the prior art, significant advantages; because Even with machine presses with a comparatively large required change volume, which is defined in machine presses according to the invention by the difference between the maximum and the minimum volume of the hydraulic space of the cylinder memory, it can be ensured with a comparatively small high-pressure gas storage that constantly in the at least one hydraulic drive unit That is, over all operating phases of the machine press reliably above the ambient pressure lying base pressure prevails. In this sense, provided according to the present invention high-pressure gas storage can make do with a fraction of that size, which according to the DE 102009052531 A1 having provided pressure accumulator. Even the space required for the cylinder memory and the high-pressure gas storage combined is still significantly less than the space required for the pressure accumulator of the generic machine press, being added as a further advantage that by the possible in the present invention, spatial separation of cylinder storage and high-pressure gas storage increased flexibility in terms of use of space with the option of particularly compact executed hydraulic drive systems consists. In concrete implementation of the present invention, for example, with a high-pressure gas storage with a volume of about 0.3 to 0.51, a hydraulic drive unit with a change volume in the order of 101 are kept constantly below a base pressure between 2 and 3 bar, said Such a case typically the Effective area of the hydraulic space on the piston unit by a factor between 50 and 150, more typically by a factor between 75 and 100 is greater than the effective area of the high-pressure gas storage on the piston unit.

In Abhängigkeit von den spezifischen Gegebenheiten lässt sich die vorliegende Erfindung in verschiedensten konstruktiven Ausführungsvarianten technisch umsetzen. In diesem Sinne zeichnet sich eine erste bevorzugte Weiterbildung der vorliegenden Erfindung dadurch aus, dass der Druckfluidraum - bevorzugt zentral - innerhalb der Kolbeneinheit angeordnet ist, und zwar dergestalt, dass er gegenüber der zylindrischen Außenfläche eines in ihn mehr oder weniger tief eindringenden Tauchrohres, das mit dem Hochdruck-Gasspeicher in Verbindung steht, abgedichtet ist. Der Hydraulikraum kann dabei insbesondere von der vollständigen Stirnfläche der Kolbeneinheit begrenzt werden. Gemäß einer Abwandlung kann der Druckfluidraum (als zylindrischer Hohlraum) innerhalb eines an der Kolbeneinheit vorgesehenen Vorsprungs, welcher in den Hydraulikraum hineinragt, vorgesehen sein, wobei der Druckfluidraum durch ein in dem besagten zylindrischen Hohlraum dichtend geführtes Kolbenelement begrenzt ist. Der Druckfluidraum kann dabei ggf. ringförmig ausgeführt sein.Depending on the specific circumstances, the present invention can be technically implemented in a wide variety of design variants. In this sense, a first preferred embodiment of the present invention is characterized in that the pressure fluid chamber - preferably centrally - is disposed within the piston unit, in such a way that it with respect to the cylindrical outer surface of him more or less deeply penetrating immersion tube with the high-pressure gas storage is in communication, is sealed. The hydraulic space can be limited in particular by the complete end face of the piston unit. According to a modification, the pressure fluid space (as a cylindrical cavity) may be provided within a projection provided on the piston unit which projects into the hydraulic space, the pressure fluid space being delimited by a piston element sealingly guided in said cylindrical cavity. The pressure fluid space can optionally be designed annular.

Weiterhin besteht insoweit ein erheblicher Gestaltungsspielraum, als das in dem Hochdruck-Gasspeicher komprimierte Gas entweder direkt auf die Kolbeneinheit wirken kann, oder aber - durch Zwischenschaltung eines flüssigen Wirkmediums - mittelbar. Mit anderen Worten, in dem Druckfluidraum des Zylinderspeichers kann sich als Druckfluid entweder das Gas des Hochdruck-Gasspeichers befinden oder aber ein flüssiges Druckfluid, welches der Übertragung des in dem Hochdruck-Gasspeicher herrschenden Drucks auf den Druckfluidraum und der entsprechenden Beaufschlagung der Kolbeneinheit dient.Furthermore, there is a considerable scope for design insofar as the gas compressed in the high-pressure gas reservoir acts either directly on the piston unit can, or - by interposition of a liquid active medium - indirectly. In other words, either the gas of the high-pressure gas reservoir can be in the pressure fluid chamber of the cylinder reservoir, or a liquid pressure fluid which serves to transmit the pressure prevailing in the high-pressure gas reservoir to the pressurized fluid chamber and the corresponding pressurization of the piston unit.

Die anspruchsgemäße Angabe, wonach der die Kolbeneinheit des Zylinderspeichers beaufschlagende Druckfluidraum mit einem Hochdruck-Gasspeicher in Verbindung steht, darf im Übrigen nicht dahingehend verstanden werden, dass es sich bei dem Druckfluidraum und dem Hochdruck-Gasspeicher um zwei räumlich abgegrenzte Volumina handelt. Vielmehr ist eine konstruktive Umsetzung der vorliegenden Erfindung durchaus auch dergestalt möglich, dass der Druckfluidraum innerhalb des Zylinderspeichers auf der funktional dem Hydraulikraum abgewandten Seite der Kolbeneinheit - ggf. in dieser räumlich untergebracht - vorgesehen ist und zugleich das Volumen des Hochdruck-Gasspeichers (oder zumindest einen Teil hiervon) bildet bzw. mit diesem einen gemeinsamen gasgefüllten Hohlraum bildet. Insoweit ist - wegen baulicher Details - auf die Erläuterung eines der in der Zeichnung veranschaulichten Ausführungsbeispiele zu verweisen.The claim according to which the pressurized fluid chamber acting upon the piston unit of the cylinder reservoir is associated with a high-pressure gas accumulator may not otherwise be understood to mean that the pressure fluid chamber and the high-pressure gas accumulator are two spatially delimited volumes. Rather, a constructive implementation of the present invention is also quite possible in such a way that the pressure fluid space within the cylinder memory on the side facing away from the hydraulic chamber of the piston unit - possibly accommodated in this spatially - is provided and at the same time the volume of the high-pressure gas storage (or at least one Part thereof) forms or forms with this a common gas-filled cavity. In that regard - due to structural details - to refer to the explanation of one of the illustrated in the drawings embodiments.

Gemäß einer wiederum anderen bevorzugten Weiterbildung der vorliegenden Erfindung bedient der Hochdruck-Gasspeicher noch eine weitere Funktion der erfindungsgemäßen Maschinenpresse, namentlich indem er mit einem Feder-Gasspeicher identisch ist, welcher einen Rückhub-Arbeitsraum der zugeordneten Antriebseinheit beaufschlagt. Durch eine solche Integration mehrerer Funktionen in eine einzige bauliche Komponente des Antriebssystems lässt sich nicht nur - im Sinne eines besonders kompakten Antriebssystems - der erforderliche Platzbedarf reduzieren; vielmehr lassen sich auf diese Weise auch Kosten einsparen.According to yet another preferred embodiment of the present invention, the high pressure gas storage operates Yet another function of the machine press according to the invention, namely by being identical to a spring gas storage, which acts on a return stroke working space of the associated drive unit. Such integration of multiple functions in a single structural component of the drive system not only - in the sense of a particularly compact drive system - can reduce the space required; rather, costs can be saved in this way.

Im Folgenden wird die vorliegende Erfindung anhand von vier in der Zeichnung beispielhaft, mehr oder weniger schematisch veranschaulichten hydraulischen Antriebseinheiten, wie sie Bestandteil bevorzugter Ausführungsformen erfindungsgemäßer Maschinenpressen sein können, erläutert. Dabei zeigt

Fig. 1
ein erstes bevorzugtes Ausführungsbeispiel einer solchen hydraulischen Antriebseinheit,
Fig. 2
ein zweites bevorzugtes Ausführungsbeispiel einer solchen hydraulischen Antriebseinheit,
Fig. 3
ein drittes bevorzugtes Ausführungsbeispiel einer solchen hydraulischen Antriebseinheit und
Fig. 4
ein viertes bevorzugtes Ausführungsbeispiel einer solchen hydraulischen Antriebseinheit.
In the following, the present invention will be explained with reference to four hydraulic drive units exemplified in the drawing by way of example, more or less schematically, as they may be part of preferred embodiments of machine presses according to the invention. It shows
Fig. 1
A first preferred embodiment of such a hydraulic drive unit,
Fig. 2
A second preferred embodiment of such a hydraulic drive unit,
Fig. 3
a third preferred embodiment of such a hydraulic drive unit and
Fig. 4
A fourth preferred embodiment of such a hydraulic drive unit.

Die Zeichnung verzichtet darauf, die Maschinenpresse als ganzes abzubilden, und beschränkt sich auf die Widergabe der für die vorliegende Erfindung maßgeblichen, sich auf das jeweilige Antriebssystem beziehenden Aspekte. So können die Maschinenpressen, für die die nachstehend näher erläuterten Ausführungsbeispiele der Antriebssysteme bestimmt sind, hinsichtlich ihres grundsätzlichen Aufbaus insbesondere dem Stand der Technik (vgl. z.B. DE 102009052531 A1 ) entsprechen.The drawing dispenses with the machine press as a whole, and is limited to the reproduction of the relevant for the present invention, on the respective drive system related aspects. Thus, the machine presses for which the embodiments of the drive systems explained in more detail below are intended, with regard to their basic construction, in particular the prior art (cf. DE 102009052531 A1 ) correspond.

Das auf den oberen Werkzeugträger der Maschinenpresse, um dessen abwärts gerichtete Bewegung zu bewirken, wirkende geschlossene hydraulische Antriebssystem umfasst jeweils mindestens eine hydraulische Antriebseinheit 1. Typischerweise umfasst das betreffende Antriebssystem jeder Maschinenpresse jeweils zwei der veranschaulichten Antriebseinheiten, so dass in der folgenden Beschreibung hierauf abgestellt wird.The closed hydraulic drive system acting on the upper tool carrier of the machine press to effect its downward movement comprises at least one hydraulic drive unit 1. Typically, the respective drive system of each machine press comprises two of the illustrated drive units, so that will be described in the following description ,

Jede der beiden Antriebseinheiten 1 umfasst ihrerseits eine hydraulische Zylinder-Kolben-Einheit 2 - es können ggf. auch mehrere Zylinder-Kolben-Einheiten 2 vorgesehen sein - mit einem Zylinder 3 und einem darin geführten Kolben 4, dessen Kolbenstange 5 mit dem oberen Werkzeugträger der Maschinenpresse fest verbunden ist, und ein die hydraulische Zylinder-Kolben-Einheit 2 beaufschlagendes Hydraulikaggregat 6 mit einer durch einen (hinsichtlich der Drehrichtung umschaltbaren) Elektromotor 7 angetriebenen, als Reversierpumpe ausgeführten Hydraulikpumpe 8.Each of the two drive units 1 in turn comprises a hydraulic cylinder-piston unit 2 - it may optionally be provided more cylinder-piston units 2 - with a cylinder 3 and a guided therein piston 4, the piston rod 5 with the upper tool carrier of Machine press is firmly connected, and a hydraulic cylinder-piston unit 2 acted upon hydraulic unit 6 with a by a (reversible with respect to the direction of rotation) electric motor 7, designed as a reversible hydraulic pump eighth

Der obere Werkzeugträger ist mittels einer Federeinrichtung in seine obere Endlage vorgespannt. Die Federeinrichtung ist dergestalt in die hydraulischen Zylinder-Kolben-Einheiten 2 der beiden Antriebseinheiten 1 integriert, dass jeweils der Kolbenstangenarbeitsraum 9 der hydraulischen Zylinder-Kolben-Einheiten 2 hydraulisch mit einem zugeordneten, unter einer Gas-Vorspannung stehenden externen Druckspeicher 10 verbunden ist.The upper tool carrier is biased by means of a spring device in its upper end position. The spring device is integrated into the hydraulic cylinder-piston units 2 of the two drive units 1 such that each of the piston rod working space 9 of the hydraulic cylinder-piston units 2 is hydraulically connected to an associated, under a gas bias external pressure accumulator 10.

Der Hydraulikantrieb der Maschinenpresse ist zwischen einem Eilgang und einem Pressgang umschaltbar. Dabei erfolgt - nachdem die aufwärts gerichtete Kraft der (vorstehend beschriebenen) Federeinrichtung ständig in einer solchen Höhe auf den oberen Werkzeugträger wirkt, dass dessen Gewicht und das aller mit ihm gekoppelten bewegbaren Komponenten der Maschinenpresse sowie die Schließkraft, welche durch den in den beiden hydraulischen Antriebseinheiten herrschenden Basisdruck impliziert wird (s.u.), überkompensiert und der obere Werkzeugträger in seine oberste Stellung vorgespannt wird - auch im Eilgang eine aktive Bewegung des oberen Werkzeugträgers durch den Hydraulikantrieb, nicht indessen eine freie Bewegung aufgrund der Schwerkraft. Erreicht wird dies, indem in die Kolben 4 der beiden hydraulischen Zylinder-Kolben-Einheiten 2, nämlich jeweils eine darin eingebrachte Bohrung 11 jeweils ein Hilfskolben 12 eintaucht. Näheres hierzu ist der AT 8633 U1 (Fig. 3 und 4 samt zugehörige Beschreibung) und der DE 102009052531 A1 entnehmbar. Im Ergebnis wird von dem Hydraulikaggregat 6 im Eilgang eine vergleichsweise kleine erste wirksame Kolbenfläche 13 beaufschlagt, im Pressgang demgegenüber eine wesentlich größere zweite wirksame Kolbenfläche, die sich aus der ersten wirksamen Kolbenfläche 13 des Hilfsarbeitsraums 15 und der Ringfläche 16 des Kolbenarbeitsraums 17 zusammensetzt. Zur Umschaltung zwischen dem Eilgang und dem Pressgang dient das Ventil 18, das im Eilgang die Verbindung des Hydraulikaggregats 6 zum Kolbenarbeitsraum 17 sperrt, im Pressgang demgegenüber öffnet. Im Eilgang erfolgt ein Füllen des Kolbenarbeitsraums 17 über den über ein Rückschlagventil 14 abgesicherten Pfad des Nachsaugventils 19.The hydraulic drive of the machine press can be switched between a rapid traverse and a press pass. In this case - after the upward force of the spring device (described above) constantly acts at such a height on the upper tool carrier that its weight and all coupled to it movable components of the machine press and the closing force, which by the in the two hydraulic drive units prevailing base pressure is (see below), overcompensated and the upper tool carrier is biased to its uppermost position - even at rapid traction active movement of the upper tool carrier by the hydraulic drive, but not a free movement due to gravity. This is achieved by a respective auxiliary piston 12 dips into the piston 4 of the two hydraulic cylinder-piston units 2, namely in each case a bore 11 introduced therein. More about this is the AT 8633 U1 ( Fig. 3 and 4 together with its description) and the DE 102009052531 A1 removable. As a result, a comparatively small first effective piston surface 13 is acted upon by the hydraulic unit 6 at rapid traverse, in the Pressing contrast, a much larger second effective piston area, which is composed of the first effective piston surface 13 of the auxiliary working space 15 and the annular surface 16 of the piston working chamber 17. To switch between the rapid traverse and the press gear, the valve 18, which blocks the connection of the hydraulic unit 6 to the piston working chamber 17 in rapid traverse, opens in the press passage on the other hand. In rapid traverse filling of the piston working chamber 17 via the secured via a check valve 14 path of the Nachsaugventils 19th

Für den Pressgang wird das Ventil 18 umgeschaltet, so dass das Hydraulikaggregat 6 parallel den Kolbenarbeitsraum 17 und den Hilfsarbeitsraum 15 beaufschlagt. Am Ende der Schließbewegung, d.h. typischerweise wenn der obere Werkzeugträger eine vorgegebene Position erreicht, wird die Förderung des Hydraulikaggregats 6 heruntergefahren und gestoppt, so dass der obere Werkzeugträger anhält. Das Werkzeug hält dann kurze Zeit inne, bevor der sog. "Dekompressionshub" einsetzt, d.h. das langsame, kontrollierte Abheben des oberen Werkzeugs und Öffnen der Presse über einen geringen Hub (z.B. 2-3 mm) durch Förderrichtungsumkehr des Hydraulikaggregats. Am Ende des Dekompressionshubes, d.h. wenn der hohe Druck in der Zylinder-Kolben-Einheit 2 zumindest im Wesentlichen abgebaut ist, werden das Ventil 18 und das Nachsaugventil 19 umgesteuert, so dass der Kolben 4 unter der Einwirkung der Federeinrichtung einfährt. Das Einfahren des Kolbens 4 erfolgt dabei im Eilgang kontrolliert (gebremst), indem der Hilfsarbeitsraum 15 über das weiterhin mit gegenüber dem Schließen der Presse umgekehrter Förderrichtung betriebene Hydraulikaggregat 6 kontrolliert und gesteuert entleert wird. Insoweit ist bei dieser hydraulischen Antriebseinheit die Förderleistung des Hydraulikaggregats 6 um- und einstellbar.For the pressing operation, the valve 18 is switched over, so that the hydraulic unit 6 acts in parallel on the piston working chamber 17 and the auxiliary working space 15. At the end of the closing movement, ie typically when the upper tool carrier reaches a predetermined position, the delivery of the hydraulic unit 6 is shut down and stopped, so that the upper tool carrier stops. The tool then stops for a short time before the so-called "decompression stroke" begins, ie the slow, controlled lifting of the upper tool and opening of the press over a small stroke (eg 2-3 mm) by reversing the conveying direction of the hydraulic unit. At the end of the decompression stroke, ie when the high pressure in the cylinder-piston unit 2 is at least substantially reduced, the valve 18 and the Nachsaugventil 19 are reversed, so that the piston 4 retracts under the action of the spring means. The retraction of the piston 4 takes place in the Rapid traverse controlled (braked) by the auxiliary working space 15 is controlled and controlled emptied via the further operated with respect to the closing of the press reverse flow direction hydraulic unit 6. In that regard, in this hydraulic drive unit, the delivery rate of the hydraulic unit 6 can be changed over and adjusted.

Das Hydrauliksystem ist hermetisch abgeschlossen. Hierzu ist ein Vorratsbehälter 20 für die Hydraulikflüssigkeit vorgesehen, welcher einen volumenveränderlichen Hydraulikraum (Vorratsraum) 21 umfasst, wobei die maximale Volumendifferenz des Vorratsraumes 21 auf das Wechselvolumen der hydraulischen Zylinder-Kolben-Einheit 2 abgestimmt ist.The hydraulic system is hermetically sealed. For this purpose, a reservoir 20 is provided for the hydraulic fluid, which comprises a volume-variable hydraulic chamber (reservoir) 21, wherein the maximum volume difference of the reservoir 21 is tuned to the change volume of the hydraulic cylinder-piston unit 2.

Die Hydraulikflüssigkeit ist in dem Hydrauliksystem dergestalt eingespannt, dass in diesem ständig und überall - und somit insbesondere in dem Vorratsraum 21 - zumindest ein über dem Umgebungsdruck liegender Basisdruck herrscht. Bei sämtlichen Ausführungsbeispielen ist hierzu, in konstruktiver Umsetzung der vorliegenden Erfindung, der Vorratsbehälter 20 als Zylinderspeicher 22 mit einem durch einen Zylinder 23 und einer darin verschiebbar geführten Kolbeneinheit 24 begrenzten Vorratsraum (Hydraulikraum) 21 ausgeführt. Die Kolbeneinheit 24 wird auf ihrer dem Hydraulikraum 21 funktional gegenüberliegenden Seite von einem Druckfluidraum 25 beaufschlagt. Dieser steht seinerseits mit einem Hochdruck-Gasspeicher 26 in Verbindung. Die Wirkfläche 27 des Druckfluidraumes 25 an der Kolbeneinheit 24 ist klein gegenüber der Wirkfläche 28 des Hydraulikraumes 21 an der Kolbeneinheit 24.The hydraulic fluid is clamped in the hydraulic system in such a way that it constantly and everywhere - and thus in particular in the reservoir 21 - at least one above ambient pressure base pressure prevails. In all embodiments, for this purpose, in a constructive implementation of the present invention, the reservoir 20 as a cylinder memory 22 with a by a cylinder 23 and a piston unit 24 slidably guided therein guided reservoir (hydraulic chamber) 21 executed. The piston unit 24 is acted upon by a pressure fluid space 25 on its side which is functionally opposite the hydraulic space 21. This is in turn connected to a high-pressure gas storage 26 in conjunction. The active surface 27 the pressure fluid space 25 on the piston unit 24 is small compared to the effective area 28 of the hydraulic space 21 on the piston unit 24.

Bei der in Fig. 1 gezeigten Ausführungsform ist der Druckfluidraum 25 zentral innerhalb der Kolbeneinheit 24 angeordnet. Er ist gegenüber der zylindrischen Außenfläche 29 eines in ihn mehr oder weniger tief eindringenden Tauchrohres 30, das mit dem Hochdruck-Gasspeicher 26 in Verbindung steht, abgedichtet. Der Hochdruck-Gasspeicher 26 ist als Hydrospeicher ausgeführt, dessen Ölseite mit dem Druckfluidraum 25 verbunden ist. Auf der Rückseite der Kolbeneinheit 24 herrscht - über eine entsprechende Belüftungsöffnung 43 - Umgebungsdruck. Der Hydraulikraum 21 ist durch die vollständige Stirnfläche 28 der Kolbeneinheit 24 begrenzt.At the in Fig. 1 In the embodiment shown, the pressure fluid space 25 is arranged centrally within the piston unit 24. It is sealed against the cylindrical outer surface 29 of a more or less deeply penetrating immersion tube 30, which is in communication with the high-pressure gas storage 26. The high-pressure gas storage 26 is designed as a hydraulic accumulator whose oil side is connected to the pressure fluid space 25. On the back of the piston unit 24 prevails - via a corresponding ventilation opening 43 - ambient pressure. The hydraulic space 21 is limited by the complete end face 28 of the piston unit 24.

Gemäß Fig. 2 ist die in Fig. 1 veranschaulichte, vorstehend erläuterte hydraulische Antriebseinheit 1 dergestalt abgewandelt, dass ein einziger Hochdruck-Gasspeicher 31 vorgesehen ist, der die Funktionen der beiden nach dem Ausführungsbeispiel nach Fig. 1 vorgesehenen Hochdruck-Gasspeicher 10 und 26 in sich vereinigt. Der Hochdruck-Gasspeicher 31 ist somit nicht nur dem Vorratsbehälter 20 funktional zugeordnet, sondern auch Teil der - hydropneumatisch ausgeführten - Federeinrichtung, indem er auch den Kolbenstangenarbeitsraum (Rückhub-Arbeitsraum) 9 beaufschlagt.According to Fig. 2 is the in Fig. 1 illustrated, described above hydraulic drive unit 1 modified such that a single high-pressure gas storage 31 is provided, the functions of the two according to the embodiment according to Fig. 1 provided high-pressure gas storage 10 and 26 combined in itself. The high-pressure gas accumulator 31 is thus not only functionally assigned to the reservoir 20, but also part of the - hydropneumatically executed - spring device by also the piston rod working space (return stroke working space) 9 applied.

Gemäß Fig. 3 ist die in Fig. 2 veranschaulichte, vorstehend erläuterte hydraulische Antriebseinheit 1 hinsichtlich des Vorratsbehälters 20 dergestalt abgewandelt, dass der Druckfluidraum 25 als Hohlraum innerhalb eines an der Kolbeneinheit 24 vorgesehenen, diese verlängernden Vorsprungs 32 angeordnet ist. Der Vorsprung 32 ragt dabei in den Hydraulikraum 21, der seinerseits eine korrespondierende Verlängerung aufweist, hinein. Der Druckfluidraum 25 ist durch einen in dem besagten Hohlraum dichtend geführten Dichtkolben 33 begrenzt. Der Dichtkolben 33 ist hier stirnseitig an einem Tauchrohr 34 angeordnet, welches den (aus diesem Grunde ringförmigen) Druckfluidraum 25 durchsetzt und gegenüber dessen zylindrischer Außenfläche 35 der Vorsprung 32 der Kolbeneinheit 24 abgedichtet ist. Der Hochdruck-Gasspeicher 31 ist an das Tauchrohr 34 angeschlossen und beaufschlagt über dieses den Druckfluidraum 25.According to Fig. 3 is the in Fig. 2 illustrated above, the hydraulic drive unit 1 with respect to the reservoir 20 modified such that the pressure fluid chamber 25 is arranged as a cavity within a provided on the piston unit 24, this extending projection 32. The projection 32 protrudes into the hydraulic chamber 21, which in turn has a corresponding extension into it. The pressure fluid space 25 is delimited by a sealing piston 33 sealingly guided in said cavity. The sealing piston 33 is here arranged on the front side of a dip tube 34, which passes through the (for this reason annular) pressure fluid chamber 25 and opposite the cylindrical outer surface 35 of the projection 32 of the piston unit 24 is sealed. The high-pressure gas accumulator 31 is connected to the dip tube 34 and acted on this the pressure fluid space 25th

Gemäß Fig. 4 ist die in Fig. 1 veranschaulichte, weiter oben erläuterte hydraulische Antriebseinheit 1 hinsichtlich des Vorratsbehälters 20 dergestalt abgewandelt, dass der Hochdruck-Gasspeicher 36, aufgrund dessen Druckvorspannung dem Hydrauliksystem ständig ein zumindest über dem Umgebungsdruck liegender Basisdruck aufgeprägt wird, innerhalb des Zylinderspeichers 22, nämlich innerhalb der Kolbeneinheit 24 angeordnet ist. Der Druckfluidraum 25 und der Gasraum des Hochdruck-Gasspeichers 36 gehen somit ineinander über, d.h. sie bilden - als ein in der Kolbeneinheit 24 angeordneter Hohlraum - eine räumlich und funktional untrennbare Einheit. Ein mit dem Zylinder des Vorratsbehälters 20 fest verbundener Tauchzapfen 37 ragt - je nach der Stellung der Kolbeneinheit - mehr oder weniger tief in den Hohlraum ein, der gegenüber der zylindrischen Außenfläche 38 des Tauchzapfes 37 abgedichtet ist. Die Wirkfläche des Hochdruck-Gasspeichers 36 auf die Kolbeneinheit 24 entspricht bei dieser Ausführungsform dem der Stirnfläche 39 des Tauchzapfens 37 gegenüberliegenden Anteil der den Hohlraum begrenzenden Stirnwand 40 der Kolbeneinheit. In dem Tauchzapfen 37 ist ein Befüllkanal 41 mit einem Rückschlagventil 42 vorgesehen, um eine mögliche Leckage des in dem Hohlraum eingespannten Druckgases ausgleichen zu können.According to Fig. 4 is the in Fig. 1 illustrated, described above hydraulic drive unit 1 with respect to the reservoir 20 such that the high-pressure gas accumulator 36, due to the pressure bias the hydraulic system is constantly impressed at least above the ambient pressure base pressure, within the cylinder reservoir 22, namely disposed within the piston unit 24 , The pressurized fluid space 25 and the gas space of the high-pressure gas reservoir 36 thus merge into one another, ie they form - as one arranged in the piston unit 24 Cavity - a spatially and functionally inseparable unit. An immersion pin 37 fixedly connected to the cylinder of the reservoir 20 protrudes more or less deeply into the cavity, depending on the position of the piston unit, which is sealed off from the cylindrical outer surface 38 of the immersion tap 37. The active surface of the high-pressure gas reservoir 36 on the piston unit 24 corresponds in this embodiment to the end face 39 of the dip pin 37 opposite proportion of the cavity bounding end wall 40 of the piston unit. In the immersion pin 37, a filling channel 41 is provided with a check valve 42 in order to compensate for a possible leakage of the pressure gas clamped in the cavity can.

Es ist zur Klarstellung darauf hinzuweisen, dass aus der Veranschaulichung der vorstehend erläuterten Ausführungsbeispiele mit diversen Detailmerkmalen keinesfalls auf eine dementsprechend beschränkte Offenbarung der vorliegenden Erfindung geschlossen werden darf, und zwar schon gar nicht dergestalt, dass die jeweiligen Einzelmerkmale jeweils nur einer solchen Kombination miteinander offenbart seien. Vielmehr sind auch andere Detailmerkmale und/oder andere Merkmalskombinationen von der vorliegenden Erfindung erfasst. Beispielsweise ist die spezifische (hydropneumatische) Ausführung der Einrichtung für den Rückhub des oberen Werkzeugträgers in keiner Weise zwingend. Vielmehr können sämtliche bekannten sonstigen, beispielsweise hydraulisch, mechanisch, elektrisch pneumatisch oder auf sonstige Weise funktionierenden Rückhubeinrichtungen vorgesehen sein. Ebenso wenig ist zwingend, dass der obere Werkzeugträger der Maschinenpresse überhaupt mit zwei unterschiedlichen Geschwindigkeiten, d.h. in einem Eingang und einem Pressgang abgesenkt werden kann, und falls ja, dass hierfür ein kombinierter Hydraulikzylinder gemäß der veranschaulichten Bauweise dient. Diverse sonstige bekannte Ausgestaltungen, die eine zweistufige Absenkbewegung des oberen Werkzeugträgers zulassen, sind ersichtlich ebenfalls im Rahmen der vorliegenden Erfindung einsetzbar.It is to be pointed out for the sake of clarification that from the illustration of the above-explained exemplary embodiments with various detail features, a correspondingly limited disclosure of the present invention may under no circumstances be concluded, certainly not in such a way that the respective individual features of only one such combination are disclosed to one another , Rather, other detail features and / or other feature combinations are covered by the present invention. For example, the specific (hydropneumatic) design of the device for the return stroke of the upper tool carrier is in no way mandatory. Rather, all known other, for example, hydraulically, mechanically, electrically pneumatically or otherwise be provided working return devices. Nor is it imperative that the upper tool carrier of the machine press can be lowered at all at two different speeds, ie in an input and a press gear, and if so, that a combined hydraulic cylinder according to the illustrated construction is used for this purpose. Various other known embodiments, which allow a two-stage lowering movement of the upper tool carrier, can also be used in the context of the present invention.

Claims (11)

  1. A machine press, in particular a bend press, having: a machine structure; a lower die carrier, which is arranged in a fixed spatial relationship to the machine structure; an upper die carrier, which can be moved up and down linearly by an operating stroke relative to the lower die carrier; and a closed hydraulic drive system, which acts on the upper die carrier, effects the downward directed movement of the upper die carrier and has at least one hydraulic drive unit (1), which in turn comprises at least one hydraulic cylinder-piston unit (2) and at least one hydraulic assembly (6), which applies a load to said cylinder-piston unit and is supplied from a storage container (20), a basic pressure above ambient pressure prevailing constantly in the storage container,
    characterised in that
    the storage container (20) is in the form of a cylindrical reservoir (22) having a hydraulic chamber (21), which is delimited by a cylinder (23) and a piston unit (24) guided displaceably therein, wherein load is applied to the piston unit on the side thereof that is functionally opposite the hydraulic chamber from a pressurised fluid chamber (25), which for its part is connected to a high-pressure gas reservoir (26, 31, 36) and the effective area (27) of which on the piston unit is small compared with the effective area (28) of the hydraulic chamber (21) on the piston unit (24).
  2. The machine press according to Claim 1, characterised in that the ratio of the effective areas (28; 27) of the hydraulic chamber (21) and of the pressurised fluid chamber (25) on the piston unit (24) is between 50 and 150.
  3. The machine press according to Claim 1 or 2, characterised in that the pressurised fluid chamber (25) is arranged - preferably centrally - inside the piston unit (24).
  4. The machine press according to Claim 3, characterised in that the pressurised fluid chamber (25) is sealed off from the cylindrical outer face (29) of an immersion tube (30), which penetrates to a greater or lesser depth into said chamber and is connected to the high-pressure gas reservoir (26).
  5. The machine press according to Claim 1 or 2, characterised in that the pressurised fluid chamber (25) is arranged as a cavity inside a projection (32) that is provided on the piston unit (24) and extends same.
  6. The machine press according to Claim 5, characterised in that the projection (32) projects into the hydraulic chamber (21).
  7. The machine press according to Claim 5 or 6, characterised in that the pressurised fluid chamber (25) is delimited by a sealing piston (33), which is guided in a sealing manner in the cavity.
  8. The machine press according to Claim 7, characterised in that the sealing piston (33) is arranged on the end of an immersion tube (34), which passes through the pressurised fluid chamber (25), and the projection (32) of the piston unit (24) is sealed off from the cylindrical outer face (35) of said immersion tube.
  9. The machine press according to any one of Claims 1 to 8, characterised in that the high-pressure gas reservoir (26) is in the form of a hydraulic reservoir, the oil side of which is connected to the pressurised fluid chamber (25).
  10. The machine press according to any one of Claims 1 to 9, characterised in that a hydropneumatic return stroke spring device acts on the upper die carrier, wherein a spring gas reservoir of the spring device is identical to the high-pressure gas reservoir (31).
  11. The machine press according to Claim 1 or 2, characterised in that a pressurised fluid chamber (25) is provided inside the cylindrical reservoir (22) on the side of the piston unit (24) that faces away from the hydraulic chamber (21), said chamber at the same time forming the volume of the high-pressure gas reservoir (36).
EP13728967.4A 2012-06-30 2013-06-07 Machine press Active EP2867009B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210013098 DE102012013098B4 (en) 2012-06-30 2012-06-30 machine press
PCT/EP2013/001678 WO2014000858A1 (en) 2012-06-30 2013-06-07 Machine press

Publications (2)

Publication Number Publication Date
EP2867009A1 EP2867009A1 (en) 2015-05-06
EP2867009B1 true EP2867009B1 (en) 2016-05-11

Family

ID=48626400

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13728967.4A Active EP2867009B1 (en) 2012-06-30 2013-06-07 Machine press

Country Status (6)

Country Link
US (1) US10421246B2 (en)
EP (1) EP2867009B1 (en)
JP (1) JP6012863B2 (en)
CN (1) CN104395064B (en)
DE (1) DE102012013098B4 (en)
WO (1) WO2014000858A1 (en)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PE20141415A1 (en) * 2011-03-21 2014-10-25 Shuanglai Yang LIFTING SYSTEM AND LIFTING METHOD FOR THE ARM OF THE OPERATING MACHINE AND OPERATING MACHINE
DE102014005352B4 (en) 2014-04-11 2016-03-10 Hoerbiger Automatisierungstechnik Holding Gmbh machine press
DE102015211796A1 (en) * 2015-06-25 2016-12-29 Robert Bosch Gmbh Hydraulic system for supplying pressure to a hydraulic cylinder with three separate pressure-sensitive surfaces and method for operating the hydraulic system
DE102015011209B4 (en) * 2015-08-26 2021-03-18 Horst Baltschun Hydraulic press
DE202015106161U1 (en) 2015-11-13 2015-11-27 Hoerbiger Automatisierungstechnik Holding Gmbh Electrohydraulic drive unit
DE102016118853B3 (en) * 2016-10-05 2017-10-26 Hoerbiger Automatisierungstechnik Holding Gmbh Electrohydraulic drive unit
DE102016118854A1 (en) 2016-10-05 2018-04-05 Hoerbiger Automatisierungstechnik Holding Gmbh Electrohydraulic drive unit
DE102017103091B4 (en) 2017-02-15 2019-05-16 Hoerbiger Automatisierungstechnik Holding Gmbh machine press
US10920795B2 (en) * 2018-11-23 2021-02-16 The Boeing Company Bootstrap hydraulic reservoir
DE102021123914A1 (en) 2021-09-15 2023-03-16 HMS - Hybrid Motion Solutions GmbH Hydraulic drive system with a 2x2Q pump unit
DE102021123910A1 (en) 2021-09-15 2023-03-16 HMS - Hybrid Motion Solutions GmbH Hydraulic drive system with a 4Q pump unit
US20230373714A1 (en) * 2022-05-23 2023-11-23 Ab Närpes Trä & Metall - Oy Närpiön Puu Ja Metalli Refuse compression apparatus and a method for operating refuse compression apparatus

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2413876A (en) * 1945-07-12 1947-01-07 Bendix Aviat Corp Hydraulic press
US3669151A (en) * 1969-11-25 1972-06-13 Kiddle Walter & Co Inc Hydraulic system accumulator arrangement
US3875365A (en) * 1970-10-30 1975-04-01 Donald Joseph Beneteau Pressure intensifier cylinder
FR2323478A1 (en) * 1975-09-10 1977-04-08 Jambon Anciens Ateliers H HYDRAULIC PRESS FOR SHEARING OR CUTTING OPERATION
DE2623428A1 (en) * 1976-05-25 1977-12-08 Transform Verstaerkungsmasch PROCEDURE FOR IMPACT OR SLOT PRESSES AND DEVICE FOR IT
US4209987A (en) * 1978-07-18 1980-07-01 Bocharov Jury A Hydraulic screw press drive
JPS5992198A (en) * 1982-11-15 1984-05-28 Sumitomo Heavy Ind Ltd Hydraulic press having pneumatic-hydraulic booster
US4777800A (en) * 1984-03-05 1988-10-18 Vetco Gray Inc. Static head charged hydraulic accumulator
SE509100C2 (en) * 1997-04-08 1998-12-07 Sunds Defibrator Ind Ab Hydraulic system for press
JPH11197779A (en) * 1998-01-14 1999-07-27 Komatsu Ltd Hydraulic pressure generating device for full enclosed die forging
CA2422879A1 (en) * 2000-09-20 2003-03-19 Laeis Bucher Gmbh Controller for a hydraulic press and method for the operation thereof
JP2005307999A (en) * 2004-04-16 2005-11-04 Ryoei Engineering Kk Oil pressure controller
AT8633U1 (en) 2005-09-19 2006-10-15 Hoerbiger Automatisierungstech HYDRAULIC DRIVE UNIT
US7520129B2 (en) * 2006-11-07 2009-04-21 Varco I/P, Inc. Subsea pressure accumulator systems
EP2215368B1 (en) * 2007-11-15 2016-01-27 Hoerbiger Automatisierungstechnik Holding GmbH Electrohydraulic booster
DE102009052531A1 (en) 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh machine press
RU2434159C1 (en) * 2010-03-17 2011-11-20 Александр Анатольевич Строганов Conversion method of heat to hydraulic energy and device for its implementation

Also Published As

Publication number Publication date
DE102012013098B4 (en) 2014-08-07
JP2015522422A (en) 2015-08-06
DE102012013098A1 (en) 2014-01-02
WO2014000858A1 (en) 2014-01-03
US10421246B2 (en) 2019-09-24
JP6012863B2 (en) 2016-10-25
US20150107466A1 (en) 2015-04-23
CN104395064A (en) 2015-03-04
CN104395064B (en) 2017-05-24
EP2867009A1 (en) 2015-05-06

Similar Documents

Publication Publication Date Title
EP2867009B1 (en) Machine press
EP2498982B1 (en) Machine press
AT505724B1 (en) DRIVE DEVICE FOR A BEND PRESS
AT509239B1 (en) DRIVE DEVICE FOR A BEND PRESS
DE102012015118B3 (en) machine press
EP3491253A1 (en) Electro-hydrostatic drive system
DE102009043034A1 (en) Prestressed hydraulic drive with variable speed pump
EP3174650A1 (en) Punching device and method for punching a workpiece
DE102005032297A1 (en) Piston-cylinder arrangement
WO2002053920A2 (en) Pressure transformer
DE202015106161U1 (en) Electrohydraulic drive unit
EP0696960B1 (en) Press-driven tool module, in particular press-driven cross-punching or bending unit
EP2934784B1 (en) Forming press
DE102016007266A1 (en) Device for direct recuperation of hydraulic energy by means of a single-acting hydraulic cylinder
DE3032430A1 (en) Fluid control valve pressure intensifier - uses four-two way valve connected to three-two way delay valves which provide reversal at preset pressure
EP2229537B1 (en) Hydraulic drive device having two pressure chambers and method for operating a hydraulic drive device having two pressure chambers
DE2916191A1 (en) POWER UNIT AS A DRIVE DEVICE, e.g. FOR FORMING, DEFORMING, COMPRESSING, HITING AND DRIVING
DE10026616B4 (en) Pressure booster, in particular hydropneumatic pressure booster
DE2654425A1 (en) Swinging axle for excavator - has pneumatically operated slide valve to change from working to travelling positions
DE4109407C2 (en) Device for precision forging on single-acting forming machines
DE4227640A1 (en) Press for the production of dimensionally stable compacts
EP0281904A1 (en) Device for limiting the stroke of the piston for the compression at a friction clutch for a friction screw press
EP2008898A1 (en) Electrically controllable assembly with a hydraulic connection
EP3338909B1 (en) Forging device
EP4026689A1 (en) Hydraulic drive unit for a press

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

17P Request for examination filed

Effective date: 20150110

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL 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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: B30B 15/16 20060101AFI20160113BHEP

Ipc: F15B 1/26 20060101ALI20160113BHEP

Ipc: F15B 3/00 20060101ALI20160113BHEP

Ipc: F15B 11/072 20060101ALI20160113BHEP

Ipc: F15B 1/24 20060101ALI20160113BHEP

INTG Intention to grant announced

Effective date: 20160202

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): AL 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 RS 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: CH

Ref legal event code: EP

Ref country code: CH

Ref legal event code: NV

Representative=s name: GRAETTINGER MOEHRING VON POSCHINGER PATENTANWA, CH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 798306

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160515

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: DE

Ref legal event code: R096

Ref document number: 502013002973

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 4

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160511

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

Ref country code: NO

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: 20160811

Ref country code: FI

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: 20160511

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: 20160511

Ref country code: NL

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: 20160511

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: 20160511

Ref country code: ES

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: 20160511

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: 20160511

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: 20160511

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: 20160812

Ref country code: RS

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: 20160511

Ref country code: PT

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: 20160912

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

Ref country code: IT

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: 20160511

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

Ref country code: CZ

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: 20160511

Ref country code: DK

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: 20160511

Ref country code: RO

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: 20160511

Ref country code: SK

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: 20160511

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: 20160511

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013002973

Country of ref document: DE

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

Ref country code: PL

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: 20160511

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: 20160511

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

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: 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: 20160511

26N No opposition filed

Effective date: 20170214

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

Ref country code: SI

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: 20160511

Ref country code: IE

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

Effective date: 20160607

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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

Ref country code: CH

Payment date: 20170626

Year of fee payment: 5

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

Ref country code: BE

Payment date: 20170621

Year of fee payment: 5

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCAR

Free format text: NEW ADDRESS: LOCHSTRASSE 19, 8268 SALENSTEIN (CH)

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170607

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

Ref country code: GB

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

Effective date: 20170607

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

Ref country code: HU

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

Effective date: 20130607

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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: 20160511

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: 20160511

Ref country code: LU

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

Effective date: 20160607

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: 20160511

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: 20160511

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

Ref country code: BG

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: 20160511

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

Ref country code: AL

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: 20160511

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180630

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

Ref country code: LI

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

Effective date: 20180630

Ref country code: CH

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

Effective date: 20180630

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502013002973

Country of ref document: DE

Representative=s name: GROSSE, SCHUMACHER, KNAUER, VON HIRSCHHAUSEN, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 502013002973

Country of ref document: DE

Owner name: HAWE ALTENSTADT HOLDING GMBH, DE

Free format text: FORMER OWNER: HOERBIGER AUTOMATISIERUNGSTECHNIK HOLDING GMBH, 86972 ALTENSTADT, DE

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

Ref country code: BE

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

Effective date: 20180630

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 798306

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180607

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

Ref country code: AT

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

Effective date: 20180607

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

Ref country code: FR

Payment date: 20210621

Year of fee payment: 9

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

Ref country code: FR

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

Effective date: 20220630

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

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

Ref country code: DE

Payment date: 20230627

Year of fee payment: 11

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

Ref country code: TR

Payment date: 20230601

Year of fee payment: 11