EP3338909B1 - Forging device - Google Patents

Forging device Download PDF

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Publication number
EP3338909B1
EP3338909B1 EP17208876.7A EP17208876A EP3338909B1 EP 3338909 B1 EP3338909 B1 EP 3338909B1 EP 17208876 A EP17208876 A EP 17208876A EP 3338909 B1 EP3338909 B1 EP 3338909B1
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EP
European Patent Office
Prior art keywords
hydraulic
forging
drive
cushion
lift drive
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EP17208876.7A
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German (de)
French (fr)
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EP3338909A1 (en
Inventor
Robert Koppensteiner
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GFM GmbH
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GFM GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/18—Drives for forging presses operated by making use of gearing mechanisms, e.g. levers, spindles, crankshafts, eccentrics, toggle-levers, rack bars
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/28—Drives for hammers; Transmission means therefor for power hammers operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
    • 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
    • B30B1/263—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 work stroke adjustment means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—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
    • B30B1/265—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 using a fluid connecting unit between drive shaft and press ram

Definitions

  • the invention relates to a forging device with at least one longitudinally guided forging punch, with a mechanical lifting drive for the forging punch, which is mounted displaceably in relation to the mechanical lifting drive, and with a hydraulic cushion which is arranged between the forging punch and the mechanical lifting drive and is connected to a hydraulic line provided with a control valve. which has at least one hydraulic cylinder, the pressure chamber of which is connected to the hydraulic cushion via the hydraulic line.
  • a shifting clutch in the drive train or an additional hydraulic drive connected via a hydraulic line to the hydraulic cylinder between the forging punches and their mechanical drives is provided, between which and the hydraulic cylinder hydraulic medium is pumped back and forth in order to lift of the mechanical lifting drive same but opposite stroke of
  • Hydraulic cylinder to prevent the effect of the mechanical lifting drive on the forging die.
  • this requires a complex hydraulic system.
  • the invention is therefore based on the object of designing a forging device with forging punches supported on mechanical lifting drives via hydraulic cushions in such a way that, with comparatively little design effort, not only the stroke position, but also in particular the stroke amplitude and the deformation rate can be influenced in a variety of ways.
  • the additional hydraulic drive consists only of at least one hydraulic cylinder, the pressure chamber of which is connected to the hydraulic cushion via the hydraulic line, the piston of this hydraulic cylinder being actuated as a function of the lifting movement of the mechanical lifting drive and the travel caused by the capacity of the pressure chamber of the hydraulic cylinder of the hydraulic cushion is smaller than the stroke of the mechanical lifting drive, the design effort is significantly reduced due to the omission of a separate hydraulic fluid system.
  • the hydraulic medium is only conveyed back and forth between the hydraulic cushion and the hydraulic cylinder depending on the activation of the control valve, which means that the mechanical lifting drive is superimposed by a hydraulic drive, because the hydraulic drive between the forging die and the mechanical lifting drive can be built up and dismantled Hydraulic cushion is effective as a lifting drive, with the help of which the stroke amplitude and the deformation rate during the forging stroke can be influenced in particular.
  • the volume of the pressure chamber of the hydraulic cylinder is decisive for the adjustment size of the hydraulic cushion.
  • the amplitude of the forging stroke must therefore be reduced by moving the hydraulic medium from the Hydraulic cushion in the pressure chamber of the hydraulic cylinder-related adjustment path of the forging stamp correspond to the reduction in the amplitude of the mechanical lifting drive.
  • the mechanical lifting drive comprises an eccentric drive with a sliding block which is rotatably mounted on the eccentric and which acts on the piston of the hydraulic cylinder with a sliding surface facing away from the forging die. If in this case the hydraulic line is released by the control valve, the eccentric drive forces hydraulic medium out of the hydraulic cushion into the hydraulic cylinder, the piston of which is released by the sliding block of the eccentric drive, so that the pressure chamber of the hydraulic cylinder decreases according to the amount of oil displaced from the hydraulic cushion increased by a piston adjustment. The synchronization of the piston actuation of the hydraulic cylinder with the eccentric drive is therefore specified.
  • the adjustment size of the hydraulic cushion that is possible in each case depends on the capacity of the pressure chamber of the hydraulic cylinder.
  • the hydraulic line of the hydraulic cushion can be connected via a respective control valve to a plurality of hydraulic cylinders which can be actuated as a function of the lifting movement of the mechanical lifting drive.
  • particularly advantageous conditions arise when the hydraulic cylinders have pressure chambers with different hydraulic volumes, so that different displacement volumes can be made available for the hydraulic medium from the hydraulic cushion by activating individual hydraulic cylinders.
  • the hydraulic cylinders can have a common, stepped housing with a stepped piston which is acted upon as a function of the lifting movement of the mechanical lifting drive.
  • a stepped piston is acted upon by the sliding block via its sliding surface facing away from the forging die.
  • the forging punch By supplying and discharging certain amounts of hydraulic fluid, the forging punch is displaced in relation to the mechanical lifting drive via the hydraulic cushion, which, when using servo valves as control valves, creates the possibility of reducing the speed of the forging punch during the working stroke compared to the speed profile specified by the mechanical lifting drive and thus the deformation speed to change, which, however, can cause considerable stress on the control valves.
  • the mechanical lifting drive can be driven by an electric servo motor, which allows the speed profile to be changed over the stroke of the mechanical lifting drive independently of the control of the hydraulic cushion.
  • the forging device comprises a forging die 2, which is guided longitudinally in a housing 1 and forms a receptacle 3, indicated purely schematically, for a forging tool, as well as a mechanical one Lifting drive 4, which is designed as an eccentric drive with an eccentric 5 and a sliding block 6 mounted on the eccentric.
  • the sliding block 6 does not act directly on the forging punch 2 with its sliding surface 7 facing the forging punch 2, but via a hydraulic cushion 8, which is determined by the pressure chamber of a cylinder 9, which is guided in the housing 1 and can be displaced coaxially with the forging punch 2, into which the forging punch 2 engages with its end forming a piston 10 .
  • the hydraulic cushion 8 is connected via a hydraulic line 11 and a control valve 12 to the pressure chamber 13 of a hydraulic cylinder 14 , the piston 15 of which is supported on the sliding surface 16 of the sliding block 6 facing away from the forging die 2 .
  • the piston 15 is pressed against the sliding block 6 in a resilient manner.
  • the hydraulic cylinder 14 is connected to a pressure accumulator 18 via a switching valve 17, which causes the piston 15 to be acted upon by a hydraulic spring.
  • the system of the cylinder 9 for the hydraulic cushion 8 on the sliding block 6 is ensured in a similar way.
  • the forging punch 2 is supported on auxiliary pistons 19 which are acted upon by a hydraulic medium from a pressure accumulator, so that the forging punch 2 is held in contact with the sliding block 6 by means of a hydraulic spring with the hydraulic cushion 8 being interposed.
  • the forging punch 2 is driven exclusively via the eccentric drive 4 .
  • the height of the hydraulic cushion 8 determines the stroke position of the forging punch 2. Since an exchange of hydraulic fluid between the hydraulic cushion 8 and the hydraulic cylinder 14 is prevented when the control valve 12 is closed, the piston 15 must be pressurized via the pressure accumulator 18 in order to ensure that the piston 15 rests on the Sliding surface 16 of the sliding block 6 to secure. To do this, the switching valve 17 must be opened.
  • the displacement of the hydraulic medium from the hydraulic cushion 8 into the pressure chamber 13 of the hydraulic cylinder 14 reduces the height of the hydraulic cushion 8 and thus influences the actuating movement of the forging punch 2, the working stroke of which is reduced by the hydraulic cushion 8 in accordance with the actuating movement superimposed on the working stroke of the eccentric drive 4 .
  • the hydraulic medium is again displaced from the pressure chamber 13 of the hydraulic cylinder 14 into the hydraulic cushion 8.
  • control valve 12 is designed as a servo valve
  • the hydraulic medium flow between the hydraulic cushion 8 and the hydraulic cylinder 14 can be controlled, which allows the speed of the forging punch 2 to be changed during the working stroke and thus the deformation speed to be influenced.
  • Appropriate loading of the hydraulic cushion 8 also makes it possible to influence the stroke frequency, as is known per se. However, it is not only possible to reduce the stroke frequency, but also to double the stroke frequency of the forging punch 2 if the volumes of the hydraulic cushion 8 and the hydraulic cylinder 14 are adjusted and mutually coordinated and the hydraulic cushion 8 and the pressure accumulator 17 are controlled accordingly, if the Pressure accumulator 17 provides sufficient hydraulic fluid for an additional working stroke of the forging die 2 during the idle stroke of the mechanical lifting drive.
  • the embodiment after 2 differs from the after the 1 only in that the hydraulic cushion 8 interacts with a plurality of hydraulic cylinders 14 which are each connected to the hydraulic line 11 of the hydraulic cushion 8 via separately controllable control valves 12 .
  • a common, stepped housing 20 with a stepped piston 21 which cooperates with the individual hydraulic cylinders 14 piston sections forms. Since the pressure chambers 13 of the individual hydraulic cylinders 14 have different absorption volumes, the activation of the individual hydraulic cylinders 14 makes it possible to convey hydraulic medium back and forth in different quantities between the hydraulic cushion 8 and the individual hydraulic cylinders 14, which has a graduated influence on the movement of the forging punch 2 and thus allows a good adaptation of the forging device to different forging tasks. A further influence on the rate of deformation arises when the eccentric shaft of the eccentric drive 4 is driven by an electric servomotor, with the help of which the rotational speed for the eccentric 5 and thus the progression of the lifting speed can be controlled.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Description

Die Erfindung bezieht sich auf eine Schmiedevorrichtung mit wenigstens einem längsgeführten Schmiedestempel, mit einem mechanischen Hubantrieb für den gegenüber dem mechanischen Hubantrieb verschiebbar gelagerten Schmiedestempel und mit einem zwischen dem Schmiedestempel und dem mechanischen Hubantrieb angeordneten Hydraulikpolster, der an eine mit einem Steuerventil versehene Hydraulikleitung angeschlossen ist, der wenigstens einen Hydraulikzylinder aufweist, dessen Druckraum über die Hydraulikleitung mit dem Hydraulikpolster verbunden ist.The invention relates to a forging device with at least one longitudinally guided forging punch, with a mechanical lifting drive for the forging punch, which is mounted displaceably in relation to the mechanical lifting drive, and with a hydraulic cushion which is arranged between the forging punch and the mechanical lifting drive and is connected to a hydraulic line provided with a control valve. which has at least one hydraulic cylinder, the pressure chamber of which is connected to the hydraulic cushion via the hydraulic line.

Um die Hubfrequenz einer mit einem mechanischen Hubantrieb versehenen Schmiedevorrichtung bei konstantem mechanischen Hubantrieb verändern zu können, ist es bekannt ( AT 404 440 B ), den gegenüber dem mechanischen Hubantrieb in Hubrichtung verschiebbar gelagerten, ein Schmiedewerkzeug aufnehmenden Schmiedestempel über einen Hydraulikpolster gegenüber dem mechanischen Hubantrieb abzustützen und den Hydraulikpolster über ein Steuerventil mit einer Hydraulikmittelversorgungsanlage zu verbinden. Wird der Hydraulikpolster durch ein Öffnen des Steuerventils während eines Arbeitshubs des mechanischen Hubantriebs durch ein Verdrängen des Hydraulikmittels in die Hydraulikmittelversorgungsanlage abgebaut, so kann über den Hydraulikpolster keine Druckkraft auf den Schmiedestempel übertragen werden, sodass der Arbeitshub des mechanischen Hubantriebs keinen Arbeitshub des Schmiedestempels nach sich zieht. Erst beim Auffüllen des Hydraulikpolsters aus der Hydraulikmittelversorgungsanlage während des Leerhubs des mechanischen Hubantriebs kann bei gesperrtem Steuerventil im nachfolgenden Arbeitshub des mechanischen Hubantriebs ein Arbeitshub des Schmiedestempels erfolgen. Ein durch den Druckabbau des Hydraulikpolsters entstehender Leerhub bei jedem zweiten Arbeitshub des mechanischen Hubantriebs führt somit zu einer Halbierung der Hubfrequenz.In order to be able to change the stroke frequency of a forging device provided with a mechanical stroke drive with a constant mechanical stroke drive, it is known ( AT 404 440 B ), to support the forging die, which is mounted displaceably in relation to the mechanical lifting drive in the lifting direction and accommodates a forging tool, via a hydraulic cushion in relation to the mechanical lifting drive and to connect the hydraulic cushion to a hydraulic medium supply system via a control valve. If the hydraulic cushion is reduced by opening the control valve during a working stroke of the mechanical lifting drive by displacing the hydraulic medium into the hydraulic medium supply system, no pressure force can be transmitted to the forging punch via the hydraulic cushion, so that the working stroke of the mechanical lifting drive does not result in a working stroke of the forging punch . Only when the hydraulic cushion is filled from the hydraulic medium supply system during the idle stroke of the mechanical lifting drive can a working stroke of the forging punch take place with the control valve blocked in the subsequent working stroke of the mechanical lifting drive. On due to the pressure reduction of the hydraulic cushion The resultant idle stroke with every second working stroke of the mechanical lifting drive thus leads to a halving of the stroke frequency.

Zur Einstellung der Hublage der Schmiedewerkzeuge einer Schmiedevorrichtung ist es darüber hinaus bekannt ( AT 406 648 B ), den durch einen Exzenterantrieb beaufschlagbaren, ein Schmiedewerkzeug aufnehmenden Schmiedestempel zu teilen und zwischen den beiden Teilen des Schmiedestempels einen Hydraulikpolster vorzusehen, der über ein Steuerventil an eine Hydraulikanlage angeschlossen ist, sodass die Höhe des Hydraulikpolsters und damit der Abstand der beiden Schmiedestempelteile voneinander über die Hydraulikanlage eingestellt werden können. Neben der dadurch bedingten hydraulischen Hublagenverstellung ergibt sich ein hydraulischer Zusatzantrieb, der dem Exzentertrieb überlagert werden kann, was eine Beeinflussung der Verformungsverhältnisse und der Verformungsgeschwindigkeiten erlaubt. Nachteilig ist allerdings der mit der zusätzlichen Hydraulikanlage verbundene Konstruktions- und Steueraufwand. Um die Schmiedestempel einer Schmiedevorrichtung zusätzlich unabhängig von einem hierfür vorgesehenen mechanischen Hubantrieb, vorzugsweise einem Exzentertrieb, antreiben zu können, ist es schließlich bekannt ( EP 1 093 871 A2 , welche die Basis für den Oberbegriff des Anspruchs 1 bildet), zwischen den Schmiedestempeln und ihren mechanischen Hubantrieben einen an eine Hydraulikmittelanlage angeschlossenen Hydraulikzylinder vorzusehen, der bei abgeschaltetem mechanischen Hubantrieb und einer Druckbeaufschlagung über die Hydraulikmittelanlage einen hydraulischen Hubantrieb ermöglicht, bei seiner Sperrung jedoch einen Hydraulikpolster bildet, über den der Hub des mechanischen Hubantriebs auf den Schmiedestempel übertragen wird. Zum Abschalten des mechanischen Hubantriebs ist entweder eine Schaltkupplung im Antriebsstrang oder ein zusätzlicher, über eine Hydraulikleitung mit dem Hydraulikzylinder zwischen den Schmiedestempeln und deren mechanischen Antrieben verbundener hydraulischer Antrieb vorgesehen, zwischen dem und dem Hydraulikzylinder Hydraulikmittel hin-und hergepumpt wird, um mit einem zum Hub des mechanischen Hubantriebs gleichen, jedoch gegensinnigen Hub desIt is also known to adjust the stroke position of the forging tools of a forging device ( AT 406 648 B ), to divide the forging die, which can be acted upon by an eccentric drive and which accommodates a forging tool, and to provide a hydraulic cushion between the two parts of the forging die, which is connected to a hydraulic system via a control valve, so that the height of the hydraulic cushion and thus the distance between the two parts of the forging die exceed the Hydraulic system can be adjusted. In addition to the resulting hydraulic stroke position adjustment, there is a hydraulic additional drive that can be superimposed on the eccentric drive, which allows the deformation ratios and deformation speeds to be influenced. A disadvantage, however, is the construction and control effort associated with the additional hydraulic system. In order to be able to drive the forging punches of a forging device independently of a mechanical lifting drive provided for this purpose, preferably an eccentric drive, it is finally known ( EP 1 093 871 A2 , which forms the basis for the preamble of claim 1), to provide a hydraulic cylinder connected to a hydraulic system between the forging punches and their mechanical lifting drives, which allows a hydraulic lifting drive when the mechanical lifting drive is switched off and pressure is applied via the hydraulic system, but a hydraulic cushion when it is blocked forms, via which the stroke of the mechanical lifting drive is transmitted to the forging die. To switch off the mechanical lifting drive, either a shifting clutch in the drive train or an additional hydraulic drive connected via a hydraulic line to the hydraulic cylinder between the forging punches and their mechanical drives is provided, between which and the hydraulic cylinder hydraulic medium is pumped back and forth in order to lift of the mechanical lifting drive same but opposite stroke of

Hadraulikzylinder die Wirkung des mechanischen Hubantriebs auf den Schmiedestempel zu unterbinden. Allerdings ist hierfür eine aufwendige Hydraulikanlage erforderlich.Hydraulic cylinder to prevent the effect of the mechanical lifting drive on the forging die. However, this requires a complex hydraulic system.

Der Erfindung liegt somit die Aufgabe zugrunde, eine Schmiedevorrichtung mit über Hydraulikpolster an mechanischen Hubantrieben abgestützten Schmiedestempeln so auszugestalten, dass mit einem vergleichsweise geringen Konstruktionsaufwand in vielfältiger Weise nicht nur auf die Hublage, sondern insbesondere auch auf die Hubamplitude und die Verformungsgeschwindigkeit Einfluss genommen werden kann.The invention is therefore based on the object of designing a forging device with forging punches supported on mechanical lifting drives via hydraulic cushions in such a way that, with comparatively little design effort, not only the stroke position, but also in particular the stroke amplitude and the deformation rate can be influenced in a variety of ways.

Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved with the features of claim 1.

Da der zusätzliche hydraulische Antrieb lediglich aus wenigstens einem Hydraulikzylinder besteht, dessen Druckraum über die Hydraulikleitung mit dem Hydraulikpolster verbunden ist, wobei der Kolben dieses Hydraulikzylinders in Abhängigkeit von der Hubbewegung des mechanischen Hubantriebs betätigt wird und wobei der durch das Aufnahmevolumen des Druckraums des Hydraulikzylinders bedingte Stellweg des Hydraulikpolsters kleiner als der Hub des mechanischen Hubantriebs ist, reduziert sich der Konstruktionsaufwand durch den Wegfall einer gesonderten Hydraulikmittelanlage erheblich. Das Hydraulikmittel wird ja lediglich in Abhängigkeit von der Ansteuerung des Steuerventils zwischen dem Hydraulikpolster und dem Hydraulikzylinder hin-und hergefördert, was eine Überlagerung des mechanischen Hubantriebs durch einen hydraulischen Antrieb mit sich bringt, weil der zwischen dem Schmiedestempel und dem mechanischen Hubantrieb auf- und abbaubare Hydraulikpolster als Hubtrieb wirksam ist, mit dessen Hilfe insbesondere auf die Hubamplitude und auf die Verformungsgeschwindigkeit während des Schmiedehubs Einfluss genommen werden kann. Das Aufnahmevolumen des Druckraums des Hydraulikzylinders ist für die Verstellgröße des Hydraulikpolsters maßgebend. Bei einem vorgegebenen Hub des mechanischen Hubantriebs muss zur Verringerung der Amplitude des Schmiedehubs demnach der durch die Verlagerung des Hydraulikmittels vom Hydraulikpolster in den Druckraum des Hydraulikzylinders bedingte Stellweg des Schmiedestempels der Verringerung der Amplitude des mechanischen Hubantriebs entsprechen. Dies bedeutet, dass der durch das Aufnahmevolumen des Druckraums des Hydraulikzylinders bedingte Stellweg des Hydraulikpolsters kleiner als der Hub des mechanischen Antriebs sein muss.Since the additional hydraulic drive consists only of at least one hydraulic cylinder, the pressure chamber of which is connected to the hydraulic cushion via the hydraulic line, the piston of this hydraulic cylinder being actuated as a function of the lifting movement of the mechanical lifting drive and the travel caused by the capacity of the pressure chamber of the hydraulic cylinder of the hydraulic cushion is smaller than the stroke of the mechanical lifting drive, the design effort is significantly reduced due to the omission of a separate hydraulic fluid system. The hydraulic medium is only conveyed back and forth between the hydraulic cushion and the hydraulic cylinder depending on the activation of the control valve, which means that the mechanical lifting drive is superimposed by a hydraulic drive, because the hydraulic drive between the forging die and the mechanical lifting drive can be built up and dismantled Hydraulic cushion is effective as a lifting drive, with the help of which the stroke amplitude and the deformation rate during the forging stroke can be influenced in particular. The volume of the pressure chamber of the hydraulic cylinder is decisive for the adjustment size of the hydraulic cushion. For a given stroke of the mechanical lifting drive, the amplitude of the forging stroke must therefore be reduced by moving the hydraulic medium from the Hydraulic cushion in the pressure chamber of the hydraulic cylinder-related adjustment path of the forging stamp correspond to the reduction in the amplitude of the mechanical lifting drive. This means that the travel of the hydraulic cushion caused by the capacity of the pressure chamber of the hydraulic cylinder must be smaller than the stroke of the mechanical drive.

Besonders einfache Konstruktionsbedingungen ergeben sich, wenn der mechanische Hubantrieb einen Exzentertrieb mit einem auf dem Exzenter drehbar gelagerten Gleitstein umfasst, der mit einer dem Schmiedestempel abgewandten Gleitfläche den Kolben des Hydraulikzylinders beaufschlagt. Wird nämlich in diesem Fall die Hydraulikleitung durch das Steuerventil freigegeben, so wird durch den Exzentertrieb Hydraulikmittel aus dem Hydraulikpolster in den Hydraulikzylinder verdrängt, dessen Kolben durch den Gleitstein des Exzentertriebs freigegeben wird, sodass sich der Druckraum des Hydraulikzylinders entsprechend der aus dem Hydraulikpolster verdrängten Ölmenge unter einer Kolbenverstellung vergrößert. Die Synchronisation der Kolbenbetätigung des Hydraulikzylinders mit dem Exzentertrieb ist daher vorgegeben.Particularly simple design conditions arise when the mechanical lifting drive comprises an eccentric drive with a sliding block which is rotatably mounted on the eccentric and which acts on the piston of the hydraulic cylinder with a sliding surface facing away from the forging die. If in this case the hydraulic line is released by the control valve, the eccentric drive forces hydraulic medium out of the hydraulic cushion into the hydraulic cylinder, the piston of which is released by the sliding block of the eccentric drive, so that the pressure chamber of the hydraulic cylinder decreases according to the amount of oil displaced from the hydraulic cushion increased by a piston adjustment. The synchronization of the piston actuation of the hydraulic cylinder with the eccentric drive is therefore specified.

Wie bereits ausgeführt wurde, hängt die jeweils mögliche Verstellgröße des Hydraulikpolsters vom Aufnahmevolumen des Druckraums des Hydraulikzylinders ab. Um diese Abhängigkeit für verschiedene Verstellgrößen in einfacher Art nützen zu können, kann die Hydraulikleitung des Hydraulikpolsters über je ein Steuerventil mit mehreren in Abhängigkeit von der Hubbewegung des mechanischen Hubantriebs betätigbaren Hydraulikzylindern verbunden sein. Besonders vorteilhafte Bedingungen ergeben sich in diesem Zusammenhang, wenn die Hydraulikzylinder Druckräume mit unterschiedlichen Hydraulikvolumen aufweisen, sodass durch das Ansteuern einzelner Hydraulikzylinder jeweils unterschiedliche Verdrängungsvolumen für das Hydraulikmittel aus dem Hydraulikpolster zur Verfügung gestellt werden können.As has already been explained, the adjustment size of the hydraulic cushion that is possible in each case depends on the capacity of the pressure chamber of the hydraulic cylinder. In order to be able to use this dependency for different adjustment values in a simple manner, the hydraulic line of the hydraulic cushion can be connected via a respective control valve to a plurality of hydraulic cylinders which can be actuated as a function of the lifting movement of the mechanical lifting drive. In this context, particularly advantageous conditions arise when the hydraulic cylinders have pressure chambers with different hydraulic volumes, so that different displacement volumes can be made available for the hydraulic medium from the hydraulic cushion by activating individual hydraulic cylinders.

Damit alle eingesetzten Hydraulikzylinder synchron zum mechanischen Hubantrieb betätigt werden können, können die Hydraulikzylinder ein gemeinsames, abgestuftes Gehäuse mit einem Stufenkolben aufweisen, der in Abhängigkeit von der Hubbewegung des mechanischen Hubantriebs beaufschlagt wird. Dies bedeutet bei einem Einsatz eines Exzentertriebs als mechanischen Hubantrieb, dass der Stufenkolben durch den Gleitstein über dessen dem Schmiedestempel abgewandte Gleitfläche beaufschlagt wird.So that all the hydraulic cylinders used can be actuated synchronously with the mechanical lifting drive, the hydraulic cylinders can have a common, stepped housing with a stepped piston which is acted upon as a function of the lifting movement of the mechanical lifting drive. When using an eccentric drive as a mechanical lifting drive, this means that the stepped piston is acted upon by the sliding block via its sliding surface facing away from the forging die.

Durch das Zu- und Abführen bestimmter Hydraulikmittelmengen wird der Schmiedestempel über den Hydraulikpolster gegenüber dem mechanischen Hubantrieb verlagert, was beim Einsatz von Servoventilen als Steuerventile die Möglichkeit schafft, die Geschwindigkeit des Schmiedestempels während des Arbeitshubs gegenüber dem durch den mechanischen Hubantrieb vorgegebenen Geschwindigkeitsverlauf und damit die Verformungsgeschwindigkeit zu ändern, was allerdings erhebliche Beanspruchungen der Steuerventile mit sich bringen kann. Zur Vermeidung einer allfälligen Überlastung der Steuerventile, aber auch zu einer weitergehenden Anpassung der Verformungsgeschwindigkeit an besondere Anforderungen kann der mechanische Hubantrieb durch einen elektrischen Servomotor angetrieben werden, der eine von der Ansteuerung des Hydraulikpolsters unabhängige Änderung des Geschwindigkeitsverlaufs über den Hub des mechanischen Hubantriebs erlaubt.By supplying and discharging certain amounts of hydraulic fluid, the forging punch is displaced in relation to the mechanical lifting drive via the hydraulic cushion, which, when using servo valves as control valves, creates the possibility of reducing the speed of the forging punch during the working stroke compared to the speed profile specified by the mechanical lifting drive and thus the deformation speed to change, which, however, can cause considerable stress on the control valves. To avoid any overloading of the control valves, but also to further adapt the deformation speed to special requirements, the mechanical lifting drive can be driven by an electric servo motor, which allows the speed profile to be changed over the stroke of the mechanical lifting drive independently of the control of the hydraulic cushion.

In der Zeichnung ist der Erfindungsgegenstand beispielsweise dargestellt. Es zeigen

Fig. 1
eine erfindungsgemäße Schmiedevorrichtung in einem schematischen
Axialschnitt und
Fig. 2
eine der Fig. 1 entsprechende Darstellung einer Ausführungsvariante
einer erfindungsgemäßen Schmiedevorrichtung.
In the drawing, the subject of the invention is shown as an example. Show it
1
a forging device according to the invention in a schematic
axial section and
2
one of the 1 corresponding representation of a variant
a forging device according to the invention.

Die Schmiedevorrichtung nach der Fig. 1 umfasst einen in einem Gehäuse 1 längsgeführten Schmiedestempel 2, der eine rein schematisch angedeutete Aufnahme 3 für ein Schmiedewerkzeug bildet, sowie einen mechanischen Hubantrieb 4, der als Exzenterantrieb mit einem Exzenter 5 und einem auf dem Exzenter gelagerten Gleitstein 6 ausgebildet ist. Der Gleitstein 6 wirkt mit seiner dem Schmiedestempel 2 zugekehrten Gleitfläche 7 nicht unmittelbar auf den Schmiedestempel 2 ein, sondern über einen Hydraulikpolster 8, der durch den Druckraum eines im Gehäuse 1 koaxial zum Schmiedestempel 2 verschiebbar geführten Zylinders 9 bestimmt wird, in den der Schmiedestempel 2 mit seinem einen Kolben 10 bildenden Ende eingreift.The forging device according to the 1 comprises a forging die 2, which is guided longitudinally in a housing 1 and forms a receptacle 3, indicated purely schematically, for a forging tool, as well as a mechanical one Lifting drive 4, which is designed as an eccentric drive with an eccentric 5 and a sliding block 6 mounted on the eccentric. The sliding block 6 does not act directly on the forging punch 2 with its sliding surface 7 facing the forging punch 2, but via a hydraulic cushion 8, which is determined by the pressure chamber of a cylinder 9, which is guided in the housing 1 and can be displaced coaxially with the forging punch 2, into which the forging punch 2 engages with its end forming a piston 10 .

Der Hydraulikpolster 8 ist über eine Hydraulikleitung 11 und ein Steuerventil 12 mit dem Druckraum 13 eines Hydraulikzylinders 14 verbunden, dessen Kolben 15 an der vom Schmiedestempel 2 abgekehrten Gleitfläche 16 des Gleitsteins 6 abgestützt ist. Damit eine stetige Anlage des Kolbens 15 am Gleitstein 6 sichergestellt wird, wird der Kolben 15 federnd an den Gleitstein 6 angedrückt. Zu diesem Zweck ist der Hydraulikzylinder 14 über ein Schaltventil 17 an einen Druckspeicher 18 angeschlossen, was eine Beaufschlagung des Kolbens 15 durch eine hydraulische Feder bewirkt. In ähnlicher Weise wird die Anlage des Zylinders 9 für den Hydraulikpolster 8 am Gleitstein 6 gewährleistet. Der Schmiedestempel 2 stützt sich auf Hilfskolben 19 ab, die von einem Druckspeicher mit einem Hydraulikmittel beaufschlagt werden, sodass der Schmiedestempel 2 mithilfe einer hydraulischen Feder unter Zwischenschaltung des Hydraulikpolsters 8 in Anlage am Gleitstein 6 gehalten wird.The hydraulic cushion 8 is connected via a hydraulic line 11 and a control valve 12 to the pressure chamber 13 of a hydraulic cylinder 14 , the piston 15 of which is supported on the sliding surface 16 of the sliding block 6 facing away from the forging die 2 . In order to ensure that the piston 15 is in constant contact with the sliding block 6 , the piston 15 is pressed against the sliding block 6 in a resilient manner. For this purpose, the hydraulic cylinder 14 is connected to a pressure accumulator 18 via a switching valve 17, which causes the piston 15 to be acted upon by a hydraulic spring. The system of the cylinder 9 for the hydraulic cushion 8 on the sliding block 6 is ensured in a similar way. The forging punch 2 is supported on auxiliary pistons 19 which are acted upon by a hydraulic medium from a pressure accumulator, so that the forging punch 2 is held in contact with the sliding block 6 by means of a hydraulic spring with the hydraulic cushion 8 being interposed.

Ist das Steuerventil 12 geschlossen und damit der Hydraulikpolster 8 abgesperrt, so wird der Schmiedestempel 2 ausschließlich über den Exzentertrieb 4 angetrieben. Die Höhe des Hydraulikpolsters 8 bestimmt die Hublage des Schmiedestempels 2. Da bei geschlossenem Steuerventil 12 ein Hydraulikmittelaustausch zwischen dem Hydraulikpolster 8 und dem Hydraulikzylinder 14 unterbunden wird, ist die Beaufschlagung des Kolbens 15 über den Druckspeicher 18 erforderlich, um die Anlage des Kolbens 15 an der Gleitfläche 16 des Gleitsteins 6 zu sichern. Dazu ist das Schaltventil 17 zu öffnen. Wird das Steuerventil 12 an der Hydraulikleitung 11 zwischen dem Hydraulikpolster 8 und dem Hydraulikzylinder 14 geöffnet und das Schaltventil 17 geschlossen, so wird während des Arbeitshubs des Exzentertriebs 4 Hydraulikmittel aus dem Hydraulikpolster 8 in den Hydraulikzylinder 14 verdrängt, dessen Druckraum 13 ein in Abhängigkeit vom Druckraum des Zylinders 9 für den Hydraulikpolster 8 gewähltes Volumen aufweist, sodass die Abnahme der Höhe des Hydraulikpolsters 8 dem Hubweg des Kolbens 15 des Hydraulikzylinders 14 entspricht. Durch die Verdrängung des Hydraulikmittels aus dem Hydraulikpolster 8 in den Druckraum 13 des Hydraulikzylinders 14 wird die Höhe des Hydraulikpolsters 8 verringert und damit die Stellbewegung des Schmiedestempels 2 beeinflusst, dessen Arbeitshub entsprechend der sich dem Arbeitshub des Exzentertriebs 4 überlagernden Stellbewegung durch den Hydraulikpolster 8 verringert wird. Während des Leerhubs des Exzentertriebs 4 wird das Hydraulikmittel wieder aus dem Druckraum 13 des Hydraulikzylinders 14 in den Hydraulikpolster 8 verdrängt.If the control valve 12 is closed and the hydraulic cushion 8 is thus shut off, the forging punch 2 is driven exclusively via the eccentric drive 4 . The height of the hydraulic cushion 8 determines the stroke position of the forging punch 2. Since an exchange of hydraulic fluid between the hydraulic cushion 8 and the hydraulic cylinder 14 is prevented when the control valve 12 is closed, the piston 15 must be pressurized via the pressure accumulator 18 in order to ensure that the piston 15 rests on the Sliding surface 16 of the sliding block 6 to secure. To do this, the switching valve 17 must be opened. If the control valve 12 on the hydraulic line 11 between the hydraulic cushion 8 and the hydraulic cylinder 14 is opened and the switching valve 17 is closed, then during the working stroke of the eccentric drive 4 Hydraulic medium is displaced from the hydraulic cushion 8 into the hydraulic cylinder 14, the pressure chamber 13 of which has a volume selected as a function of the pressure chamber of the cylinder 9 for the hydraulic cushion 8, so that the decrease in the height of the hydraulic cushion 8 corresponds to the stroke of the piston 15 of the hydraulic cylinder 14. The displacement of the hydraulic medium from the hydraulic cushion 8 into the pressure chamber 13 of the hydraulic cylinder 14 reduces the height of the hydraulic cushion 8 and thus influences the actuating movement of the forging punch 2, the working stroke of which is reduced by the hydraulic cushion 8 in accordance with the actuating movement superimposed on the working stroke of the eccentric drive 4 . During the idle stroke of the eccentric drive 4, the hydraulic medium is again displaced from the pressure chamber 13 of the hydraulic cylinder 14 into the hydraulic cushion 8.

Wird das Steuerventil 12 als Servoventil ausgebildet, so kann die Hydraulikmittelströmung zwischen dem Hydraulikpolster 8 und dem Hydraulikzylinder 14 gesteuert werden, was eine Veränderung der Geschwindigkeit des Schmiedestempels 2 während des Arbeitshubs und damit eine Einflussnahme auf die Verformungsgeschwindigkeit erlaubt. Durch eine entsprechende Beaufschlagung des Hydraulikpolsters 8 ist auch eine Einflussnahme auf die Hubfrequenz möglich, wie dies an sich bekannt ist. Es wird aber nicht nur eine Herabsetzung der Hubfrequenz, sondern bei einer angepassten, gegenseitigen Abstimmung der Volumen des Hydraulikpolsters 8 und des Hydraulikzylinders 14 und einer entsprechenden Ansteuerung des Hydraulikpolsters 8 sowie des Druckspeichers 17 auch eine Verdoppelung der Hubfrequenz des Schmiedestempels 2 möglich, wenn über den Druckspeicher 17 ausreichend Hydraulikmittel für einen zusätzlichen Arbeitshub des Schmiedestempels 2 während des Leerhubs des mechanischen Hubantriebs gesorgt wird.If the control valve 12 is designed as a servo valve, the hydraulic medium flow between the hydraulic cushion 8 and the hydraulic cylinder 14 can be controlled, which allows the speed of the forging punch 2 to be changed during the working stroke and thus the deformation speed to be influenced. Appropriate loading of the hydraulic cushion 8 also makes it possible to influence the stroke frequency, as is known per se. However, it is not only possible to reduce the stroke frequency, but also to double the stroke frequency of the forging punch 2 if the volumes of the hydraulic cushion 8 and the hydraulic cylinder 14 are adjusted and mutually coordinated and the hydraulic cushion 8 and the pressure accumulator 17 are controlled accordingly, if the Pressure accumulator 17 provides sufficient hydraulic fluid for an additional working stroke of the forging die 2 during the idle stroke of the mechanical lifting drive.

Die Ausführungsform nach der Fig. 2 unterscheidet sich von der nach der Fig. 1 lediglich dadurch, dass der Hydraulikpolster 8 mit mehreren Hydraulikzylindern 14 zusammenwirkt, die je über gesondert ansteuerbare Steuerventile 12 mit der Hydraulikleitung 11 des Hydraulikpolsters 8 verbunden sind. Zur Konstruktionsvereinfachung bilden die Hydraulikzylinder 14 gemäß der Fig. 2 ein gemeinsames, abgestuftes Gehäuse 20 mit einem Stufenkolben 21, der mit den einzelnen Hydraulikzylindern 14 zusammenwirkenden Kolbenabschnitte formt. Da die Druckräume 13 der einzelnen Hydraulikzylinder 14 ein unterschiedliches Aufnahmevolumen aufweisen wird es durch die Ansteuerung der einzelnen Hydraulikzylinder 14 möglich, Hydraulikmittel in unterschiedlichen Mengen zwischen dem Hydraulikpolster 8 und den einzelnen Hydraulikzylindern 14 hin- und herzufördern, was eine gestufte Einflussnahme auf die Bewegung des Schmiedestempels 2 und damit eine gute Anpassung der Schmiedevorrichtung an unterschiedliche Schmiedeaufgaben erlaubt. Eine weitere Einflussnahme auf die Verformungsgeschwindigkeit ergibt sich, wenn die Exzenterwelle des Exzentertriebs 4 durch einen elektrischen Servomotor angetrieben wird, mit dessen Hilfe sich die Drehgeschwindigkeit für den Exzenter 5 und damit der Verlauf der Hubgeschwindigkeit steuern lässt.The embodiment after 2 differs from the after the 1 only in that the hydraulic cushion 8 interacts with a plurality of hydraulic cylinders 14 which are each connected to the hydraulic line 11 of the hydraulic cushion 8 via separately controllable control valves 12 . To the Design simplification form the hydraulic cylinder 14 according to 2 a common, stepped housing 20 with a stepped piston 21 which cooperates with the individual hydraulic cylinders 14 piston sections forms. Since the pressure chambers 13 of the individual hydraulic cylinders 14 have different absorption volumes, the activation of the individual hydraulic cylinders 14 makes it possible to convey hydraulic medium back and forth in different quantities between the hydraulic cushion 8 and the individual hydraulic cylinders 14, which has a graduated influence on the movement of the forging punch 2 and thus allows a good adaptation of the forging device to different forging tasks. A further influence on the rate of deformation arises when the eccentric shaft of the eccentric drive 4 is driven by an electric servomotor, with the help of which the rotational speed for the eccentric 5 and thus the progression of the lifting speed can be controlled.

Claims (7)

  1. Forging device having at least one longitudinally guided forging die (2), having a mechanical lift drive for the forging die (2), which is mounted to be displaceable with respect to the mechanical lift drive, and having a hydraulic cushion (8) which is disposed between the forging die (2) and the mechanical lift drive and which is connected to a hydraulic line (11) of a hydraulic drive, the hydraulic line being provided with a control valve (12), the hydraulic drive comprising at least one hydraulic cylinder (14), the pressure chamber (13) of which is connected via the hydraulic line (11) to the hydraulic cushion (8), characterised in that the piston (15) of the hydraulic cylinder (14) can be actuated in dependence upon the lifting movement of the mechanical lift drive, and that the displacement of the hydraulic cushion (8), which is conditional upon the reception volume of the pressure chamber (13) of the hydraulic cylinder (14), is smaller than the lift of the mechanical lift drive.
  2. Forging device as claimed in claim 1, characterised in that the mechanical lift drive comprises an eccentric drive (4) with a slide block (6) which is rotatably mounted on the eccentric (5) and which acts upon the piston (15) of the hydraulic cylinder (14) by means of a sliding surface (16) facing away from the forging die (2).
  3. Forging device as claimed in claim 1 or 2, characterised in that the hydraulic line (11) of the hydraulic cushion (8) is connected via a respective control valve (12) to a plurality of hydraulic cylinders (14) which can be actuated in dependence upon the lifting movement of the mechanical lift drive.
  4. Forging device as claimed in claim 3, characterised in that the hydraulic cylinders (14) comprise pressure chambers (13) with different hydraulic volumes.
  5. Forging device as claimed in claim 3 or 4, characterised in that the hydraulic cylinders (14) comprise a common stepped housing (20) with a stepped piston (21) which can be actuated in dependence upon the lifting movement of the mechanical lift drive.
  6. Forging device as claimed in claims 2 and 5, characterised in that the stepped piston (21) can be acted upon by the sliding surface (16) of the slide block (6), which faces away from the forging die (2).
  7. Forging device as claimed in any one of claims 1 to 6, characterised in that the mechanical lift drive can be driven by an electric servomotor.
EP17208876.7A 2016-12-22 2017-12-20 Forging device Active EP3338909B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA51175/2016A AT519527B1 (en) 2016-12-22 2016-12-22 forge

Publications (2)

Publication Number Publication Date
EP3338909A1 EP3338909A1 (en) 2018-06-27
EP3338909B1 true EP3338909B1 (en) 2022-06-15

Family

ID=60702347

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17208876.7A Active EP3338909B1 (en) 2016-12-22 2017-12-20 Forging device

Country Status (2)

Country Link
EP (1) EP3338909B1 (en)
AT (1) AT519527B1 (en)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3005404A (en) * 1959-09-01 1961-10-24 Tucker & Sons Hydraulic connecting unit for punch-press rams
US4148209A (en) * 1978-04-07 1979-04-10 Kawasaki Yukoh Kabushiki Kaisha Forging press
AT404440B (en) * 1996-09-17 1998-11-25 Gfm Holding Ag METHOD FOR CONTROLLING THE STROKE FREQUENCY OF A FORGING MACHINE AND FORGING MACHINE FOR CARRYING OUT THE METHOD
AT407617B (en) * 1999-10-07 2001-05-25 Gfm Beteiligungs & Man Gmbh FORGING MACHINE

Also Published As

Publication number Publication date
EP3338909A1 (en) 2018-06-27
AT519527B1 (en) 2018-10-15
AT519527A1 (en) 2018-07-15

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