EP2258498A1 - Mechanical press for fine cutting, reforming and/or shaping workpieces - Google Patents
Mechanical press for fine cutting, reforming and/or shaping workpieces Download PDFInfo
- Publication number
- EP2258498A1 EP2258498A1 EP20090007351 EP09007351A EP2258498A1 EP 2258498 A1 EP2258498 A1 EP 2258498A1 EP 20090007351 EP20090007351 EP 20090007351 EP 09007351 A EP09007351 A EP 09007351A EP 2258498 A1 EP2258498 A1 EP 2258498A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- mechanical press
- press according
- frame
- motors
- phase synchronous
- 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.)
- Granted
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Classifications
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- 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
- B30B1/10—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 toggle mechanism
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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
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- 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
- B30B1/10—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 toggle mechanism
- B30B1/14—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 toggle mechanism operated by cams, eccentrics, or cranks
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/14—Control arrangements for mechanically-driven presses
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/26—Programme control arrangements
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/869—Means to drive or to guide tool
- Y10T83/8821—With simple rectilinear reciprocating motion only
- Y10T83/8841—Tool driver movable relative to tool support
- Y10T83/8845—Toggle links, one link pivoted to tool support
Definitions
- the invention relates to a mechanical press for fineblanking, forming and / or embossing of workpieces, comprising a machine frame composed of a head piece and an O-frame, a hanging attached to the head piece, extending into the O-frame fine blanking or forming head with a fixed thereto upper tool part, a guided in the O-frame vertically on a lifting axis plunger, which is provided with a table top for fixing a lower tool part, and arranged below the plunger toggle drive.
- a second tab is connected at one end to the plunger and at the other end to the connecting rod.
- the fixed bearing of this known modified toggle lever is located above the press ram and the pivot point associated with this fixed point pivots about this fixed point.
- the upper hinge point associated with the press ram describes a curved path.
- Such a modified toggle drive leads to a slowing of the plunger movement, so that the material remains at bottom dead center enough time for plastic flow.
- the disadvantage is that on the one hand the bearing for the connecting rod belonging to the tab and the plunger are on different mutually shifted axes and on the other hand, the fixed bearing for the eccentric shaft is arranged close to the plunger.
- the present invention seeks to provide a mechanical press for fineblanking, forming and embossing operations, the flywheel works in a wide nominal force range, the rigidity of the toggle lever at top dead center significantly improved, reduces the massiveness of the machine frame and with a significantly reduced drive power despite elimination of the flywheel manages.
- the solution according to the invention is based on the finding that the stroke axis of the plunger must be arranged on the axis of the fixed bearing for the triangular connecting rod, so that at the top dead center of the plunger, the articulated arms connecting the fixed bearing and the connecting rod and the plunger and the connecting rod reach a largely extended position can.
- the extended position of the articulated arms acting on the plunger horizontal force components take very low values, so that a largely optimal power transmission from the eccentric and motor on the plunger is made possible without significant loss and wear of the plunger.
- the substantially equilateral triangle formed connecting rod has two superimposed hinge points, of which the lower pivot point pivots about a disk-like lower articulated arm about a foot side arranged on the O-frame fixed bearing and the upper articulated arm associated with the ram with the lower disk-like articulated arm has a largely extended position relative to the lifting axis, the locating bearing of the lower articulated arm being located on the lifting axis of the ram and the connecting rod being assigned two eccentric shafts aligned with their axes and mounted in fixed bearings, the opposite shaft ends are connected to their simultaneous parallel drive with three-phase synchronous motors, the motors are adjustable to mutually equal path-time characteristics by means of a computer connected to the motors.
- designed as an O-frame stand of the machine frame has foot-side and parallel juxtaposed backpack-like pockets for the formation of the fixed bearing of the eccentric shaft and the horizontal connection of the three-phase synchronous motors.
- the mutually facing ends of the eccentric shafts are mechanically firmly connected to each other. This can advantageously be done by a coupling piece, which connects the two shaft ends with each other in a rotationally fixed.
- the three-phase synchronous motors are then horizontally aligned with their drive shafts in alignment with each other and are mechanically frictionally connected via one gear each having one end of the eccentric shaft.
- the three-phase synchronous motors are controlled by the computer as a unit, so that the required electrical values of the motors can be set so that the value-time characteristics of both motors are identical.
- the mutually facing ends of the eccentric shafts are not connected to each other, so are designed to be open.
- the three-phase synchronous motors then independently transmit their drive power gearless to the eccentric shafts.
- Each three-phase synchronous motor is controlled separately by the computer and set to identical path-time characteristics. But it can also be different path-time characteristics are selected to compensate for any tilting of the plunger with eccentric tool load.
- the head piece torsion on the O-frame is held by screw.
- the head piece and O-frame made of thin-walled high-strength ductile iron.
- Fig. 1 a partial representation of a toggle press according to the prior art
- Fig. 2 a schematic representation of the kinematics according to the prior art
- FIG. 3a and 3b schematic representations of the kinematics according to the invention at the top and bottom dead center
- Fig. 4 a perspective view of the machine frame of O-frame without mounted head piece with inserted ram and eccentric shafts
- Fig. 5 a section along the line AA the Fig. 4 .
- Fig. 6 a fragmentary perspective view of the machine frame with connected by eccentric shaft and gearbox three-phase synchronous motors
- Fig. 7 a section along the line BB of Fig. 6 and
- Fig. 8 a perspective view of the machine frame of O-frame and head piece.
- the Fig. 1 shows a toggle press 1 of the prior art, which is assumed.
- a plunger 3 is mounted vertically displaceable.
- a table 4 (see Fig. 2 ), which is mounted on the machine frame 2.
- the table 4 serves to receive a lower tool and the plunger 3 is adapted for receiving an upper tool.
- the plunger 3 is driven by a ram actuated, to which a modified toggle mechanism 5 belongs, which is driven by an eccentric shaft 6.
- This is driven by a gear means, such as a gear, and an electric motor.
- a gear means such as a gear
- an electric motor between the electric motor and the gear, an auxiliary gear, for example a planetary gear, can be arranged.
- the kinematics of the known toggle mechanism 5 goes out of the Fig. 1 and 2 out.
- a bearing point L1 eccentric shaft 6 On the rotatably mounted on a bearing point L1 eccentric shaft 6 is seated an eccentric 7.
- a connecting rod 8 is mounted with a corresponding connecting rod bearing 9.
- the connecting rod 8 has at its end remote from the eccentric 7 a head 10, on which two spaced-apart bearings 11 and 12 are formed.
- the bearings define a triangle with the center of the connecting rod bearing 9. This goes in particular from the Fig. 2 out.
- the corresponding distances are designated as distances E5, E6 and E8.
- the eccentricity of the eccentric 7 is the dimension E4.
- the eccentric shaft 6 is rotatable about a rotation axis D which is stationary in the machine frame 2.
- L1 denotes the fixed bearing for the eccentric shaft. 6
- the connecting rod 8 is connected via tabs or articulated arms 13 and 14 with the machine frame 2 and the plunger 3.
- the tab 13 is pivotally mounted by means of a bearing pin 15 at the connection portion 16 of the connecting rod 8 and at its other end with a bearing pin 17 fixed to the machine frame 2.
- This bearing pin 17 forms for the tab 13, the fixed bearing L2, which is thus arranged above the plunger 3 and 4 of the table.
- the tab 13 is with E7 in Fig. 2 designated.
- the tab 14 is pivotable at its one end about a bearing pin 18 in the terminal portions 19 of the connecting rod 8, while the other end of the tab 14 is pivotable about a bearing pin 20 in the plunger 3.
- the Fig. 3a to 3b schematically shows the kinematics of the toggle lever in the bottom and top dead center of the plunger in the press according to the invention.
- the plunger 3 carries a table top 21, at the one not shown lower tool part is fixed, so that the table top 21 performs with the tool part as well a lifting movement.
- the connecting rod 8 forms like the Fig.
- 3a and 3b schematically show an equilateral effective triangle DE whose base G denotes the head 10 of the connecting rod 8 and two superimposed hinge points 22 and 23 has.
- a disc-like articulated arm 24 is pivoted at one end thereof, while the other end of the articulated arm 24 is pivotally mounted in the hinge point 25 of the plunger 3.
- a fixed bearing FL1 In alignment with the vertical stroke axis HU of the plunger 3 is the base side of the machine frame 2, a fixed bearing FL1, in which a disk-like trained lower articulated arm 26 is fixedly mounted with its one end.
- the articulated arm 26 is thus pivotable about the bearing FL1.
- the other end of the articulated arm 26 is pivoted at the lower pivot point 23 of the connecting rod 8.
- a hinge point 28 on which the eccentric 7 engages, which is rotatable about a stationary bearing FL2 held on the machine frame 2.
- This bearing FL2 is approximately in alignment with the lower hinge point 23, so that the bearing FL1 of the lower articulated arm 26 and the bearing FL2 of the eccentric shaft 6 can be arranged in the foot or in the machine frame 2 and thus lie close to the center of gravity of the entire press structure.
- Fig. 3a is the plunger 3 in bottom dead center UT.
- the lower mounted in the bearing FL1 articulated arm 26 has completed a pivoting movement, which is indicated by the pivoting path S1.
- the articulated arms 24 and 26 have moves accordingly with their articulation points 22 and 23.
- the Fig. 3b shows the plunger 3 at top dead center OT.
- the articulated arms 24, 26 and the base side G of the connecting rod 8 take a largely extended position, which is characterized in that the deflection of the articulated arm 24 and 26 is only about 4 ° relative to the stroke axis HU of the plunger 3. This makes it possible to significantly minimize horizontal force components in the power transmission to the plunger 3, so that the power transmission from the drive to the plunger can be done largely without loss and at the same time the wear of the plunger 3 is reduced to its plunger guide.
- FIG. 4 the O-frame 29 of the machine frame 2 with mounted ram 3 is shown in perspective.
- the O-frame 29 is made of high-strength nodular cast iron.
- At the foot-side rear side of the O-frame 29 are each two with lateral openings 31 (see Fig. 8 ) provided, backpack-like pockets 30 formed.
- an eccentric shaft 6 is mounted, whose axes D are aligned with each other in alignment.
- the mutually facing shaft ends 32 of the two eccentric shafts 6 are rotatably connected to each other by a coupling piece 33 (see Fig. 6 ).
- Each of the eccentric shafts 6 engages in each case the disk-like connecting rod 8 inserted in the pockets 30, which is mounted on the eccentric shaft 6 by a connecting rod bearing.
- the pockets 30 on the O-frame 29 form the fixed bearing FL2 for the eccentric shafts 6 and support the following described synchronous three-phase motors 34 and 35 (see Fig. 6 ).
- Fig. 5 making a cut along the AA line of the Fig. 4 represents, illustrates the extended position of Fig. 3 schematically illustrated disc-like articulated arm 24 and 26 at the top dead center of the plunger. 3
- the Fig. 6 shows a fragmentary perspective view of the interconnected with the coupling piece 33, mutually facing shaft ends 32 of the eccentric shafts 6.
- the opposite ends 36 of the eccentric shafts 6 are respectively connected via a planetary gear 37 with the three-phase synchronous motors 34 and 35.
- a three-phase synchronous motors 34 and 35 can be used by the special kinematics of the toggle drive according to the invention small engines with high torques at low engine speeds without flywheel. Therefore, torque motors have proven particularly suitable.
- the parallel synchronous three-phase synchronous motors 34 and 35 are each connected to a computer belonging to the computer 38, which processes the machine data and the two motors identical path-time characteristics (see Fig. 7 ). This is done as follows.
- the setpoints which are based on the machine and process data of the fineblanking or forming process, are determined via a virtual master axis.
- the virtual axis is a non-existing drive whose speed and bearing values are determined by the computer and given to the motors as control variables in coordination with the process parameters.
- the two torque motors run as slave axes to the virtual master axis.
- the Fig. 8 shows the machine frame 2 in a perspective view. It is composed of the O-frame 29 and a head piece 39.
- the head piece 39 is placed on the O-frame 29 and fixed by means of high-strength screw 27 at the upper part of the O-frame 2 torsion-free. For this purpose, 29 holes are introduced with internal thread in the upper part of the O-frame, are screwed into the bolt with external thread.
- the head piece 39 is fixed by nuts screwed onto the bolts.
- the headpiece 39 is formed so that an unillustrated fine blanking or forming head can be mounted thereon with an upper tool part that can be positioned in a hanging position through the top opening of the O-frame 29 in height.
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Abstract
Description
Die Erfindung betrifft eine mechanische Presse zum Feinschneiden, Umformen und/oder Prägen von Werkstücken, mit einem aus einem Kopfstück und einem O-Gestell zusammengesetzten Maschinengestell, einem am Kopfstück hängend befestigten, in das O-Gestell hineinreichenden Feinschneid- oder Umformkopf mit einem daran fixierten oberen Werkzeugteil, einem im O-Gestell vertikal auf einer Hubachse geführten Stößel, der mit einer Tischplatte zur Befestigung eines unteren Werkzeugteils versehen ist, und einem unterhalb des Stößels angeordneten Kniehebelantrieb.The invention relates to a mechanical press for fineblanking, forming and / or embossing of workpieces, comprising a machine frame composed of a head piece and an O-frame, a hanging attached to the head piece, extending into the O-frame fine blanking or forming head with a fixed thereto upper tool part, a guided in the O-frame vertically on a lifting axis plunger, which is provided with a table top for fixing a lower tool part, and arranged below the plunger toggle drive.
Aus der
Von Nachteil ist jedoch, dass einerseits das Festlager für die zum Pleuel gehörige Lasche und der Stößel auf unterschiedliche zueinander verschobenen Achsen liegen und anderseits das Festlager für die Exzenterwelle nahe beim Stößel angeordnet ist. Dies führt dazu, dass im oberen Totpunkt keine weitgehende Strecklage der Laschen erreicht werden kann, so dass die Steifigkeit und damit die Kraftübertragung auf den Stößel immer mit horizontal wirkenden Kraftkomponenten einhergeht, wodurch der Stößelverschleiß und auch die Krafteinleitung in den Stößel erhöht werden muss. All dies hat wiederum nachteilige Folgen für das Maschinengestell, das massiver ausgeführt werden muss, und auf die Antriebsleistung von den Motoren, die höhere Drehmomente erbringen müssen.From the
The disadvantage, however, is that on the one hand the bearing for the connecting rod belonging to the tab and the plunger are on different mutually shifted axes and on the other hand, the fixed bearing for the eccentric shaft is arranged close to the plunger. This leads to the fact that in the top dead center no extensive stretched position of the tabs can be achieved, so that the rigidity and thus the Power transmission to the plunger is always associated with horizontally acting force components, whereby the plunger wear and also the introduction of force into the plunger must be increased. All this, in turn, has detrimental consequences for the machine frame, which must be made more massive, and on the drive power of the motors, which must provide higher torques.
Bei diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, ein mechanische Presse für Feinschneid-, Umform- und Prägevorgänge bereitzustellen, die schwungradlos in einem breiten Nennkraftbereich arbeitet, die Steifigkeit des Kniehebels im oberen Totpunkt deutlich verbessert, die Massivität des Maschinengestells reduziert und mit einer deutlich herabgesetzten Antriebsleistung trotz Wegfalls des Schwungrads auskommt.In this prior art, the present invention seeks to provide a mechanical press for fineblanking, forming and embossing operations, the flywheel works in a wide nominal force range, the rigidity of the toggle lever at top dead center significantly improved, reduces the massiveness of the machine frame and with a significantly reduced drive power despite elimination of the flywheel manages.
Diese Aufgabe wird durch eine Presse der eingangs genannten Gattung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a press of the type mentioned with the features of
Vorteilhafte Ausgestaltungen der erfindungsgemäßen Presse sind den Unteransprüchen entnehmbarAdvantageous embodiments of the press according to the invention can be taken from the subclaims
Der erfindungsgemäßen Lösung liegt die Erkenntnis zugrunde, dass die Hubachse des Stößels auf der Achse des Festlagers für den dreiecksartigen Pleuel angeordnet sein muss, damit im oberen Totpunkt des Stößels die das Festlager und das Pleuel sowie den Stößel und das Pleuel verbindenden Gelenkarme eine weitgehende Strecklage erreichen können.
In der Strecklage der Gelenkarme nehmen die auf den Stößel wirkenden horizontalen Kraftkomponenten sehr geringe Werte an, so dass eine weitgehend optimale Kraftübertragung vom Exzenter und Motor auf den Stößel ohne nennenswerten Verlust und Verschleiß des Stößels ermöglicht wird.
Dies wird dadurch erreicht, dass unterhalb des Stößels ein schwungradloser Kniehebelantrieb angeordnet ist, dessen im Wesentlichen gleichseitig ausgebildetes Wirkdreieck aufweisendes Pleuel zwei übereinander angeordnete Gelenkpunkte aufweist, von denen der untere Gelenkpunkt über einen scheibenartig ausgebildeten unteren Gelenkarm um ein fußseitig am O-Gestell angeordnetes Festlager schwenkt und der dem Stößel zugeordnete oberen Gelenkarm mit dem unteren scheibenartig ausgebildeten Gelenkarm im OT eine weitgehende Strecklage zur Hubachse einnimmt, wobei das Festlager des unteren Gelenkarms auf der Hubachse des Stößels liegt und dem Pleuel zwei mit ihren Achsen fluchtenden, in Festlagern gelagerten Exzenterwellen zugeordnet sind, deren abgewandte Wellenenden zu ihrem gleichzeitig parallelen Antrieb mit Drehstrom-Synchronmotoren verbunden sind, wobei die Motore auf untereinander gleiche Weg-Zeit-Kennwerte mittels eines mit den Motoren verbundenen Rechners einstellbar sind.The solution according to the invention is based on the finding that the stroke axis of the plunger must be arranged on the axis of the fixed bearing for the triangular connecting rod, so that at the top dead center of the plunger, the articulated arms connecting the fixed bearing and the connecting rod and the plunger and the connecting rod reach a largely extended position can.
In the extended position of the articulated arms acting on the plunger horizontal force components take very low values, so that a largely optimal power transmission from the eccentric and motor on the plunger is made possible without significant loss and wear of the plunger.
This is achieved in that below the plunger, a flywheel toggle lever drive is arranged, the substantially equilateral triangle formed connecting rod has two superimposed hinge points, of which the lower pivot point pivots about a disk-like lower articulated arm about a foot side arranged on the O-frame fixed bearing and the upper articulated arm associated with the ram with the lower disk-like articulated arm has a largely extended position relative to the lifting axis, the locating bearing of the lower articulated arm being located on the lifting axis of the ram and the connecting rod being assigned two eccentric shafts aligned with their axes and mounted in fixed bearings, the opposite shaft ends are connected to their simultaneous parallel drive with three-phase synchronous motors, the motors are adjustable to mutually equal path-time characteristics by means of a computer connected to the motors.
Von besonderer Bedeutung ist, dass die Festlager für die Exzenterwellen und den unteren Gelenkarmen fußseitig am O-Gestell angeordnet sind. Diese Maßnahme hat in Verbindung mit dem erfindungsgemäßen Antriebskonzept den außerordentlichen Vorteil, dass die Festlager am Fuß des Maschinengestells liegen und damit sehr nahe am Schwerpunkt des gesamten Pressenaufbaus. Dies ermöglicht, die Masse des Maschinengestells weiter zu reduzieren.Of particular importance is that the bearings for the eccentric shafts and the lower articulated arms are arranged on the foot side of the O-frame. This measure has in connection with the drive concept according to the invention the extraordinary advantage that the fixed bearing at the foot of the machine frame and thus very close to the center of gravity of the entire press structure. This makes it possible to further reduce the mass of the machine frame.
Nach einer weiteren Ausgestaltung der Erfindung besitzt der als O-Gestell ausgeführte Ständer des Maschinengestells fußseitig und parallel nebeneinander angeordnete rucksackartige Taschen für die Ausbildung der Festlager der Exzenterwelle und der horizontalen Anbindung der Drehstrom-Synchronmotoren.According to a further embodiment of the invention, designed as an O-frame stand of the machine frame has foot-side and parallel juxtaposed backpack-like pockets for the formation of the fixed bearing of the eccentric shaft and the horizontal connection of the three-phase synchronous motors.
In einer weiteren bevorzugten Ausführungsform der Erfindung sind die einander zugewandten Enden der Exzenterwellen mechanisch fest miteinander verbunden. Dies kann vorteilhaft durch ein Kupplungsstück erfolgen, das die beiden Wellenenden miteinander drehfest verbindet.In a further preferred embodiment of the invention, the mutually facing ends of the eccentric shafts are mechanically firmly connected to each other. This can advantageously be done by a coupling piece, which connects the two shaft ends with each other in a rotationally fixed.
Die Drehstrom-Synchronmotoren sind dann mit ihren Antriebswellen fluchtgenau horizontal zueinander ausgerichtet und über je ein Getriebe mit jeweils einem Ende der Exzenterwelle mechanisch kraftschlüssig verbunden. In diesem Fall werden die Drehstrom-Synchronmotoren durch den Rechner als eine Einheit angesteuert, so dass die erforderlichen elektrischen Werte der Motoren so eingestellt werden können, dass die Wert-Zeit-Kennlinien beider Motoren identisch sind.The three-phase synchronous motors are then horizontally aligned with their drive shafts in alignment with each other and are mechanically frictionally connected via one gear each having one end of the eccentric shaft. In this case, the three-phase synchronous motors are controlled by the computer as a unit, so that the required electrical values of the motors can be set so that the value-time characteristics of both motors are identical.
In einer weiteren Ausführungsform der Erfindung sind die einander zugewandten Enden der Exzenterwellen nicht miteinander verbunden, also offen ausgeführt sind.
Die Drehstrom-Synchronmotore übertragen dann unabhängig voneinander ihre Antriebsleistung getriebelos auf die Exzenterwellen. Jeder Drehstrom-Synchronmotor wird durch den Rechner separat angesteuert und auf miteinander identische Weg-Zeit-Kennlinien eingestellt. Es können aber auch unterschiedliche Weg-Zeit-Kennlinien gewählt werden, um eine eventuelle Kippung des Stößels bei exzentrischer Werkzeugbelastung zu kompensieren.In a further embodiment of the invention, the mutually facing ends of the eccentric shafts are not connected to each other, so are designed to be open.
The three-phase synchronous motors then independently transmit their drive power gearless to the eccentric shafts. Each three-phase synchronous motor is controlled separately by the computer and set to identical path-time characteristics. But it can also be different path-time characteristics are selected to compensate for any tilting of the plunger with eccentric tool load.
Es hat sich als zweckmäßig erwiesen, Drehstrom-Synchronmotore mit einem hohen Drehmoment bei geringer Motordrehzahl, beispielsweise Torquemotore, einzusetzen.It has proven to be expedient to use three-phase synchronous motors with a high torque at low engine speed, for example torque motors.
Es ist weiterhin von Vorteil, die Getriebe als Planetengetriebe auszuführen. Dies stellt eine geringe Massenträgheit bei hoher Kompaktheit sicher.It is also advantageous to carry out the transmission as a planetary gear. This ensures a low mass inertia with high compactness.
In weiterer bevorzugter Ausgestaltung der Erfindung ist das Kopfstück torsionsfrei am O-Gestell durch Schraubverbindungen gehalten. Zweckmäßigerweise besteht das Kopfstück und O-Gestell aus dünnwandigem hochfesten Sphäroguss.In a further preferred embodiment of the invention, the head piece torsion on the O-frame is held by screw. Conveniently, the head piece and O-frame made of thin-walled high-strength ductile iron.
Weitere Vorteile und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen.Further advantages and details of the invention will become apparent from the following description with reference to the accompanying drawings.
Die Erfindung soll nachstehend an einem Ausführungsbeispiel näher erläutert werden.
Es zeigtThe invention will be explained in more detail below using an exemplary embodiment.
It shows
Die
Der Stößel 3 wird durch einen Stößelantrieb betätigt, zu dem ein modifiziertes Kniehebelgetriebe 5 gehört, das von einer Exzenterwelle 6 angetrieben ist. Diese wird über ein Getriebemittel, beispielsweise ein Zahnrad, und über einen Elektromotor angetrieben. Zwischen dem Elektromotor und dem Zahnrad kann ein Vorsatzgetriebe, beispielsweise ein Planetengetriebe, angeordnet sein.The
Die Kinematik des bekannten Kniehebelgetriebes 5 geht aus den
Das Pleuel 8 ist über Laschen bzw. Gelenkarme 13 und 14 mit dem Maschinengestell 2 und dem Stößel 3 verbunden. Die Lasche 13 ist mittels eines Lagerbolzens 15 am Anschlussbereich 16 des Pleuels 8 schwenkbar und an seinem anderen Ende mit einem Lagerbolzen 17 ortsfest am Maschinengestell 2 gelagert. Dieser Lagerbolzen 17 bildet für die Lasche 13 das Festlager L2, das damit oberhalb des Stößels 3 und des Tisches 4 angeordnet ist. Die Lasche 13 ist mit E7 in
Die Lasche 14 ist an ihrem einen Ende um einen Lagerbolzen 18 in den Anschlußbereichen 19 des Pleuels 8 schwenkbar, während das andere Ende der Lasche 14 um einen Lagerbolzen 20 im Stößel 3 schwenkbar ist.The connecting
The
Das Festlager L2, also der ortsfeste Punkt, mit dem die Lasche 13 am Maschinengestell 2 festgelegt ist, liegt nicht auf der vertikalen Hubachse HU des Stößels 3. Dies führt dazu, dass die Laschen 13 und 14 keine ausreichende Strecklage am oberen Totpunkt OT erreichen, so dass auf den Stößel 3 entsprechende horizontale Kraftkomponenten einwirken, die nachteilig für die Lebensdauer des Stößels und seiner Führung sind und die dazu beitragen, dass die für den Feinschneid- oder Umformvorgang zur Verfügung stehende Nennpresskraft reduziert wird, was wiederum Antriebsaggregate mit höheren Drehmomenten erforderlich macht. Dies hat auch nachteilige Auswirkungen auf die Massivität der Maschinengestelle, das schwerer und stabiler ausgeführt werden muss, um die zusätzlichen horizontalen Kräfte aufnehmen zu können.The fixed bearing L2, so the fixed point with which the
Die
Die von zwei Drehstrom-Synchronmotore (siehe
Der Stößel 3 trägt eine Tischplatte 21, an der ein nicht dargestelltes unteres Werkzeugteil befestigt ist, so dass die Tischplatte 21 mit dem Werkzeugteil ebenso eine Hubbewegung ausführt.
Das Pleuel 8 bildet wie die
In Flucht der vertikalen Hubachse HU des Stößels 3 liegt fußseitig am Maschinengestell 2 ein Festlager FL1, in dem ein scheibenartig ausgebildeter unterer Gelenkarm 26 mit seinem einen Ende ortsfest gelagert ist. Der Gelenkarm 26 ist damit um das Festlager FL1 schwenkbar. Das andere Ende des Gelenkarms 26 ist am unteren Gelenkpunkt 23 des Pleuels 8 schwenkbar angelenkt.
An der Spitze des Wirkdreiecks DE des Pleuels 8 befindet sich ein Gelenkpunkt 28, an dem der Exzenter 7 angreift, der um ein am Maschinengestell 2 ortsfest gehaltenes Festlager FL2 drehbar ist. Dieses Festlager FL2 liegt etwa in Flucht des unteren Gelenkpunktes 23, so dass das Festlager FL1 des unteren Gelenkarms 26 und das Festlager FL2 der Exzenterwelle 6 fußseitig im oder am Maschinengestells 2 angeordnet werden können und damit nahe zum Schwerpunkt des gesamten Pressenaufbaus liegen.
In
Die
Hierdurch gelingt es, horizontale Kraftkomponenten bei der Kraftübertragung auf den Stößel 3 erheblich zu minimieren, so dass die Kraftübertragung vom Antrieb auf den Stößel weitgehend ohne Verluste erfolgen kann und zugleich auch der Verschleiß des Stößels 3 an seiner Stößelführung reduziert wird.The
That of two three-phase synchronous motors (see
The
The connecting
In alignment with the vertical stroke axis HU of the
At the top of the effective triangle DE of the connecting
In
The
This makes it possible to significantly minimize horizontal force components in the power transmission to the
In
Die
Dies läuft wie folgt ab. Die Sollwerte, die sich nach den Maschinen- und Prozessdaten des Feinschneid- oder Umformvorgages richten, werden über eine virtuelle Leitachse ermittelt. Die virtuelle Achse ist ein nicht real existierender Antrieb, dessen Drehzahl- und Lagerwerte durch den Rechner ermittelt und als Steuerungsgrößen in Abstimmung mit den Prozessparametern den Motoren vorgegebenen werden. Die beiden Torquemotoren laufen als Slaveachsen zur virtuellen Leitachse.The
This is done as follows. The setpoints, which are based on the machine and process data of the fineblanking or forming process, are determined via a virtual master axis. The virtual axis is a non-existing drive whose speed and bearing values are determined by the computer and given to the motors as control variables in coordination with the process parameters. The two torque motors run as slave axes to the virtual master axis.
Die
Das Kopfstück 39 ist so ausgebildet, dass ein nicht dargestellter Feinschneid- oder Umformkopf mit einem oberen Werkzeugteil daran montiert werden kann, der in hängender Anordnung durch die obere Öffnung des O-Gestells 29 in der Höhe positioniert werden kann.The
The
Bezugszeichenliste
- Kniehebelpresse
- 1
- Maschinengestell
- 2
- Stößel
- 3
- Fester Tisch
- 4
- Kniehebelgelenk
- 5
- Exzenterwelle
- 6
- Exzenter
- 7
- Pleuel
- 8
- Pleuellager
- 9
- Kopf von 9
- 10
- Lagerstellen
- 11, 12
- Obere Lasche
- 13
- Untere Lasche
- 14
- Lagerbolzen
- 15
- Anschlussbereiche von 9
- 16
Lagerbolzen für Lasche 13- 17
Lagerbolzen für Lasche 13- 18
- Anschlußbereiche von 9
- 19
Lagerbolzen für Lasche 14- 20
- Hubbewegliche Tischplatte
- 21
- Oberer
Gelenkpunkt am Pleuel 8 - 22
- Unter
Gelenkpunkt am Pleuel 8 - 23
- Scheibenartiger Gelenkarm
- 24
Gelenkpunkt im Stößel 3- 25
- Scheibenartiger Gelenkarm
- 26
- SChraubverbindungen
- 27
- Gelenkpunkt an dem der Exzenterwelle
- Zugewandten Ende des
Pleuels 8 - 28
- O-
Gestell von 2 - 29
- Rucksackartige Taschen am Fuß des O-Gestells
- 30
- Seitliche Öffnungen in 30
- 31
- Einander
zugewandte Wellenenden von 6 - 32
- Kupplungsstück
- 33
- Drehstrom-Synchronmotore
- 34, 35
Abgewandte Wellenenden von 6- 36
- Planetengetriebe
- 37
- Rechner
- 38
- Kopfstück
- 39
Drehachse von 6- D
- Gleichseitiges Wirkdreieck
- DE
Exzentrizität von 6- E4
- Abstände der Lager
- E1....E3,E5...E7
Hubachse von 3- HU
- Festlager für Exzenterwelle
- FL1
- Festlager für unteren Gelenkarm
- FL2
Lagerstelle der Exzenterwelle 6- L1
Festlager für Lasche 13- L2
- Oberer Totpunkt
- OT
- Schwenkbahn
- S1
- Kurvenbahn
- S2
- Unterer Totpunkt
- UT
- Toggle Press
- 1
- machine frame
- 2
- tappet
- 3
- Fixed table
- 4
- Toggle joint
- 5
- eccentric shaft
- 6
- eccentric
- 7
- pleuel
- 8th
- connecting rod bearing
- 9
- Head of 9
- 10
- bearings
- 11, 12
- Upper flap
- 13
- Lower tab
- 14
- bearing bolt
- 15
- Connection areas of 9
- 16
- Bearing pin for
tab 13 - 17
- Bearing pin for
tab 13 - 18
- Connection areas of 9
- 19
- Bearing pin for
tab 14 - 20
- Lifting table top
- 21
- Upper hinge point at the connecting
rod 8 - 22
- Under hinge point at the connecting
rod 8 - 23
- Disc-like articulated arm
- 24
- Hinge point in the
ram 3 - 25
- Disc-like articulated arm
- 26
- screw
- 27
- Hinge point on the eccentric shaft
- Facing end of the connecting
rod 8 - 28
- O-frame of 2
- 29
- Backpack-like pockets at the foot of the O-frame
- 30
- Side openings in 30
- 31
- Mutually facing shaft ends of 6
- 32
- coupling
- 33
- Three-phase synchronous motors
- 34, 35
- Opposite shaft ends of 6
- 36
- planetary gear
- 37
- computer
- 38
- headpiece
- 39
- Rotation axis of 6
- D
- Equilateral effective triangle
- DE
- Eccentricity of 6
- E4
- Distances of the bearings
- E1 .... E3, E5 E7 ...
- Lifting axle of 3
- HU
- Fixed bearing for eccentric shaft
- FL1
- Fixed bearing for lower articulated arm
- FL2
- Bearing point of the
eccentric shaft 6 - L1
- Fixed bearing for
tab 13 - L2
- Top Dead Center
- OT
- pivot path
- S1
- cam track
- S2
- Bottom dead center
- UT
Claims (13)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20090007351 EP2258498B1 (en) | 2009-06-03 | 2009-06-03 | Mechanical press for fine cutting, reforming and/or shaping workpieces |
CA2705649A CA2705649C (en) | 2009-06-03 | 2010-05-27 | Mechanical press for fine blanking, forming and/or stamping of work pieces |
JP2010126757A JP5702079B2 (en) | 2009-06-03 | 2010-06-02 | Mechanical press device for precision punching, deformation and / or stamping of workpieces |
KR1020100052464A KR101765904B1 (en) | 2009-06-03 | 2010-06-03 | Mechanical press for fine blanking, forming and/or stamping of work pieces |
CN2010101974031A CN101905263A (en) | 2009-06-03 | 2010-06-03 | The punching machine that is used for fine-edge blanking, shaping and/or stamped workpieces |
US12/793,127 US8230781B2 (en) | 2009-06-03 | 2010-06-03 | Mechanical press for fine blanking, forming and/or stamping of work pieces |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20090007351 EP2258498B1 (en) | 2009-06-03 | 2009-06-03 | Mechanical press for fine cutting, reforming and/or shaping workpieces |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2258498A1 true EP2258498A1 (en) | 2010-12-08 |
EP2258498B1 EP2258498B1 (en) | 2012-12-26 |
Family
ID=41268308
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20090007351 Active EP2258498B1 (en) | 2009-06-03 | 2009-06-03 | Mechanical press for fine cutting, reforming and/or shaping workpieces |
Country Status (6)
Country | Link |
---|---|
US (1) | US8230781B2 (en) |
EP (1) | EP2258498B1 (en) |
JP (1) | JP5702079B2 (en) |
KR (1) | KR101765904B1 (en) |
CN (1) | CN101905263A (en) |
CA (1) | CA2705649C (en) |
Cited By (4)
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CN102173075A (en) * | 2010-12-14 | 2011-09-07 | 山东科技大学 | Mechanical servo press |
EP2527136A1 (en) * | 2011-05-27 | 2012-11-28 | Siempelkamp Maschinen- und Anlagenbau GmbH & Co. KG | Continuous press for pressing mats into pressing boards |
WO2019170571A1 (en) * | 2018-03-05 | 2019-09-12 | Arcofil S.A. | Electric torque motor press |
CN112091145A (en) * | 2020-09-28 | 2020-12-18 | 高密三江机械制造有限公司 | Toggle rod mechanism of horizontal forging machine and machining process thereof |
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DE102012102527B4 (en) * | 2012-03-23 | 2014-10-09 | Schuler Pressen Gmbh | Press drive with several working areas |
US9387529B2 (en) * | 2013-03-15 | 2016-07-12 | Honda Motor Co., Ltd. | Forming press |
RU2583211C1 (en) * | 2014-11-18 | 2016-05-10 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Московский государственный технологический университет "СТАНКИН" (ФГБОУ ВПО МГТУ "СТАНКИН") | Knuckle-joint drive mechanical press with double passage of extreme position of slider |
US10744550B2 (en) * | 2017-04-25 | 2020-08-18 | Stolle Machinery Company, Llc | Eccentric second connecting rod subassembly |
CN107159832B (en) * | 2017-06-20 | 2018-11-27 | 安徽普伦智能装备有限公司 | It is a kind of to forge robot automatically |
EA038760B1 (en) * | 2018-06-20 | 2021-10-15 | Республиканское Государственное Предприятие На Праве Хозяйственного Ведения "Институт Механики И Машиноведения Имени Академика У.А. Джолдасбекова" | Knuckle-joint press mechanism |
WO2020239736A1 (en) | 2019-05-27 | 2020-12-03 | Bobst Mex Sa | Platen press with a press toggle mechanism |
CN112959711B (en) * | 2021-02-04 | 2023-02-17 | 一重集团大连工程技术有限公司 | Eight-connecting-rod press transmission mechanism |
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- 2010-06-02 JP JP2010126757A patent/JP5702079B2/en active Active
- 2010-06-03 KR KR1020100052464A patent/KR101765904B1/en active IP Right Grant
- 2010-06-03 CN CN2010101974031A patent/CN101905263A/en active Pending
- 2010-06-03 US US12/793,127 patent/US8230781B2/en active Active
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US2334082A (en) * | 1941-10-13 | 1943-11-09 | Major E Gates | Molding press |
US2471563A (en) * | 1944-02-25 | 1949-05-31 | Major E Gates | Toggle press and method for molding articles from granular material |
EP0993932A2 (en) * | 1998-10-12 | 2000-04-19 | STRIP's d.o.o. Podjetje za svetovanje trzenje in proizvodnjo | Press with toggle drive |
DE19935656A1 (en) | 1999-07-29 | 2001-02-01 | Schuler Pressen Gmbh & Co | Presses from press model range have machine frames for which both the ram guide and the bearing for the ram drive are mounted at coincident, invariant points across the range |
DE19935655A1 (en) | 1999-07-29 | 2001-02-01 | Schuler Pressen Gmbh & Co | Press from press model range has transmission arrangement containing supplementary transmission specific to given press to implement different strokes for different presses of range |
DE10065260A1 (en) | 2000-12-29 | 2002-07-11 | Schuler Pressen Gmbh & Co | System for defining the structure of a press |
DE10065256A1 (en) | 2000-12-29 | 2002-07-11 | Schuler Pressen Gmbh & Co | Drive device for at least one press ram has ram connected to planetary transmission by at least two connecting rods |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102173075A (en) * | 2010-12-14 | 2011-09-07 | 山东科技大学 | Mechanical servo press |
EP2527136A1 (en) * | 2011-05-27 | 2012-11-28 | Siempelkamp Maschinen- und Anlagenbau GmbH & Co. KG | Continuous press for pressing mats into pressing boards |
WO2012163766A1 (en) * | 2011-05-27 | 2012-12-06 | Siempelkamp Maschinen- Und Anlagenbau Gmbh & Co. Kg | Continuous press for compressing pressed-material mats into pressed-material boards |
WO2019170571A1 (en) * | 2018-03-05 | 2019-09-12 | Arcofil S.A. | Electric torque motor press |
CN111819071A (en) * | 2018-03-05 | 2020-10-23 | 阿科菲尔公司 | Electric torque motor press |
CN112091145A (en) * | 2020-09-28 | 2020-12-18 | 高密三江机械制造有限公司 | Toggle rod mechanism of horizontal forging machine and machining process thereof |
Also Published As
Publication number | Publication date |
---|---|
CA2705649C (en) | 2017-02-14 |
CN101905263A (en) | 2010-12-08 |
KR20100130567A (en) | 2010-12-13 |
US8230781B2 (en) | 2012-07-31 |
KR101765904B1 (en) | 2017-08-07 |
JP2010279999A (en) | 2010-12-16 |
EP2258498B1 (en) | 2012-12-26 |
US20100319554A1 (en) | 2010-12-23 |
CA2705649A1 (en) | 2010-12-03 |
JP5702079B2 (en) | 2015-04-15 |
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