EP0927630B1 - Press, in particular punch press - Google Patents
Press, in particular punch press Download PDFInfo
- Publication number
- EP0927630B1 EP0927630B1 EP97121919A EP97121919A EP0927630B1 EP 0927630 B1 EP0927630 B1 EP 0927630B1 EP 97121919 A EP97121919 A EP 97121919A EP 97121919 A EP97121919 A EP 97121919A EP 0927630 B1 EP0927630 B1 EP 0927630B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- connecting rod
- pivotally mounted
- press
- double arm
- link members
- 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.)
- Expired - Lifetime
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/0064—Counterbalancing means for movable press elements
-
- 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
- B30B1/02—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 lever mechanism
- B30B1/06—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 lever mechanism operated by cams, eccentrics, or cranks
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
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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
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
- Y10T74/18176—Crank, pitman, lever, and slide
-
- 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
- Y10T83/8696—Means to change datum plane of tool or tool presser stroke
- Y10T83/87—By varying length of tool stroke
-
- 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
- Y10T83/8848—Connecting rod articulated with tool support
Definitions
- the present invention relates to a Press with at least one pressure column and articulated on it Tappet for connection to at least one Tool for shaping a band-shaped, gradually advanced workpiece, which press a press frame and one stored in the same Has drive shaft on which drive shaft at least one connecting rod unit is mounted eccentrically.
- Such presses are known in the professional world Stamping presses referred to and the present invention concerns in particular a so-called high-speed Punch press.
- Such presses are becoming bigger today Nominal force and large tool space.
- the Ram are driven by a drive shaft of the press about an arrangement of power transmission elements driven, which in turn must be very stable, one should have high spring stiffness and accordingly high Have masses.
- the punch press has the CH-A-543 376 a large distance between the pressure columns, which is beneficial to the ram tipping stiffness affects.
- the driving force of the Drive shaft on the components transmitting the ram formed such that the in the vertical direction oscillating masses are largely balanced.
- counterweight units are still available complete balancing of the vertical oscillating masses necessary, with the result that additional inertia and bearing friction arise.
- the training of the machine parts, which drives the drive force from the drive shaft to the Tappets transmit such that long power transmission paths prevail, with which a larger one Machine suspension is generated, which is disadvantageous affect the punching process.
- the components that are used Serve height adjustment and at the deflection point of the Forces, i.e. Bearing of the two-armed lever of the mentioned punch press are arranged with the double punching force.
- the CH-A-574 323 shows a punch press, at which is the machine parts which are the driving force of the drive shaft on the plunger do not transmit long Form power transmission paths.
- the one-armed levers reduce them to the Drive connecting rod and on the components for adjusting the ram height acting forces.
- the pressure columns have a little mutual distance on what's going on adversely affects the ram tipping stiffness. in the further large balancing masses are required correspondingly high inertial forces, moments of inertia and Cause bearing friction.
- the invention seeks to remedy this.
- the object of the invention is a punch press, in particular to create high-speed punch press, the small one Power transmission paths between the drive shaft and the Tappet, and thus a small machine suspension has, but a large mutual distance allowed between the pressure columns and thus tilting the plunger is advantageously counteracted, the one long tool installation space without excessive climbing the masses of the components for the transmission of the driving force allowed on the pestle, and that no additional, vertically acting balancing masses are required.
- the punching machine according to the invention as it is is characterized in claim 1, has an eccentric mounted connecting rod unit, each with a rocker link and a one-armed lever attached to it a respective pressure column is connected.
- the advantages achieved by the invention can be seen in particular in that the components for Transmission of the driving force from the drive shaft to the plunger is rigid and hardly resilient and Small even in the case of long tool installation spaces Form moving masses. As a result, they are only small Masses of counterweights necessary. Continue kicking in Operation of the punch press only small dynamic mass inertial forces and moments and a minimum of bearing friction on.
- the drive shaft 1 of the punch press is in the Machine frame 2 stored, the top through a cover plate 3 is complete.
- the drive of the drive shaft 1 is done by one (not shown) engine and one Belt drive, of which a pulley 4 is drawn is.
- the driving force is from the pulley 4 via a brake / clutch device 5 on the drive shaft 1 transferred.
- brake / clutch devices are well known and for a detailed Description is, for example, on CH-A-546 141 pointed out.
- the drive shaft 1 has an eccentric Section 7 on which a connecting rod unit is mounted which is generally designated by reference number 8.
- the connecting rod unit 8 has two connecting rod members 9, 10. 5 and 6, the further will be described below, the connecting rod unit 8 four connecting rods 11, 12, 13, 14.
- the connecting rods 9, 10 are at their lower ends of a common connecting rod pin 15 enforced.
- the connecting rod 15 is at both ends with a sliding block 16, 17 in connection.
- the sliding block 16 is guided in the guide 18, and the sliding block 17th is guided in the guide 19.
- the tabs 20, 21, 22, 23 articulated on the connecting rod 15 there are four tabs 20, 21, 22, 23 articulated.
- the tabs 20, 21 form a first Pair of tabs, in which the upper ends of the tabs 20, 21 protrude into the connecting rod 10.
- the tabs 22, 23 form a second pair of tabs, in which the upper Protrude ends of the tabs 20, 23 into the connecting rod 9.
- the tab 20 of the first pair of tabs 20, 21 is at its lower end on a first pivot link 24 hinged.
- the tab 21 of the first pair of tabs 20, 21 is articulated on a second pivot member 25.
- the tab 22 of the second pair of tabs 22, 23 is also articulated on the second pivot pin member 25.
- the Tab 23 of the second pair of tabs 22, 23 is on one third pivot member 26 articulated.
- the first pivot link 24 and the third Swivel pin member 26 are in a first two-armed Lever 27 used, which is thus over the tabs 20 and 23rd to accommodate the arrow height with the connecting rods 9 and 10 is articulated.
- the second pivot member 25 is in one second two-armed lever 28 is used, which thus over the tabs 21 and 22 for receiving the arrow height also articulated with the connecting rods 9 and 10 is.
- Guide pillars 58, 59 protrude from the plunger 57 down that in the tape running level 60 in column guides 61, 62 are guided.
- the strip running level is in punch presses 60 defined as the level that is defined by the Gradually advanced metal strip to be machined is determined.
- Under the ram 57 is the with the tool platen connected to the machine frame 2 63.
- the connecting rod members 9, 10 of the connecting rod unit 1 have extensions 64, 65 at the top. On these extensions 64, 65 cross rods 66, 67 are articulated by the Extensions 64, 65 from in opposite directions point.
- the reference numerals 68, 69 denote the pivot pins.
- the cross bars 66, 67 are in their of the Extensions distal ends with pivot pins 70, 71 with eccentrically mounted counterweight parts 72, 73 connected. The bearings of these counterweight parts 72, 73 are with the reference numerals 74, 75 indicated.
- balance weight parts 72, 73 serve to the horizontal components of the rotating Compensate the unbalanced mass of the punch press.
- the dimensions, lengths of the lever arms and Masses of all components for driving the plunger 57 and the plunger 57 itself are dimensioned such that none resulting unbalance occurs in the vertical direction, i.e. it is not an additional leveling compound Compensate for any vertical Imbalance components necessary.
- the pressure columns 51, 52 have a very large distance from each other. Hence they are at the most possible points on the ram 57, so that with an eccentric punching load of the Ram 57 ensures resistance to tipping is.
- the power transmission path from the connecting rod unit 8 to ram 57 is extremely short. So that is under punching load a minimal suspension of the Components participating in the power transmission ensured which are correspondingly very rigid components. Continue the components are designed such that they are overall have a small mass. This means that the acceleration and deceleration forces are small and moreover can the bearing loads and thus the bearing friction low being held. Consequently, the drive power can be low being held.
- the camp games are also smaller and it can produce products with higher precision getting produced.
- the connecting rod unit 8 shown in FIG. 1 obviously moves in the vertical direction between a top position (top dead center position) and a bottom position (bottom dead center position) and goes through a middle position, from the top and the lowest position has the same distance.
- the geometric axes determine this central position the articulation points of the components for the transmission of the Driving force a geometric straight line. That is, see 2 that the longitudinal central axes of the bolts, or Pins 24, 30, 32, 50, 36 on the one hand and 24, 29, 31, 49, 35 on the other hand, lie on a common straight line. This has the advantage that the rashes of Levers 28, 34 and 27, 33 on the operation of the punch press are limited to a minimum.
- FIGS. 3 and 4 The execution of the The punch press according to the invention is shown in FIGS. 3 and 4 in particular a single-shaft, two-point punch press, i.e. a punch press with two pressure columns 51, 52.
- the invention is also, for example applicable to a single-shaft four-point punch press, which execution below with reference to the 5 and 6 will be described.
- the stamping press shown has one Drive shaft 1, which is mounted in the machine frame 2 is, the cover plate with the reference number 3 is designated.
- the drive is from a not shown Motor via a belt drive, of which the Pulley 4 can be seen.
- the reference number 5 denotes the clutch / brake device from which the brake disc 6 is visible.
- the on the eccentric section 7 of the The connecting rod unit 8 mounted on the drive shaft 1 has four connecting rod elements 11, 12, 13, 14 arranged side by side on.
- the connecting rods 11, 12, 13, 14 are with one common connecting rod bolt 15 connected.
- the connecting rod bolt protrudes at its outer ends 15 in a sliding block 16, 17, and in his middle area is another sliding block 76 arranged.
- the sliding blocks 16, 17 are in guides 18, 19 out and the further sliding block 76 is in the Leadership 77 led.
- the four tabs 78, 79, 80, 81 that over the Connecting rod bolts 15 on the two connecting rod members 11, 12 are articulated, form a first bracket group, and the four tabs 82, 83, 84, 85 that over the connecting rod bolt 15 are articulated on the two connecting rod members 13, 15, form a second tab group.
- the inner two, right next to each other arranged tabs 79, 80 of the first tab group 78, 79, 80, 81 are via a common pivot link 86 hinged to a first two-armed lever 87.
- the outer two tabs 78, 81 of the first Tab group 78, 79 80, 81 are each one separate pivot pin member 88, or 89 on a second two-armed lever 90 articulated.
- the inner two, right next to each other arranged tabs 83, 84 of the second tab group 82, 83, 84, 85 are via another common pivot link 91 on a third two-armed lever 92 articulated.
- the outer two tabs 82, 85 of the second Tab group 82, 83, 84, 85 are each one another separate pivot pin member 93 or 94 on one fourth two-armed lever 95 articulated.
- the first two-armed lever 87 and the one next to it third two-armed lever 92 arranged on it are on one common bolt 30 stored.
- the second are two-armed Lever 90 and the fourth lever 95 arranged next to it mounted on a common bolt 29.
- the first two-armed lever 87 is over one Swivel pin 96 on a first single-armed lever 97 articulated to which a first pressure column 98 is articulated is.
- the second two-armed lever 90 is over one Swivel pin 99 on a second one-armed lever 100 on which a second pressure column 101 is articulated.
- the third two-armed lever 92 is over a pivot pin 102 on a third one-armed lever 103 articulated on which a third pressure column 104 is articulated.
- the fourth two-armed lever 95 is over a pivot pin 105 on a fourth one-armed lever 106 articulated on which a fourth pressure column 107 is articulated.
- the four pressure columns 98, 101, 104, 107 are articulated together on the plunger 57, so that a Four-point suspension of the plunger 57 is present.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
- Presses And Accessory Devices Thereof (AREA)
- Punching Or Piercing (AREA)
- Solid-Sorbent Or Filter-Aiding Compositions (AREA)
- Mounting, Exchange, And Manufacturing Of Dies (AREA)
Abstract
Description
Die vorliegende Erfindung betrifft eine Presse mit mindestens einer Drucksäule und daran angelenktem Stössel zur Verbindung mit mindestens einem Werkzeug zur formgebenden Bearbeitung eines bandförmigen, schrittweise vorgeschobenen Werkstückes, welche Presse einen Pressenrahmen und eine in demselben gelagerte Antriebswelle aufweist, auf welcher Antriebswelle mindestens eine Pleueleinheit exzentrisch gelagert ist.The present invention relates to a Press with at least one pressure column and articulated on it Tappet for connection to at least one Tool for shaping a band-shaped, gradually advanced workpiece, which press a press frame and one stored in the same Has drive shaft on which drive shaft at least one connecting rod unit is mounted eccentrically.
Solche Pressen werden in der Fachwelt als Stanzpressen bezeichnet und die vorliegende Erfindung betrifft insbesondere eine sogenannte schnelllaufende Stanzpresse. Solche Pressen werden heute mit grosser Nennkraft und grossen Werkzeugeinbauräumen gebaut. Die Stössel werden von einer Antriebswelle der Presse her über eine Anordnung von Kraftübertragungselementen angetrieben, die ihrerseits sehr stabil sein müssen, eine hohe Federsteifigkeit aufweisen sollen und demgemäss hohe Massen aufweisen.Such presses are known in the professional world Stamping presses referred to and the present invention concerns in particular a so-called high-speed Punch press. Such presses are becoming bigger today Nominal force and large tool space. The Ram are driven by a drive shaft of the press about an arrangement of power transmission elements driven, which in turn must be very stable, one should have high spring stiffness and accordingly high Have masses.
Das bedeutet, dass im Betrieb einer schnelllaufenden Stanzpresse äusserst grosse Massen mit äusserst hohen Hubzahlen bewegt werden, womit sehr hohe Massenkräfte sowie hohe Beschleunigungs- und Verzögerungskräfte auftreten.That means that in operation one high-speed punch press with extremely large masses extremely high stroke rates are moved, making very high Inertial forces as well as high acceleration and Delay forces occur.
Im Betrieb einer schnelllaufenden Stanzpresse entstehen durch den Stössel und die Kraftübertragungselemente nicht nur sehr hohe Trägheitskräfte und Trägheitsmomente, sondern auch sehr hohe Unwuchtkräfte und Unwuchtmomente, die ausgeglichen werden müssen. Zum Ausgleichen der Unwuchtkräfte und Unwuchtmomente werden Ausgleichsgewichtseinrichtungen, also Ausgleichsmassen benötigt, die ihrerseits zusätzliche Trägheitskräfte und Trägheitsmomente erzeugen und in ihren Lagern und den Lagern ihrer Antriebsglieder Reibkräfte erzeugen. In the operation of a high-speed punch press arise from the ram and the power transmission elements not only very high inertial forces and moments of inertia, but also very high unbalance forces and Imbalance moments that need to be compensated. To the Compensate the unbalance forces and unbalance moments Balance weight devices, i.e. balance masses needed, which in turn additional inertia and Generate moments of inertia and in their bearings and Bearings of their drive members generate frictional forces.
Weiter werden an solche Stanzpressen hohe Anforderungen an die Genauigkeit und Güte der mit ihnen hergestellten Produkte gestellt.Such stamping presses continue to be high Requirements for the accuracy and quality of using them manufactured products.
Es sind viele Stanzpressen bekannt geworden, die gute konstruktive Lösungen zu einzelnen der beschriebenen Problemen beinhalten, jedoch führen Konstruktionen, die für einen gegebenen Problembereich vorteilhaft sind oft zu Nachteilen bei einem anderen Problembereich.Many punch presses have become known the good constructive solutions to some of the described Include problems, but designs lead that are beneficial for a given problem area often at a disadvantage in another problem area.
Beispielsweise weist die Stanzpresse nach der CH-A-543 376 einen grossen Abstand der Drucksäulen auf, was sich vorteilhaft auf die Stössel-Kippsteifigkeit auswirkt. Weiter sind die die Antriebskraft von der Antriebswelle auf den Stössel übertragenden Bauteile derart ausgebildet, dass die in vertikaler Richtung oszillierenden Massen grösstenteils ausgeglichen sind. Jedoch sind immer noch Ausgleichsgewichtseinheiten zum vollständigen Ausgleichen der in vertikaler Richtung oszillierenden Massen notwendig, mit der Folge, dass zusätzliche Trägheitskräfte und Lagerreibungen entstehen. Insbesondere ist die Ausbildung der Maschinenteile, welche die Antriebskraft von der Antriebswelle auf den Stössel übertragen derart ausgebildet, dass lange Kraftübertragungswege vorherrschen, womit eine grössere Maschinenfederung erzeugt wird, welche sich nachteilig auf den Stanzprozess auswirken. Die Bauteile, die zur Stösselhöhenverstellung dienen und am Umlenkpunkt der Kräfte, d.h. Lagerstelle des zweiarmigen Hebels der genannten Stanzpresse angeordnet sind, werden mit der doppelten Stanzkraft belastet.For example, the punch press has the CH-A-543 376 a large distance between the pressure columns, which is beneficial to the ram tipping stiffness affects. Next are the driving force of the Drive shaft on the components transmitting the ram formed such that the in the vertical direction oscillating masses are largely balanced. However, counterweight units are still available complete balancing of the vertical oscillating masses necessary, with the result that additional inertia and bearing friction arise. In particular, the training of the machine parts, which drives the drive force from the drive shaft to the Tappets transmit such that long power transmission paths prevail, with which a larger one Machine suspension is generated, which is disadvantageous affect the punching process. The components that are used Serve height adjustment and at the deflection point of the Forces, i.e. Bearing of the two-armed lever of the mentioned punch press are arranged with the double punching force.
Die CH-A-574 323 zeigt eine Stanzpresse, bei welcher die Maschinenteile, welche die Antriebskraft von der Antriebswelle auf den Stössel übertragen keine langen Kraftübertragungswege bilden. Durch die Kraftaufteilung über die einarmigen Hebel reduzieren sich die auf den Antriebspleuel und auf die Bauteile zur Stösselhöhenverstellung einwirkenden Kräfte. Jedoch weisen die Drucksäulen einen kleinen gegenseitigen Abstand auf, was sich nachteilig auf die Stössel-Kippsteifigkeit auswirkt. Im weiteren sind grosse Ausgleichsmassen erforderlich, die entsprechend hohe Trägheitskräfte, Trägheitsmomente und Lagerreibungen verursachen.The CH-A-574 323 shows a punch press, at which is the machine parts which are the driving force of the drive shaft on the plunger do not transmit long Form power transmission paths. Through the distribution of forces The one-armed levers reduce them to the Drive connecting rod and on the components for adjusting the ram height acting forces. However, the pressure columns have a little mutual distance on what's going on adversely affects the ram tipping stiffness. in the further large balancing masses are required correspondingly high inertial forces, moments of inertia and Cause bearing friction.
Hier will die Erfindung Abhilfe schaffen. Aufgabe der Erfindung ist es, eine Stanzpresse, insbesondere schnelllaufende Stanzpresse zu schaffen, die kleine Kraftübertragungswege zwischen der Antriebswelle und dem Stössel, und damit eine kleine Maschinenfederung aufweist, jedoch einen grossen gegenseitigen Abstand zwischen den Drucksäulen erlaubt und damit einem Kippen des Stössels vorteilhaft entgegengewirkt wird, die einen langen Werkzeugeinbauraum ohne ein übergrosses Ansteigen der Massen der Bauteile zur Übertragung der Antriebskraft auf den Stössel erlaubt, und die keine zusätzlichen, vertikal wirkenden Ausgleichsmassen benötigt.The invention seeks to remedy this. The object of the invention is a punch press, in particular to create high-speed punch press, the small one Power transmission paths between the drive shaft and the Tappet, and thus a small machine suspension has, but a large mutual distance allowed between the pressure columns and thus tilting the plunger is advantageously counteracted, the one long tool installation space without excessive climbing the masses of the components for the transmission of the driving force allowed on the pestle, and that no additional, vertically acting balancing masses are required.
Die erfindungsgemässe Stanzmaschine, wie sie
in Anspruch 1 gekennzeichnet ist, weist eine exzentrisch
gelagerte Pleueleinheit auf, die über unmittelbar jeweils ein Wippenglied
und einen daran angelenkten einarmigen Hebel mit
einer jeweiligen Drucksäule verbunden ist.The punching machine according to the invention, as it is
is characterized in
Die durch die Erfindung erreichten Vorteile sind insbesondere darin zu sehen, dass die Bauteile zur Übertragung der Antriebskraft von der Antriebswelle auf den Stössel steif und kaum federnd ausgebildet sind und auch im Fall von langen Werkzeugeinbauräumen kleine bewegte Massen bilden. Dadurch sind auch lediglich kleine Massen der Ausgleichsgewichte notwendig. Weiter treten im Betrieb der Stanzpresse nur kleine dynamische Massenträgheitskräfte und -momente und ein Minimum an Lagerreibungen auf.The advantages achieved by the invention can be seen in particular in that the components for Transmission of the driving force from the drive shaft to the plunger is rigid and hardly resilient and Small even in the case of long tool installation spaces Form moving masses. As a result, they are only small Masses of counterweights necessary. Continue kicking in Operation of the punch press only small dynamic mass inertial forces and moments and a minimum of bearing friction on.
Nachfolgend wird der Erfindungsgegenstand anhand von Ausführungswegen darstellenden Zeichnungen beispielsweise näher erläutert.The subject of the invention is as follows on the basis of drawings showing execution routes for example explained in more detail.
Es zeigt:
Die Antriebswelle 1 der Stanzpresse ist im
Maschinenrahmen 2 gelagert, der oben durch eine Deckplatte
3 abgeschlossen ist. Der Antrieb der Antriebswelle
1 erfolgt von einem (nicht gezeichneten) Motor und einem
Riemenantrieb, von welchem eine Riemenscheibe 4 gezeichnet
ist. Die Antriebskraft wird von der Riemenscheibe 4
über eine Brems-/Kupplungsvorrichtung 5 auf die Antriebswelle
1 übertragen. Solche Brems-/Kupplungsvorrichtungen
sind allgemein bekannt, und für eine detaillierte
Beschreibung wird beispielsweise auf die CH-A-546 141
hingewiesen.The
In den Figuren ist zur Verdeutlichung die
Bremsscheibe 6 der Brems-/Kupplungsvorrichtung
eingezeichnet.In the figures, the is for
Die Antriebswelle 1 weist einen exzentrischen
Abschnitt 7 auf, auf welchem eine Pleueleinheit gelagert
ist, die allgemein mit der Bezugsziffer 8 bezeichnet ist.The
Bei der Ausführung nach der Fig. 3 und 4
weist die Pleueleinheit 8 zwei Pleuelglieder 9, 10 auf.
Bei der Ausführung nach den Fig. 5 und 6, die weiter
unten noch beschreiben sein wird, weist die Pleueleinheit
8 vier Pleuelglieder 11, 12, 13, 14 auf.3 and 4
the connecting
Die Pleuelglieder 9, 10 sind bei ihren
unteren Enden von einem gemeinsamen Pleuelbolzen 15
durchsetzt. Der Pleuelbolzen 15 steht bei beiden Enden
mit einem Gleitstein 16, 17 in Verbindung. Der Gleitstein
16 ist in der Führung 18 geführt, und der Gleitstein 17
ist in der Führung 19 geführt.The connecting
Am Pleuelbolzen 15 sind vier Laschen 20, 21,
22, 23 angelenkt. Die Laschen 20, 21 bilden ein erstes
Laschenpaar, bei welchem die oberen Enden der Laschen 20,
21 in das Pleuelglied 10 hineinragen. Die Laschen 22, 23
bilden ein zweites Laschenpaar, bei welchem die oberen
Enden der Laschen 20, 23 in das Pleuelglied 9 hineinragen.On the connecting
Die Lasche 20 des ersten Laschenpaares 20, 21
ist bei ihrem unteren Ende an einem ersten Schwenkzapfenglied
24 angelenkt. Die Lasche 21 des ersten Laschenpaars
20, 21 ist an einem zweiten Schwenkzapfenglied 25 angelenkt.
Die Lasche 22 des zweiten Laschenpaars 22,23 ist
ebenfalls am zweiten Schwenkzapfenglied 25 angelenkt. Die
Lasche 23 des zweiten Laschenpaars 22, 23 ist an einem
dritten Schwenkzapfenglied 26 angelenkt.The
Das erste Schwenkglied 24 und das dritte
Schwenkzapfenglied 26 sind in einem ersten zweiarmigen
Hebel 27 eingesetzt, der somit über die Laschen 20 und 23
zur Aufnahme der Pfeilhöhe mit den Pleuelgliedern 9 und
10 gelenkig verbunden ist.The
Das zweite Schwenkzapfenglied 25 ist in einem
zweiten zweiarmigen Hebel 28 eingesetzt, der somit über
die Laschen 21 und 22 zur Aufnahme der Pfeilhöhe ebenfalls
mit den Pleuelgliedern 9 und 10 gelenkig verbunden
ist.The
Bei der gezeigten Ausführung sind die als
Wippenglieder arbeitenden zweiarmigen Hebel 27, 28
punktsymmetrisch ausgebildet. Sie weisen bei der
gezeichneten Ausführung Hebelarme mit derselben Länge
auf. Es sind jedoch auch Ausführungen mit ungleich langen
Hebelarmen vorgesehen. Diese zweiarmigen Hebel 27, 28
sind über Bolzen 29, 30 im Maschinenrahmen 2 gelagert
(Fig. 2 und Fig. 4).In the embodiment shown, they are as
Rocker members working two-
Bei ihrem von den Laschen 20, 21, 22, 23
entfernten Ende sind die zweiarmigen Hebel 27, 28 über
Schwenkzapfen 31, 32 an einarmigen Hebeln 33, 34
angelenkt. Beim anderen Ende sind die einarmigen Hebel
33, 34 über Schwenkzapfen 35, 36 und Laschen 37, 38 an
den Spindelmuttern 39, 40 der Stösselhöhenverstellvorrichtungen
41, 42 angelenkt, von welchen die Spindeln 43,
44, die Geradführungszapfen 45, 46, die im Maschinenrahmen
2 geführt sind und die Antriebszahnräder 47, 48
zum Rotieren der Spindeln 43, 44 gezeichnet sind. In der
Fig. 4 sind für die einarmigen Hebel zusätzlich zu den
Bezugsziffern 33, 34 auch Bezugsziffern 33', 34'
eingetragen. Der Grund dafür ist, dass jeder dieser Hebel
aus konstruktiven Gründen zwei einzelne nebeneinander
angeordnete Arme, nämlich 33, 33' und 34, 34' aufweist.With her of the
Eine detaillierte Beschreibung dieser Stösselhöhenverstellvorrichtungen kann der US-A-5 052 257 entnommen werden.A detailed description of this Ram height adjustment devices can be found in US-A-5 052 257 be removed.
An jedem einarmigen Hebel 33, 34 ist über
einen Schwenkzapfen 49, 50 eine Drucksäule 51, 52
angelenkt, welche Drucksäulen 51, 52 durch bewegliche
Dichtungen 53, 54 hindurchverlaufen und über Bolzen 55,
56 am Stössel 57 angelenkt sind.On each one-
Es ist zu bemerken, dass bei der gezeichneten
Ausführung der Abstand zwischen den die Drucksäulen 51,
52 tragenden Schwenkzapfen 49, 50 und den Schwenkzapfen
35, 36 bei den Stösselhöhenverstellvorrichtungen 41, 42
grösser ist als der Abstand zwischen den die Drucksäulen
51, 52 tragenden Schwenkzapfen 49, 50 und den Schwenkzapfen
31, 32 bei den zweiarmigen Hebeln 27, 28. Diese
relativen Abstände sind nicht zwingend. Es können bei
weiteren Ausführungen andere Abstandsverhältnisse
vorhanden sein. It should be noted that with the drawn
Execution of the distance between the
Vom Stössel 57 ragen Führungssäulen 58, 59
nach unten, die in der Bandlaufebene 60 in Säulenführungen
61, 62 geführt sind. In Stanzpressen wird die Bandlaufebene
60 als diejenige Ebene definiert, die durch das
schrittweise vorgeschobene, zu bearbeitende Metallband
bestimmt ist. Unter dem Stössel 57 befindet sich die mit
dem Maschinenrahmen 2 verbundene Werkzeugaufspannplatte
63.
Die Pleuelglieder 9, 10 der Pleueleinheit 1
weisen oben Fortsätze 64, 65 auf. An diesen Fortsätzen
64, 65 sind Querstangen 66, 67 angelenkt, die von den
Fortsätzen 64, 65 aus in entgegengesetzte Richtungen
weisen. Die Bezugsziffern 68, 69 bezeichnen die Anlenkbolzen.
Die Querstangen 66, 67 sind bei ihren von den
Fortsätzen entfernten Enden über Anlenkbolzen 70, 71 mit
exzentrisch gelagerten Ausgleichsgewichtsteilen 72, 73
verbunden. Die Lagerstellen dieser Ausgleichsgewichtsteile
72, 73 sind mit den Bezugsziffern 74, 75
angedeutet.The connecting
Diese Ausgleichsgewichtsteile 72, 73 dienen
dazu, die horizontalen Komponenten der rotierenden
Unwuchtmasse der Stanzpresse auszugleichen.These
Die Dimensionen, Längen der Hebelarme und
Massen aller Bauteile zum Antrieb des Stössels 57 sowie
der Stössel 57 selbst sind derart bemessen, dass keine
resultierende Unwucht in vertikaler Richtung auftritt,
d.h. es ist keine zusätzliche Ausgleichsmasse zum
Ausgleichen von irgendwelchen vertikalen
Unwuchtskomponenten notwendig.The dimensions, lengths of the lever arms and
Masses of all components for driving the
Betrachtet man den Weg der Kraftübertragung
von der Pleueleinheit 8 zum Stössel 57 und die Ausbildung
der entsprechenden Bauteile der Stanzpresse, lässt sich
folgendes feststellen.Looking at the way of power transmission
from the connecting
Die Drucksäulen 51, 52 weisen einen sehr
grossen Abstand von einander auf. Folglich sind sie bei
den äusserst möglichen Stellen am Stössel 57 angelenkt,
so dass bei einer aussermittigen Stanzbelastung des
Stössels 57 der Widerstand gegen ein Kippen gewährleistet
ist.The
Der Kraftübertragungsweg von der Pleueleinheit
8 zum Stössel 57 ist äusserst kurz. Damit ist
unter Stanzbelastung eine minimale Federung der an der
Kraftübertragung teilnehmenden Bauteile sichergestellt,
welche entsprechend sehr steife Bauteile sind. Weiter
sind die Bauteile derart ausgebildet, dass sie insgesamt
eine kleine Masse aufweisen. Damit sind die Beschleunigungs- und Verzögerungskräfte klein und überdies können
die Lagerbelastungen und somit die Lagerreibungen tief
gehalten werden. Folglich kann die Antriebsleistung tief
gehalten werden. Auch werden die Lagerspiele kleiner und
es können Erzeugnisse mit einer höheren Präzision
hergestellt werden.The power transmission path from the connecting
Die in der Fig. 1 gezeichnete Pleueleinheit 8
bewegt sich in vertikaler Richtung gesehen offensichtlich
zwischen einer obersten Stellung (obere Totpunktstellung)
und einer untersten Stellung (untere Totpunktstellung)
und durchläuft eine Mittelstellung, die von der obersten
und untersten Stellung denselben Abstand aufweist. In
dieser Mittelstellung bestimmen die geometrischen Achsen
der Anlenkstellen der Bauteile zur Übertragung der
Antriebskraft eine geometrische Gerade. Das heisst, siehe
Fig. 2, dass die Längsmittelachsen der Bolzen, bzw.
Zapfen 24, 30, 32, 50, 36 einerseits und 24, 29, 31, 49,
35 andererseits, auf einer gemeinsamen Geraden liegen.
Damit ergibt sich der Vorteil, dass die Ausschläge der
Hebel 28, 34, bzw. 27, 33 im Betrieb der Stanzpresse auf
ein Minimum beschränkt sind.The connecting
Die oben beschriebene Ausführung der
erfindungsgemässen Stanzpresse zeigt in den Figuren 3 und
4 insbesondere eine Einwellen-Zweipunkt-Stanzpresse, d.h.
eine Stanzpresse mit zwei Drucksäulen 51, 52.The execution of the
The punch press according to the invention is shown in FIGS. 3 and
4 in particular a single-shaft, two-point punch press, i.e.
a punch press with two
Die Erfindung ist jedoch auch beispielsweise bei einer Einwellen-Vierpunkt-Stanzpresse anwendbar, welche Ausführung nachfolgend unter Bezugnahme auf die Fig. 5 und 6 beschrieben wird.However, the invention is also, for example applicable to a single-shaft four-point punch press, which execution below with reference to the 5 and 6 will be described.
Aus Gründen der Klarheit werden für diese Beschreibung so weit wie mögliche dieselben Bezugsziffern verwendet, die für die vorgehende Beschreibung verwendet worden ist.For the sake of clarity, these are Description the same reference numerals as far as possible used for the previous description has been.
Die gezeichnete Stanzpresse weist eine
Antriebswelle 1 auf, die im Maschinenrahmen 2 gelagert
ist, wobei die Deckplatte mit der Bezugsziffer 3
bezeichnet ist.The stamping press shown has one
Der Antrieb erfolgt von einem nicht gezeichneten
Motor über einen Riemenantrieb, von welchem die
Riemenscheibe 4 ersichtlich ist. Die Bezugsziffer 5
bezeichnet die Kupplungs-/Bremsvorrichtung, von welcher
die Bremsscheibe 6 sichtbar ist.The drive is from a not shown
Motor via a belt drive, of which the
Die auf dem exzentrischen Abschnitt 7 der
Antriebswelle 1 gelagerte Pleueleinheit 8 weist vier
nebeneinander angeordnete Pleuelglieder 11, 12, 13, 14
auf. Die Pleuelglieder 11, 12, 13, 14 sind mit einem
gemeinsamen Pleuelbolzen 15 verbunden.The on the
An seinen äusseren Enden ragt der Pleuelbolzen
15 in je einen Gleitstein 16, 17, und in seinem
mittleren Bereich ist ein weiterer Gleitstein 76
angeordnet. Die Gleitsteine 16, 17 sind in Führungen 18,
19 geführt und der weitere Gleitstein 76 ist in der
Führung 77 geführt.The connecting rod bolt protrudes at its outer ends
15 in a sliding
Auf dem Pleuelbolzen 15 sind acht Laschen 78,
79, 80, 81, 82, 83, 84, 85 gelagert.On the connecting
Die vier Laschen 78, 79, 80, 81, die über dem
Pleuelbolzen 15 an den zwei Pleuelgliedern 11, 12
angelenkt sind, bilden eine erste Laschengruppe, und die
vier Laschen 82, 83, 84, 85, die über dem Pleuelbolzen
15 an den zwei Pleuelgliedern 13, 15 angelenkt sind,
bilden eine zweite Laschengruppe.The four
Die inneren zwei, unmittelbar nebeneinander
angeordneten Laschen 79, 80 der ersten Laschengruppe 78,
79, 80, 81 sind über ein gemeinsames Schwenkzapfenglied
86 an einem ersten zweiarmigen Hebel 87 angelenkt.The inner two, right next to each other
arranged
Die äusseren zwei Laschen 78, 81 der ersten
Laschengruppe 78, 79 80, 81 sind über jeweils ein
separates Schwenkzapfenglied 88, bzw. 89 an einem zweiten
zweiarmigen Hebel 90 angelenkt.The outer two
Die inneren zwei, unmittelbar nebeneinander
angeordneten Laschen 83, 84 der zweiten Laschengruppe 82,
83, 84, 85 sind über ein weiteres gemeinsames Schwenkzapfenglied
91 an einem dritten zweiarmigen Hebel 92
angelenkt.The inner two, right next to each other
arranged
Die äusseren zwei Laschen 82, 85 der zweiten
Laschengruppe 82, 83, 84, 85 sind über jeweils ein
weiteres separates Schwenkzapfenglied 93 bzw. 94 an einem
vierten zweiarmigen Hebel 95 angelenkt.The outer two
Der erste zweiarmige Hebel 87 und der neben
ihm angeordnete dritte zweiarmige Hebel 92 sind auf einem
gemeinsamen Bolzen 30 gelagert.The first two-
In gleicher Weise sind der zweite zweiarmige
Hebel 90 und der neben ihm angeordnete vierte Hebel 95
auf einem gemeinsamen Bolzen 29 gelagert.In the same way, the second are two-
Der erste zweiarmige Hebel 87 ist über einen
Schwenkzapfen 96 an einem ersten einarmigen Hebel 97
angelenkt, an welchem eine erste Drucksäule 98 angelenkt
ist. Der zweite zweiarmige Hebel 90 ist über einen
Schwenkzapfen 99 an einem zweiten einarmigen Hebel 100
angelenkt, an welchem eine zweite Drucksäule 101
angelenkt ist. Der dritte zweiarmige Hebel 92 ist über
einen Schwenkzapfen 102 an einem dritten einarmigen Hebel
103 angelenkt, an welchem eine dritte Drucksäule 104
angelenkt ist. Der vierte zweiarmige Hebel 95 ist über
einen Schwenkzapfen 105 an einem vierten einarmigen Hebel
106 angelenkt, an welchem eine vierte Drucksäule 107
angelenkt ist.The first two-
Die vier Drucksäulen 98, 101, 104, 107 sind
gemeinsam am Stössel 57 angelenkt, so dass eine
Vierpunktaufhängung des Stössels 57 vorhanden ist. The four
Die restlichen Baueinheiten dieser zweiten Ausführung, z.B. Massenausgleichsgewichte mit deren Antrieb, Stösselhöhenverstellung, Stösselführung, etc. sind gleich denjenigen der ersten Ausführung ausgebildet, so dass sich eine nochmalige Beschreibung derselben erübrigt. Zu bemerken ist lediglich, dass bei der zweiten Ausführung verschiedene Baueinheiten im Vergleich mit der ersten Ausführung doppelt vorhanden sind. Der Längsschnitt der zweiten Ausführung gleicht dem Längsschnitt der ersten Ausführung nach Fig. 1.The remaining units of this second Execution, e.g. Mass balance weights with their Drive, ram height adjustment, ram guide, etc. are the same as those of the first embodiment, so that there is another description of the same superfluous. The only thing to note is that the second Execution of different units in comparison with the first version are duplicated. The longitudinal section the second version is similar to the longitudinal section the first embodiment of FIG. 1st
Claims (11)
- Press with at least one pressing column (51, 52; 98, 101, 104, 107) and a ram (57) pivotally mounted thereto to be connected to at least one tool for a shape producing working of a strip-shaped workpiece which is advanced step by step, which press includes a press frame (2) and a drive shaft (1) which is supported in same, on which drive shaft (1) at least one connecting rod unit (8) is supported eccentrically, characterized in that the connecting rod unit (8) is connected to a respective pressing column directly via a rocking member (27, 28; 87, 90, 92, 95) and thereafter via a single arm lever (33, 34, 97, 100, 103, 106) pivotally mounted to the rocking member (27, 28; 87, 90, 92, 95).
- Press according to claim 1, characterized in that the rocking member (27, 28; 87, 90, 92, 95) is of a point symmetrical design and is supported at its point of symmetry in the press frame (2).
- Press according to claim 1 or 2, characterized in that the rocking member (27, 28; 87, 90, 92, 95) is designed as a double arm lever.
- Press according to one of the preceding claims, characterized in that the double arm lever (27, 28; 87, 90, 92, 95) which forms the rocking member is supported in the press frame (2) for rotation about a stationary axis (29, 30), is pivotally mounted at one end to the connecting rod unit (8), and at the opposite end directly to the single arm lever (33, 34; 97, 100, 103, 106), which single arm lever (33, 34; 97, 100, 103, 106) is pivotally mounted at its end remote from the double arm lever (27, 28; 87, 90, 92, 95) to a device (41, 42) for adjusting the height position of the ram mounted to the press frame (2).
- Press according to one of the preceding claims, characterized in that the dimensions, masses and lengths of the lever arms of the structural members which move when the press is in operation are selected such, that when the press is in operation the vertical component of the moving masses is zero, so that no structures for a vertical balancing of masses are needed.
- Press according to one of the preceding claims, characterized in that the double arm levers (27, 28; 87, 90, 92, 95), in order to compensate for the height of arrow, are pivotally mounted to the connecting rod unit (8) via link members (20, 21, 22, 23; 78 - 85), and that in one operational position of the press the pivot axes and axes of rotation, respectively of the points where the single arm levers (33, 34; 97, 100, 103, 106) are connected to the devices (41, 42) for the adjusting of the height position of the ram, of the points where the pressing columns (51, 52; 98, 101, 104, 107) are pivotally mounted to the single arm levers (33, 34; 97, 100, 103, 106), of the points where the single arm levers (33, 34; 97, 100, 103, 106) are pivotally mounted to the double arm levers (27, 28; 87, 90, 92, 95), of the points where the double arm levers (27, 28; 87, 90, 92, 95) are pivotally supported, and of the points where the double arm levers (27, 28; 87, 90, 92, 95) are pivotally mounted to the link members (20-23; 79-85) connecting them to the connecting rod unit (8), are located on a straight line common to all.
- Press according to one of the preceding claims, characterized in that the connecting rod unit (8) includes projecting extensions (64, 65) which are located relative to the drive shaft (1) opposite of the point where the connecting rod unit (8) is pivotally mounted to the link members (20-23; 78-85) via which the connecting rod unit (8) is connected to the double arm levers (27, 28; 87, 90, 92, 95), further wherein lateral bars (60, 67) extend from the projecting extensions (64, 65) in opposite directions and are pivotally mounted at their ends remote from the projecting extensions (64, 65) each to an eccentrically supported mass balancing weight body (72, 73), which mass balancing weight bodies (72, 73) are adapted to balance the horizontal components of the rotating unbalanced mass of the punch-press.
- Press according to one of the preceding claims, characterized in that the connecting rod unit (8) comprises at least two connecting rod members (9, 10; 11-14) which connecting rod members (9, 10; 11-14) are connected via link members (20-23; 78-85) for the absorbing of the heights of arrow to at least two double arm levers (27, 28; 87, 90, 92, 95) which extend in opposite directions away from each other and in which a connecting rod pin (15) is received at the end remote from the drive shaft (1), which is connected to slider members (16, 17; 76) for a rectilinear guiding of the connecting rod members (9, 10; 11-14), on which connecting rod pin (15) the link members (20, 21; 22, 23; 78, 79; 80, 81; 82, 83; 84, 85) are arranged in pairs in such a manner that the link members (20, 21; 22, 23; 78, 79; 80, 81; 82, 83; 84, 85) of each pair project at their first end into a respective connecting rod member (9, 10; 11-14).
- Press according to claim 8, characterized in that the one link member (20, 23; 78, 81; 82, 85) of each pair of link members is pivotally mounted to one of the double arm levers (27; 90, 95) via a pivot pin member (24, 26; 88, 89; 93, 94) and the other link member (21, 22; 79, 80; 83, 84) is pivotally mounted via a further pivot pin member (25; 88, 91) to a further double arm lever (28; 87, 92) extending in the opposite direction of the first named double arm lever.
- Press according to claim 9, characterized in that the connecting rod unit (8) comprises two connecting rod members (9, 10) arranged side by side and accordingly a group of four link members (20-23) arranged side by side, of which the inner two link members (21, 22) which are located directly side by side are pivotally mounted via a pivot pin member (25) common to both to one of the double arm levers (28), and the outer two link members (20, 23) which are located remote from each others are pivotally mounted by a respective separate pivot pin member (24, 26) to the further double arm lever (27) which projects in the opposite direction of the first named one.
- Press according to claim 9, characterized in that the connecting rod unit comprises four connecting rod members (11-14) located side by side and accordingly eight link members (78-85) located side by side which are divided in two groups (78-81; 82-85) of four link members located side by side, that the inner two link members (79, 80) of the one group (78-81) located directly side by side are pivotally mounted via a pivot pin member (86) common to both to a first double arm lever (87) and the outer two link members (78, 81) of this one group (78-81) located remote from each other are pivotally mounted each via a respective separate pivot pin member (88, 89) to a second double arm lever (90) extending in an opposite direction relative to the first one, that the inner two link members (83, 84) of the other link member group (82-85) which are located directly side by side are pivotally mounted via a further common pivot pin member (91) to a third double arm lever (92) which extends in the same direction as the first double arm lever (87) that the outer two link members (82, 85) of the other link member group (82-85) which are located remote from each other are pivotally mounted each via a respective pivot pin member (93, 94) to a fourth lever (95) extending in an opposite direction relative to the third one, which four double arm levers (87, 90, 92, 95) are pivotally mounted each to a single arm lever (97, 100, 103, 106) which is mounted to a pressing column ((98, 101, 104, 107) so that the ram (57) of the press is suspended on four pressing columns (98, 101, 104, 107).
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ES97121919T ES2137754T3 (en) | 1997-12-12 | 1997-12-12 | PRESS, ESPECIALLY STAMP PRESS. |
AT97121919T ATE184236T1 (en) | 1997-12-12 | 1997-12-12 | PRESS, ESPECIALLY PUNCHING PRESS |
EP97121919A EP0927630B1 (en) | 1997-12-12 | 1997-12-12 | Press, in particular punch press |
DE59700425T DE59700425D1 (en) | 1997-12-12 | 1997-12-12 | Press, especially punch press |
SG1998003925A SG73558A1 (en) | 1997-12-12 | 1998-09-29 | A press specifically punch press |
US09/182,021 US6055903A (en) | 1997-12-12 | 1998-10-29 | Press, specifically punch press |
JP33533298A JP3343220B2 (en) | 1997-12-12 | 1998-11-26 | Presses, especially punch presses |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP97121919A EP0927630B1 (en) | 1997-12-12 | 1997-12-12 | Press, in particular punch press |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0927630A1 EP0927630A1 (en) | 1999-07-07 |
EP0927630B1 true EP0927630B1 (en) | 1999-09-08 |
Family
ID=8227789
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97121919A Expired - Lifetime EP0927630B1 (en) | 1997-12-12 | 1997-12-12 | Press, in particular punch press |
Country Status (7)
Country | Link |
---|---|
US (1) | US6055903A (en) |
EP (1) | EP0927630B1 (en) |
JP (1) | JP3343220B2 (en) |
AT (1) | ATE184236T1 (en) |
DE (1) | DE59700425D1 (en) |
ES (1) | ES2137754T3 (en) |
SG (1) | SG73558A1 (en) |
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US6405576B1 (en) * | 1999-11-30 | 2002-06-18 | Aida Engineering Co., Ltd. | Linear slide press machine |
EP1193046A1 (en) * | 2000-09-30 | 2002-04-03 | Bruderer Ag | Method for controlling the mutual angular position between the slide and the clamping table of a punch press and punch press for carrying out this method |
EP1251530A3 (en) * | 2001-04-16 | 2004-12-29 | Shipley Company LLC | Dielectric laminate for a capacitor |
JP3897562B2 (en) * | 2001-10-24 | 2007-03-28 | アイダエンジニアリング株式会社 | Mechanical press |
EP1600223A1 (en) * | 2004-05-27 | 2005-11-30 | Trumpf Werkzeugmaschinen GmbH + Co. KG | Punching machine with motor driven rotating- /lifting mechanism |
DE102005001878B3 (en) * | 2005-01-14 | 2006-08-03 | Schuler Pressen Gmbh & Co. Kg | Servo press with toggle mechanism |
JP4313816B2 (en) * | 2006-12-27 | 2009-08-12 | 株式会社山田ドビー | Press machine |
EP2008799A1 (en) | 2007-06-28 | 2008-12-31 | Bruderer Ag | Die cutting press |
CN103419387B (en) * | 2013-08-27 | 2015-05-20 | 南京理工大学 | High-speed precise numerical control press mechanism with driving and driven combination drive |
CN103507286A (en) * | 2013-10-09 | 2014-01-15 | 德清三原色信息科技有限公司 | Small-scale punch press with gantry-type structure |
US20170108096A1 (en) * | 2015-10-14 | 2017-04-20 | Vamco International, Inc. | Apparatus and method for adjusting the stroke length of a movable member |
TWI588014B (en) * | 2016-12-20 | 2017-06-21 | 金豐機器工業股份有限公司 | Puncher with an automatic adjusting balancer |
CN109318518A (en) * | 2018-10-10 | 2019-02-12 | 南京理工大学 | A kind of enclosed Duo Gan dieing machine mechanism |
CN109203536B (en) * | 2018-10-10 | 2021-05-07 | 南京理工大学 | Double-lever high-speed precision punch mechanism |
WO2020211931A1 (en) * | 2019-04-16 | 2020-10-22 | Bruderer Ag | Punching press |
CN110947849B (en) * | 2019-12-25 | 2024-04-16 | 江苏万意节能科技有限公司 | Left-right conveying device for cutting off finished products of double-row stamping line of steel heald |
CN116852782A (en) * | 2021-01-14 | 2023-10-10 | 何春远 | Method for manufacturing press machine by lever method and application thereof |
EP4059676B1 (en) * | 2021-03-17 | 2023-06-07 | Krug & Priester GmbH & Co. KG | Cutting machine with blade depth adjustment |
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US4156387A (en) * | 1974-09-03 | 1979-05-29 | Bruderer Ag | Apparatus for mass compensation at a machine driven by a crank drive |
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US4276823A (en) * | 1979-01-11 | 1981-07-07 | R W M-Raster-Werkzeugmaschinen Gmbh | Eccentric press |
CH679471A5 (en) * | 1989-05-03 | 1992-02-28 | Bruderer Ag | |
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-
1997
- 1997-12-12 AT AT97121919T patent/ATE184236T1/en active
- 1997-12-12 ES ES97121919T patent/ES2137754T3/en not_active Expired - Lifetime
- 1997-12-12 DE DE59700425T patent/DE59700425D1/en not_active Expired - Lifetime
- 1997-12-12 EP EP97121919A patent/EP0927630B1/en not_active Expired - Lifetime
-
1998
- 1998-09-29 SG SG1998003925A patent/SG73558A1/en unknown
- 1998-10-29 US US09/182,021 patent/US6055903A/en not_active Expired - Lifetime
- 1998-11-26 JP JP33533298A patent/JP3343220B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
ES2137754T3 (en) | 1999-12-16 |
JPH11245088A (en) | 1999-09-14 |
DE59700425D1 (en) | 1999-10-14 |
SG73558A1 (en) | 2000-06-20 |
ATE184236T1 (en) | 1999-09-15 |
US6055903A (en) | 2000-05-02 |
EP0927630A1 (en) | 1999-07-07 |
JP3343220B2 (en) | 2002-11-11 |
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