EP0435992B1 - Presse und methode für materialbearbeitung - Google Patents

Presse und methode für materialbearbeitung Download PDF

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Publication number
EP0435992B1
EP0435992B1 EP90910808A EP90910808A EP0435992B1 EP 0435992 B1 EP0435992 B1 EP 0435992B1 EP 90910808 A EP90910808 A EP 90910808A EP 90910808 A EP90910808 A EP 90910808A EP 0435992 B1 EP0435992 B1 EP 0435992B1
Authority
EP
European Patent Office
Prior art keywords
links
crank
die carrier
linkage
die
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
Application number
EP90910808A
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English (en)
French (fr)
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EP0435992A1 (de
Inventor
Andrew Stephen Moseley
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
VERSON HME Ltd
Original Assignee
VERSON HME Ltd
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Filing date
Publication date
Application filed by VERSON HME Ltd filed Critical VERSON HME Ltd
Publication of EP0435992A1 publication Critical patent/EP0435992A1/de
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Publication of EP0435992B1 publication Critical patent/EP0435992B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B44—DECORATIVE ARTS
    • B44B—MACHINES, APPARATUS OR TOOLS FOR ARTISTIC WORK, e.g. FOR SCULPTURING, GUILLOCHING, CARVING, BRANDING, INLAYING
    • B44B5/00—Machines or apparatus for embossing decorations or marks, e.g. embossing coins
    • B44B5/0052—Machines or apparatus for embossing decorations or marks, e.g. embossing coins by pressing
    • B44B5/0057—Machines or apparatus for embossing decorations or marks, e.g. embossing coins by pressing using more than one die assembly simultaneously
    • 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
    • B30B1/106—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 another toggle mechanism
    • 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

Definitions

  • the present invention relates to a press which comprises a frame, a crank mounted for turning relative to the frame about a crank axis, a first die carrier guided by the frame for reciprocation along a rectilinear path and means for transmitting motion to the first die carrier from the crank.
  • the invention has been devised primarily for use in a coining press which comprises a second die carrier and a collar within which respective dies mounted on the die carriers engage a workpiece.
  • the first die carrier is advanced towards the second die carrier to effect the coining operation.
  • the first die carrier is then retracted and the second die carrier is advanced so that the die thereon ejects the workpiece from the collar.
  • the workpieces are fed to and from a position between the dies across a feed surface. It is desirable that the die on the first carrier should be held with its coining face co-planar with the feed surface during feeding of each workpiece onto and from that die.
  • a coining press having a toggle linkage for transmitting motion from a crank-driven connecting rod to a first die carrier.
  • the connecting rod moves with simple harmonic motion but this motion is modified by the toggle linkage.
  • Abutments are provided for arresting travel of the first die carrier with a member of the toggle linkage in a direction away from the other die carrier so that the first die will remain in a position with its coining face co-planar with a feed surface, whilst the member of the toggle linkage continues to move away from the other die carrier and then returns.
  • This arrangement provides a satisfactory dwell of the die on the first die carrier but each cycle of operation of the machine involves impact of the member of the toggle linkage with the first die carrier as the clearance between these is eliminated. This contributes to vibration of the machine.
  • a further factor contributing to vibration is the vertical acceleration and deceleration of the first die carrier and of the adjacent member of the toggle linkage.
  • US-A-3,661,008 discloses a press comprising a frame, a crank mounted for turning relative to the frame about a crank axis, a first die carrier guided by the frame for reciprocation along a rectilinear path, a linkage for transmitting motion to the first die carrier and a connecting rod for transmitting motion from the crank to the linkage.
  • the linkage comprises first and second links pivotally connected to each other and to a third link at their one ends whilst second ends of the links are connected respectively to the frame and the first die carrier.
  • a further link has one end connected to the frame and its other end is pivotally connected to the other end of the third link and to a crankshaft which extends upwardly from a crank rotatable about an axis disposed below and laterally offset from the rectilinear path of the first die carrier.
  • the press is unsymmetrical and experiences out of balance forces. Furthermore, when the linkage is arranged to move the first die carrier in one direction, a portion of the connecting rod which is remote from the crank moves in substantially the same direction so that vibration which results from acceleration of the first die carrier occurs.
  • a press comprising a frame, a crank mounted for turning relative to the frame about a crank axis, a first die carrier guided by the frame for reciprocation along a rectilinear path, a linkage for transmitting motion to the first die carrier and a connecting rod for transmitting motion from the crank to the linkage, wherein the linkage includes a pair of corresponding links with the crank axis lying between the corresponding links, and a further pair of corresponding links; the links of one of said pairs are connected with the frame for pivoting relative thereto about respective axes, the links of the other of said pairs are connected with the first die carrier for pivoting relative thereto about respective pivot axes which move with the first die carrier relative to the frame, each link of the one pair is pivotally connected with a respective link of the other pair and wherein there is provided means for transmitting drive from the connecting rod to the links of both pairs wherein the rectilinear path along which the first die carrier is guided would, if produced, intersect
  • this path is so arranged that this path extends generally in a direction of movement of the first die carrier. Movement of the connecting rod in a direction which is substantially opposite to that in which the first die carrier is moving reduces the effect of acceleration of the first die carrier, in particular the vibration which results from acceleration of the first die carrier.
  • the present invention enables a press to be operated at a higher speed than can a press as disclosed in GB 1,476,757 or US 3,661,008.
  • the linkage is so arranged that the pair of corresponding links between which the crank axis lies move towards and away from the crank axis in unison. If the links have substantially the same mass and are arranged in a corresponding manner, the forces required to produce this movement will balance.
  • a method of working material between a pair of dies wherein a crank is rotated at substantially uniform speed and reciprocates a first member with simple harmonic motion, the motion of the first member is converted to a converted motion other than simple harmonic motion and the converted motion is applied to one of the dies to reciprocate the one die, wherein movement is transmitted to a first of the dies from a rotating crank via a connecting rod and a linkage, wherein movement of the mass of the one die and of parts which reciprocate with the one die in one direction is substantially compensated for by movement of a further mass in a substantially opposite direction, and wherein, as the first die moves in one direction towards the other die, the centre of gravity of the connecting rod moves away from the other die, and there is no substantial movement of the centre of gravity of the linkage in a direction transverse to said one direction.
  • the press shown in the drawings comprises a frame which includes a bed 11, a cross-head 13 disposed above the bed and pillars 12 connecting the cross-head with the bed.
  • a crank shaft 14 is supported for rotation relative to the frame about a horizontal crank axis 15 by means of suitable bearings.
  • suitable bearings there is provided a pair of bearings and the crank 16 is disposed between the bearings.
  • crank shaft 14 On one end portion of the crank shaft 14, there is provided a brake and means for transmitting drive to the crank shaft from an electric motor or other prime mover (not shown).
  • a flywheel also may be mounted on the crank shaft.
  • the brake, flywheel and transmission means may be constructed and arranged in a known manner.
  • first die carrier 19 which, in the example illustrated, is a lower die carrier, for reciprocation relative to the frame along a rectilinear, vertical path which, if produced, would intersect the crank axis 15.
  • the die carrier 19 is disposed above the crank shaft 14.
  • an upper die carrier 20 which is also guided for reciprocation along a rectilinear, vertical path.
  • ejector drive means 21 which is connected with the crank shaft 14 by a belt and pulley drive 22.
  • the ejector drive means and the upper die carrier may be constructed and arranged in a known manner.
  • the press includes a feed surface 23, across which workpieces can be fed to and from a position between respective dies mounted on the die carriers 19 and 20.
  • Feed means is provided for feeding the workpieces across the feed surface 23.
  • the feed means may be a dial plate or other known feed means and provision may be made for transmitting drive in a known manner from the crankshaft 14 to the feed means.
  • There is supported in a position spaced above the feed surface 23 by a distance slightly greater than the thickness of workpieces intended to be worked in the press a collar 24 or ring die.
  • a connecting rod 24 For transmitting motion from the crank 16 to the lower die carrier 19, there is provided a combination of a connecting rod 24 and a toggle linkage 25.
  • the connecting rod 24 executes simple harmonic motion. This motion is modified by the toggle linkage 25 so that the lower die carrier 19 does not execute simple harmonic motion.
  • the lower die carrier dwells in a position such that a coining surface of a die mounted on the lower die carrier is substantially flush with the feed surface 23. Whilst the coining surface of the lower die is flush with this surface, a workpiece which has been coined is moved from the lower die and a workpiece blank is moved into a position directly above the lower die.
  • the toggle linkage 25 comprises a first link 26 and a second link 27 which are pivotally connected to each other adjacent to first ends of these links for relative movement about a pivot axis 32.
  • the first link 26 is also pivotally connected with the first die carrier 19.
  • the second link 27 is pivotally connected adjacent to its end remote from the link 26 with the frame 10 for movement relative to the frame about a pivot axis 33 which is fixed with respect to the frame.
  • this means is provided for transmitting motion from the connecting rod 24 to the links 26 and 27.
  • this means comprises a third link 28 connected adjacent to one of its ends with the first and second links for pivoting relative thereto about the pivot axis 32 and connected adjacent to its opposite end with the connecting rod 24 for pivoting relative thereto about a pivot axis 34.
  • the frame 10 incorporates guide means 35 for guiding that end portion of the connecting rod 24 which is adjacent to the pivot axis 34 along a rectilinear path, the centre line 36 of which coincides with the centre line of the path of travel of the lower die carrier 19 and which passes through the centres of respective coining faces of the dies.
  • the crank shaft 14 turns, the axis 34 is reciprocated along this path and the axis 32 is moved towards and away from the path. Accordingly, the upper end portion of the link 26 is caused to move upwardly and downwardly by rotation of the shaft. It would be within the scope of the invention to pivotally connect the link 26 adjacent to its upper end directly with the lower die carrier 19. In this case, the pivot connection would be intersected by the centre line 36.
  • the toggle linkage comprises fourth, fifth and sixth links 29, 30 and 31 which correspond respectively to the first, second and third links but which are disposed at a side of the centreline 36 opposite to that at which the first, second and third links are disposed.
  • the first and fourth links may be pivotally connected with the lower die carrier 19 for movement relative thereto about a common pivot axis which lies on the centreline 36.
  • a beam 37 which is interposed between the lower die carrier, on the one hand, and the links 27 and 29, on the other hand.
  • the beam is connected with the lower die carrier 19 for pivoting relative thereto about a pivot axis 38 which intersects the centreline 36. Since the lower die carrier is guided by the frame for reciprocation along a path parallel to the centreline 36, the axis 38 is constrained also to move along the centreline 36 and always intersects that centreline.
  • the first link 26 is connected adjacent to its upper end with the beam 37 adjacent to one end of the beam for relative pivoting about a pivot axis 39.
  • the fourth link 29 is connected adjacent to its upper end with the beam adjacent to an opposite end of the beam for relative pivoting about a pivot axis 40.
  • the fourth link 29 is pivotally connected adjacent to its lower end with the fifth link 30 and the sixth link 31 for relative pivoting of these links about a pivot axis 41.
  • the fifth link 30 Adjacent to an end remote from the pivot axis 41, the fifth link 30 is connected with the frame 10 for pivoting about a pivot axis 42 which is fixed with respect to the frame.
  • the pivot axes 32, 33, 34 and 38 to 42 are all parallel to the crank axis 15 and are distributed around that axis.
  • the linkage 25 is represented in Figure 1 in the condition which corresponds to a T.D.C. position of the crank 16 and a B.D.C. position of the lower die carrier 19.
  • the third and sixth links 28 and 31 are substantially co-linear.
  • the pivot axes 32,34 and 41 may lie on a rectilinear line which is perpendicular to the centreline 36.
  • the connecting rod 24 and the pivot axis 34 descend along the centreline 36. This causes the links 28 and 31 to depart from a co-linear relation, so drawing towards the centreline 36 the pivot axes 32 and 41.
  • each of the links 26 to 31 and the connecting rod 24 are subjected during operation to tensile and compressive stresses but are not subjected to any bending load.
  • the length of the connecting rod 24 departs from a parallel relation with the centreline 36. Accordingly, tensile and compressive forces in the connecting rod exert on the pivot which defines the pivot axis 34 forces having both a vertical component and a horizontal component. These horizontal components are borne by the guide means 35 and are transmitted directly to the frame.
  • first and second links 26 and 27 move in unison respectively with the fourth and fifth links 29 and 30.
  • the horizontal component of acceleration of the pivot axis 32 is exactly equal and opposite to the horizontal component of acceleration of the pivot axis 41. Accordingly, these horizontal components of acceleration do not contribute significantly to vibration of the press.
  • the linkage 25 illustrated in the accompanying drawings is arranged for use with a connecting rod 24 which extends from the crank axis 15 in a direction away from the first die carrier 19.
  • the connecting rod may be arranged to extend upwardly from the crank.
  • the third and sixth links would be arranged to drive the pivotal connection between the first and second links away from the pivotal connection between the fourth and fifth links as the connecting rod is driven upwardly, so that the first die carrier would move downwardly during upward movement of the connecting rod.
  • the mass which moves downwardly when the first die carrier moves upwardly is constituted by the crank, connecting rod and by the linkage.
  • the linkage 25 provides two, corresponding paths for the transmission of force from the connecting rod 24 to the lower die carrier 19. Accordingly, the magnitude of the force transmitted by each link of the linkage 25 is approximately half of that force which would be transmitted by the links of a press having the same duty but only a single pair of links, corresponding to the first and second links 26 and 27 of the illustrated arrangement. Accordingly, the links can be relatively light and the aggregate mass of the linkage 25 is not excessive.
  • the mass of the connecting rod 24 is considerably less than is the mass of the first die carrier 19. Even the aggregate of the mass of the connecting rod, the mass of the link 28 and the mass of the link 31 and associated parts which move with the axis 34, may be considerably less than the aggregate of the mass of the first die carrier, the beam 37 and other parts which move with the axis 38.
  • the distance through which the axis 34 moves vertically is considerably greater than is the distance which the axis 38 moves vertically. Accordingly, the movement of the smaller mass represented by the parts which move with the axis 34 is able to compensate for the movement of the larger mass of the parts which move the axis 38.
  • the centre of mass of the asembly comprising the crank and any associated counterweights, the connecting rod, the linkage 25, the beam 37 and the lower die carrier 19 is maintained almost stationary during each cycle 19 of operation of the press.
  • the position of this centre of mass does not move more than 30 mm and preferably not more than 10 mm.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Forging (AREA)

Claims (6)

  1. Presse mit einem Rahmen (10), einer Kurbel (14), die relativ zum Rahmen drehbar um eine Kurbelachse (15) befestigt ist, einem ersten Stempelträger (19), der zur Hin- und Herbewegung entlang einer geradlinigen Bahn von dem Rahmen geführt ist, einem Gestänge (26, 27, 28) zur Übertragung der Bewegung auf den ersten Stempelträger (19) und einer Pleuelstange (24) zur Übertragung der Bewegung von der Kurbel (14) auf das Gestänge (26, 27, 28), dadurch gekennzeichnet, daß das Gestänge ein Paar sich entsprechender Stangen (26, 29), zwischen denen die Kurbelachse (15) liegt, und ein weiteres Paar sich entsprechender Stangen (27, 30) enthält; wobei die Stangen (27, 30) von einem der Paare mit dem Rahmen (10) verbunden und drehbar zu diesem um die jeweiligen Achsen (33, 42) sind, und die Stangen (26, 29) von dem anderen Paar mit dem ersten Stempelträger (19) verbunden und drehbar zu diesem um die jeweiligen Drehachsen (39, 40) sind, welche sich mit dem ersten Stempelträger relativ zum Rahmen (10) bewegen, und jede Stange (27, 30) des einen Paares mit einer jeweiligen Stange des anderen Paares drehbar verbunden ist, wobei ein Mittel zur Antriebsübertragung von der Pleuelstange auf die Stangen beider Paare vorgesehen ist und die geradlinige Bahn entlang welcher der erste Stempelträger geführt ist - falls verlängert - die Kurbelachse kreuzen würde, und das Gestänge angeordnet ist, den ersten Stempelträger (19) in eine Richtung zu bewegen, wenn sich ein von der Kurbel abgewandter Abschnitt der Pleuelstange (24) im wesentlichen in eine entgegengesetzte Richtung bewegt.
  2. Presse nach Anspruch 1, dadurch gekennzeichnet, daß sich die Pleuelstange (24) von der Kurbel (14) in einer von dem ersten Stempelträger (19) weggerichteten Richtung erstreckt.
  3. Presse nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Gestänge erste (26), zweite (27) und dritte (28) Stangen enthält, die angrenzend an jeweilige erste Endabschnitte drehbar um eine parallel zur Kurbelachse (15) verlaufende Drehachse (32) miteinander verbunden sind, und das Gestänge des weiteren vierte (29), fünfte (30) und sechste (31) Stangen enthält, welche angrenzend an erste Endabschnitte drehbar um eine weitere, parallel zur Kurbelachse (15) verlaufende Drehachse (41) miteinander verbunden sind, wobei die dritten (28) und sechsten (31) Stangen miteinander und mit der Pleuelstange (24) angrenzend an zweite Endabschnitte der dritten und sechsten Stangen drehbar verbunden sind, wobei die zweiten (27) und fünften (30) Stangen mit dem Rahmen (10) angrenzend an zweite Endabschnitte der zweiten und fünften Stangen drehbar verbunden sind, und wobei die ersten (26) und vierten (29) Stangen mit dem ersten Stempelträger (19) angrenzend an zweite Endabschnitte der ersten (26) und vierten (29) Stangen drehbar verbunden sind.
  4. Presse nach Anspruch 3, dadurch gekennzeichnet, daß das Gestänge weiterhin umfaßt einen Balken (37), wobei gegenüberliegende Endabschnitte des Balkens (37) drehbar mit den jeweiligen ersten (26) und vierten (29) Stangen angrenzend an deren zweiten Enden drehbar verbunden sind, und ein Mittelabschnitt des Balkens drehbar mit dem ersten Stempelträger (19) verbunden ist.
  5. Presse mit einem Rahmen (10), einem ersten Stempelträger (19), der bei der Hin- und Herbewegung entlang einer geradlinigen Bahn von dem Rahmen (10) geführt wird, einer Kurbel (14), die drehbar zu dem Rahmen (10) um eine Kurbelachse befestigt ist, und einem Gestänge (26-31) zur Umwandlung der durch die Drehung der Kurbel (14) bei einer gleichmäßigen Drehzahl erzeugten, einfachen harmonischen Bewegung in eine sich von der einfachen harmonischen Bewegung unterscheidende, umgewandelte Bewegung und zur Anwendung der umgewandelten Bewegung an dem ersten Stempelträger (19), wobei das Gestänge (26-31) angeordnet ist, eine erhebliche Masse in eine Richtung zu bewegen, wenn der erste Stempelträger (19) in eine entgegengesetzte Richtung bewegt wird.
  6. Verfahren zur Materialbearbeitung zwischen einem Paar von Stempeln, bei dem eine Kurbel (14) mit im wesentlichen gleichmäßiger Drehzahl gedreht wird und ein erstes Bauteil (24) mit einer einfachen harmonischen Bewegung hin- und herbewegt, wobei die Bewegung des ersten Bauteils (24) in eine sich von der harmonischen Bewegung unterscheidende, umgewandelte Bewegung umgewandelt wird, und die umgewandelte Bewegung bei einem der Stempel angewendet wird, um diesen hin- und herzubewegen, wobei die Bewegung von einer sich drehenden Kurbel (14) Über eine Pleuelstange (24) und ein Gestänge (26-31) auf einen ersten der Stempel Übertragen wird, dadurch gekennzeichnet, daß die Bewegung der Masse von dem einen Stempel sowie von Teilen, die sich mit dem einen Stempel in einer Richtung hin- und herbewegen, im wesentlichen durch eine Bewegung einer weiteren Masse in eine im wesentlichen entgegengesetzte Richtung ausgeglichen wird, und wobei sich der Schwerpunkt der Pleuelstange von dem anderen Stempel wegbewegt, während sich der erste Stempel in eine Richtung auf den anderen Stempel zubewegt, und wobei keine erhebliche Bewegung des Schwerpunktes des Gestänges (26-31) in einer quer zu der einen Richtung verlaufenden Richtung auftritt.
EP90910808A 1989-07-22 1990-07-20 Presse und methode für materialbearbeitung Expired - Lifetime EP0435992B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB8916823 1989-07-22
GB8916823A GB2234196B (en) 1989-07-22 1989-07-22 Press and method of working material
PCT/GB1990/001116 WO1991001214A1 (en) 1989-07-22 1990-07-20 Press and method of working material

Publications (2)

Publication Number Publication Date
EP0435992A1 EP0435992A1 (de) 1991-07-10
EP0435992B1 true EP0435992B1 (de) 1995-06-07

Family

ID=10660495

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90910808A Expired - Lifetime EP0435992B1 (de) 1989-07-22 1990-07-20 Presse und methode für materialbearbeitung

Country Status (6)

Country Link
EP (1) EP0435992B1 (de)
JP (1) JP2895219B2 (de)
AT (1) ATE123440T1 (de)
DE (1) DE69019939T2 (de)
GB (1) GB2234196B (de)
WO (1) WO1991001214A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4113568C1 (de) * 1991-04-25 1992-05-21 Curt 8122 Penzberg De Niebling
DE4411900C2 (de) * 1994-04-07 2002-07-04 Graebener Pressensysteme Gmbh Prägepresse, insbesondere Münzprägepresse
JPH10128597A (ja) * 1996-10-28 1998-05-19 Aida Eng Ltd リンクを用いたプレスのスライド駆動装置

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1801575A (en) * 1927-11-04 1931-04-21 Delco Remy Corp Molding press
GB397558A (en) * 1931-12-31 1933-08-31 Frank Humphris Improvements in presses and other pressure-exerting machines
GB502808A (en) * 1937-09-24 1939-03-24 Frank Humphris Improvements in or relating to machines employed for moulding or producing articles from plastic, granular or powdered substances, or from metal
US2269758A (en) * 1938-10-12 1942-01-13 Noronha Rubber Products Corp D Mechanical press
CH354331A (fr) * 1959-05-05 1961-05-15 Bobst Fils Sa J Mécanisme d'entraînement de la platine mobile d'une presse à platines
FR1431926A (fr) * 1965-02-05 1966-03-18 Forges Et Acieries Du Saut Du Dispositif de manoeuvre à couple variable et à fonctionnement de sécurité
GB1285181A (en) * 1969-03-19 1972-08-09 Wickman Mach Tool Sales Ltd Presses
US3661008A (en) 1970-03-17 1972-05-09 Wickman Mach Tool Sales Ltd Presses
CH541369A (de) * 1970-06-10 1973-09-15 Schuler Gmbh L Vorrichtung zum gleichzeitigen spanlosen Bearbeiten von zwei Metallwerkstücken an zwei Arbeitsstellen
CH543375A (de) * 1971-10-01 1973-10-31 Bruderer Ag Einrichtung zur Führung des Bärs einer Stanzmaschine
DE2346810C3 (de) * 1973-09-18 1978-08-10 Theodor Graebener Maschinenfabrik, 5931 Netphen Münzprägemaschine
CH581281A5 (de) * 1974-09-03 1976-10-29 Bruderer Ag
DE2912927A1 (de) * 1979-03-31 1980-10-16 Schuler Gmbh L Antrieb fuer eine presse
EP0057741B1 (de) * 1981-02-11 1984-08-01 L. SCHULER GmbH Pressenantrieb

Also Published As

Publication number Publication date
WO1991001214A1 (en) 1991-02-07
ATE123440T1 (de) 1995-06-15
JPH04505289A (ja) 1992-09-17
GB8916823D0 (en) 1989-09-06
EP0435992A1 (de) 1991-07-10
JP2895219B2 (ja) 1999-05-24
DE69019939D1 (de) 1995-07-13
DE69019939T2 (de) 1995-10-19
GB2234196A (en) 1991-01-30
GB2234196B (en) 1993-02-17

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