EP0881047A2 - Dispositif d'entraínement pour une presse d'estampage - Google Patents

Dispositif d'entraínement pour une presse d'estampage Download PDF

Info

Publication number
EP0881047A2
EP0881047A2 EP98109290A EP98109290A EP0881047A2 EP 0881047 A2 EP0881047 A2 EP 0881047A2 EP 98109290 A EP98109290 A EP 98109290A EP 98109290 A EP98109290 A EP 98109290A EP 0881047 A2 EP0881047 A2 EP 0881047A2
Authority
EP
European Patent Office
Prior art keywords
drive device
connecting rod
coupling element
drive
axis
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.)
Withdrawn
Application number
EP98109290A
Other languages
German (de)
English (en)
Other versions
EP0881047A3 (fr
Inventor
Hartmut Prof. Dr.-Ing. Hoffmann
Roland Dr.-Ing. Golle
Bertram Schäfer
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.)
L Schuler GmbH
Original Assignee
L Schuler GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by L Schuler GmbH filed Critical L Schuler GmbH
Publication of EP0881047A2 publication Critical patent/EP0881047A2/fr
Publication of EP0881047A3 publication Critical patent/EP0881047A3/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
    • B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
    • B26F1/38—Cutting-out; Stamping-out
    • B26F1/40—Cutting-out; Stamping-out using a press, e.g. of the ram type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • B26D5/14—Crank and pin means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/10—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks

Definitions

  • the invention relates to a drive device for a punching or cutting press in which the ram passes through the drive device is mechanically positively driven.
  • the quality of those obtained from the metal strip Improve cutting parts. This applies in particular to the Condition of the peripheral surfaces of the cut parts, which in the separation process have been generated.
  • the interface is usually divided into a flow area and a fracture area, with the edges of the Cut part a feed area and on the opposite side Form the ridge. Both the catchment area and the Burrs are mostly undesirable. Beyond that often pay attention to the quality of the interface themselves that are as smooth and perpendicular to the Flat sides of the cut part should be aligned.
  • the quality of the cut parts can be largely determined by affect the cutting speed.
  • high-speed shear cutting process at which the cutting speeds For example, over 4 m / s can have very good cutting results be achieved.
  • High cutting speeds with mechanical Achieving tappet drives is in two ways Problematic. Toward high cutting speeds with an eccentric drive, e.g. through high speeds reached the drive, it drops for further transport and for positioning the sheet metal strip standing time below a critical level, so that arising Tolerances and the wear of appropriate facilities increases. The drive speed would also be up to increase such a measure that both the eccentric with regard to the forces and wear it would be difficult to control and the service life of the Cutting or punching tools due to the increased chemical Load would decrease to a great extent.
  • the drive device is as a coupling detent gear formed that from a continuous uniform Rotary motion on a plunger is a striking motion generated.
  • the coupling latch gear has a Crank-serving drive element on that via a coupling element is connected to a connecting rod.
  • the coupling element is articulated in the middle on a rocker. The arrangement is such that the common Center of gravity of the drive element and the coupling element lies on the axis of rotation around which the drive element turns.
  • the cutting speeds have been included 0.5 - 1 m / s, with the drive device according to the invention allows a cutting speed that is about ten times larger.
  • the increased cutting speed leads to a significantly improved cut quality, it is possible to cut parts without indentation and without creating burrs.
  • the interface has essentially only a fracture area that is very fine-grained. Overall, the geometric accuracy can also be determined improve, in particular largely the interface is aligned at right angles to the rest of the cut part.
  • the cutting tools larger cutting gaps are provided without the Cut part quality unduly impaired.
  • the inertia acts of the metal strip at least to a certain extent as an abutment for the penetrating into the sheet metal strip Cutting punch. This will reduce the share of force transmitted from the stamp to the sheet metal strip forwarded laterally to the cutting dies and at the Supported matrix. This can also be the geometric accuracy improve.
  • the drive element is preferably essentially as a disc with an eccentrically arranged opening formed in which the also substantially disc-shaped Coupling element is mounted.
  • the disc-shaped coupling element is driven by the rotating drive element in an orbit led around the main axis of rotation, with which Drive element acts as a crank.
  • the unit of crank and Coupling element is balanced, however, because their individual centers of gravity in relation to the main axis of rotation diametrically opposite.
  • the coupling element is off-center with a rocker connected, the other end, for example.
  • On the press frame is pivotally mounted.
  • the swing arm can be used as one-armed lever, as a counterweight lever or be designed as a disc. By an opposite Lever or an opposing disc can be used if necessary a complete mass balance is achieved will.
  • the connecting rod pivot point is a symmetrical path.
  • the connecting rod there will be a course the ram height depending on the rotation of the drive element achieved where the lowering and the The ram is lifted symmetrically.
  • An asymmetrical Course for example a quick lowering and a bit allows slower lifting of the plunger thereby achieve that the eccentric axis, the swing arm pivot point and the connecting rod pivot point at the corners of a Triangle.
  • the coupling element and, if necessary, the rocker element can also use the connecting rod's inertial forces and the plunger compensated by appropriate counterforces will. This can affect the stroke movement of the Plunger of the connecting rod and with respect to the pivoting movement of the connecting rod take place separately, each accordingly moving counterweights are provided.
  • Such a balanced drive device can with relatively high Speeds are operated.
  • the forming press can be used as an embossing, Forge or hammer press be formed.
  • a cutting press 1 and 2 is a cutting press 1 with a drive device 2 illustrates a continuous rotary motion into a quick stroke motion a plunger 3 implements.
  • the plunger 3 carries one Cutting punch 4, which has a corresponding, stationary Die 6 is assigned.
  • a sheet metal strip 7 is guided, that with a feed and not illustrated Positioning device then step by step in the direction T between the punch 4 and the Die 6 is continued when the cutting punch 4th is in an upper position.
  • the drive device 2 has a main axis of rotation 11 rotatably mounted disc 12, which as Drive element of the drive device 2 serves and over a shaft 13 is driven continuously rotating.
  • the Disc 12 has an eccentricity against the Main axis of rotation 11 offset opening 14 in which one Disk 16 is rotatably mounted about an eccentric axis 17.
  • the focus of the disc 16 is on the eccentric axis 17.
  • the focus of the disc 12 is this Center of gravity with respect to the main axis of rotation 11 diametrically opposite, so that the overall focus of the from the Disks 12, 16 unit formed on the main axis of rotation 11 lies.
  • the disc 16 On the disc 16 is off-center at a connecting rod pivot point P attached to a connecting rod 18 over which the Disk 16 with the one stored in a straight guide 19 Ram 3 is connected.
  • a connecting rod pivot point P Around the middle of the straight one Connection line between the eccentric axis 17 and the The connecting rod pivot point P is the disk 16 at a rocker pivot point S pivotally connected to a rocker 21. This is about a pivot axis 22 fixed to the frame pivoted.
  • the disc 16 thus forms that Coupling element of a coupling ratchet gear, its crank by the eccentricity E of the opening 14 in the disk 12 is formed. It also belongs to the coupling detent gear the swing arm 21.
  • the swing arm 21 and the imaginary extension of the Swing 21 close in all or at least almost all rotational positions of the disc 12 with one another acute angle. This ensures that the connecting rod 18 the downward, sudden component of motion the disk 16 serving as a coupling on the plunger 3 transmits.
  • the essential dimensions of the coupling latch mechanism can be determined from the diagram shown in FIG. 4.
  • the relationship between the length of the crank or eccentricity E and the length l 21 of the rocker 21 is illustrated on the abscissa.
  • the ordinate shows the ratio of the center distance l 1 , which is the distance between the main axis of rotation 11 and the pivot axis 22, and the length l 21 of the rocker.
  • sin ⁇ 1 the sines of the coupling angle are entered in the position of top dead center.
  • the parameter sin ⁇ 4th is the sine of the coupling angle when leaving the rest phase.
  • the rest phase is the area in which the tappet remains in its upper stroke area.
  • the area designated I in FIG. 4 is a Design range, in particular for the ratchet gear is expedient if the drive device 2 is used to drive a cutting tool.
  • Fig. 5 illustrates the plunger over large parts the angle of rotation of the disc 12 near its upper Dead center kept. Only in a relatively small one Angular range that can be set to any size, the plunger 3 moves in a rapid stroke lowered to its bottom dead center and below returned again. The plunger 3 reaches how results from the sharp increase in its movement curve K, a very high speed, which is currently conceivable technically rollable range of 10 m / s, but can also be much higher if appropriately interpreted can.
  • FIG Curve V plotted with a simple Eccentric drive is reached.
  • a higher ram speed with the coupling detent gear but also a shortened stroke reached.
  • the higher ram speed allowed without excessive Increasing the number of strokes a very fast punching process, which enables an improved quality of cut parts.
  • good geometric accuracy can be achieved by Elimination of the edge feed zone and the burr on the Cutting as well as by improving the squareness of the dividing surfaces are made possible.
  • the interface is essentially due to a fine-grained fracture area is formed and the flow area is reduced or suppressed.
  • FIGS. 3a to 3d To illustrate the function of the as a coupling detent gear trained drive device 2 is in following with reference to FIGS. 3a to 3d.
  • the rotating disk 12 guides the disk 16 on a Eccentric track about the main axis of rotation 11, so that the eccentric axis 17, which is also the central axis of the disk 16 forms the main axis of rotation 11 on a circle with the Radius E circled.
  • the rocker 21 prevents one Rotates the disc 16 and leads to the rotation of the Disc 12 a pendulum motion. This overlays a vertical movement so that the connecting rod pivot point P is the symmetrical path B illustrated in FIG. 3a goes through.
  • the coupling ratchet mechanism is at least in relation to the Rotation of the disks 12 and 16 balanced. However can still 21 free inertia forces from the rocker going out. These can be countered by one driven swing arm can be compensated. Besides, can the rocker 21 can be designed as a disc, if necessary assigned an oppositely driven disc is.
  • FIGS. 6, 6a and 7 Arrangements can be used.
  • the horizontal, through which Pivotal movement of the connecting rod 18 caused moments of inertia can be compensated by a counterweight 24 be articulated at an articulation device 26, in which the connecting rod 18 is also articulated with the tappet 3 connected is.
  • a transmission device 27 drives this a rod 28 counterweight held counter to that Connecting rod 18 in a swivel motion.
  • the transmission device 27 can by two intermeshing, each gears connected to the connecting rod 18 or the rod 28 be educated.
  • the plunger 3 can each with a joint 29 End of two two-armed levers pointing away from each other 31, 32, which are connected to the plunger 3 the opposite end each carry a counterweight 33.
  • the levers 31, 32 are mounted on rockers 34, 35.
  • the disc 12 In the drive device according to FIGS. 1 and 2 is the disc 12 with the shaft 13 via a bracket 36 connected, which extends from the shaft 13 to one in the Extends near the circumference of the disk 12 point.
  • a storage device 37 serve the disc 12 on its peripheral surface 38th stores.
  • the rollers 40 can also as Serve drive means. If necessary, they can be used as gears be formed when the peripheral surface 38 of the Disk 12 is also toothed.
  • the disc 12 is then floating between the rollers or gears 40 stored.
  • the connecting rod 18 be forked and on both sides of the disc 16 attack each on the connecting rod pivot point P.
  • the Disk 12 can also on its peripheral surface Roller bearings in the machine frame, i.e. the Rollers 40 are guided into a cage and are not stationary, but all around the disc 12.
  • FIG Figure 9 Another modified embodiment of the drive device 2 is extremely schematized in FIG Figure 9 illustrates.
  • this embodiment that formed by the disks 12, 16 and the rocker 21 Coupling ratchet gear designed so that an asymmetrical Movement course is generated, as it is in FIG. 10 is illustrated.
  • the main difference to the Embodiments of the coupling ratchet mechanism described above is that the eccentric axis 17 of the Swing arm pivot point S and the connecting rod pivot point P here do not lie on a straight line but define a triangle. That of the eccentric axis 17, the pivot point S and the connecting rod pivot point P defined blunt Angle opens away from the rocker 21.
  • the plunger 3 and in particular the Connection point between the connecting rod 18 and the tappet 3 is arranged below the pivot axis 22 so that the Main axis of rotation 11, the pivot axis 22 and the connection point define a right angle with each other, there is a curve in which a very fast Downstroke and a slightly slower ascending stroke be achieved.
  • a drive device for the plunger 3 is designed as a coupling detent gear.
  • the crank and the coupling of the coupling latch gear are designed that regardless of the current position of the Elements to each other the resulting focus on is the main axis of rotation 11 about which the crank rotates.
  • Such a coupling ratchet enables the number of strokes required for punching presses, the mechanically positively driven plunger a sudden Labor movement is granted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Press Drives And Press Lines (AREA)
EP98109290A 1997-05-28 1998-05-22 Dispositif d'entraínement pour une presse d'estampage Withdrawn EP0881047A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19722245 1997-05-28
DE1997122245 DE19722245A1 (de) 1997-05-28 1997-05-28 Antriebseinrichtung für eine schnellaufende Stanz- und Schneidpresse

Publications (2)

Publication Number Publication Date
EP0881047A2 true EP0881047A2 (fr) 1998-12-02
EP0881047A3 EP0881047A3 (fr) 1999-11-24

Family

ID=7830679

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98109290A Withdrawn EP0881047A3 (fr) 1997-05-28 1998-05-22 Dispositif d'entraínement pour une presse d'estampage

Country Status (2)

Country Link
EP (1) EP0881047A3 (fr)
DE (1) DE19722245A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008057019A1 (de) 2008-11-12 2010-05-20 Reinhard Schmid Umformwerkzeug zur Bearbeitung von Werkstücken
CN107671937A (zh) * 2017-10-27 2018-02-09 惠州市齐力建筑工程有限公司 一种用于对建筑材料打孔的自动打孔机构
CN108437519A (zh) * 2018-03-23 2018-08-24 沈义琪 一种医疗用废弃纸盒压缩设备
CN109159163A (zh) * 2018-06-28 2019-01-08 湖州吾爱食品有限公司 一种切断效率高的食品加工用切断装置
CN112140169A (zh) * 2020-10-21 2020-12-29 周书勇 一种竹笋剥皮分段装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10217026C1 (de) * 2002-04-12 2003-12-04 Fraunhofer Ges Forschung Schneideinrichtung
DE102004043189B3 (de) * 2004-09-03 2005-08-25 Msa Maschinenbau - Service - Automatisierungstechnik Gmbh Schneidpresse
DE102009003655B4 (de) 2009-03-23 2012-01-19 Thyssenkrupp Steel Europe Ag Verfahren zum Herstellen einer Blechplatine, sowie eine Blechplatine und das Umformwerkzeug zum Herstellen eines Bleches mit einem Dickenübergang an einer Verbindungskante

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2610524A (en) * 1948-06-23 1952-09-16 Frederick K Maust Counterbalancing device
CH302228A (de) * 1950-01-31 1954-10-15 Svetsmekano Ab Maschine zum Schneiden von Blech.
DE2000669A1 (de) * 1969-01-13 1970-08-13 Gulf Western Ind Products Comp Presse
GB1241726A (en) * 1968-05-23 1971-08-04 Aida Tekkosho Kk A slide drive mechanism in a press
DE4308475A1 (de) * 1993-03-17 1994-09-22 Pressen Engineering Essen Gmbh Antrieb für den Stößel einer Schnittpresse oder Umformmaschine
DE29515426U1 (de) * 1994-11-23 1995-11-30 Gebr. Edelhoff GmbH & Co. KG Werkzeugmaschinenfabrik, 42329 Wuppertal Mechanische Presse

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2610524A (en) * 1948-06-23 1952-09-16 Frederick K Maust Counterbalancing device
CH302228A (de) * 1950-01-31 1954-10-15 Svetsmekano Ab Maschine zum Schneiden von Blech.
GB1241726A (en) * 1968-05-23 1971-08-04 Aida Tekkosho Kk A slide drive mechanism in a press
DE2000669A1 (de) * 1969-01-13 1970-08-13 Gulf Western Ind Products Comp Presse
DE4308475A1 (de) * 1993-03-17 1994-09-22 Pressen Engineering Essen Gmbh Antrieb für den Stößel einer Schnittpresse oder Umformmaschine
DE29515426U1 (de) * 1994-11-23 1995-11-30 Gebr. Edelhoff GmbH & Co. KG Werkzeugmaschinenfabrik, 42329 Wuppertal Mechanische Presse

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008057019A1 (de) 2008-11-12 2010-05-20 Reinhard Schmid Umformwerkzeug zur Bearbeitung von Werkstücken
CN107671937A (zh) * 2017-10-27 2018-02-09 惠州市齐力建筑工程有限公司 一种用于对建筑材料打孔的自动打孔机构
CN108437519A (zh) * 2018-03-23 2018-08-24 沈义琪 一种医疗用废弃纸盒压缩设备
CN109159163A (zh) * 2018-06-28 2019-01-08 湖州吾爱食品有限公司 一种切断效率高的食品加工用切断装置
CN112140169A (zh) * 2020-10-21 2020-12-29 周书勇 一种竹笋剥皮分段装置

Also Published As

Publication number Publication date
DE19722245A1 (de) 1998-12-03
EP0881047A3 (fr) 1999-11-24

Similar Documents

Publication Publication Date Title
DE2655583C2 (de) Stichsäge
DE3044083C2 (de) Stanzeinrichtungen für Stanzautomaten zum Stanzen von Bögen aus Papier, Pappe u. dgl.
DE69935543T2 (de) Säge mit hin und her gehendem Sägeblatt
DE19521050C2 (de) Kniehebel-Antriebsvorrichtung
DE112013001648B4 (de) Pressenantrieb mit mehreren Arbeitsbereichen
DE3750404T2 (de) Reibschweissgerät.
EP0647283B1 (fr) Mecanique d'armures pour une machine a tisser
DE102004040163C5 (de) Rundläufertablettenpresse
EP0881047A2 (fr) Dispositif d'entraínement pour une presse d'estampage
EP1980351A2 (fr) Scie à métaux
EP2960374A1 (fr) Appareil de travail doté d'un moulin à bocards ou d'un outil de percussion ayant une transmission à bielle oblique
EP0724953B1 (fr) Poinçonneuse avec espace allongé pour le montage de poinçons
DE2131013C2 (de) Ziehpresse
DE2318970B2 (de) Fliegende Schere oder Stanze für laufendes Material
DE202019106534U1 (de) Stahlblechfördermechanismus an einer Stanze
DE683535C (de) Antriebsvorrichtung fuer die Wirkwerkzeuge von Kettenwirkmaschinen
EP0953438B1 (fr) Presse à estamper, en particulier presse rapide
DE102006026261B3 (de) Stoßvorrichtung zum Stoßen von Nuten für Werkzeugmaschinen mit einem Werkzeugdrehantrieb, insbesondere für CNC-Drehmaschinen
CH638720A5 (de) Presse.
DE69508535T2 (de) Nockenvorrichtung
CH646375A5 (de) Antrieb fuer eine presse.
DE1939888A1 (de) Schmiedepresse
EP0381919A2 (fr) Machine de forgeage pour le forgeage continu de matériau en forme de boudin, notamment de brames provenant de la coulée continue
DE545042C (de) Vorrichtung zum Brechen von Kohle, Steinen oder aehnlichen Stoffen
DE4218955C2 (de) Antrieb für eine Exzenterwelle einer Exzenterschmiedepresse

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): CH DE ES FR GB LI SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHULER PRESSEN GMBH & CO. KG

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RIC1 Information provided on ipc code assigned before grant

Free format text: 6B 26F 1/40 A, 6B 26D 5/14 B, 6B 30B 1/14 B

17P Request for examination filed

Effective date: 20000510

AKX Designation fees paid

Free format text: CH DE ES FR GB LI SE

17Q First examination report despatched

Effective date: 20020924

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20030405