EP0356809A1 - Dispositif pour le réglage de la course dans une presse à poinçonner - Google Patents

Dispositif pour le réglage de la course dans une presse à poinçonner Download PDF

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Publication number
EP0356809A1
EP0356809A1 EP89115109A EP89115109A EP0356809A1 EP 0356809 A1 EP0356809 A1 EP 0356809A1 EP 89115109 A EP89115109 A EP 89115109A EP 89115109 A EP89115109 A EP 89115109A EP 0356809 A1 EP0356809 A1 EP 0356809A1
Authority
EP
European Patent Office
Prior art keywords
clutch
eccentric shaft
disc
push rod
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP89115109A
Other languages
German (de)
English (en)
Other versions
EP0356809B1 (fr
Inventor
Martin Brunner
Helmut Messner
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.)
Bruderer AG
Original Assignee
Bruderer AG
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 Bruderer AG filed Critical Bruderer AG
Publication of EP0356809A1 publication Critical patent/EP0356809A1/fr
Application granted granted Critical
Publication of EP0356809B1 publication Critical patent/EP0356809B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/263—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks work stroke adjustment means
    • 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
    • Y10T74/21—Elements
    • Y10T74/211—Eccentric
    • Y10T74/2111—Plural, movable relative to each other [including ball[s]]
    • Y10T74/2112—Concentric
    • 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
    • Y10T83/8843—Cam or eccentric revolving about fixed axis

Definitions

  • the present invention relates to a device for stroke adjustment of a punch press with an eccentric shaft and an eccentric bush mounted thereon to form a double eccentric, with a drive flywheel driven by the machine drive and a disc clutch for coupling the drive flywheel to the eccentric shaft, with a disc brake which acts on the eccentric shaft and with a spring-loaded locking pin guided in a radial bore of the eccentric shaft, which is used to lock the eccentric shaft with the eccentric bushing.
  • the stroke adjustment is carried out hydraulically or mechanically, the associated adjusting members being moved by additional drives and running into the same from the end region of the eccentric shaft which is turned away from the flywheel. If the punch press in question is not a two-stroke machine but a multiple-stroke machine, the stroke movement to the associated feed device must also be reset after the stroke has been changed.
  • the feed drive is also connected to the eccentric shaft, so that the connection between the eccentric shaft and the feed drive must be interrupted when the UTP or OTP is entered again.
  • there are additional drives for actuating the corresponding actuators used which are also arranged at that end region of the eccentric shaft which is opposite from the flywheel.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problems of creating a device for adjusting the stroke of a punch press, in which no additional drives are necessary, so that a simpler and more compact design is achieved.
  • the device is advantageously designed in such a way that the control device in the eccentric shaft of the rotatably mounted, axially immovable shaft section, which is non-rotatably connected to the clutch disc of the further disk clutch, is adjoined by a threaded section which is screwed to a thread of a push rod which is translationally displaceable in the eccentric shaft is that the push rod and the locking pin have mutually interacting force transmission means, by means of which the translatory displacement of the push rod in the axial direction of the eccentric shaft can be converted into a movement of the locking pin in the radial direction thereof.
  • the control device can also control the tensioning or relaxation of the tensioned clutch disk.
  • a push rod of the control device advantageously has a collar which rests on the tensionable coupling disk, by means of which the tensioning state of the tensionable coupling disk can be changed depending on the axial position of the push rod.
  • the single figure shows a sectional view through an embodiment of the lifting device according to the invention adjustment of a punch press.
  • An eccentric shaft 1 is rotatably mounted in the machine frame 8.
  • An eccentric bushing 2 is mounted on the inner eccentric section 32 thereof by means of bearings 33.
  • two connecting rods 34 are mounted on them, which in turn are connected to the ram of the punch press (not shown).
  • the punch press is driven by the machine drive 4, which has a positionable drive with a correspondingly controlled electric motor, e.g. DC motor, is.
  • a respective rotational position of its rotor at a particular standstill can therefore be precisely controlled.
  • the motor drives a pulley 35 which is connected to one or more belts 3, e.g. V-belt, with the drive flywheel 5 is drive-connected.
  • the drive from the flywheel 5 to the eccentric shaft 1 takes place via a disk clutch 6.
  • This has a clutch disk 26, which is firmly connected to the eccentric shaft 1.
  • the clutch disc 26 is equipped with friction linings 36. Further, the clutch disc 26, i.e. In particular, their friction linings 36 are arranged in the flywheel 5 and in particular between the flywheel 5 and an annular piston 27.
  • This ring piston is rotatably supported by bolts 38 in the flywheel 5, but axially displaceable.
  • Tension springs 39 act on these bolts 38, which tension the annular piston 27 away from the clutch disc 26.
  • Compressed air from the pneumatic control is introduced into the annular space 37 via a feed arrangement 40. If the annular piston 27 is pressurized accordingly with compressed air, it is against the restoring force of the tension springs 39 on the clutch disc 26, i.e. their friction linings 36, pressed on and bends them up a little so that a frictional engagement with the flywheel 5 takes place.
  • the disc clutch 6 is thus closed and the eccentric shaft 1 is rotated by the flywheel 5 via the clutch disc 26.
  • the brake disc 41 is also firmly connected to the eccentric shaft 1 and acts between the machine housing 8 and a ring piston 42 which is pressurized with compressed air and biased by springs 43.
  • the springs 43 tension the ring piston 42 for contact with the machine housing 8, so that in this case the eccentric shaft 1 is locked. If compressed air is supplied via the supply line 44, the annular piston 42 moves away from the machine housing, so that the eccentric shaft 1 can be freely rotated.
  • the disk clutch 6 If, therefore, with reference to the preceding section, the disk clutch 6 is engaged, the disk brake 7 must be released at the same time in order to allow the eccentric shaft 1 to rotate.
  • a bore 9 is formed in the inner eccentric section 32 of the eccentric shaft 1.
  • a locking pin 10 is slidably mounted in the radial direction of the eccentric shaft 1.
  • This locking pin engages with at least one projection, for example a toothing 11, in an internal toothing 12 of the eccentric bushing 2 mounted on the eccentric shaft 1.
  • this locking pin is tensioned by means of a spring 45 for engagement in the eccentric bushing 2.
  • the locking pin 10 is further provided with an opening 24, which will be discussed in more detail later.
  • the feed drive 14 is arranged.
  • the front end of the eccentric shaft 1 has an axially projecting, annular projection 46.
  • a bevel gear 29 which drives the drive shaft 48 of the feed device via a further gear 47.
  • a tensionable clutch disc 13 is arranged between the bevel gear 29 and the annular projection 46 of the eccentric shaft 1. This is resilient and can be designed as a plate spring.
  • a further disk clutch 15 is arranged in the annular piston 27 of the disk clutch 6.
  • Your clutch disc 16 is fixedly connected to a shaft section 17 which forms part of the actual control device. If the clutch disc 16 of the further disc clutch 15 is pressed by an additional annular piston 28, which is non-rotatably but axially displaceably mounted in the first-mentioned annular piston 27, by applied compressed air against the biasing force of the return spring 49 against the annular piston 27, the rotary movement of the flywheel 5 is via the Ring piston 27 and the clutch disc 16 transferred to the shaft portion 17.
  • This shaft section is rotatable in the eccentric shaft 1 and is axially immovable.
  • the shaft section 17 has an externally threaded section 18 at its end opposite the clutch disk 16. This external thread section 18 is screwed into an internal thread 19 of a push rod 20.
  • This internal thread 19 Connected to this internal thread 19 is a section of the push rod 20 designed as a control wedge 22.
  • This control wedge 22 has a run-up slope 23.
  • the above-mentioned opening 24 of the locking pin 10 has a wall section which rests on this run-up slope 23.
  • the push rod 20 finally continues to the collar 21, by means of which the tensionable clutch disc 13 is tensioned or relaxed.
  • a recess is formed in the bevel gear 29. This serves to receive a locking bolt 31 which is displaceably mounted in the machine housing 8. When the clutch disc 13 is relaxed, whereby the power transmission to the feed drive 14 is interrupted, the locking bolt 31 can be moved into the recess 30 and the feed can be locked accordingly.
  • a recess 52 of a locking bolt 53 which ends with a piston 54 which can be pressurized with compressed air and is tensioned away from the eccentric bushing by a return spring 55. If the piston 54 is pressurized with compressed air, the locking bolt 53 moves in the recess 52, so that the eccentric bush 2 is locked.
  • the machine drive 4 When the machine drive 4 is at a standstill, the further disk clutch 15 remains released. The disc clutch 6 is closed and the disc brake 7 is released.
  • the machine drive 4 which, as already mentioned, is a positionable drive with an electric motor, is controlled in such a way that it rotates the eccentric shaft 1 into the “top dead center” position via the drive belt 3 and the flywheel 5 and the closed clutch 6. In this position, the motor of the drive 4 is stopped, and now the disc brake 7 is closed, and thus the eccentric shaft 1 is locked in the "top dead center” position mentioned.
  • the corresponding position is monitored or controlled by the switch 50.
  • the figure illustrates the position of the push rod 20 or the collar 21 with the clutch disc 13 just relaxed, so that the end disc 51 acting on the switch 50 is in the position shown.
  • the brake 7 is closed and the clutch 6 acting on the eccentric shaft 1 is opened.
  • the eccentric shaft 1 is thus locked against rotation.
  • the further disk clutch 15 is closed.
  • the motor of the drive 4 is put into operation again, and the shaft section 17 is thus rotated further via the closed further coupling 15, with the result that the push rod 20 and in particular the one on it trained control part 22 is moved to the right with the ramp slope 23.
  • This run-up slope 23 interacts with the wall portion 25 of the opening 24 in the locking pin 10, so that the locking pin 10 is extended against the force of the spring 45 out of the recess or internal toothing 12 of the eccentric bushing 2.
  • the position of the control part 22 corresponding to the complete extension is monitored by a further limit switch 56, which also interacts with the end plate 51 of the push rod 20.
  • the eccentric shaft 1 is rotated by operating the motor of the drive 4 due to the now closed clutch 6 until it has reached the "new stroke" position, that is to say the position which assumes a newly selected stroke.
  • the eccentric shaft 1 is rotated by exactly 180 °, in the case of a multiple-stroke machine by so many degrees that are necessary to achieve the new stroke.
  • the eccentric bushing 2 remains locked or held in the drawn position due to the engaging locking bolt 53.
  • it obviously rotates together with the connecting rods 34 and the tappet (not shown) in the vertical direction relative to the machine frame, in accordance with the distance corresponding to reaching the new stroke.
  • the new stroke is now set.
  • the brake 7 and the further disk clutch 15 acting on the push rod 20 are closed and the clutch 6 acting on the eccentric shaft 1 is released.
  • the motor of the drive 4 is rotated in the opposite direction of rotation and thus the shaft section 17 is closed via the closed further coupling 15 rotated back and thus the push rods 20 are withdrawn through the external thread section 18 and the internal thread 19 (to the left in the drawing).
  • This also moves the control part 22 with the run-up slope 23 (to the left) until the locking pin 10 engages completely in the internal toothing 12 (or recess) and thus the eccentric sleeve 2 is locked with the eccentric shaft 1, now in the "new stroke" position is.
  • the further disk clutch 15 on the one hand and the tensionable clutch disk 13 on the other hand are now dimensioned such that the ratio: torque that can be transmitted through tensioned clutch disk 13 to: torque that can be transmitted through the disk clutch 15 is selected such that when the closed disk clutch 15 continues to rotate, it then only slips begins after the tensionable clutch disc 13 is tensioned to transmit the torque required in operation.
  • the push rod 20 moves to the left until the disk clutch 15 slips and thus the tensionable clutch disk 13 is tensioned by the collar 21 with the predetermined operating torque. So there is a construction here that works like a torque wrench.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Presses And Accessory Devices Thereof (AREA)
EP89115109A 1988-08-31 1989-08-16 Dispositif pour le réglage de la course dans une presse à poinçonner Expired - Lifetime EP0356809B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3240/88A CH677336A5 (fr) 1988-08-31 1988-08-31
CH3240/88 1988-08-31

Publications (2)

Publication Number Publication Date
EP0356809A1 true EP0356809A1 (fr) 1990-03-07
EP0356809B1 EP0356809B1 (fr) 1992-12-09

Family

ID=4251683

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89115109A Expired - Lifetime EP0356809B1 (fr) 1988-08-31 1989-08-16 Dispositif pour le réglage de la course dans une presse à poinçonner

Country Status (5)

Country Link
US (1) US4987794A (fr)
EP (1) EP0356809B1 (fr)
JP (1) JP2552000B2 (fr)
CH (1) CH677336A5 (fr)
DE (1) DE58902956D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2008799A1 (fr) * 2007-06-28 2008-12-31 Bruderer Ag Presse à découper
WO2017035671A1 (fr) * 2015-09-02 2017-03-09 Bruderer Ag Presse d'emboutissage et/ou de formage

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0547351B1 (fr) * 1991-12-02 1996-05-08 Aida Engineering, Ltd. Dispositif de réglage de la course du coulisseau dans une presse
DE10007505B4 (de) * 2000-02-18 2007-06-14 Schuler Pressen Gmbh & Co. Kg Elektrische Antriebsvorrichtung
WO2004009186A1 (fr) * 2002-07-24 2004-01-29 Burrows Golf, Inc. Connexion temporaire tige de baton de golf-composant
EP2363215B1 (fr) * 2010-03-05 2012-10-31 HINTERKOPF GmbH Dispositif de formage
CN104494183A (zh) * 2014-09-15 2015-04-08 上海天阖机械设备有限公司 一种蜗轮手动一体互换式单冲压片机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2155463A5 (fr) * 1971-10-01 1973-05-18 Bruderer Ag
DE2534626A1 (de) * 1974-09-03 1976-03-11 Bruderer Ag Vorrichtung fuer den massenausgleich bei mittels kurbeltrieb angetriebenen maschinen
GB2189731A (en) * 1986-04-28 1987-11-04 Bruderer Ag Stroke adjustment in punching machines

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3677597D1 (de) * 1986-06-06 1991-03-28 Schuler Gmbh L Vorrichtung an einer presse mit exzenterwelle zum verstellen des stoesselhubes.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2155463A5 (fr) * 1971-10-01 1973-05-18 Bruderer Ag
DE2534626A1 (de) * 1974-09-03 1976-03-11 Bruderer Ag Vorrichtung fuer den massenausgleich bei mittels kurbeltrieb angetriebenen maschinen
GB2189731A (en) * 1986-04-28 1987-11-04 Bruderer Ag Stroke adjustment in punching machines

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2008799A1 (fr) * 2007-06-28 2008-12-31 Bruderer Ag Presse à découper
US8739595B2 (en) 2007-06-28 2014-06-03 Bruderer Ag Punching press
WO2017035671A1 (fr) * 2015-09-02 2017-03-09 Bruderer Ag Presse d'emboutissage et/ou de formage

Also Published As

Publication number Publication date
JPH02104500A (ja) 1990-04-17
EP0356809B1 (fr) 1992-12-09
CH677336A5 (fr) 1991-05-15
US4987794A (en) 1991-01-29
DE58902956D1 (de) 1993-01-21
JP2552000B2 (ja) 1996-11-06

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