EP0135063B1 - Vorgreiferantrieb - Google Patents

Vorgreiferantrieb Download PDF

Info

Publication number
EP0135063B1
EP0135063B1 EP84108794A EP84108794A EP0135063B1 EP 0135063 B1 EP0135063 B1 EP 0135063B1 EP 84108794 A EP84108794 A EP 84108794A EP 84108794 A EP84108794 A EP 84108794A EP 0135063 B1 EP0135063 B1 EP 0135063B1
Authority
EP
European Patent Office
Prior art keywords
cam
control
control lever
auxiliary
shaft
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
Application number
EP84108794A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0135063A3 (en
EP0135063A2 (de
Inventor
Josef Mathes
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.)
Manroland AG
Original Assignee
MAN Roland Druckmaschinen 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 MAN Roland Druckmaschinen AG filed Critical MAN Roland Druckmaschinen AG
Priority to AT84108794T priority Critical patent/ATE38183T1/de
Publication of EP0135063A2 publication Critical patent/EP0135063A2/de
Publication of EP0135063A3 publication Critical patent/EP0135063A3/de
Application granted granted Critical
Publication of EP0135063B1 publication Critical patent/EP0135063B1/de
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F21/00—Devices for conveying sheets through printing apparatus or machines
    • B41F21/04—Grippers
    • B41F21/05—In-feed grippers
    • 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
    • Y10T74/18288—Cam and lever

Definitions

  • the invention relates to a pre-gripper control for sheet-fed printing machines with a control cam fixedly arranged on the shaft of a cylinder for generating the pre-gripper movement by means of a control lever which is pivotally mounted on the frame and is supported on the control cam via a first cam roller, with a follower curve on which a second cam Cam roller supports, and a suspension effective between the cam rollers, which keeps the cam rollers in constant contact with the curves.
  • a device of this type is described by DE-PS 677 130.
  • Cam gears are generally used to generate the reciprocating movement of the pre-gripper of a sheet-fed printing press.
  • a force must be applied to the control lever that presses the cam roller against the control cam even if it wants to lift off the curve due to the inertia of the drive and the pre-gripper. This is necessary in order to avoid damage to the gearboxes, to reduce vibrations in the machine and to ensure that the sheet is fed into the printing press in a suitable manner.
  • DE-PS 677 130 describes a pre-gripper control for sheet-fed printing machines.
  • Two cam disks are attached to the shaft of the printing cylinder and rotate in a fixed relationship with each other with the printing cylinder.
  • a sliding roller runs on the first cam disk and is mounted in the control lever, which drives the pre-gripper via a pull rod.
  • the control lever can be pivoted about a fixed axis.
  • a second lever is pivotally mounted on the same axis, in which a sliding roller is also attached. This second slide roller runs on the second cam.
  • the end of the second lever is extended beyond the frame-fixed bearing and provided with a horn-shaped extension.
  • a compression spring is attached between this horn-shaped extension and the first control lever.
  • the curves of the two cams are coordinated so that the spring between the two levers is always under the same tension during the pre-gripper movement and does not perform a working stroke. This ensures that the sliding rollers are constantly in contact with the cam discs, but that no unnecessary movements occur in the drive at the same time.
  • a disadvantage of this arrangement is that the two cam disks lie in two planes in the direction of the pressure cylinder axis and two separate levers are provided. These are also on two different levels. Although no relative movements are now provided between the two levers, the prestressing forces applied by the compression spring and the acceleration forces resulting from the movements will have to be transmitted via the common axis of the two levers.
  • the space is particularly occupied by the arrangement of the curves axially one behind the other on the pressure cylinder axis. This is disadvantageous precisely because the wheel trains of the printing unit drive must also be accommodated here.
  • the gearbox for controlling the pre-gripper has three control cams.
  • a main curve is used to generate the superimposed pre-gripper movement.
  • a second runner curve is used to control the gripper.
  • a third swivel curve is used to generate a superimposed swivel movement of the gripper.
  • the curves, in particular the main curve and the runner curve are arranged on parallel shafts, both shafts having opposite directions of rotation. In addition, both curves are in one plane.
  • the transmission is very complicated because it consists of a large number of control levers.
  • the suspension of the various cam rollers to the respective control cams can only be solved with great effort within the entire transmission system.
  • the invention is therefore based on the object of creating an extremely space-saving rigid and precisely running pre-gripper drive which is also of a very simple and robust design.
  • control curve on a first shaft and the follower curve on a second shaft makes it possible to design the control lever in one piece. This makes it very rigid and compact. The entire arrangement lies only axially to the shafts of the printing press in one plane. This saves a lot of installation space in this direction and the cam drive can be placed in places on the machine drive that are less stressed by other components than the shaft of the pressure cylinder. If the side curve is arranged on a shaft that rotates more slowly than the machine cycle, it must be provided with a corresponding number of identical curves. The difficulties in producing such a curve inevitably lead to manufacturing inaccuracies and asymmetries between the curve parts.
  • Fig. 1 an overview of the entire cam mechanism for driving the pre-gripper is given in a schematic representation.
  • the control cam 1 is attached to the shaft 2 of the take-up drum 3.
  • the control curve 1 then runs at the same speed as the take-up drum 3.
  • the runner curve 4 is attached to the shaft 5 of the printing cylinder 6.
  • the pressure cylinder 6 has twice the diameter of the take-up drum 3. It also runs at half the speed of the take-up drum 3. Accordingly, the runner curve 4 is provided with two identical curves 7 which are offset by 180 ° and are arranged continuously merging into one another on the curve. This coordinates the sequence of movements between control curve 1 and runner curve 4.
  • the control lever 8 is pivotally mounted on the axis 9 fixed to the frame on the side stand 10 in the same plane in which the control curve 1 and the runner curve 4 lie.
  • the first cam roller 12, which is in contact with the control cam 1 is mounted on the control lever 8 via an axis 11.
  • the second cam roller 13 is mounted on the control lever 8 via the suspension to be described later.
  • the connecting rod 14 for driving the pre-gripper is connected to the control lever 8 via a bolt 15.
  • the movement network of the pre-gripper is contained in control curve 1.
  • the runner curve 4 ensures that the first cam roller 12 always runs exactly on the control curve 1 and its two curves 7 are designed accordingly.
  • the side curve 4 rotates only by 180 °. So the curve 7 corresponding to the control curve 1 must be included on the side curve 4 on half the curve circumference.
  • the size of the side curve 4 is only dependent on gear ratios on the control lever 8. A larger curve contains smaller slopes at higher peripheral speeds, while a small curve has larger slopes at lower peripheral speeds. This is less important kinematically than in relation to the production of the curves. The effort increases with the size. With small curves, the limit is determined by curve transitions and production equipment.
  • the two curves 1, 4 rotate with their respective shafts 2, 5.
  • the control lever 8 is guided over the cam rollers 12, 13 between the curves 1, 4 and swings about the axis 9 fastened to the frame of the sheet-fed printing press must match each other.
  • the sequence of movements of the control lever 8 produces a reciprocating movement on the pre-gripper, in the course of which paper sheets are transferred from a feed table to grippers on the pressure cylinder 6.
  • the control curve 1 must therefore ensure that the paper sheets are accelerated from the standstill to the peripheral speed of the printing cylinder 6 from a standstill.
  • the pre-gripper then goes back to fetch the next sheet of paper.
  • the suspension of the second cam roller 13 is shown in detail in FIGS.
  • the second cam roller 13 is mounted on the eccentric 16 on the bearing element 17.
  • the bearing element 17 is provided centrally with its two bearing ends 18 with a bore 19.
  • the bore 19 is designed at one end within one of the bearing ends 18 of the bearing element 17 as a square 20. In this square 20, one end of a torsion bar spring 21 is pinned.
  • the bearing element 17 is mounted with the corresponding bearing end 18 in a bore 22 of the control lever 8.
  • the other end of the torsion bar spring 21 is fastened in a guide element 23.
  • the guide element 23 receives the second bearing end 18 of the bearing element 17 on an inner bearing surface 24.
  • the guide element 23 itself is held by an outer guide surface 25 in a bore 26 of the control lever 8.
  • the guide element 23 is secured with a clamping ring 27 via screws 28 on the control lever 8 against rotation.
  • the torsion bar spring 21 is provided at each end with a square 29.
  • the guide element 23 is provided with a square 30 in the center of its guide surfaces 24, 25.
  • the torsion bar spring 21 sits with its square ends 29 in the square 20 in the bearing element 17 and the square 30 in the guide element 23. Since the bearing element 17 is rotatably supported via its bearing ends 18, si the torsion bar spring 21 now secures the bearing element 17 against rotation.
  • the second cam roller 13 is arranged on the eccentric 16 on the bearing element 17, a spring action occurs when the second cam roller 13 is displaced by rotation of the bearing element 17 and thus of the eccentric 16 on the torsion bar spring 21.
  • the restoring force that acts on the second cam roller 13 and acts on the runner curve 4 is dependent on the angular position between the eccentricity E of the eccentric 16 on the bearing element 17 and the direction of force application on the second cam roller 13 from the runner curve 4.
  • this arrangement only small spring deflections are possible, since the installation space is relatively strongly limited by the force effects and by the size of the outer cam roller 13.
  • this extremely compact design is desirable. Since the suspension is used to compensate for manufacturing inaccuracies on the follower curve 4, only a spring travel in the range of less than one millimeter is necessary for tolerance compensation and for applying a pretensioning force. The movement of the suspension is damped by the friction of the bearing ends 18 in the bore 22 and the inner guide surface 24 in the guide element 23.
  • a locking pin 31 is inserted in the eccentric 16 at the end, which engages in a guide slot 32 in the guide element 23. If the spring breaks, the bearing element 17 can then only rotate as far as the width of the guide slot 32 in relation to the locking pin 31 permits.
  • the guide slot 32 will of course be chosen so wide that all manufacturing inaccuracies on the side curve 4 can be compensated for, ie that necessary small spring travel is allowed. With the help of the locking pin 31, the torsion bar spring 21 can also be brought to the necessary pretension.
  • FIG. 4 shows a variant for the suspension of the second cam roller 13.
  • the cam roller 13 is arranged on an auxiliary lever 33 which is pivotally attached to the control lever 8 by means of a bolt 34.
  • a compression spring assembly 35 is arranged between the auxiliary lift 33 and the control lever 8. It is held by a screw bolt 36 and is provided with a spacer sleeve 37.
  • the friction is generated between the screw bolt 36 and the auxiliary lever 33, but also in the compression spring assembly 35.
  • this drive is very compact for the pre-gripper of a sheet-fed printing press. This has made it possible to place the entire cam drive under the gear train of the machine drive, so that much less installation space is required axially. In this way, space for other drive elements can be gained and the transfer of dynamic forces to the pre-gripper drive can be relocated to shorter distances and more rigid elements. Overall, the pre-gripper drive has been optimized and equipped for higher speeds.
  • the arrangement of the curves 1, 4 on two shafts 2, 5 and in one plane also has the advantage that complex support structures for the mounting of the control lever 8 are no longer necessary.
  • the flow of force runs in only one level and does not have to be diverted from a first to a second level via cranked levers that cause bending moments. This also simplifies the storage itself, since the axial force components resulting from the bending moments are eliminated and the bending moments themselves do not have to be absorbed by support elements.

Landscapes

  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
  • Vehicle Body Suspensions (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Power Steering Mechanism (AREA)
EP84108794A 1983-09-14 1984-07-25 Vorgreiferantrieb Expired EP0135063B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84108794T ATE38183T1 (de) 1983-09-14 1984-07-25 Vorgreiferantrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3333050 1983-09-14
DE19833333050 DE3333050A1 (de) 1983-09-14 1983-09-14 Vorgreiferantrieb

Publications (3)

Publication Number Publication Date
EP0135063A2 EP0135063A2 (de) 1985-03-27
EP0135063A3 EP0135063A3 (en) 1986-12-03
EP0135063B1 true EP0135063B1 (de) 1988-10-26

Family

ID=6208969

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84108794A Expired EP0135063B1 (de) 1983-09-14 1984-07-25 Vorgreiferantrieb

Country Status (5)

Country Link
US (1) US4583728A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
EP (1) EP0135063B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JPS6087050A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
AT (1) ATE38183T1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (1) DE3333050A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3608959B3 (de) * 1986-03-18 2004-11-18 TDW Gesellschaft für verteidigungstechnische Wirksysteme mbH Aktivpanzerung
DE3621384A1 (de) * 1986-06-26 1988-01-14 Roland Man Druckmasch Vorrichtung zum antrieb eines schwingenden vorgreifers einer druckmaschine
DE3621385A1 (de) * 1986-06-26 1988-01-14 Roland Man Druckmasch Vorrichtung zum antrieb eines schwingenden vorgreifers einer druckmaschine
DE3626185A1 (de) 1986-08-01 1988-02-18 Heidelberger Druckmasch Ag Getriebe zur bildung einer zyklisch ablaufenden bewegung aus einer rotationsbewegung
DE3628907A1 (de) * 1986-08-26 1988-03-10 Koenig & Bauer Ag Bogenwendevorrichtung in einer bogenrotationsdruckmaschine
DE3632769A1 (de) * 1986-09-26 1988-04-07 Roland Man Druckmasch Klemmgreifer fuer bogenrotationsdruckmaschinen
KR930006217B1 (ko) * 1988-01-29 1993-07-09 가부시끼가이샤 미쯔바 덴끼세이사 꾸쇼 진동 발생장치
DE3830946C3 (de) * 1988-09-12 1997-06-05 Heidelberger Druckmasch Ag Kurvengetriebe zum periodischen Schwenken einer Vorgreifereinrichtung
DE3901599A1 (de) * 1989-01-20 1990-08-02 Heidelberger Druckmasch Ag Greiferanordnung an bogenverarbeitenden maschinen, insbesondere bogenoffsetdruckmaschinen
US5456128A (en) * 1989-07-06 1995-10-10 Heidelberger Druckmaschinen Ag Cam oscillating drive in a printing machine with kinetic/potential energy storage means for damping undesired oscillations
DE4101813C2 (de) * 1990-01-31 1997-12-04 Kba Planeta Ag Schwinganlagenantrieb
DD291728A5 (de) * 1990-01-31 1991-07-11 Planeta Druckmaschinenwerk Ag,De Kurvengetriebe
DE4012498C1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) * 1990-04-19 1991-11-14 Man Roland Druckmaschinen Ag, 6050 Offenbach, De
US5176036A (en) * 1991-10-16 1993-01-05 Overton Corporation Parallel shaft drive and indexing machine
DE4316599C2 (de) * 1993-05-18 1997-03-27 Heidelberger Druckmasch Ag Getriebeanordnung
DE19835005B4 (de) * 1997-12-20 2016-08-11 Heidelberger Druckmaschinen Ag Kurvengesteuertes Leistungsausgleichsgetriebe für ein Bogenbeschleunigungssystem
DE20119467U1 (de) 2001-11-29 2002-02-14 MAN Roland Druckmaschinen AG, 63075 Offenbach Kurvenbahngetriebe, insbesondere für eine Bogendruckmaschine
DE10258271A1 (de) * 2002-01-11 2003-07-24 Heidelberger Druckmasch Ag Vorrichtung zur Unterstützng der Andrückkraft einer Steuerrolle an eine zugehörige Steuerkurve
DE102020114465A1 (de) * 2020-05-29 2021-12-02 Kiekert Aktiengesellschaft Antriebseinheit für kraftfahrzeug-technische Anwendungen

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE677130C (de) * 1932-12-08 1939-06-19 Faber & Schleicher Akt Ges Vorgreifersteuerung fuer Bogendruckmaschinen
DE800128C (de) * 1948-10-02 1950-09-22 Maschf Augsburg Nuernberg Ag Vorgreifersteuerung fuer Zweitourendruckmaschinen
US3263991A (en) * 1964-04-24 1966-08-02 Miehle Goss Dexter Inc Control and trip means for infeed gripper mechanism
CS177648B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) * 1975-05-29 1977-08-31
DD142694A1 (de) * 1979-04-02 1980-07-09 Guenter Weisbach Bogenrotationsdruckmaschine mit einem von unten arbeitenden vorgreifer

Also Published As

Publication number Publication date
DE3333050C2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1987-06-11
EP0135063A3 (en) 1986-12-03
US4583728A (en) 1986-04-22
JPS6087050A (ja) 1985-05-16
EP0135063A2 (de) 1985-03-27
DE3333050A1 (de) 1985-03-28
ATE38183T1 (de) 1988-11-15

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