US3929069A - Gripper control for sheet-fed rotary printing presses - Google Patents

Gripper control for sheet-fed rotary printing presses Download PDF

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Publication number
US3929069A
US3929069A US363043A US36304373A US3929069A US 3929069 A US3929069 A US 3929069A US 363043 A US363043 A US 363043A US 36304373 A US36304373 A US 36304373A US 3929069 A US3929069 A US 3929069A
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United States
Prior art keywords
shaft
cam
gripper
spring
bearing
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
US363043A
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English (en)
Inventor
Hans-Georg Jahn
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.)
Heidelberger Druckmaschinen AG
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Heidelberger Druckmaschinen AG
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Publication date
Application filed by Heidelberger Druckmaschinen AG filed Critical Heidelberger Druckmaschinen AG
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Publication of US3929069A publication Critical patent/US3929069A/en
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Expired - Lifetime 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

Definitions

  • a gripper control for a sheet-fed printing press includes a shaft on which an impression cylinder is mounted.
  • a cam is mounted on the shaft and the cam operates an actuating means to provide an oscillating motion to a gripper means for feeding sheets to the press in synchronism with the rotation of the shaft.
  • Spring means are provided to apply a biasing force to the oscillating motion of the gripper means, and control means are provided to control the spring force dependent on the rotation of the shaft.
  • This invention relates to a gripper control for sheetfed, rotary printing presses. More particulary the invention relates to a gripper control of the type in which a cam is mounted on a shaft and drives a hollow shaft supporting the gripper mechanism in an oscillating manner by means of a cam roller and a drive linkage. A pretensioned torsion spring which biases the cam roller against the cam by means of the drive linkage is accommodated in the hollow shaft.
  • Cam-controlled gripper drives are known in which the grippers are swung or operated in a form-locking manner by means of auxiliary cams.
  • these known drives are very expensive and are justifiable only for printing presses handling large sheet sizes.
  • Cam-controlled gripper drives are also known in which a cam roller is held in positive engagement with a cam by means of a spring. These known drives have the disadvantage that due to the large angle of oscillation of the grippers, large spring excursions or expansion are produced which result in spring forces that have an unfavorable effect on the drive mechanism.
  • the maximum speed of the printing press as well as its proneness or tendency to produce striping are strongly influenced by the above-mentioned characteristic of the spring forces.
  • the aforementioned object is achieved by providing a torsion spring having one end which is fastened to a bearing shaft and which is rotatably disposed in a hollow shaft.
  • the bearing shaft protrudes from the hollow shaft and is provided with an eccentric cam.
  • a chain is connected to the curve segment of the eccentric cam closest to the axis of symmetry of the bearing shaft.
  • the chain is connected to a crank mounted on a shaft in such a manner that the chain is wound onto or unwound from the eccentric cam during each back and forth rotation of the hollow shaft.
  • FIG. 1 is a schematic representation illustrating the operation of a gripper drive according to one embodiment of the invention.
  • FIG. 2 is a top view, partly in section, of the gripper drive represented in FIG. 1.
  • FIG. 3 is an elevational view of the spring compensation arrangement of the gripper drive.
  • FIG. 4 is a time-travel diagram or graph in which the degrees of arc are plotted on the abscissa and the angle of rotation of the drive lever and bearing shaft are plotted on the ordinate.
  • FIG. 5 is a diagram or graph representing the difference between the angles of rotation of the drive lever and the bearing shaft.
  • FIG. 6 is a diagram or graph representing the spring characteristics of the torsion spring.
  • FIG. 2 a single-revolution shaft 1 of an impression cylinder 2.
  • a control cam 4 is provided on the drive side of the printing press in front of a drive gear 3 for driving a gripper mechanism.
  • the shaft 1 of the impression cylinder 2 is supported in sleeve bearings 5 and 6 in the side walls 7 and 8 respectively, of the printing press.
  • a cam roller 9, which is rotatably mounted on a roller lever 10, runs on or follows the control cam 4.
  • the roller lever 10 is fulcrumed at a bearing post 11 which is supported on the side wall 7.
  • the roller lever 10 is attached or operatively connected to a drive lever 13 by means of a link 12.
  • the drive lever 13 is firmly connected to a plug 14 which closes off the longitudinal end of a hollow shaft 15 and is firmly connected with the shaft 15.
  • the hollow shaft 15 carries a gripper bar 16 by means of two fulcrumed levers 17 and 18 and is supported in the side walls 7 and 8 by sleeve bearings 19 and 20 respectively.
  • a torsion spring 21 Inside the hollow shaft 15 there extends a torsion spring 21, one end of which is attached to the previously mentioned plug 14 and the other end of which is firmly connected with a bearing shaft member 22.
  • This bearing shaft 22 is arranged rotatably in needle bearings 23 at that end of the hollow shaft 15 which faces away from the plug 14.
  • the free end of the bearing shaft 22, which protrudes from the hollow shaft 15, is equipped with an eccentric circular cam 24 as best may be seen in FIG. 3.
  • the cam 24 is arranged eccentrically to the axis of symmetry 25 of the bearing shaft 22.
  • a chain 26 In the part of the curve of the cam 24 which is closest to the axis of symmetry 25, there is fastened a chain 26.
  • the chain 26 is fastened in such a manner that it is wound up and down on the curved and eccentric surface 27 of the circular cam 24 when the bearing shaft 22 rotates or rocks back and forth.
  • the other end of the chain 26 is connected with a crank 28 which is secured or pinned to the end of the shaft 1 of the impression cylinder 2 which protrudes from the center of the bearing of-thesidewalls 8 as shown in FIG n I During one revolution of the impression cylinder 2,
  • the roller lever 10 and thereby also the drive lever 13 is swung, due to the design of the cam 4, from the solid to the dashed position (FIG. 1) and back again.
  • the gripper bar 16 executes a movement toward a non-illustrated feed table and then moves back again to the impression cylinder 2 with a gripped sheet.
  • the torsion spring 21 is pretensioned and therefore causes the cam roller 9 to be always pressed or biased against the running or operating surface of the control cam 4 by means of the drive lever 13, the link 12, and the roller lever 10.
  • the crank 28 which also rotates with the impression cylinder 2 causes rotation of the bearing shaft 22 via the chain 26 in such a manner that the pretension of the torsion spring 21 changes only little, or not at all, during the stroke of the gripper bars 16.
  • the change of the pretension of the torsion spring 21 during the operating cycle can be varied as desired by appropriate design of the curved surface 27 of the cam 24.
  • FIG. 4 shows a time-travel diagram in which the time t in degrees of arc is plotted on the abscissa and the rotation angles or of the drive lever 13 and B of the bearing shaft 22, respectively, are plotted on the ordinate.
  • the angle of rotation travelled by the drive lever 13 per unit time is shown by the curve c, while the curvef represents the angle of rotation of the bearing shaft 22.
  • the drive lever 13 has travelled through the angle of rotation a, while at the same time, the bearing shaft 22 has been rotated through the angle [3,.
  • the difference of the angles of rotation is therefore a, B 7 that is, the pretension of the torsion spring 21 has increased slightly, as the drive lever 13 leads the bearing shaft 22.
  • the gripper bars 16 swing back, however, the bearing shaft 22 leads, so that again a slight increase of the pretension of the torsion spring 21 occurs.
  • the spring characteristic h of the torsion spring 21 is shown wherein the torque is represented as a function of the spring excursion or twist, that is, the angle of rotation or angle of torsion of the torsion spring 21.
  • a is the twist of the torsion spring 21 for the pretension torque M If the bearing shaft 22 did not co-rotate during the operating cycle, further torsion of the torsion spring 21 by the angle of rotation 01 would result in addition to the pretension.
  • the torque produced by the torsion spring 21 would increase to M
  • the bearing shaft 22 does co-rotate through the crank 28 and the chain 4 26, only a slight additional torsion by an angle 'y occurs, so that the torque actually produced by the torsion spring 21 increases maximally only to M
  • Gripper control means for sheet-fed printing presses comprising a shaft on which an impression cylinder is mounted, oscillatably mounted gripper means for feeding sheets to the printing press, a cam mounted on said shaft, actuating means operatively connected between said cam and said gripper means to oscillate said gripper means by said cam and said actuating means upon rotation of said shaft, spring means connected to said actuating means to apply a spring force to the oscillating motion of said gripper means, and control means connected to said spring for controlling said spring force, said control means being connected to said shaft, wherein said gripper means includes a hollow shaft, said acutating means including a lever arrangement operable by said cam for oscillating said hollow shaft, and said spring means comprises a torsion spring extending in said hollow shaft, a bearing shaft member oscillatably mounted in said hollow shaft, said torsion spring having one end thereof attached to said bearing shaft member, said control means including a mechanical connection between said bearing shaft member and said impression cylinder shaft, said mechanical connection comprising a crank mounted on said
  • a gripper control according to claim 1 including bearing means rotatably supporting said bearing shaft member in said hollow shaft, said bearing shaft protruding from the end of said hollow shaft, said eccentric cam being mounted on said protruding end of said bearing shaft member.

Landscapes

  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
  • Separation, Sorting, Adjustment, Or Bending Of Sheets To Be Conveyed (AREA)
  • Discharge By Other Means (AREA)
US363043A 1972-05-23 1973-05-23 Gripper control for sheet-fed rotary printing presses Expired - Lifetime US3929069A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2224932A DE2224932C2 (de) 1972-05-23 1972-05-23 Vorgreifersteuerung für Bogenrotationsdruckmaschinen

Publications (1)

Publication Number Publication Date
US3929069A true US3929069A (en) 1975-12-30

Family

ID=5845584

Family Applications (1)

Application Number Title Priority Date Filing Date
US363043A Expired - Lifetime US3929069A (en) 1972-05-23 1973-05-23 Gripper control for sheet-fed rotary printing presses

Country Status (12)

Country Link
US (1) US3929069A (ja)
JP (1) JPS5113050B2 (ja)
AT (1) AT318665B (ja)
CS (1) CS161998B2 (ja)
DD (1) DD104765A5 (ja)
DE (1) DE2224932C2 (ja)
DK (1) DK136415C (ja)
FR (1) FR2186009A5 (ja)
GB (1) GB1399199A (ja)
IT (1) IT985949B (ja)
NL (1) NL148830B (ja)
SE (1) SE384839B (ja)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4120244A (en) * 1976-02-07 1978-10-17 Heidelberger Druckmaschinen Aktiengesellschaft Gripper movement changeover device on a sheet-turning drum for perfector printing machines
US4133263A (en) * 1975-10-22 1979-01-09 Heidelberger Druckmaschinen Ag Sheet-turning drum for printing machines convertible from printing on one side of a sheet to printing on both sides of a sheet and vice versa
US4665823A (en) * 1985-11-01 1987-05-19 Arthur S. Diamond Paper support bar for a sheet-fed printing press
US4869169A (en) * 1987-01-16 1989-09-26 M.A.N. - Roland Apparatus for chain transfer conveyance of sheet printed in a press
EP1155833A2 (de) * 2000-05-16 2001-11-21 MAN Roland Druckmaschinen AG Steuervorrichtung für Vorgreifergreifer eines Vorgreifers in einer Bogenverarbeitungsmaschine
US20050211122A1 (en) * 2004-03-26 2005-09-29 Heidelberger Druckmaschinen Ag Speed-dependent pressing force
US20080290594A1 (en) * 2007-05-24 2008-11-27 Heidelberger Druckmaschinen Ag Transfer Drum for Conveying a Sheet in a Machine of the Graphic Arts Industry

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3728520A (en) * 1971-11-10 1973-04-17 Cubic Corp Credit card sensing apparatus

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US834107A (en) * 1904-06-09 1906-10-23 Gen Electric Power-operated brake.
US2767653A (en) * 1952-05-16 1956-10-23 Babicz George Blanket cylinder construction for printing machines
US2776136A (en) * 1950-06-22 1957-01-01 Maschf Augsburg Nuernberg Ag Gripper bar support for sheet printing press
US2926909A (en) * 1959-03-17 1960-03-01 Miehle Goss Dexter Inc Sheet transfer mechanism
US2991072A (en) * 1957-03-09 1961-07-04 Maschf Augsburg Nuernberg Ag Folding gripper control means in rotary printing machines
US3151552A (en) * 1963-04-17 1964-10-06 Miehle Goss Dexter Inc Spring gripper assembly
US3257109A (en) * 1964-01-06 1966-06-21 Miehle Goss Dexter Inc Regenerative system for alternating motion
US3385597A (en) * 1967-01-16 1968-05-28 Miller Printing Machinery Co Sheet holding and transfer apparatus
US3412995A (en) * 1966-09-22 1968-11-26 Pitney Bowes Inc Ram drive mechanism
US3463484A (en) * 1967-07-12 1969-08-26 Planeta Veb Druckmasch Werke Sheet gripping control mechanism for printing machines

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE834107C (de) * 1950-05-20 1952-03-17 Maschf Augsburg Nuernberg Ag Vorgreifersteuerung fuer Bogendruckmaschinen
US3016753A (en) * 1958-11-10 1962-01-16 Gen Motors Corp Windshield wiper drive mechanism

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US834107A (en) * 1904-06-09 1906-10-23 Gen Electric Power-operated brake.
US2776136A (en) * 1950-06-22 1957-01-01 Maschf Augsburg Nuernberg Ag Gripper bar support for sheet printing press
US2767653A (en) * 1952-05-16 1956-10-23 Babicz George Blanket cylinder construction for printing machines
US2991072A (en) * 1957-03-09 1961-07-04 Maschf Augsburg Nuernberg Ag Folding gripper control means in rotary printing machines
US2926909A (en) * 1959-03-17 1960-03-01 Miehle Goss Dexter Inc Sheet transfer mechanism
US3151552A (en) * 1963-04-17 1964-10-06 Miehle Goss Dexter Inc Spring gripper assembly
US3257109A (en) * 1964-01-06 1966-06-21 Miehle Goss Dexter Inc Regenerative system for alternating motion
US3412995A (en) * 1966-09-22 1968-11-26 Pitney Bowes Inc Ram drive mechanism
US3385597A (en) * 1967-01-16 1968-05-28 Miller Printing Machinery Co Sheet holding and transfer apparatus
US3463484A (en) * 1967-07-12 1969-08-26 Planeta Veb Druckmasch Werke Sheet gripping control mechanism for printing machines

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4133263A (en) * 1975-10-22 1979-01-09 Heidelberger Druckmaschinen Ag Sheet-turning drum for printing machines convertible from printing on one side of a sheet to printing on both sides of a sheet and vice versa
US4120244A (en) * 1976-02-07 1978-10-17 Heidelberger Druckmaschinen Aktiengesellschaft Gripper movement changeover device on a sheet-turning drum for perfector printing machines
US4665823A (en) * 1985-11-01 1987-05-19 Arthur S. Diamond Paper support bar for a sheet-fed printing press
US4869169A (en) * 1987-01-16 1989-09-26 M.A.N. - Roland Apparatus for chain transfer conveyance of sheet printed in a press
EP1155833A2 (de) * 2000-05-16 2001-11-21 MAN Roland Druckmaschinen AG Steuervorrichtung für Vorgreifergreifer eines Vorgreifers in einer Bogenverarbeitungsmaschine
EP1155833A3 (de) * 2000-05-16 2003-10-01 MAN Roland Druckmaschinen AG Steuervorrichtung für Vorgreifergreifer eines Vorgreifers in einer Bogenverarbeitungsmaschine
US20050211122A1 (en) * 2004-03-26 2005-09-29 Heidelberger Druckmaschinen Ag Speed-dependent pressing force
US7370580B2 (en) * 2004-03-26 2008-05-13 Heidelberger Druckmaschinen Ag Control roller having speed-dependent pressing force
US20080290594A1 (en) * 2007-05-24 2008-11-27 Heidelberger Druckmaschinen Ag Transfer Drum for Conveying a Sheet in a Machine of the Graphic Arts Industry

Also Published As

Publication number Publication date
DD104765A5 (ja) 1974-03-20
SE384839B (sv) 1976-05-24
JPS5113050B2 (ja) 1976-04-24
AT318665B (de) 1974-11-11
CS161998B2 (ja) 1975-06-10
DE2224932C2 (de) 1974-03-07
JPS4942408A (ja) 1974-04-22
FR2186009A5 (ja) 1974-01-04
IT985949B (it) 1974-12-30
NL7307121A (ja) 1973-11-27
DE2224932B1 (de) 1973-08-16
NL148830B (nl) 1976-03-15
DK136415C (da) 1978-03-13
DK136415B (da) 1977-10-10
GB1399199A (en) 1975-06-25

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