US3448686A - Form roller setting and control means - Google Patents

Form roller setting and control means Download PDF

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Publication number
US3448686A
US3448686A US598983A US3448686DA US3448686A US 3448686 A US3448686 A US 3448686A US 598983 A US598983 A US 598983A US 3448686D A US3448686D A US 3448686DA US 3448686 A US3448686 A US 3448686A
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Prior art keywords
plate cylinder
roller
form roller
rollers
radius
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US598983A
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English (en)
Inventor
Carl E Bohman
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Miehle Goss Dexter Inc
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Miehle Goss Dexter Inc
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/30—Arrangements for tripping, lifting, adjusting, or removing inking rollers; Supports, bearings, or forks therefor
    • B41F31/301—Devices for tripping and adjusting form rollers

Definitions

  • the form inking and dampening rollers be capable of automatically adapting to the different diameter plate cylinders so that manual readjustments are not required each time a new module having a different diameter plate cylinder is installed. This has not been possible heretofore because of the physical characteristics of the known form roller control means.
  • One known type of form roller control means comprises eccentrics and adjustable links which are connected directly to the form roller support and thus hold the respective form rollers rigidly in position. While this type of mechanism is satisfactory for conventional presses, it is not suitable for variable cut-off presses. Because of its relatively inflexible nature, the form rollers would have to be manually retracted and then readjusted relative to the new plate cylinder each time a different module was inserted and since the squeeze between each form roller and the plate cylinder must be accurately set, considerable time would be lost in making the readjustments. Moreover, the range of adjustment of such mechanisms is relatively limited and only a comparatively small variation in plate cylinder diameters could be accommodated.
  • the principal object of this invention resides in the provision of new and improved means for initially setting and thereafter maintaining the contact relation between the form rollers and the plate cylinder of the printing press.
  • Another object resides in the provision of improved form roller setting and control means which will assure a minimal pressure change at the form roller-plate cylinder interface when plate cylinders of different diameters are installed.
  • a further object resides in the provision of improved form roller setting and control means which will accommodate discreet variations in the radius of the form roller.
  • Still another object resides in the provision of improved setting and control means for resiliently biased form rollers which will assure a minimal pressure change at the form roller-plate cylinder interface when the plate cylinder is skewed for register purposes.
  • a further object resides in the provision of improved form roller setting and control means which includes a spiral shaped disc mounted coaxially with the form roller and having a predetermined characteristic, i.e. the radius thereof is a linear function of the angular displacement from a predetermined reference point, such that the requirements for a coacting stop associated with each one of a plurality of different diametered, interchangeable plate cylinders can be predetermined, without specific knowledge of the actual form roller size, so as to maintain a pre-established contact relationship at the form rollerplate cylinder interface upon interchanging the different diametered plate cylinders.
  • FIGURE 1 is a side elevational view showing the invention as incorporated in a variable cut-off web press of the interchangeable module type;
  • FIGURE 2 is a sectional view taken substantially along line 2-2 of FIGURE 1;
  • FIGURES 3 and 4 are schematic views illustrating the approximate positions assumed by the various form rollers when minimum and maximum diameter plate cylinders, respectively, are installed.
  • variable cut-off web offset press For the purpose of illustration, a preferred embodiment of the invention has been shown as incorporated in a variable cut-off web offset press in conjunction with which its use is particularly advantageous.
  • the invention is not limited to ues in variable cut-off presses and that it constitutes a convenient and effective means for adjusting the form rollers in conventional presses as well.
  • variable cut-off offset press selected for the purpose of illustrating the invention, essentially, comprises a base unit having spaced side frames and 11 each of which has an aligned recess provided in one vertical edge thereof to accommodate interchangeable printing modules such as that generally indicated by the reference number 12.
  • a plurality of such printing modules will be provided for each base unit, each of which essentially comprises end frame members 13 and 14 in which a plate cylinder 16 and a coacting blanket cylinder 17 are rotatably mounted.
  • the plate and blanket cylinders of each of the modules preferably differ in diameter from the plate and blanket cylinders of the other modules and, therefore, a multiplicity of product sizes can be printed by simply selecting a module having the appropriate size cylinders and mounting it in the base unit.
  • the respective blanket cylinders When mounted in operative position the respective blanket cylinders are adapted to coact with a common impression cylinder 18 which is adjustably mounted in the base unit so that it can be moved into operative position relative to the respective blanket cylinders to provide the desired impression pressure on a web passing through the nip of said cylinders.
  • the inking mechanism also comprises a part of the base unit and, in a press of this type, it is highly desirable, if not actually essential, that the form rollers of said mechanism be capable of adapting automatically to the respective plate cylinders each time a different module is inserted and regardless of any change in the diameter of the plate cylinder within the size range of a given press.
  • This has not been possible heretofore because of the inherent limitations of the known form roller control devices and, therefore, it has been necessary to effect time consuming, manual adjustments of the individual form rollers each time a different module was installed.
  • the inking mechanism essentially comprises a series of rollers such as the distributing rollers 20 and 21 which function to convey a continuous supply of ink from a reservoir, not shown, to the vibrator roller 22.
  • These rollers are all suitably supported in the base unit side frames 10 and 11, the vibrator roller 22, for example, being journalled in bushings 23 so that it can be rotated and axially reciprocated about a fixed axis.
  • the ink is transferred to the first two form rollers 24 and 25 which deposit the ink in the form of a thin film on a form carried by the plate cylinder 16.
  • a portion of the ink is transferred by means of a distributor roller 26 to the third and fourth form rollers 27 and 28, respectively, which are in contact with the plate cylinder and a second vibrator roller 29 which may be mounted in the same manner as roller 22 for rotation and axial reciprocation in the side frames 10 and 11.
  • the form rollers 24, 25, 27 and 28 must be adjustable relative to the plate cylinder and the respective vibrator rollers in order to establish the desired squeeze at the respective inter-faces. They must also be capable of shifting bodily about the axes of the vibrator rollers so that they can accommodate different diameter plate cylinders ranging between the minimum and maximum sizes as illustrated in FIGURES 3 and 4, respectively.
  • the mounting means for the form roller 25 comprises a bracket 31 mounted on the projecting end of the vibrator roller bushing 23 so that it is free to swing about the axis of the vibrator roller 22.
  • the bracket 31 carries an eccentric bushing .32 formed with a reduced diameter, laterally projecting portion 33 that is mounted for rotation in a bore 34 provided in the bracket.
  • Worm teeth 36 formed in the periphery of the projecting portion 33 are arranged to mesh with a worm 37 rotatably mounted in the bracket for adjustment purposes.
  • the worm shaft projects beyond the bracket 31 and it is squared as at 38, see FIGURE 1, to receive a tool whereby the worm can be rotated to in turn rotate the eccentric bushing 32 relative to the bracket.
  • the bushing 32 is provided with a form roller socket which consists of a base portion 39 and a releasable cap 40 in which the roller bearing 41 carried at the end of the shaft 42 of the form roller 25 is seated.
  • the form roller can be adjusted relative to the vibrator roller to establish the desired squeeze at the form roller-vibrator roller interface and this setting will remain constant regardless of any angular adjustment of the form roller about the axis of the vibrator roller.
  • the form roller is arranged to be biased toward the plate cylinder by resilient means which, as illustrated in FIGURE 1, may consist of a coil spring 43.
  • This spring is mounted about a rod 44 having one end thereof slideably mounted in a pivot block 46 on the side frame 10 with the opposite end thereof being pivotally connected as at 47 to the bracket 31.
  • the spring 43 is confined between the block 46 and a collar 48 on the rod 44 and thus it exerts a force tending to move the form roller toward the plate cylinder about the axis of the vibrator roller.
  • a coil spring has been illustrated as the resilient biasing means for the form roller, this is merely by way of example and it will be readily apparent that any other suitable means such as hydraulic or pneumatically actuated devices can be used for this purpose.
  • the form roller is arranged to be controlled by coacting stops in the form of an arcuate segment 49 located on the module and a non-circular control disc 51 associated with the bracket 31.
  • the control disc is arranged to be rotatable relative to the bracket and for this purpose it is formed with a reduced diameter portion 52 which fits into a bore formed in the bushing 32 and in a manner that its axis is precisely coincident with the axis of the form roller.
  • a worm wheel 53 which also is rotatable in the bushing and it is arranged to be interlocked with the control disc by means of a diametrically disposed rib or tongue 54 formed on the end face of the worm wheel, which is adapted to fit into a corresponding groove 56 formed in the adjacent end face of the control disc.
  • the worm wheel and control disc are secured together as a unit in the bushing by means of the bolt 57 so that they cannot move axially in the bushing but they are permitted to rotate within the bore for roller adjustment purposes.
  • Adjustment of the control disc is effected by means of the worm 58 located in the bushing 32 and which meshes with the worm teeth 59 of the worm wheel.
  • the worm 58 also has a squared projecting end 61 to accommodate a wrench whereby adjustment thereof can be effected.
  • the periphery of the control disc has a spiral configuration and therefore, by imparting appropriate angular adjustment to said disc, it will be evident that the center distance between the form roller and the plate cylinder can be varied to obtain the desired squeeze at the interface.
  • the spiral surface of the disc is formed on a radius which is a linear function of the angular displacement from a predetermined reference point or, stated in another way, the radius is a linear function of the angular displacement of the contact point of the disc with the coacting arcuate segment.
  • the actual rate of change of the radius is dependent upon the characteristics of a particular press and it is preferably one that will provide a maximum range of adjustment and yet will not adversely affect the established form roller setting when the plate cylinder is skewed for register purposes.
  • the rate of change may vary between .0001 and .002 inch per degree or more, depending upon the type of control desired. For example, if a wide range of adjustment is not essential, a rate of change of .0001 inch per degree will afford very precise, micrometric type of adjustments of the form roller which will remain virtually constant even when maximum skewing adjustments of the plate cylinder are made. On the other hand, if a greater range of adjustment is desired, a rate of change of .002 inch per degree may be used. This would still provide accurate control of the form roller setting and although some change in squeeze would be caused by skewing adjustments of the plate cylinder such change would remain within acceptable limits under most circumstances.
  • the rate of change of the radius may be increased substantially beyond .002 inch per degree but it will be recognized that as the rate of change is increased the capability of effecting very fine adjustments of the form roller will decrease.
  • roller 25 spectively, than for roller 25 and thus their respective arc segments 63 and 64 are dimensioned accordingly.
  • the radius of the respective arcuate segments can be predetermined from the geometry of the various elements and without specific knowledge of the actual sizes of the respective form rollers, so that upon installation of the module, each form roller will automatically assume the proper contact relation with the plate cylinder.
  • the radius of the plate cylinder, the vibrator roller and the mean radius of each form roller is known as is also the center distance between the vibrator roller and the plate cylinder. From this information it is possible to locate the position the center of the form roller will assume upon installation of a given plate cylinder as -well as the angles of the triangle which is formed by connecting the centers of the plate cylinder, the form roller and the vibrator roller.
  • the mean radius of the control disc also is known and by using this as a basis it is possible to determine what the radius of'the arcuate segment must be to maintain the established contact relation between the form roller and the plate cylinder because the mean radius of the control disc plus the radius of the arcuate segment must equal the radius of the plate cylinder plus the radius of the form roller, less that amount which is necessary to provide the desired squeeze at the form roller-plate cylinder interface.
  • each form roller will be positioned automatically relative to the particular plate cylinder upon insertion of the module into the base unit.
  • this difference can readily be compensated, up to A; inch in either direction, by appropriate angular adjustment of the control disc.
  • control disc Once the control disc has been adjusted to compensate for the actual form roller diameter, no further adjustments thereof will be required when interchanging modules. This adjustment is only used thereafter at infrequent intervals when the form roller wears to such extent as to require a compensating adjustment.
  • the adjacent end of the plate cylinder will move to a limited extent in a path substantially normal to a plane extending through the axis of the plate and blanket cylinders, as indicated by the arrow in FIGURE 1
  • the extent of this skewing adjustment is generally limited to about .020 inch to either side of center, it is sufficient nevertheless to disturb the setting of the form rollers across the width of the plate cylinder. It is necessary therefore to have the form rollers shift in unison with the plate cylinder to avoid the need for effecting manual readjustments.
  • control discs also will follow the arcuate segments under the influence of the biasing springs 43 and, therefore, the respective form rollers will maintain their preestablished contact relation with the plate cylinder.
  • Such skewing adjustments Will obviously produce a slight shift in the contact point of the control discs with the respective arcuate segments, but the angular displacement of the contact point will, because of the rate of change of the spiral disc as previously described, result in a squeeze change which is so minute that it is well within acceptable limits.
  • bracket 72 To prevent any appreciable angular displacement of the bracket 72 when the housing 69 is rotated, it is connected to the module end frame 13 by means of a link 76.
  • One end of the link is pivotally connected to the bracket as at 77 whereas the other end is pivotally connected at 78 to an offset flange 79 secured to the end frame.
  • the link 76 will thus permit the bracket to shift laterally with the plate cylinder, but it will prevent it from turning about the axis thereof when the housing 69 is rotated.
  • this invention comprises a relatively simple and effective means for setting and controlling resiliently biased form inking rollers in conventional presses as well as in variable cut-off presses which require maximum flexibility to accommodate a relatively wide range of plate cylinder diameters.
  • the invention has been illustrated and described as applied to the form inking rollers of a printing press, it will be readily apparent that it is applicable to the form dampening rollers of such press which were not illustrated in the interest of simpilicity.
  • a printing press having a plate cylinder, at least one coacting form roller for applying a fluid substance to the peripheral surface of the plate cylinder, and resilient means for biasing the form roller toward the plate cylinder
  • means for controlling the center distance between the form roller and plate cylinder comprising a relatively fixed stop associated with the plate cylinder, a coacting, non-circular control member mounted coaxially with said form roller, the radius of said control member being a linear function of the angular shift of the contact point of said member with the fixed stop, and means for rotating the control member about the axis of the form roller.
  • control member comprises a spiral cam having a radius which varies at a linear rate of .0001 to .002 inch per degree
  • control member comprises a spiral cam having a radius which varies at a linear rate of .0004- inch per degree.
  • said fixed stop comprises an arcuate segment formed on a radius having its center coincident with the axis of the plate cylinder.
  • the means for rotating said bushing includes a worm rotatably mounted in the bracket and coacting worm teeth formed in the periphery of said bushing.

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  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Coating Apparatus (AREA)
  • Rotary Presses (AREA)
US598983A 1966-12-05 1966-12-05 Form roller setting and control means Expired - Lifetime US3448686A (en)

Applications Claiming Priority (1)

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US59898366A 1966-12-05 1966-12-05

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US598983A Expired - Lifetime US3448686A (en) 1966-12-05 1966-12-05 Form roller setting and control means

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US (1) US3448686A (enExample)
CH (1) CH484748A (enExample)
DE (1) DE1611249A1 (enExample)
FR (1) FR1584975A (enExample)
GB (1) GB1145438A (enExample)
SE (1) SE342579B (enExample)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3559569A (en) * 1968-02-23 1971-02-02 Adamovske Strojirny Np Damping unit for an offset printing machine
US3774537A (en) * 1970-07-15 1973-11-27 Stevens Corp Rotary offset printing press with removable plate cylinder unit
US3935815A (en) * 1971-10-21 1976-02-03 Ab Printing Equipment Inking apparatus for printing press
US4271760A (en) * 1978-07-27 1981-06-09 Machines Chambon Printing machines of the offset type
US4362098A (en) * 1980-08-04 1982-12-07 Faustel, Inc. Rotary printing press using flexible plates
US4397237A (en) * 1981-03-31 1983-08-09 M.A.N.-Roland Druckmaschinen Aktiengesellschaft Roller train structure for use with printing machine
US4441423A (en) * 1981-03-14 1984-04-10 Koenig & Bauer Aktiengesellschaft Collect-printing unit for security printing for use in a rotary printing press
US4479431A (en) * 1981-04-01 1984-10-30 Koenig & Bauer Aktiengesellschaft Collect-printing unit for security printing for use in a rotary printing press
FR2547241A1 (fr) * 1983-06-10 1984-12-14 Didde Graphic Systems Corp Mecanisme de reglage de la pression entre rouleaux pour une presse d'impression offset
US4503771A (en) * 1982-03-03 1985-03-12 M.A.N. Roland Druckmaschinen Aktiengesellschaft Mechanism for engaging, disengaging and adjusting applicator rollers with respect to the plate cylinder of printing machines
US4584940A (en) * 1983-09-23 1986-04-29 Koenig & Bauer Ag Inking unit for rotary printing machine
US4972771A (en) * 1986-07-12 1990-11-27 Miller-Johannisberg Druckmaschinen Gmbh Film dampener unit for offset printing presses
EP0437230A3 (en) * 1990-01-10 1991-11-27 Komori Corporation Inking apparatus for printing press
EP0616889A1 (fr) * 1993-03-24 1994-09-28 Komori-Chambon Sa Appareil d'impression offset à cassette amovible
EP0903228A3 (en) * 1997-08-08 1999-08-25 Komori Corporation Adjusting mechanism for ink forme rollers in a printing machine
US6347585B1 (en) 1998-08-04 2002-02-19 Goss Graphic Systems, Inc. Variable gap stabilizer
EP1155843A3 (de) * 2000-05-15 2002-10-30 MAN Roland Druckmaschinen AG Vorrichtung zum Einstellen einer Auftragwalze am Plattenzylinder einer Druckmaschine
US20070068406A1 (en) * 2005-08-27 2007-03-29 Man Roland Druckmaschinen Ag Printing unit for a press
US20090078135A1 (en) * 2007-09-25 2009-03-26 Gallus Druckmaschinen Gmbh Printing Unit, Printing Press and Method of Producing Labels or Self-Adhesive Labels in a Printing Press
DE102011055817A1 (de) * 2011-11-29 2013-05-29 Sdf Schnitt-Druck-Falz Spezialmaschinen Gmbh Druckwerk für den Nass-Offset-Druck

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3691956A (en) * 1970-11-20 1972-09-19 North American Rockwell Flat adjusting and throw-off arrangement for form roller in printing press
FR2527988A1 (fr) * 1982-06-04 1983-12-09 Creusot Loire Dispositif d'encrage pour machine d'impression
DE3434647C2 (de) * 1984-09-21 1986-07-31 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Farbwerk für Rotationsdruckmaschinen
DE19506923C1 (de) * 1995-02-28 1996-06-27 Roland Man Druckmasch Feuchtwerk für eine Offsetdruckmaschine
DE19514197A1 (de) * 1995-04-15 1996-10-17 Roland Man Druckmasch Nachstellvorrichtung für Farb- und Feuchtmittelauftragwalzen
DE19514198C2 (de) * 1995-04-15 1997-04-30 Roland Man Druckmasch Nachstellvorrichtung für Farb- und Feuchtmittelauftragwalzen einer Offsetrotationsdruckmaschine
DE10148501A1 (de) * 2001-10-01 2003-04-30 Koenig & Bauer Ag Farbwerk
DE102005014255A1 (de) * 2005-03-30 2006-10-05 Koenig & Bauer Ag Lagerung von Walzen und/oder Zylindern in Druckwerken von Rotationsdruckmaschinen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1470194A (en) * 1922-02-28 1923-10-09 Glenn P Robinson Roller-setting apparatus for printing presses
US2539383A (en) * 1941-08-11 1951-01-30 Davidson Corp Inking mechanism for printing presses
US2853943A (en) * 1953-12-15 1958-09-30 Harris Intertype Corp Plate cylinder and inking roller throwoffs
US3065690A (en) * 1959-12-30 1962-11-27 American Type Founders Co Inc Plate cylinder mountings for printing presses
US3323452A (en) * 1965-01-15 1967-06-06 Miehle Goss Dexter Inc Variable cut-off web offset press

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1470194A (en) * 1922-02-28 1923-10-09 Glenn P Robinson Roller-setting apparatus for printing presses
US2539383A (en) * 1941-08-11 1951-01-30 Davidson Corp Inking mechanism for printing presses
US2853943A (en) * 1953-12-15 1958-09-30 Harris Intertype Corp Plate cylinder and inking roller throwoffs
US3065690A (en) * 1959-12-30 1962-11-27 American Type Founders Co Inc Plate cylinder mountings for printing presses
US3323452A (en) * 1965-01-15 1967-06-06 Miehle Goss Dexter Inc Variable cut-off web offset press

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3559569A (en) * 1968-02-23 1971-02-02 Adamovske Strojirny Np Damping unit for an offset printing machine
US3774537A (en) * 1970-07-15 1973-11-27 Stevens Corp Rotary offset printing press with removable plate cylinder unit
US3935815A (en) * 1971-10-21 1976-02-03 Ab Printing Equipment Inking apparatus for printing press
US4271760A (en) * 1978-07-27 1981-06-09 Machines Chambon Printing machines of the offset type
US4362098A (en) * 1980-08-04 1982-12-07 Faustel, Inc. Rotary printing press using flexible plates
US4441423A (en) * 1981-03-14 1984-04-10 Koenig & Bauer Aktiengesellschaft Collect-printing unit for security printing for use in a rotary printing press
US4397237A (en) * 1981-03-31 1983-08-09 M.A.N.-Roland Druckmaschinen Aktiengesellschaft Roller train structure for use with printing machine
US4479431A (en) * 1981-04-01 1984-10-30 Koenig & Bauer Aktiengesellschaft Collect-printing unit for security printing for use in a rotary printing press
US4503771A (en) * 1982-03-03 1985-03-12 M.A.N. Roland Druckmaschinen Aktiengesellschaft Mechanism for engaging, disengaging and adjusting applicator rollers with respect to the plate cylinder of printing machines
FR2547241A1 (fr) * 1983-06-10 1984-12-14 Didde Graphic Systems Corp Mecanisme de reglage de la pression entre rouleaux pour une presse d'impression offset
US4584940A (en) * 1983-09-23 1986-04-29 Koenig & Bauer Ag Inking unit for rotary printing machine
US4972771A (en) * 1986-07-12 1990-11-27 Miller-Johannisberg Druckmaschinen Gmbh Film dampener unit for offset printing presses
EP0437230A3 (en) * 1990-01-10 1991-11-27 Komori Corporation Inking apparatus for printing press
EP0616889A1 (fr) * 1993-03-24 1994-09-28 Komori-Chambon Sa Appareil d'impression offset à cassette amovible
FR2702996A1 (fr) * 1993-03-24 1994-09-30 Komori Chambon Appareil d'impression offset à cassette amovible.
US5394798A (en) * 1993-03-24 1995-03-07 Komori-Chambon S.A. Offset printing apparatus with removable cassette
EP0903228A3 (en) * 1997-08-08 1999-08-25 Komori Corporation Adjusting mechanism for ink forme rollers in a printing machine
US6058837A (en) * 1997-08-08 2000-05-09 Komori Corporation Inking device for printing machine
US6347585B1 (en) 1998-08-04 2002-02-19 Goss Graphic Systems, Inc. Variable gap stabilizer
EP1155843A3 (de) * 2000-05-15 2002-10-30 MAN Roland Druckmaschinen AG Vorrichtung zum Einstellen einer Auftragwalze am Plattenzylinder einer Druckmaschine
JP3410081B2 (ja) 2000-05-15 2003-05-26 エム・アー・エヌ・ローラント・ドルックマシーネン・アクチエンゲゼルシャフト 印刷機のプレート胴とインクローラの接触調節装置
US20070068406A1 (en) * 2005-08-27 2007-03-29 Man Roland Druckmaschinen Ag Printing unit for a press
US20090078135A1 (en) * 2007-09-25 2009-03-26 Gallus Druckmaschinen Gmbh Printing Unit, Printing Press and Method of Producing Labels or Self-Adhesive Labels in a Printing Press
US8505450B2 (en) * 2007-09-25 2013-08-13 Gallus Druckmaschinen Gmbh Printing unit, printing press and method of producing labels or self-adhesive labels in a printing press
DE102011055817A1 (de) * 2011-11-29 2013-05-29 Sdf Schnitt-Druck-Falz Spezialmaschinen Gmbh Druckwerk für den Nass-Offset-Druck

Also Published As

Publication number Publication date
FR1584975A (enExample) 1970-01-09
GB1145438A (en) 1969-03-12
SE342579B (enExample) 1972-02-14
CH484748A (de) 1970-01-31
DE1611249A1 (de) 1971-12-09

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