EP0510962B1 - Innenschneckentrieb und oszillierende Walze für ein Feuchtwerk in einer Offsetdruckmaschine - Google Patents

Innenschneckentrieb und oszillierende Walze für ein Feuchtwerk in einer Offsetdruckmaschine Download PDF

Info

Publication number
EP0510962B1
EP0510962B1 EP19920303644 EP92303644A EP0510962B1 EP 0510962 B1 EP0510962 B1 EP 0510962B1 EP 19920303644 EP19920303644 EP 19920303644 EP 92303644 A EP92303644 A EP 92303644A EP 0510962 B1 EP0510962 B1 EP 0510962B1
Authority
EP
European Patent Office
Prior art keywords
worm gear
shaft
roller
bearing unit
roller shell
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
EP19920303644
Other languages
English (en)
French (fr)
Other versions
EP0510962A1 (de
Inventor
John Mcphee
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.)
Baldwin Graphic Systems Inc
Original Assignee
Baldwin Graphic Systems Inc
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 Baldwin Graphic Systems Inc filed Critical Baldwin Graphic Systems Inc
Publication of EP0510962A1 publication Critical patent/EP0510962A1/de
Application granted granted Critical
Publication of EP0510962B1 publication Critical patent/EP0510962B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/15—Devices for moving vibrator-rollers

Definitions

  • the present invention relates to a novel internal worm drive and also to an oscillating roller assembly for use in dampening systems in printing presses.
  • a large majority of the continuous type dampening systems in use today with lithographic printing presses utilize the "squeeze roll” principle to meter out a thin film of dampening fluid, which is then further thinned before being transported and applied to the plate cylinder on the press.
  • a hard surfaced roller and a compliant surfaced roller are forced into contact with one another, and one of the rollers is partly immersed in a pan or tray containing dampening fluid.
  • This roller pair is geared together and connected to a motor drive which causes the two rollers to turn in counter rotating directions. Dampening systems utilizing this metering principle are frequently either of the "three-roll” type or of the "four-roll” type.
  • Figures 5A and 5B show two different configurations which are currently used in three-roll continuous type dampeners, in which none of the dampening rollers are equipped with mechanisms for oscillating or vibrating them in the axial direction.
  • FIGS. 5A and 5B comprise a pan 112 containing dampening fluid 113 and a pan roller 110 immersed in the fluid 113.
  • the roller 110 is a rubber pan roller which forms a flooded metering nip 114 with a chrome transfer and metering roller 116.
  • a non-metering slip nip 118 is formed between the roller 116 and a form roller 120.
  • the roller 110 is a chrome pan roller and the roller 116 (forming the metering nip 114 with the roller 110) is a rubber metering roller.
  • the form roller 120 makes a non-metering slip nip 118 with the roller 110.
  • Figures 5A and B possess common metering nip characteristics. That is, the roller 110 immersed in the pan 112 carries an excess of dampening fluid to the metering nip 114, which results in the nip becoming flooded and the excess fluid falling back into the pan.
  • Figure 6 illustrates a typical four-roll type continuous dampening system such as described in U.S. Patent 4,887,533, which contains one roller which is equipped with a mechanism for oscillating it in the axial direction.
  • a pan 212 contains dampening fluid 213 and a chrome pan roller 210 is immersed in the fluid 213.
  • a flooded nip 214 is formed between the roller 210 and a rubber slip roller 216.
  • a non-metering slip nip 218 is formed between the roller 216 and an oscillating chrome roller 219 which also forms a nip with a rubber form roller 220. The latter also forms a nip with a plate cylinder 222.
  • a problem sometimes encountered in printing with the lithographic printing press is the appearance of streaks or lines in the printed or image areas. Typically, these streaks occur in the direction of paper travel, and they may appear as a single line, or in a regularly spaced pattern of lines, such as in corduroy fabric.
  • a common cause of such streaks on presses equipped with continuous-type dampening systems is the lack of, or an insufficient number of, rollers in the dampening system that are equipped with mechanisms for oscillating the rollers in the axial direction.
  • Another method which can be used to provide oscillatory motion to a dampening system roller is to add a mechanism coupled to the press drive which is capable of imparting such motion.
  • oscillating drive mechanisms are incorporated into a press after it has been operated for some time, because of the space limitations it is generally not possible to utilize the proven worm drive concept with such a mechanism.
  • the self-contained mechanisms for generating an oscillating motion in the axial direction of the printing press roller have all utilized some form of a barrel cam.
  • This basic mechanism consists of a rotating cylindrical cam which impacts same type of axial motion to a cam follower.
  • These mechanisms can be characterized further according to the three types of cam surfaces employed: continuous single revolution barrel, continuous duplex or cross threaded, and dual discontinuous cam surfaces of opposite lead.
  • the most straightforward mechanism is the single barrel type, where a barrel cam is mounted on the inside of the roller and one or more followers are secured to the non-rotating roller shaft.
  • the cam can be mounted on the shaft and the follower(s) on the roller.
  • U.S. Patent No 2,040,331 is an example of such a device where the gears are located inside the roller.
  • U.S. Patent No. 2040331 describes a dampening system for lithographic printing presses, including a dampening roller provided by an oscillating roller assembly comprising:
  • the second type of device also uses a continuous cam having a multi-rotational surface.
  • a cam is known as a duplex or cross-threaded cam and is exemplified by the cams disclosed in U.S. Patent Nos. 715,902 and 4,040,682. In these designs, several revolutions of the roller are required to produce one cycle of oscillatory motion.
  • One problem encountered with this type of prior art device is that the mechanism is prone to jam as a result of wear.
  • One of the various objects of the present invention is to provide an improved dampening system for lithographic printing presses.
  • the invention provides provides a dampening system for lithographic printing presses as set out in appended claim 1.
  • a self-contained roller drive mechanism generates a pure harmonic motion in the axial direction.
  • Preferred oscillating dampening roller assemblies in accordance with the invention are rugged and reliable, compact and can be manufactured at low cost.
  • an internal worm drive means which includes a worm gear and also a substantially hollow tubular worm having an outer surface and an inner surface.
  • the inner surface of the tubular worm has at least one internal worm thread engaging the worm gear.
  • the axis of rotation of the tubular worm is substantially perpendicular to the axis of rotation of the worm gear. Rotation of the tubular worm about its axis causes the worm gear mated with the internal worm threads of the inner surface of the tubular worm to rotate about its axis.
  • oscillating roller assembly suitable for use as a dampening roller, which utilizes the internal worm drive described above.
  • the oscillating roller assembly has a shaft and a bearing unit mounted along the shaft.
  • the shaft and the bearing unit are substantially coaxial.
  • a worm gear having a plurality of teeth is disposed in a slotted space in the bearing unit and the shaft such that the rotational axis of the worm gear is substantially perpendicular to the longitudinal axis of the shaft and the longitudinal axis of the bearing unit.
  • the slotted space containing the worm gear has first and second opposite longitudinal ends in the shaft.
  • a pair of substantially coaxial eccentric cams are integrally affixed to opposite surfaces of the worm gear.
  • a roller shell having at least one internal thread is circumferentially mounted around the bearing unit such that the internal thread of the roller shell engages the teeth of the worm gear.
  • Rotation of the roller shell about its longitudinal axis causes the worm gear to rotate about its axis, thereby causing the cams affixed thereto to alternately contact the opposite longitudinal ends of the slotted space in the shaft.
  • the bearing unit oscillates back and forth along the shaft.
  • the bearing unit oscillates, it also causes the roller shell to oscillate back and forth along the shaft in substantial unison with the bearing unit.
  • a preferred self-driven oscillating roller according to the invention can be used in any one of the three positions in a three-roll type dampener to eliminate streaks and to facilitate the use of alcohol substitutes in fountain solution.
  • it can be used in the form roller position of a four-roll type dampening system, with the advantage that the harmonic oscillatory motion generated by its drive mechanism will avoid the generation of horizontal streaks.
  • It can, of course, also be used in either of the two other positions, i.e., the metering roller or transfer roller positions that are available in this type dampener.
  • the roller described here finds use in all types of dampening systems in use.
  • Fig. 1 is an exposed side view of an internal worm drive embodying the present invention.
  • Fig. 2 is an exposed top view of an oscillating roller assembly embodying the present invention.
  • Fig. 3 is a cross-sectional view of the oscillating roller assembly shown in Fig. 2 taken through line 2′-2′.
  • Fig. 4A is an exposed side view of the oscillating roller assembly shown in Fig. 2.
  • Fig. 4B is a second exposed side view of the oscillating roller assembly shown in Fig. 2.
  • Figs. 5A and 5B illustrate two types of three-roll dampening systems currently in use with lithographic printing presses.
  • Fig. 6 is an example of a four-roll dampening system currently in use with lithographic printing processes.
  • Fig. 1 is a cross-sectional cut-away view of an internal worm drive means 10 according to one embodiment of the present invention.
  • the internal worm drive means includes a tubular worm 11.
  • the tubular worm is manufactured from any substantially rigid and durable material known in the art.
  • the tubular worm 11 is made of metal or metal alloy; most preferably, steel.
  • the outer diameter of the tubular worm 11 can vary according to the uses for which it will be put.
  • the tubular worm 11 has an outer surface 12 and an inner surface 14.
  • the inner surface 14 of the tubular worm 11 is threaded in either a right- or left-handed manner.
  • the active surface of the inner threaded surface 14 have a surface finish of not greater than about 24 microinches (about 6.1 x 10 -4 mm). while the inner surface 14 of the tubular worm 11 is shown in Fig. 1 with a single thread, it is also within the scope of the invention that the inner surface have a double threaded worm.
  • a worm gear 16 which is provided as part of the internal worm drive means 10.
  • the worm gear 16 has a plurality of teeth 18. Each tooth of the worm gear 16 will engage the threads on the inner surface 14 of the tubular worm 11. As the tubular worm 11 rotates about its longitudinal axis "B", its thread on the inner surface 14 will engage each tooth 18 of the worm gear 16, thereby causing the worm gear 16 to rotate about its transverse axis through its center "A".
  • the axis of rotation of the worm gear 16 is substantially perpendicular to the longitudinal axis of rotation of the tubular worm 11 of the internal worm drive 10.
  • the worm gear 16 is also preferably made from a durable alloy such as, for example, case hardened steel. It is especially desirable that the active surface of the worm gear teeth 18 have a surface finish of not greater than about 8.1 x 10 -4 mm (about 32 microinches).
  • the worm gear 16 may additionally have eccentric cams 20, 22 integrally affixed to its opposite surfaces.
  • Fig. 1 shows one of the cams.
  • the second cam would be mounted to the worm gear 16 on the opposite side.
  • the two cams would preferably be substantially coaxial.
  • the cams 20, 22 attached to the worm gear 16 will drive additional components hereafter to be described.
  • an oscillating roller assembly 24 As that term is used herein, the word “oscillating” refers to reciprocating motion along an axis, for example the axis "B".
  • the oscillating roller assembly 24 utilizes the aforementioned novel internal worm drive concept typified by the tubular worm 11 in conjunction with the internal worm gear 16/dual eccentric cam 20, 22 combination shown in Fig. 1.
  • a substantially circular shaft 26 is provided for mounting a bearing unit 28.
  • the shaft is preferably a "dead" shaft, with no rotational, lateral or longitudinal motion. The opposite ends of the shaft can be mounted to another structure (not shown).
  • the being unit 28 is disposed along the shaft 26.
  • the bearing unit 28 is also substantially circular and substantially coaxial with the shaft 26.
  • the shaft 26 may have an optional axial oil hole for filling and recirculation of oil.
  • a worm gear 29 Housed within the bearing unit 28 and shaft 26 is a worm gear 29 having the plurality of teeth 30. Worm gear 29 and teeth 30 correspond to the worm gear 16 and teeth 18 shown in Fig. 1.
  • the worm gear 29 is mounted and contained in slotted space 31 cut or machined, for example, out of the bearing unit 28 and shaft 26. Points 31A and 31B in Fig. 3 represent the transverse boundaries of slotted space 31, while points 31C and 31D represent the upper and lower boundaries.
  • the worm gear 29 is mounted so as that its rotational axis about the point "A" (through the center of the worm gear) is substantially perpendicular to the longitudinal axis of the shaft 26 about the point "B". Point "B" also represents the longitudinal axis of the bearing unit 28.
  • the worm gear 29 may have a right or left hand helix. In any event, the helix hand of the worm gear 29 will be equal and opposite to that of the threaded inner surface of the roller shell hereinafter described. In one embodiment of the invention shown in Figs. 2 through 4, the helix angle is about 3.14 degrees.
  • the worm gear 29 is preferably made from a durable metallic alloy.
  • Manganese bronze is one material for the worm gear, but most preferably the material is a steel alloy. While the worm gear 29 may have any number of teeth, it is desirable that the gear have about sixteen teeth.
  • the worm gear preferably also has a tooth-to-tooth composite error of not greater than about 2.54 x 10 -2 mm (about 0.001 inches) and a total composite error of not greater than about 5.1 x 10 -2 mm (about 0.002 inches). It is especially preferred that the active surface of the worm gear teeth 30 have a surface finish of not greater than about 8.1 x 10 -4 mm (about 32 microinches). Also especially preferred is the hardness of the worm gear, which should preferably be in the range of about R c 55 - 60 ("Rockwell C").
  • the worm gear 29 is mounted in the slotted space 31 in the bearing unit 28 and shaft 26 by a pair of needle bearings 32, 33 pressed through the central bore "A" of the worm gear 29.
  • the worm gear needle bearings 32, 33 surround a dowel pin 34 also mounted through the shaft 26 and bearing unit 28.
  • the dowel pin 34 is further supported by a pair of standard drill bushings 35A and 35B.
  • the drill bushings are positioned through the shaft 26 and prevent worm gear rotation and deflection about the axis "B”.
  • the drill bushings 35A, 35B are also pressed into the bearing unit 28 to allow the bearing unit 28 to move axially as the dowel pin 34 moves.
  • Others means of mounting the worm gear 29 may occur to those skilled in the art, and are certainly within the scope of the invention.
  • the bushings 35A and 35B ride in a longitudinal groove 36 in the shaft 26.
  • the longitudinal groove 36 has endpoints 36A and 36B.
  • the longitudinal groove 36 extends the full transverse width of the shaft 26 through the slotted space 31.
  • Figs. 4A and 4B show one of the cams 39.
  • Cams 39 and 40 correspond to the cams 20 and 22 shown in Fig. 1.
  • Cams 39 and 40 can have substantially identical diameters within about 1.3 x 10 -2 mm (about 0.0005 inches).
  • the cams 39, 40 will alternatively contact the shaft 26 at points 41A, 41B and 42A, 42B shown in Fig. 2.
  • Points 41A, 41B and 42A, 42B are at longitudinal opposite ends of the slotted space 31, respectively.
  • Figs. 4A and 4B show points 41A and 42A.
  • Contact points 41A and 42A are substantially coplanar, while points 41B and 42B are substantially coplanar. Endpoints 36A and 36B of longitudinal groove 36 extends slightly beyond the contact points 41A, 41B and 42A, 42B, respectively, in the longitudinal direction.
  • a roller shell 44 which corresponds to the tubular worm 11 shown as part of the internal worm drive 10 in Fig. 1.
  • the roller shell 44 is substantially coaxial with the bearing unit 28 and the shaft 26.
  • the roller shell 44 is shown with an outer surface 45 and an inner surface 46.
  • the outer surface 45 may be plated or may be covered with a covering material. If the outer surface 45 is plated, then it should be smooth and preferably machine-ground. If the outer surface 45 is covered with an optional cover 47 made of rubber or other material, the outer surface may be rough.
  • the inner surface 46 of the roller shell 44 is internally threaded.
  • the threading of the inner surface 46 can be right-handed or left-handed, and is opposite to that of the worm gear 29.
  • the thread of the inner surface 46 engages the teeth 30 of the worm gear 29.
  • it is preferred that the surface of the inner threaded surface 46 have a surface finish of not greater than about 6.1 x 10 -4 mm (about 24 microinches).
  • the threaded inner surface should also preferably have a hardness in the range of about R c 62 - 70.
  • Fig. 4A the teeth 30 of the worm gear 29 are shown engaging the threaded inner surface 46 of the roller shell 44.
  • eccentric cam 39 is shown contacting the shaft 26 at point 41A.
  • Eccentric cam 40 would further contact the shaft 26 at point 41B such that points 41B and 42B would be substantially coplanar in the transverse direction.
  • roller shell 44 will cause the point "A” of the worm gear 29 to move in a reverse direction from end point 36B through the center of groove 36 until point "A" approaches end position 36A.
  • cam 39 will contact point 42A on the shaft and cam 40 will contact point 42B, thereby causing the bearing unit to move in the opposite axial direction.
  • point "A” of the worm gear 29 will move back and forth between end points 36A and 36B of groove 36.
  • cams 39 and 40 will alternately contact point 41A, 41B and 42A, 42B on the shaft, respectively, thereby causing the bearing unit 28 to oscillate along the shaft 26.
  • the roller shell 44 will also oscillate in substantial unison with the bearing unit 28.
  • a pair of crank arms could be pinned at one end to the shaft, while their otherends are mounted on the cams.
  • a double threaded tubular worm could be used in conjunction with a mating worm gear to impart faster oscillatory motion to the bearing unit.
  • bearings 48 and 50 shown in Figs. 4A and 4B.
  • Bearing 48 is pressed into a first retainer 52.
  • the retainer 52 has threaded holes to facilitate dissemble of the retainer.
  • An end plug 54 constrains retainer 52 in the axial direction by pushing against a shoulder 56 in the axial direction.
  • Bearing 50 is pressed into the roller shell 44.
  • the bearings 48, 50 provide bearing surface support for the bearing unit 28 of the roller assembly 24. These also serve to prevent excess "play" of the bearing unit 28 in the axial direction along the shaft 26.
  • the roller shell 44 moves to the left in the axial direction.
  • the roller shell 44 moves to the right in the axial direction.
  • the oscillating roller assembly heretofore described will find quick application as an dampening roller assembly for use with dampening systems for lithographic printing presses, for example.
  • the oscillating roller assembly will be especially preferred over those currently utilized in the art due to lower replacement costs resulting from less wear.
  • Those skilled in the art may find other applications for the novel design of the worm drive mechanism which utilizes the internally threaded worm, as well as for the oscillating roller assembly.

Landscapes

  • Rotary Presses (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)

Claims (6)

  1. Feuchtwerk für lithographische Druckerpressen bzw. Offsetdruckmaschinen mit einer durch eine Drehschwingwalzenanordnung (24) bereitgestellten Feucht(auftrag)walze, welche Anordnung umfaßt:
    a. eine Achse (26)
    b. eine längs der Achse (26) montierte bzw. gelagerte Lagereinheit (28),
    c. einen um die Lagereinheit (28) und die Achse (26) herum montierten Walzenmantel (44) und
    d. ein an der Achse (26) montiertes bzw. gelagertes, mit dem Walzenmantel (44) mitdrehbares Schneckenrad (29),
    dadurch gekennzeichnet, daß
    e. das Schneckenrad (29) eine Anzahl von Zähnen (30) aufweist und in einem geschlitzten bzw. ausgesparten Raum (31) in Lagereinheit (28) und Achse (26) so angeordnet ist, daß die Drehachse (A) des Schneckenrads im wesentlichen senkrecht zur Längsachse (B) von Lagereinheit und Achse liegt, wobei der ausgesparte Raum erste und zweite, gegenüberliegende Enden (41A, 41B; 42A, 42B) in der Achse aufweist,
    f. das Feuchtwerk ferner zwei im wesentlichen koaxiale, einstückig an gegenüberliegenden (Stirn-)Flächen des Schneckenrads angebrachte bzw. angeformte Exzenterkurven (39, 40) aufweist, welche Kurven abwechselnd an den gegenüberliegenden Enden des ausgesparten Raums an der Achse angreifen, und
    g. der Walzenmantel (44) mindestens ein umfangsmäßig um die lagereinheit herum angeordnetes (mounted) Innengewinde (46) aufweist, derart, daß das Innengewinde (46) mit den Zähnen (30) des Schneckerrads (29) zusammengreift, wodurch bei einer Drehung des Walzenmantels des Schneckenrad in Drehung versetzt wird, wodurch wiederum die Kurven (39, 40) dazu gebracht werden, an den gegenüberliegenden Enden des ausgesparten Raums (31) abwechselnd an der Achse anzugreifen, so daß die Lagereinheit und der Walzenmantel zum Oszillieren bzw. Schwingen längs der Achse gebracht werden.
  2. Feuchtwerk nach Anspruch 1, ferner umfassend einen abnehmbaren, umfangsmäßig um den Walzenmantel herum angeordneten Überzug.
  3. Feuchtwerk nach Anspruch 1, wobei das Schneckenrad eine rechtsgängige Steigung (helix) aufweist und das Innengewinde des Walzenmantels linksgängig ist.
  4. Feuchtwerk nach Anspruch 1, wobei das Schneckenrad in Achse und Lagereinheit mittels eines durch die Achse des Sehneckenrads (hindurch) montierten bzw. eingesetzten Lagerzapfens (34) durch zwei den Lagerzapfen umfangsmäßig umgehende Nadellager (32, 33) getragen bzw. gelagert ist, wobei der Lagerzapfen von zwei Bohrungs-Büchsen (35A, 35B) getragen ist.
  5. Feuchtwerk nach Anspruch 1, wobei der Walzenmantel ein mit den Zähnen des Schneckenrads zusammengreifendes Doppel(gang)-Innenschneckengewinde aufweist.
  6. Feuchtwerk nach Anspruch 1, wobei zwei Kurbelarme die Drehbewegung des Schneckenrads in die Oszillier- oder Schwingbewegung der Lagereinheit umsetzen.
EP19920303644 1991-04-24 1992-04-23 Innenschneckentrieb und oszillierende Walze für ein Feuchtwerk in einer Offsetdruckmaschine Expired - Lifetime EP0510962B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US69059591A 1991-04-24 1991-04-24
US690595 2000-10-17

Publications (2)

Publication Number Publication Date
EP0510962A1 EP0510962A1 (de) 1992-10-28
EP0510962B1 true EP0510962B1 (de) 1996-07-10

Family

ID=24773114

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920303644 Expired - Lifetime EP0510962B1 (de) 1991-04-24 1992-04-23 Innenschneckentrieb und oszillierende Walze für ein Feuchtwerk in einer Offsetdruckmaschine

Country Status (3)

Country Link
EP (1) EP0510962B1 (de)
JP (1) JP2622792B2 (de)
DE (1) DE69212056T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6772685B2 (en) 2001-10-25 2004-08-10 Heidelberger Druckmaschinen Ag Combination of a distributor roller of a printing machine and a traversing mechanism therefor, inking unit and printing press having the combination

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10227516B4 (de) * 2001-10-25 2012-10-18 Heidelberger Druckmaschinen Ag Changiermechanismus für eine Reibwalze einer Druckmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4509426A (en) * 1983-10-21 1985-04-09 Hardin Philip J Autoreversing dual axial speed ink roller

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6772685B2 (en) 2001-10-25 2004-08-10 Heidelberger Druckmaschinen Ag Combination of a distributor roller of a printing machine and a traversing mechanism therefor, inking unit and printing press having the combination

Also Published As

Publication number Publication date
JPH05345405A (ja) 1993-12-27
DE69212056D1 (de) 1996-08-14
DE69212056T2 (de) 1996-12-12
JP2622792B2 (ja) 1997-06-18
EP0510962A1 (de) 1992-10-28

Similar Documents

Publication Publication Date Title
CA1311149C (en) Film dampener unit for offset printing presses
US4606269A (en) Register adjustment device for a rotary printing machine
US4509426A (en) Autoreversing dual axial speed ink roller
US4583728A (en) Auxiliary gripper drive
US5054393A (en) Internal worm drive and oscillating roller assembly for use in inking systems for printing presses
US6655278B2 (en) Apparatus for fine positional adjustment of a plate cylinder for multicolor image registration
US4467720A (en) Spiral-type ductor
EP0510962B1 (de) Innenschneckentrieb und oszillierende Walze für ein Feuchtwerk in einer Offsetdruckmaschine
US5154092A (en) Internal worm drive and oscillating roller assembly for use in inking systems for printing presses
US4809606A (en) Oscillating form roller and apparatus and method for controlling the oscillation thereof
US4620481A (en) Inking unit for a printing machine
US4672894A (en) High rotational speed autoreversing axially oscillating ink roller
US2506778A (en) Ink roller vibrator
JP2846075B2 (ja) 周方向レジスタ装置
GB2076929A (en) Converting rotary to linear motion
US5230285A (en) Printing press coating apparatus having an oscillating roller assembly
EP0372233B1 (de) Walze für ein Farbwerk von Druckmaschinen
US4466347A (en) Device for conveying ink or a damping agent
US4833987A (en) Axially oscillating ink distributing roller having a unitary rocker follower
US5228389A (en) Oscillating form roller in the inking mechanism of a printing press
JP2946234B2 (ja) 印刷ロール
JPS60165282A (ja) 印刷装置のインキ供給装置
US4364281A (en) Driving mechanism for tool slides of punching and bending machines
US4962705A (en) Dampener for an offset printing machine
US3107580A (en) Gear shaper

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: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19930212

17Q First examination report despatched

Effective date: 19940920

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

REF Corresponds to:

Ref document number: 69212056

Country of ref document: DE

Date of ref document: 19960814

ET Fr: translation filed
ET1 Fr: translation filed ** revision of the translation of the patent or the claims
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20020401

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20020403

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20020417

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20020418

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030423

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031101

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20030423

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031231

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050423