EP1991419B1 - Druckwerke einer druckmaschine - Google Patents

Druckwerke einer druckmaschine Download PDF

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Publication number
EP1991419B1
EP1991419B1 EP07712406A EP07712406A EP1991419B1 EP 1991419 B1 EP1991419 B1 EP 1991419B1 EP 07712406 A EP07712406 A EP 07712406A EP 07712406 A EP07712406 A EP 07712406A EP 1991419 B1 EP1991419 B1 EP 1991419B1
Authority
EP
European Patent Office
Prior art keywords
roller
cylinder
printing
plane
transfer
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.)
Not-in-force
Application number
EP07712406A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1991419A2 (de
Inventor
Bernd Kurt Masuch
Georg Schneider
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.)
Koenig and Bauer AG
Original Assignee
Koenig and Bauer 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 Koenig and Bauer AG filed Critical Koenig and Bauer AG
Priority to EP07712406A priority Critical patent/EP1991419B1/de
Priority to EP08163740A priority patent/EP2014469A2/de
Priority claimed from PCT/EP2007/051955 external-priority patent/WO2007099148A2/de
Publication of EP1991419A2 publication Critical patent/EP1991419A2/de
Application granted granted Critical
Publication of EP1991419B1 publication Critical patent/EP1991419B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/26—Arrangement of cylinder bearings
    • B41F13/30—Bearings mounted on sliding supports
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/34—Cylinder lifting or adjusting devices
    • B41F13/40—Cylinder lifting or adjusting devices fluid-pressure operated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/004—Driving means for ink rollers
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/26—Construction of inking rollers
    • 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
    • B41F31/304—Arrangements for inking roller bearings, forks or supports
    • B41F31/307—Sliding bearings
    • 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
    • B41F31/32—Lifting or adjusting devices
    • B41F31/36—Lifting or adjusting devices fluid-pressure operated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/10—Constitutive elements of driving devices
    • B41P2213/11—Motors
    • B41P2213/124—Electric motors
    • B41P2213/126—Rotary electric motors

Definitions

  • the invention relates to a printing unit of a printing press according to the preamble of claim 1.
  • each bearing a pin of the cylinder bearing housing for adjusting a distance between the cylinders by means of an arrangement of pressure cylinders with mutually equal, mutually different or groupwise equal forces acted upon and thereby adjustable, wherein the respective effective direction of the pressure medium cylinder is in each case rectified.
  • the adjustable forces can be adjusted or preselected during machine running or even before the start of the machine run with a setting preselector control or regulating device, wherein in the case that the device is a control device, this sensor is associated with a sensor that its observations reports to the controller.
  • the set by the control unit to the pressure medium cylinders pressure can, for. B. according to the running speed of the cylinder or according to the speed of these cylinders within wide limits during operation of the device as desired continuously be adjusted.
  • a device for switching on and off as well as setting of inking or dampening rollers of a printing machine wherein a programmable logic controller automatically controls the position of a Farbwerks- or dampening roller with respect to a stationary distributor roller based on an input predetermined Anstell horres.
  • the programmable controller outputs a control command to an electrically controlled actuator, wherein the trained as a DC motor actuator forwards the control command to an actuator, wherein the actuator for the mechanical adjustment of the inking unit or dampening roller is responsible.
  • the electrically controlled actuator and the actuator are arranged in a roller lock of the adjustable inking or dampening roller.
  • control values for other positions in the programmable logic controller can be stored for different types of production.
  • control values for the inking unit or dampening rollers are dependent on the selected type of production, whereby preset control values for the different positions corresponding to the type of production are determined by the programmable logic controller with a program.
  • WO 03/049946 A2 and the WO 2004/028810 A1 methods are known for operating an inking unit or dampening unit of a printing press, wherein at least three rollers or cylinders are provided in the inking unit or dampening unit, which can come into contact with each other in at least two roller strips, and wherein at least one of the rollers is adjustable relative to the other rollers is mounted a machine frame.
  • the adjustably mounted roller is pressed for variable adjustment of the respective contact pressure in the two roller strips with an adjustable in size and direction force in the gap between the adjacent rollers.
  • an applicator roller of a short inking unit is provided whose diameter corresponds to that of the associated forme cylinder.
  • pressure actuators and linear bearings are provided for the placement of the printing cylinder cylinders.
  • the DE 32 23 352 A1 discloses a printing unit whose inking roller a same
  • Diameter as the forme cylinder has.
  • the printing unit works with rewetting, whereby the inking unit is formed as a short inking unit by a paint tray, an anilox roller and an applicator roller.
  • the EP 1 029 672 A1 discloses a rubber roller in a printing press, which can be adjusted by two pressure-actuable actuators to two adjacent frame-fixed rollers.
  • an inking unit having two applicator rollers, wherein the applicator rollers are adjustable by means of pressure medium actuators actuators to a form cylinder.
  • the EP 1 559 548 A1 shows an adjustment system for rollers, with an applicator roller to a form cylinder is adjustable via a fluid-actuated actuator.
  • the GB 2 398 272 A deals with the problem of minimizing contrast problems in the print image, which result from the defined color zone sections when feeding color into an inking unit. It discloses in a schematic representation of a prior art, a drawing vertically arranged under a form roller distributor cylinder.
  • the invention has for its object to provide a printing unit of a printing machine ..
  • linear bearings for cylinders and / or the applicator roll with movable stops allows a pressure-relevant setting of the cylinder and further an automatic basic setting - for a new configuration, a new blanket, etc.
  • this has a co-acting with the forme cylinder Aufragwalze whose diameter is as large as that of the forme cylinder. If the application roller is the same size, there is more room for operation and (semi-) automatic plate changing systems. Due to the large applicator roller a supporting effect is exerted on the preferably simple large form cylinder. In terms of vibrations advantageous embodiment, the axes of rotation of the transfer cylinder, forme cylinder and the applicator roller of the same printing unit in Anstelllage are arranged in a same plane.
  • the two levels of two printing units of a double printing unit even coincide so that the axes of rotation of the two transfer cylinders, the forme cylinder and the two application rollers, come to lie in the same plane.
  • the plane of transfer and forme cylinder against the plane of form cylinder and applicator roll slightly, z. B. ⁇ 15 ° to each other.
  • the single-sized form cylinder advantageously has a continuous channel extending over the six sides for fastening the printing form ends.
  • the transfer cylinders have a double or even larger (eg three or four times) circumference.
  • the double-sized transfer cylinder z. B. equipped with three juxtaposed blankets, which are offset in an advantageous embodiment with the ends in the circumferential direction by 180 ° alternately to each other, and are arranged side by side in a more cost-effective design with the ends side by side.
  • two printing paper widths of three pages wide can be arranged, or a single, six-page-wide printing blanket can be arranged completely.
  • z. B. web-fed rotary printing press in particular one Multicolour web-fed rotary printing press, has at least one printing unit 01, in which a material web, short web on both sides simply or in particular successively multiple, z. B. here four times, or several tracks at the same time one or more times are printable.
  • the printing machine is particularly useful as a newspaper printing machine and the printing unit 01 for printing as newsprint, z.
  • the printing unit 01 has a plurality of (in the present case four) vertically stacked double printing units 03 for the two-sided printing in the rubber-against-rubber operation ( Fig. 2 ).
  • the double printing units 03 - here with lying in a plane E printing cylinders 06; 07 illustrated, but may in principle be formed in the form of bridge or n-printing units.
  • the double printing units 03 are each formed by two printing units 04, which each have a cylinder 06 formed as a transfer cylinder 06 and a forme cylinder 06; 07, z. B.
  • a (double) pressure point 05 is formed in Anstelllage.
  • the above components are only on the top double printing unit 03 of Fig. 2 denotes, wherein the stacked (double) printing units 03; 04 are, however, essentially identical, in particular in the embodiment of the features relevant to the invention.
  • the double printing units 03 can - as well as the below-described advantageous feature of the linear (planar) arrangement - as well contrary to the illustration in Fig. 2 as down - opening n - unit or upwardly opening U - unit be executed.
  • the printing unit 01 has one or more of the following features, depending on the requirements, the type of machine, the technology used and / or the level of expansion.
  • the printing unit 01 or the double printing unit 03 is / are z.
  • the execution by the special individual drives of the cylinder 06; 07 be further developed advantageous. This also applies in an advantageous embodiment for the mechanical independence of the drive of the inking unit 08 and possibly dampening
  • one or more of the mentioned features are also to be understood advantageously for printing units 01, which do not have printing units 04 formed as double printing units 03 in the rubber-against-rubber printing, but have printing units 04 working only in straight printing.
  • the transfer cylinder 06 of a printing unit 04 then interacts with a counter-pressure cylinder.
  • the two cylinders 06; 07 of the second printing unit 04 and the inking unit 08 can then be used only an impression cylinder.
  • FIG. 2 is a z. B. in terms of ease of use advantageous embodiment of the printing unit 01 shown, which is exemplified in the range of their double pressure point (s) 05, operationally, ie for setup and maintenance purposes (in contrast to disassembly or disassembly), divisible executed.
  • the two parts which can be separated from one another including cylinders 06, 07, inking units 08 and, if present, dampening units 09) are referred to below where necessary and / or useful with partial pressure units 01.1 and 01.2.
  • the printing cylinder 06; 07 more, especially all the web on the same side printing printing 04 on the same frame or wall section 11; 12 stored.
  • the printing cylinder 06; 07 can in principle only one-sided, d. H. be stored flying on only one end frame frame sections 11.
  • each partial pressure unit 01.1; 01.2 two front side to the cylinders 06; 07 arranged frame sections 11; 12 provided.
  • the two separable parts are hereinafter referred to as partial pressure units 01.1 and 01.2, which the respective frame sections 11; 12 and printing units 04 (printing cylinder 06, 07 and inking units 08) have.
  • the partial printing units 01.1; 01.2 are in an advantageous embodiment along a direction perpendicular to the axis of rotation of the cylinder 06; 07 to each other or movable away from each other by preferably one of both spatially fixed (here partial printing unit 01.1), ie, for example, on a floor 13 of the printing room, a fixed space carrier 13, a mounting plate 13 or a mounting frame 13 for the printing unit 01 stationary, and the Other (here partial printing unit 01.2) movable relative to the bottom 13 or support 13 or mounting plate 13 or mounting frame 13 (hereinafter carrier 13) is mounted.
  • carrier 13 the partial pressure units 01.1 and 01.2 are shown in the contracted state and can be moved apart in the region of the dividing line 10 shown schematically.
  • the outer frame sections 12 in mutually corresponding, in non-illustrated bearing elements of the frame portion 12 and the carrier 13, z. B. together a linear guide 15 forming, stored.
  • These can be assigned as rollers running in rails or else as slidable or rolling body-mounted ones Be executed linear guide elements.
  • the wall sections 11; 12 are formed so that they are in their collapsed operating position (as shown) on its side facing each other in pairs substantially complementary to each other and formed together at their parting lines 10 and the dashed lines still form a substantially closed side front.
  • the maintenance position with a distance between the two wall sections 11; 12 is not shown here.
  • the relative position of the partial pressure units 01.1; 01.2 each other can also be achieved by moving the frame sections 12 or in another embodiment by both partial pressure units 01.1; 01.2 or their frame sections 11; 12 are movably mounted.
  • Shaping and transfer cylinder 07; 06 are preferably formed with a bale width of at least four, in particular six for particularly high product output six juxtaposed standing printed pages in the newspaper format, in particular in broadsheet format.
  • the forme cylinders 07 have a circumference which essentially corresponds to a printed page, in particular a stationary printed page in a newspaper format, ie. H. a printing form 22 is arranged, which extends essentially around the entire circumference and carries the printed image of only one printed page in the newspaper format.
  • the forme cylinder 07 advantageously has a channel 19 (with an opening towards the lateral surface) for receiving the printing plates 22, which is preferably formed continuously over the entire effective bale length.
  • the forme cylinder 07 can then be equipped with four or in particular six printing plates next to each other ( Fig. 3 ).
  • the continuous in the axial direction channel 19 and / or the corresponding clamping devices are designed in such a way that in the axial direction next to each other at least a plurality of individual, each one or two newspaper page width printing plates 22 are fixed.
  • the forme cylinder 07 is then in an operating situation with a respective pressure-side printing form 22 in the circumferential direction and a plurality, z. B. four or six in particular, each print page wide printing plates 22 in the longitudinal direction. It can also impression page width and two- or even dreidruckinbreite printing forms 22 mixed next to each other or only several two- or even dreidruckinbreite printing plates 22 side by side on the forme cylinder 07 may be arranged, which in total z. B. four, but in particular carry six printed images of printed pages.
  • the transfer cylinder 06 has a double large format (two newspaper pages in the scope behind each other) in a first, not shown embodiment z. B. only one channel 21 for receiving one or more (eg, two) juxtaposed elevators 23, in particular blankets 23, which in this case is then preferably also formed continuously over the entire effective bale length.
  • the transfer cylinder 06 can then be equipped with a continuous over the bale length and extending over substantially the full circumference or with two or three substantially over the full circumference reaching blankets 23 juxtaposed, the ends of which are aligned in the longitudinal direction of the cylinder 06 to each other.
  • the printing blankets 23 are preferably designed as a multi-layer printing blanket 23 made of a metal printing blanket 23, which has a dimensionally stable support plate with an elastic layer (see below).
  • this two or three blankets 23 may have side by side, the respective adjacent to each other are offset by 180 ° in the circumferential direction.
  • These staggered two or three blankets 23 may be held in two or three channel sections, which are also in the longitudinal direction of the cylinder 06 next to each other, the adjacent channel sections in the circumferential direction, however, offset by 180 ° to each other.
  • Fig. 3 and Fig. 4 show schematic representations of the printing cylinder 06; 07, wherein the transfer cylinder 06 for the purpose of increased stability with double the circumference (double large), and the forme cylinder 07 with a simple circumference (simply large) are formed.
  • the forme cylinders 07 each have an above-mentioned continuous channel 19 and in this example six single width (one printing side per printing plate 22) printing plates 22.
  • the transfer cylinder 06 in the longitudinal direction next to each other two mutually offset by 180 ° in the circumferential direction channels 21, in which two blankets 23, in particular two dreidruckprocessbreite blankets 23, are held side by side.
  • three two-page printing blankets 23 are held in three channels 21, which are offset in the longitudinal direction next to each other, but in the circumferential direction alternately to each other by 180 °.
  • the transfer cylinder 06 may alternatively be formed as a transfer cylinder 06 with a circumference of a stationary printing page, in particular newspaper page in broadsheet format, (simply large). In this case, he can then also have a single, full-length blanket 23 or two or three fully juxtaposed full-length blankets 23 in alignment.
  • Transfer cylinder 06 The not the dimension of the transfer cylinder 06 concerned features of the printing unit 01 can then be applied individually or in combination thereto.
  • cylinder units 17 executable modules have z. B. a cylinder 06; 07 with pin 63; 64 and one already on the pin 63; 64 pre-tensioned (biased and / or preset) storage unit 14 on.
  • Bearing unit 14 and cylinder 06; 07 get before their insertion into the printing unit 01 their firmly defined position to each other and are collectively in the printing unit 01 can be introduced and stiff ( Fig. 16 ).
  • the circumferences of the double-sized cylinders 06 can be between 840 and 1300 mm, in particular 860 to 1120 mm, and those of the simply large cylinders 07 correspondingly at 420 to 650 mm, in particular 430 to 560 mm or even between 430 to 540 mm.
  • the forme cylinder 07 is very critical due to its geometry in terms of deflection and cylinder vibrations.
  • FIGS. 5 to 11 schematically illustrated solution for the printing unit 04 or inking 08 helps to counteract this problem.
  • Such formed inking units 08 may be arranged in a printing unit 01 with one or more of the embodiment features.
  • Transfer cylinder 06, forme cylinder 07 and roller 28, z. B. applicator roll 28, in particular inking roller 28 are in an advantageous embodiment, as exemplified in Fig. 5 to 9 and 11 shown, arranged linearly, ie their Rotational axes are in pressure-An substantially in a common through the axes of rotation of forming and transfer cylinder 07; 06 in the pressure-on position clamped plane E.
  • the plane E of the cylinder 06 falls; 07 with a plane A together, which by the axes of rotation of the forme cylinder 07 and the cooperating roller 28, z. B. applicator roll 28, in particular inking roller 28 in pressure on (ie operating position) is formed (see example of Fig. 5 to 9 ).
  • the inking roller 28 is formed as a "large" inking roller 28 and corresponds in diameter substantially (deviation at most +/- 5%, in particular at most +/- 2%) of the forme cylinder 07 - ie z. B. substantially the length of a printed page, z. B. Newspaper page.
  • the diameter of the roller 28 is preferably the undisturbed diameter, i. without a depression caused by a hiring.
  • the diameter of the forme cylinder 07 is preferably the one with the print original, z. B. equipped with the or the printing plates 22 effective total diameter.
  • the "1: 1 inking roller” 28 supports the forme cylinder 07 due to its large diameter and the geometric arrangement (eg in plane with the channel passages).
  • the inking roller 28 in one embodiment may be slightly convex (e.g., convexity to the effective ball length of 0 to 0.5 mm, especially 0 to 0.3 mm.
  • this roller 28 would be a sleeve, z.
  • a sleeve formed roll covering, which can be pulled over the roll main body, or with a roll cover, which is in the manner of a blanket (comparable to a arranged on the transfer cylinder 06 blanket 23 see below) in a on the roller body of the roller 28 longitudinally extending channel is attached.
  • the inking roller 28 should be adjusted with a defined force. This can be done either via a bearing of the roll neck 256 in a linear bearing 252, a lever 254 which can be pivoted by a pressure-actuated actuator 253 or via an automatic roller lock 257 which can be acted upon by a pressure medium (see below).
  • the (near-cylinder cylinder) distribution cylinder 33 is advantageously arranged in one embodiment such that the connection plane E of the axes of rotation of cylinder 07 and inking roller 28 with a joint plane V between the axes of rotation of inking roller 28 and the friction cylinder 33 at an angle of z. B. 70 - 110 °, preferably 80 to 100 °, in particular 90 ° +/- 5 °, most advantageously substantially 90 °.
  • Subsequent rollers 34; 37; 36 and a form cylinder remote friction cylinder 33 ' may be formed with smaller diameters in conventional construction.
  • connection plane V between the axes of rotation of inking roller 28 and distribution cylinder 33 is substantially vertical, or at most +/- 20 °, advantageous at most +% - 10 °, in particular at most +/- 5 ° deviates from the vertical.
  • This criterion may be particularly advantageous when the plane E is inclined to the horizontal.
  • the form cylinder near the distribution cylinder 33 acts on the one hand with the large inking roller 28 and upstream with at least one roller 34, z. B. ink roller 34, in particular transfer roller 34 (eg., With a soft surface), in particular two transfer rollers 34 together.
  • the latter receives the ink in turn via at least one further transfer roller 34 (eg with a soft surface), a roller 37, in particular a film roller 37 and a roller 36, in particular a ductor or dipping roller 36 from an ink fountain 38.
  • Dipping and film roller 36; 37 can also be replaced by another ink feed or metering system (eg pumping system in the pumping inking unit, or lifter system in the lifting inking unit).
  • the distribution cylinders 33, 33 ' are common or individually, by a separate, from the cylinders 06; 07 independent drive motor driven by rotation.
  • the roller 36 is preferably, and optionally further provided for the film roller 37, a separate rotary drive motor.
  • the traversing movement of the distribution cylinder 33; 33 ' can be carried out with increased demand for variability, jointly or individually, by a separate drive means, or as provided here with reduced effort, by a rotational movement in axial movement forming gear.
  • a dampening form roller 41 in its geometric arrangement can also support the forme cylinder 07.
  • the dampening roller 41 may preferably be arranged such that the connection plane E between the axes of rotation of forme cylinder 07 and inking roller 28 with a joint plane F between the axes of rotation of forme cylinder 07 and dampening roller 41 at an angle of z. B. 70 - 110 °, preferably 80 to 100 °, in particular 90 + / 5 °, most advantageously substantially 90 °.
  • connection plane F between the axes of rotation of forme cylinder 07 and dampening form roller 41 is substantially vertical, or at most +/- 20 °, advantageously at most +/- 10 °, in particular at most +/- 5 ° deviates from the vertical.
  • This criterion can be particularly advantageous if the printing unit 04 or the plane E is inclined to the horizontal.
  • this dampening roller 41 may preferably have substantially the circumference of the forme cylinder 07 and / or be advantageously convex (+/- 5%, in particular up to +/- 2%).
  • the dampening unit 09 is preferably designed as a so-called contactless dampening unit 09, in particular spray dampening unit 09, the dampening solution being transferred contactlessly from a fountain solution source 44 to a last roller 43 of the dampening unit 09.
  • This can be done, for example, by contactless spinning, contactless brushing or otherwise, but preferably by spray nozzles of a spray bar 44.
  • spray bar 44 and forme cylinder 07 in series three rollers 41; 42; 43 before (without possibly existing rider rollers), so the cooperating with the printing plate roller 41, z. B. applicator roll 41, z. B.
  • a dampening roller 41 preferably with softer Surface (eg rubber), a subsequent hard-surface roller 42 (eg, chrome or stainless steel), which is preferably designed as an iridescent friction cylinder 42, and the roller 43 receiving the dampening solution from the fountain solution source 44 in the three-roller dampening unit 09 soft surface (eg rubber) running.
  • a fourth roller not shown with z. B. hard surface, which receives the dampening solution.
  • the distribution cylinder 42 by its own, of the cylinders 06; 07 independent drive motor driven by rotation, wherein the two rollers 41 and 43 are driven by friction.
  • a separate rotary drive motor can also be provided for the roller 43.
  • the traversing movement of the friction cylinder 42 can take place by means of its own drive means or, as provided here with reduced effort, by means of a gearbox which converts its rotational movement into axial movement.
  • the roller 42 is provided with a color-friendly or oleophilic surface (i.e., wetting angle with corresponding fluid, in particular the color, smaller than 90 °), e.g. made of rubber or plastic (eg a polyamide material) is formed.
  • a color-friendly or oleophilic surface i.e., wetting angle with corresponding fluid, in particular the color, smaller than 90 °
  • the lateral surfaces of all three rollers 41; 42; 43 of the dampening unit 09 with a color-friendly or oleophilic surface i.e., contact angle of wetting with corresponding fluid, in particular the color, less than 90 °
  • the middle roller 42 of the three rollers 41; 42; 43 of the dampener roller train a color-friendly upper or lateral surface 45 made of plastic, z.
  • a polyamide material such as in particular Rilsan on.
  • a "soft" surface is to be understood here as meaning a surface elastically yielding in the radial direction, ie having a modulus of elasticity in the radial direction of preferably at most 200 MPa, in particular less than or equal to 100 MPa.
  • the the Dampening agent of the dampening solution source 44 receiving roller 43 and / or the roller below in the direction of the forme cylinder 07 roller 42 preferably has a lateral surface with a hardness in the range between 55 ° and 80 ° Shore A.
  • the roller 41 applying the dampening solution to the forme cylinder 07 preferably has a lateral surface 45 with a hardness in the range between 25 ° and 35 ° Shore A.
  • the dampening unit 09 can also be designed as a contact dampening unit 09 (film dampening unit, lifter, cloth or brush dampening unit) with a total of three rolls between dampening solution master and forme cylinder 07 in series.
  • the wet film on the distribution cylinder 42 of the dampening 09 can in the embodiment according to Fig. 5 be smoothed by an additional roller 261.
  • actuator 253 and pivotable lever 254 can in Fig. 8 also the linear bearing 252 explained below using the example of the linear bearing 14 or the roller lock 257 explained below (US Pat. Fig. 9 ) be used.
  • Fig. 6 and Fig. 7 is the printing mechanism 04 similar to that of Fig. 5 shown, in Fig. 6 instead of the additional roller 261 now an additional roller 262, and in Fig. 7 an additional roller 263 is arranged in the inking unit 08. There may also be two or even three of said rollers 261; 262; 263 be provided simultaneously.
  • Fig. 8 the printing unit 04 is exemplified using a linear bearing 252, wherein here also individually or to several rollers 261; 262; 263 may be provided from the preceding examples.
  • Fig. 9 Finally, the printing unit 04 is shown using a roller lock 257, in which case also individually or a plurality of the above rollers 261; 262; 263 can be provided. Also, a dampening 09 of the preceding FIGS. 5 to 8 be provided. Exemplary for the dry offset (waterless) is Fig. 9 but executed without dampening unit 09. However, it may still be provided as a support roller 41 ', the roller 41'. The design for the waterless offset without dampening unit is with or without the remaining support roller 41 'on the training of the inking units 08 of FIGS. 5 to 8 transferred to. In the case of only acting as a support roller 41 'roller 41 whose surface should have a Shore A hardness of> 50, z. From 60-80.
  • the "long" inking unit is the inking roller 28, at least two series-arranged distribution cylinders 33; 33 ', at least two transfer rollers 34, at least one between the distribution cylinder 33; 33 'and one on the color path between the color supply (eg., Ink fountain 38 or ink pump bar) and the form cylinder distal distribution cylinder 33' having inking 08 very "slim" formed. That is, the inking unit 08 including ink supply (ink fountain, etc.) points in a direction parallel to a plane D, which is formed by the two cylinder 06 forming the pressure point 05, a significant, for example, factor 1, 2, greater length than in the direction perpendicular to this plane D.
  • ink supply ink fountain, etc.
  • the printing units 04 - as shown - preferably formed with pre-moistening, d. H. after the passage of a point on the forme cylinder 07 through the Nippstelle with the transfer cylinder 06, this occurs first with the dampening roller 41 and only then with the inking roller 28 in operative contact.
  • inking unit 08 is designed as a short inking unit with a large anilox roller 26 roller 26 is formed. This preferably takes the same position described above, as previously in Fig. 5 The form cylinder near the friction cylinder 33.
  • the formation of this inking unit 08 as a short inking unit 08 can in combination with one of the in Fig. 5 to 9 described dampening units 09 and / or instead of the roller lock 257 (with the corresponding actuators) in combination with the lever 254 or the linear bearing 252 may be formed.
  • Fig. 12 is exemplary for the to the FIGS. 5 to 10 described inking 08 the inking and dampening 08; 09 of the Fig. 5 but without roller 261, shown in a printing tower with four stacked double printing 03.
  • automatic or semi-automatic handling devices 24, in particular printing plate changers 24 are provided.
  • the printing unit 01 is divisible as described above with the partial printing units 01.1; 01.2 trained.
  • Fig. 12 can also be one of the other in Fig. 5 to 11 described inking or dampening 08; 09 be provided:
  • Fig. 12 is per printing unit 04, the axes of rotation of transfer cylinder 06, forme cylinder 07 and applicator roll 28 in pressure-An in one common plane E.
  • the two printing units 04 of a double printing unit 03 are offset from each other at their transfer cylinder 06 so that the two planes E of the two printing couples 04 do not coincide, ie the transfer cylinder 06 connecting plane D is inclined to at least one of the two This can be advantageous if a partial looping of the vertically running web is to be produced and / or if space or a specific orientation of the printing units is to be created by means of printing plate changers 24.
  • Fig. 12 are the above-mentioned lever 254 provided for the inking rollers 28 by way of example.
  • roller locks 257 or linear bearings 252 can also be provided for this purpose.
  • roller locks 257 When using roller locks 257 is particularly advantageous that the inking roller 28 in an ideal manner to the two cooperating rotating body (forme cylinder 07 and roller 33) can be adjusted.
  • the inking roller 28 is here - depending on action on the individual pressure chambers (see below: actuators 322) - in different directions perpendicular to the axis of rotation movable.
  • Fig. 13 shows a further embodiment of a printing unit 01 with stacked double printing units 03.
  • the four printing cylinders 06; 07 namely, the two pressure point 05 forming transfer cylinder 06 and the two associated form cylinder 07, in pressure-An in a common plane E.
  • the applicator roller 28 is not in the plane E but is offset by the above-mentioned angle ⁇ on the forme cylinder 07, while the applicator roller 28 of the cooperating printing unit 04 is arranged here in the same plane E.
  • the application roller 28 of the second printing unit 04 can also be offset by an angle ⁇ (see above).
  • Said offset of the applicator roller 28 of one of the two printing units 04, in particular of the uppermost, is particularly advantageous if the plane E of the double printing unit 03 is not perpendicular to the web running direction, but the plane E by e. 2 ° - 15 °, in particular 4 ° to 10 ° with respect to the vertical inclined to the running direction. In this case, space 28 for the printing plate or plate change is created by slight misalignment of the applicator roll.
  • a printing unit 04 with an applicator roller 28 arranged at an angle ⁇ > 0 with respect to the plane E it is advantageous to provide on the applicator roller 28 a continuous surface, i. without providing a break as resulting in the attachment of a finite lift in a duct.
  • z. B. a fixed to a roller body connected
  • z. B. vulcanized roll cover or a detachable sleeve advantage The firmly connected roll cover or sleeve can then advantageously have at least one compressible layer (comparable to a layer used in rubber blankets of the transfer cylinder).
  • the compressible layer promotes the accurate transfer of the color in the nip, since the compressible layer ensures the build-up of a contact pressure, but does not deviate to the side in contrast to purely elastic materials.
  • Fig. 29 formed as satellite printing units 02, in particular nine-cylinder printing units 02.
  • the transfer cylinder Q6 of the printing unit 04 does not act here with a second transfer cylinder 06, but with a counter-pressure cylinder 16, such as satellite cylinder 16, together.
  • Fig. 29 is a printing tower with two stacked nine-cylinder satellite printing units of a printing press, such as a web-fed rotary offset printing machine for two-sided printing along a transport path not shown through the printing press transported through substrate, such as a paper web provided.
  • Each nine-cylinder satellite printing unit comprises a central, acting as an impression cylinder 16 satellite cylinder 16 and four co-operating with the satellite cylinder 16 printing units 04th
  • each plate cylinders 07 of each nine-cylinder satellite printing unit are arranged adjacent to each other at least substantially in the horizontal direction. Also, in each case two plate cylinders 07 of each nine-cylinder satellite printing unit are arranged one above the other at least substantially in the vertical direction. The same applies to the transfer cylinder 06, whose axes form at least approximately a square.
  • Fig. 14 shows exemplary advantageous structures of a roll cover of the inking roller 28, z. B. a Farb Huaweiwalzenbezug 45 in the form of a finite roll cover, a sleeve or fixedly applied to a roller body 50.
  • a metal blanket similar structure is chosen, with a compressible layer 46, z. B. on a dimensionally stable support 47 (eg., Metal plate or metal sleeve) is applied.
  • a fabric layer 55 may be applied.
  • the outer layer 48 forms an elastic layer 48, z. B. rubber layer, which may still be covered by a cover layer 49 in a variant.
  • the cover layer 49 may, if present, have a hardness in the range of 30 ° to 45 ° Shore A, wherein this cover layer 49 made of an elastic material, preferably of a plastic, for. B. consists of a polymer and has a thickness in the range between 30 microns and 60 microns, preferably of 50 microns +/- 5%.
  • the cover layer 49 may have a microstructure on its outside transporting the ink exhibit.
  • the elastic layer 48 may have a hardness of> 50 Shore A, in particular from 60 to 80 Shore A.
  • the elastic layer 48 has z. B. have a thickness of 0.1 to 0.4 mm, in particular of 0.2 mm +/- 20%.
  • Fig. 14b has the inking roller cover 45 in place of the dimensionally stable support 47, z. B. a further fabric layer 55, wherein between this and the roller base 50, a non-illustrated adhesive layer may be provided.
  • Fig. 15 shows an embodiment of the inking roller 28, the inking roller cover 45 is formed in a sleeve.
  • air ducts 60 are provided to the lateral surface in the roll body 50 by means of which z. B. compressed air can be supplied.
  • this is a structure for the sleeve according to Fig. 14b provided, d. h with fabric layer 55 instead of a metal sleeve.
  • the blanket 23 can be particularly advantageous in all examples to carry out the blanket 23 as a metal blanket 23 executed multilayer blanket 23, which has a dimensionally stable support plate with an elastic layer.
  • the layer may then be formed with a conventional layer of a metal blanket.
  • all four printing cylinder 06; 07 (but at least three) has its own storage unit 14, in which the on / off mechanism is already integrated. It can also for three of the four cylinders 06; 07 the bearing / Abstellmechanismus having bearing units 14 and be provided for the fourth bearing units 14 without on / off mechanism.
  • the inking roller 28 can also be mounted in a variant in a linear bearing 252 or bearing unit 252. Since these essentially correspond in their structure, the following statements on the bearing unit 14 are also applicable to the linear bearing 252 or bearing unit 252. In the Fig. 17 and 18 this fact is taken into account by the reference numbers (252) in brackets.
  • Fig. 17 and 18 show a preferably linear path based bearing unit 14 (252) in the schematic longitudinal and cross-section.
  • the storage / retrieval mechanism integrating bearing unit 14 (252) has in addition to a bearing 71, z. B. radial bearing 71, for example, a cylindrical roller bearing 71, for rotatably supporting the cylinder 06; 07 storage means 72; 73 for a radial movement of the cylinder 06; 07 - for pressure on or pressure off - on.
  • the bearing unit 14 (252) (after mounting the bearing unit 14 (252) fixed to the frame) carrier-fixed bearing elements 72 and the movable against these bearing elements 73.
  • the carrier-fixed and movable bearing elements 72; 73 are as co-operating linear elements 72; 73 and together with corresponding sliding surfaces or intermediate rolling elements in total as Linear bearing 70 is formed.
  • the linear elements 72; 73 take in pairs a radial bearing 71 receiving bearing block 74, z. B. carriage 74 between them.
  • Bearing block 74 and the movable bearing elements 73 may also be made in one piece.
  • the carrier-fixed bearing elements 72 are arranged on a carrier 76, which in total with the side frame 11; 12 is connected or is.
  • the carrier 76 is designed for example as a support plate 76, which, for example, at least on a drive side, a recess 77 for the passage of a shaft 78, z. B.
  • the frame wall 11; 12 on the drive side preferably has a recess or an opening for a drive shaft 78.
  • the opposite side of the drive side does not necessarily have a recess 77 or a recess in the side frame 12; 11 may be provided.
  • a length of the linear bearing 70 is smaller than a diameter of the associated printing cylinder 06 in the direction of adjustment S; 07th
  • the clamping device 66 is here for example as z. T.
  • the coupling can also in other ways, for. B. in the circumferential direction having a positive connection, be executed.
  • the shaft 78 is formed by a recess in the side frame 11; 12 out, which is sufficiently large for the movement of the shaft 78 is dimensioned together with the bearing block 74 and which z. B. is formed in the manner of a slot.
  • a cover 69 may be provided with a slot covering the collar, which z. B. with the bearing block 74, but not connected to the shaft 78.
  • Fig. 17 illustrated one of possibly a plurality of serially arranged coupling 148, in particular multi-plate clutch 148, by a rotationally fixed connection 75, z. B. a clamping element 75, coupled.
  • the gear 150 is coupled directly to the drive motor 121 without angle and / or offset compensating coupling 148 to the shaft 78.
  • the drive motor 121 is not fixed to the frame, but arranged cylinder-tight and is connected to the cylinder 06; 07 moved. This also applies in an advantageous variant of a z.
  • FIGS. 22 to 25 shown direct drive.
  • journal 64 can preferably be moved by means of a device (not shown) for axially moving the cylinder 07, d. H. with a side register drive, be coupled.
  • linear bearings 70 in such a way that the cooperating bearing elements 72; 73 both on the assembly storage unit 14 (252) - and not a part of the side frame 11; 12 of the printing unit 01 - are provided, allows pre-assembly and pre-adjustment or adjustment of the bearing voltage.
  • the advantageous arrangement of the two bearing block 74 encompassing linear bearing 70 allows a backlash-free setting, as opposed to the two linear bearings 70 in such a way that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 06; 07 learn or record.
  • the linear bearings 70 are thus adjustable in the direction to which it is at play-free positions of the cylinder 06; 07 also arrives.
  • non-penetration and the above definition with respect to the inside width L should be understood in a broader sense to mean that, at least in the region of the intended end position, the cylinder 06; 07 and at least on a continuous path from a frame edge to the location of the end position such a "non-penetration" is present, so that the cylinder unit 17 of an open, between the two end-side side frames 11; 12 lying side without tilting, d. H.
  • the bearing units 14 (252) are in the manner on the inner walls of the side frames 11; 12 arranged that the cylinder 06; 07, in particular their bearing units 14 (252) on zylinderferner side by the side frame 11; 12 are supported, which has static and mounting advantages.
  • Identifiable linear bearings 70 thus each have pairings of corresponding cooperating bearing means 72 and 73 or their guide or effective surface areas, designed as sliding surfaces (not shown) or with rolling elements 65 arranged therebetween.
  • the guide surfaces of the frame-fixed bearing means 72 of the linear guide 70 point in the the pin 63; 64 facing half space.
  • the frame-fixed bearing means 72 engage around the bearing block 74 arranged between them.
  • the frame-fixed guide surfaces of the two linear bearings 70 thus partially surround the guide surfaces of the bearing block 74 with respect to an axial direction of the cylinder 06; 07th
  • Fig. 17 is schematically the cylinder 06; 07 with pin 63; 64 and a preassembled storage unit 14 (252).
  • This module can thus be preassembled between the side frames 11; 12 of the printing unit 01 used for easy installation and attached to designated locations.
  • the bearing units 14 (252) for forming and transfer cylinders 07; 06 - if necessary, except for the permitted operational size of the travel - be of identical construction. Due to the pre-assembled design, the effective inner surface of the radial bearing 71 and the outer effective lateral surface of the pin 63; 64 cylindrical instead of conical, since both the assembly of the bearing unit 14 (252) on the pin 63; 64 as well as the setting of the bearing clearance outside the printing unit 01 can be done.
  • the storage unit 14 (252) can be shrunk, for example.
  • the mountable as a whole unit is advantageous in the manner of an optionally partially open housing of z. B. the carrier 76, and / or z. B. a frame (in Fig. 18 without reference z. B. the four storage unit 14 (252) to all four sides outwardly limiting plates) and / or z. B. the cover 94 ( Fig. 18 ).
  • the frame-fixed bearing elements 72; 73 are arranged substantially parallel to one another and define a positioning direction S (FIG. Fig. 18 ).
  • a pressure-on-points is done by moving the bearing block 74 in the direction of pressure point by means of at least one actuator 82 applied to the bearing block 74 force, in particular by a force-controlled or a force defined actuator 82, by means of which for employment a defined or definable force in print-on direction on the bearing block 74 can be brought ( Fig. 18 ).
  • the decisive for the color transfer and thus the print quality, among other things, line force in the nip points is therefore not by a travel, but by the balance of forces between the force F and between the cylinders 06; 07 resulting line force F L and the resulting equilibrium defined.
  • cylinder 06; 07 employed in pairs by the bearing block 74 is acted upon by the correspondingly adjusted force on the / the Aktror (s) 82.
  • Aktror Aktror
  • At least the two middle of the four cylinders 06 - or in other words, at least all of the two outer cylinders 07 different cylinder 06 at least during a period of time Setting in a defined position, advantageously in the Anstelllage found by the equilibrium of forces, can be fixed or at least wegbegrenzbar.
  • bearing block 74 even during operation - at least in one direction away from the pressure point against a force, for. B. spring force, in particular a definable force, is movably mounted. This is - in contrast to the pure travel limit - on the one hand, a maximum line force when working together cylinder 06; 07 defined, and on the other hand a yielding, for example, in a web break with subsequent winder on the cylinder 06; 07, allows.
  • the bearing unit 14 (252) - at least during the setting process - a location-adjustable stop 79, which limits the travel to the pressure point 05 out.
  • the stop 79 can be moved in such a way that the stop surface 83, which acts as a stop, can be varied along the direction of adjustment at least in one region. It is thus an adjustment device (adjustable stop 79) provided in an advantageous embodiment, by means of which the position of a pressure near the end position of the bearing block 74 is adjustable.
  • a wedge drive described below.
  • the placement of the stop 79 can basically be done manually or via an actuator 84 (see below).
  • At least one resilient element 81 z. B. spring element 81, which applies a force F R from the stop 79 in a direction away from the bearing block 74.
  • the Spring member 81 causes pressure-off in the event that bearing block 74 is not otherwise prevented from moving.
  • the applied force F, the restoring force F R and the position of the stop 79 is selected such that no substantial force ⁇ F is transmitted between the stop 79 and the abutment surface of the bearing block 74 in an abutment position, for example
  • the contact force between the cylinders 06; 07 substantially determined by the voltage applied by the actuator 82 force F.
  • line force in the Nipp points is therefore not primarily defined by a travel, but at quasi-free stop 79 by the force F and the resulting balance. Basically, after finding the basic setting with the appropriate forces F, a removal of the stop 79 or a corresponding fixation, which is effective only during the basic adjustment, would be conceivable.
  • the actuator 82 can be embodied as any desired actuator 82 applying a defined force F.
  • the actuator 82 is designed as actuatable by pressure medium actuating means 82, in particular as a piston 82 movable by a fluid.
  • Advantageous in terms of possible tilting is the arrangement of several, here two, such actuators 82.
  • a liquid eg. As oil or water, used.
  • a controllable valve 93 is provided in the bearing unit 14 (252). This is performed, for example, electronically controlled and provides the hydraulic piston 82 in a position without pressure or at least to a lower pressure level, while in another position of the force F conditional pressure P is present.
  • a non-designated leakage line is provided here for safety.
  • a travel limit by a mobile, force-limited stop 88 as overload protection 88, z. B. spring element 88 may be provided, which in the operational pressure-Ab, d. H. the pistons 82 are unloaded and / or retracted, although serve as a stop 88 for the bearing block 74 in pressure-off position, but in the case of a web winder or other excessive forces from the pressure point 05 forth yields and gives a greater way free.
  • a spring force of this overload protection 88 is therefore selected to be greater than the sum of the forces from the spring elements 81.
  • z. B. only 0.3 to 4 mm, e.g. 0.5 to 3.5 mm or between 1 to 3 mm, providable.
  • the stop 79 is in the illustrated embodiment ( Fig. 18 ) as transversely to the direction of adjustment S movable wedge 79 executed, wherein the same moves the position of the respective effective stop surface 83 along the direction of adjustment S varies.
  • the wedge 79 is supported for example on a carrier-fixed stop 96.
  • an actuator 84 for example, a druckstoffbetätigbares adjusting means 84 such as a pressure medium actuated piston 84 in a working cylinder with (double-acting) piston via a z. B. designed as a piston rod 85 transmission member 85 or by an electric motor via a Threaded spindle executed transmission member 85, movable.
  • This actuator 84 can either be effective in both directions or, as shown here, be designed as a one-way reactor, which operates against a return spring 86 when activated.
  • the force of the return spring 86 is selected from the above reasons (largely force-free stop 79) so weak that the wedge 79 is held only in its correct position against gravity or vibration forces.
  • the stop 79 can also be designed in another way (for example as a plunger adjustable and fixable to the adjusting direction, etc.) in such a way that it can be varied in the adjusting direction S and-at least during the setting process-fixed stop surface 83 for the movement of the bearing block 74 in the direction of pressure point 05 forms.
  • a setting of the stopper 79 for example, directly parallel to the direction of adjustment S by a drive means, for example, a pressure medium actuated cylinder with (double-acting) piston or an electric motor.
  • the centers of rotation of the cylinder 06; 07 an imaginary connecting line or plane E (hereinafter referred to as "linear" or “flat” double printing unit 03).
  • the plane E and the incoming or outgoing web break a deviating from 90 ° internal angle between 75 and 88 °, in particular from 80 to 86 °.
  • this arrangement when the adjustment direction S is horizontal and the web is substantially vertical.
  • connection plane of the pressure point 05 forming cylinder 06 and below the plane E between the forming and transfer cylinders 07; 06 are understood, and the above to the angle to the direction of adjustment S at least one of the pressure point 05 forming cylinders 06 and the forme cylinder 07 and the plane D or E are obtained.
  • One of the pressure point 05 forming cylinder 06 can also be stationary and operationally not adjustable (but possibly adjustable) in the side frame 11; 12 may be arranged, while the other along the adjustment direction S, is movably mounted.
  • a for switching on / off operational travel along the direction of adjustment S between pressure-off and pressure-on position is z.
  • a pressure point 05 defining so-called. "0-position" is determined.
  • an adjustable stop 79 is also provided on the bearing unit 14 (252) of the first forme cylinder 07.1, in a first variant this stop 79 can now be essentially free of force be brought into contact with the corresponding abutment surface of the bearing block 74 on the first forme cylinder 07.1.
  • the stop 79 of the other transfer cylinder 06 is, for example by means of a set as a screw adjustment means 84, adjustable and lockable. He must therefore, for example, have no holding means.
  • one of the two transfer cylinders 06 although adjustable in its position, but not in the sense of an on / Abstellterrorism operatively movable but mounted frame-fixed.
  • the three other cylinders 06; 07 are in the Moving stored in the sense of on / off, wherein in a first variant, all these three cylinders 06; 07 and in the second variant, only the different from the specified transfer cylinder 06 transfer cylinder 06 has a movable stop 79 and possibly the holding means.
  • this direction of movement is selected perpendicular to the direction of adjustment S and causes unilateral actuation an inclination (so-called "cooking") of the relevant cylinder 06; 07th
  • the actuator 82 provided in the above embodiment of the bearing units 14 (252) is designed to provide an actuating travel ⁇ S suitable for engagement or deactivation, and therefore preferably has a stroke corresponding at least to ⁇ S.
  • the actuator 82 is for adjusting the Anstelltikes against each other employees rollers or cylinder 06; 07 and / or provided for carrying out the Druckan - / - off and trained accordingly.
  • the travel ⁇ S (or stroke) is for example at least 1.5 mm, in particular at least 2 mm.
  • the piston 82 is sealed against the pressure medium chamber by a peripheral to the circumference of the piston 82, near the pressure chamber near seal and guided a pressure chamber close sliding guide.
  • a second seal and a second sliding guide may additionally be provided in a region of the piston 82 remote from the pressure chamber.
  • the piston 82 instead of or in addition to the second seal, the piston 82 in addition to the outside by a membrane, for. B. rubber, especially a rolling diaphragm sealed. This is on the one hand completely with the piston 82 and on the other hand on its outer circumferential line completely with the Base body or other fixed installations of the actuator connected.
  • the printing unit 01 are both parts of the printing unit 01, in particular wall sections 11; 12 for the purpose of equipping or servicing the printing unit 01 relative to each other, in particular in a linear guide 15, and cylinder 06; 07 for adjusting the setting pressure and / or for performing the pressure on / off in linear bearings 70 within the corresponding wall section 11; 12 arranged linearly movable.
  • the concept of the single drive modules for separate printing cylinder, inking and dampening drive allows both the divisibility of printing unit 01 at the Pressure point 05 as well as the divisibility between forme cylinder 07 and inking unit 08.
  • the separate drives for printing cylinder 06; 07, inking unit 08 and possibly dampening unit 09 also allows simultaneous setup operation such as printing plate change and / or blanket washing while a Farbwerk redesign and / or pre-inking takes place.
  • the sequence programs can be different from one another in terms of duration, speed and functional sequence.
  • Exemplary are on the left side of the Fig. 20 the conditions for the dry offset, shown on the right side for the wet offset.
  • the two printing units 04 of a real double printing unit 03 are usually of the same type.
  • the drive concept is the example of an inking unit 08 with two rotationally driven friction cylinders 33; 33 '(see inking unit 08 above) and - in the case of wet offset - in contrast to the above figures) - an example of a dampening unit 09 with two rotationally driven friction cylinders 33; 33 '.
  • the drive of the printing cylinder 06; 07 takes place at least in pairs, ie it is per pair of cylinders 06, 07 from the form and associated transfer cylinder 07; 06 at least one of further printing unit cylinders mechanically independent own drive motor 121 is provided.
  • This can be z. B. as in Fig. 20 represented in each case be a separate, mechanically independent drive motor 121, or as not shown, done by pairwise drive via drive connections or trains.
  • the drive motors 121 with the two printing cylinders 06; 07 in each case via at least one torsionally rigid coupling 148, in particular at least one angle-compensating coupling 148 coupled.
  • two such couplings 148 are provided in series with an intermediate piece (or a total of a double-jointed component) which then represents a total of a displacement compensating clutch 151. This is despite mobility (on / off) of the cylinder 06; 07 a frame-fixed arrangement of the drive motors 121 possible.
  • the clutch 148 is designed in each case as a multi-disc clutch 148 or all-metal clutch and has at least one form-locking, but offset in the circumferential direction of the blades offset with two flanges disc set.
  • the coupling 151 between the functional module 122 and the forme cylinder 07 is preferably designed to enable side register control in such a way that it also receives an axial relative movement between the forme cylinder 07 and the functional module 122. This can also be done by o.g. Multi-plate clutch 148 take place, which allows an axial length change by deformation in the region of the slats.
  • An unillustrated axial drive can be provided on the same or the other frame side as the rotary drive.
  • the driven rollers 33; 33 ', in particular distribution cylinder 33; 33 'of the inking unit 09 are preferably coupled via at least one coupling 149, in particular angle deviations compensating coupling 149, with the function module 138. Since i.d.R. no turning off / on of these rollers 33; 33 ', it may be left in such a clutch 149.
  • the coupling 149 is also designed only as a rigid flange connection. The same applies to the drive on possibly as a function module 139.
  • Fig. 20 are the two distribution cylinder 33; 33 'by way of example both rotationally positively driven, here by the drive motor 128, formed.
  • Fig. 20 are the printing cylinder 06; 07 in an advantageous embodiment in each case individually a drive motor 121 driven.
  • a transmission 150 in particular a reduction gear 150, such. B. a planetary gear provided.
  • This can be structurally already pre-assembled as an auxiliary unit with the motor 121 as a structural unit as an auxiliary transmission.
  • it can also be provided as a drive or functional module, a module-like transmission, at the input of the drive motor 121 and at the output of the respective cylinder 06; 07 - in particular via an angle and / or offset compensating coupling 148 or 151 - can be coupled.
  • a drive motor 121 with gear 150 can be advantageously designed as a permanent magnet synchronous motor 121.
  • the drive motor 121 to be coupled to drive the cylinder 06; 07 as a synchronous motor 121 and / or permanent magnet excited electric motor 121, in particular as a permanent magnet synchronous motor 121, is formed.
  • This drive motor 121 is a directly driven round motor and has a stator with three-phase winding and a rotor with permanent magnets.
  • This design of the drive motor 121, in particular the permanent magnets a high power density is achieved and therefore makes the use of gear ratios unnecessary. This eliminates imprecision in the drive train and wear of mechanical elements such as gearbox.
  • the coupling between the rotational body, z. B. cylinder 06; 07, and drive motor 121 directly - ie without an axial relative movement enabling clutch and / or without an angle and / or offset compensating coupling - to the shaft 78.
  • This coupling can be rigid, but detachable.
  • the drive motor 121 z. B. not fixed to the frame, but arranged cylinder-tight and is when you turn on / off - and possibly in veryregisterverschiebung - with the cylinder 06; 07 moved.
  • Fig. 20 is the drive of the rotating component, in particular of the cylinder 06 mounted on the bearing unit 14; 07 formed with a synchronous motor 121 and / or permanent-magnet motor drive motor 121, ie formed with a portion of permanent magnets on the rotor.
  • rollers 28; 33; 34; 33 'of the inking unit 08 are in Fig. 21 for the sake of illustration to the Fig. 5 to 10 shown "pulled apart".
  • the stator is in this case, for example, directly or indirectly on the movable part of the storage unit 14, z. B. rigidly attached to the movable bearing block 74 and movable together with this.
  • the stator is mounted for example on the inner eccentric bush or the lever.
  • Fig. 21 and 22 show - z. B. regarding Farbtransport and wear advantageous - embodiments of the inking unit 08 and the inking unit drive, which in itself, but especially in conjunction with one or more features of the above printing units 01 advantages.
  • the inking 08, z. B. referred to as hereinskyges roller inking unit 08 or as a "long inking unit”, has a plurality of the above-mentioned rollers 28; 33; 33 '34;36; 37 on. It includes as in Fig. 5 to 10 an application roller 28, which applies the ink to the printing forme of the forme cylinder 07 and which transfers the ink via a forme or oscillating cylinder 33 (eg hard surface), at least one inking or transfer roller 34 (For example, with a soft surface), a second, irrelevant to the cylindrical shape rollable Reibwalze 33 'or Friction cylinder 33 ', another color or transfer roller 34 (eg., With a soft surface), an in Fig.
  • an application roller 28 which applies the ink to the printing forme of the forme cylinder 07 and which transfers the ink via a forme or oscillating cylinder 33 (eg hard surface), at least one inking or transfer roller 34 (For example, with a soft surface), a second, irrelevant to the cylindrical
  • Dipping and film roller 36; 37 (characterizing a film inking unit) can advantageously also be replaced by another ink feed or metering system (eg pumping system in the pumping inking unit, or lifting system in the lifting inking unit).
  • another ink feed or metering system eg pumping system in the pumping inking unit, or lifting system in the lifting inking unit.
  • the soft surfaces of the application and / or transfer rollers 28; 34 are yielding in the radial direction, z. B. with a rubber layer, formed in what Fig. 5 to 10 is expressed by the reinforced circular lines.
  • one of a plurality of co-acting rollers has a positive rotary drive by specifying a rotational speed (eg via a drive motor or a corresponding mechanical drive connection to another driven component)
  • a rotational speed eg via a drive motor or a corresponding mechanical drive connection to another driven component
  • an adjacent one only rotates by friction from the first-mentioned roller driven soft roller depending on Eindschreibiefe with different speed.
  • this soft roller but in addition by its own drive motor or additionally via friction in a second Nipp location would be driven by another speed-specific roller ago, this can be caused in the first case to a difference between motorized speed and by friction Speed, and in the second case to come to a difference between the two speeds caused by friction. It comes at the Nipp-places slippage and / or the drive motors or are unnecessarily heavily loaded.
  • inking unit 08 in particular for the execution of the drive to Fig. 21 in the field of ink application by the rollers 28; on the printing plate 22, is characterized by the following for Fig. 22 and 21 "true rolling" and coloring achieved:
  • the form cylinder near the distribution cylinder 33 is in Fig. 22 rotational only via friction with adjacent rollers 28; 34 driven and has its rotary drive neither an additional mechanical drive connection for driving the printing cylinder 06; 07 or another rotary forcibly driven inking roller nor its own drive motor.
  • the first distribution cylinder 33 is rotationally driven mainly via the two in this example (possibly one or three) driven by friction with the forme cylinder 07 applicator rollers 34 and has independent of the indentations in the intermediate Nipp points substantially the peripheral speed of the forme cylinder 07.
  • the form cylinder remote distribution cylinder 33 ' has, as in Fig.
  • a rotationally driving drive motor 128 to which, however, in addition to the through the rollers 33 ';34; 33 formed friction gear has no mechanical coupling to the first distribution cylinder 33.
  • the two form cylinder distant rotationally forcibly driven or it may only be the middle or the form cylinder remote friction cylinder rotationally driven forcibly.
  • the cylinder near cylinder near friction cylinder 33 has its own, only its rotational movement in a traversing motion transforming trawling 136.
  • This can be beneficial as a Be formed cam mechanism, wherein z. B. a frame-fixed axial stop cooperates with a roller-fixed curved circumferential groove or a roller-fixed axial stop in a frame-fixed circumferential groove of a cam.
  • this rotation in a iridescent Axialhub transforming gear 136 another suitable gear 136, z. B. by an eccentric exhibiting worm or crank gear, be executed.
  • the traversing gear 136 of the first friction cylinder 33 is mechanically coupled via a gear with the traversing gear 136 of the second Reibzylinders 33 'in an advantageous manner.
  • the two coupled traversing gears 136 represent a common traversing drive 162 (traversing gear 162) and are forcibly driven for their traversing movement by a drive motor.
  • the forced drive of the traversing gear 162 is effected by the drive motor 128 which rotatably drives the second distribution cylinder 33 '(FIG. Fig. 21 ).
  • Fig. 21 is an advantageous embodiment for the drive of the distribution cylinder 33; 33 ', wherein only the second distribution cylinder 33' is forcibly driven in rotation, however, both distribution cylinders 33 ', 33' are axially positively driven via the common traversing drive 162.
  • the printing cylinder 06; 07 can either in pairs by drive motors 121 per cylinder pair, or advantageously individually by a respective drive motor 121 as in Fig. 20 or 22 set out to be executed.
  • Fig. 22 is exemplified the reverse situation, with only the positive cylinder close to the friction cylinder 33 is forcibly driven in rotation.
  • the recognizable the Fig. 21 corresponding parts are for Fig. 22 not explicitly described or designated again.
  • the connection can z. B. via a spur gear 167 supporting shaft portion 168 on a pin 169 of the second ( Fig. 21 ) or first ( Fig. 22 ) Friction cylinder 33 '; 33 done.
  • a corresponding axis section 168 of the first ( Fig. 21 ) or second ( Fig. 22 ) Friction cylinder 33; 33 ' has no such spur gear 167 or no drive connection to the drive motor 128.
  • the drive connection between drive pinion 166 and spur gear 167 of the second and first Reibzylinders 33 '; 33 are preferably straight toothed and formed with a sufficient for each position of the traversing movement coverage in the teeth engagement.
  • the two distribution cylinders 33; 33 ' are, as in Fig. 21 exemplified in a formed on the side frame 147 or frame frame 147 in bearings 172, z. B. radial bearings 172 or in the side frame 11; 12 ( Fig. 22 ), which additionally allow an axial movement.
  • the assembly is the output side of the pin 169 coupled.
  • the traversing drive 162 is also by the drive motor 128, z. B. via a worm drive 173, 174, driven.
  • a worm drive 173, 174 driven.
  • a driver 177 is arranged eccentrically to the axis of rotation, which in turn z. B.
  • a crank mechanism for example via a rotatably mounted on the driver 177 lever 178 and a hinge 179, in the axial direction of the distribution cylinder 33; 33 'pressure and zugsteif with the pin 169 of the distribution cylinder 33; 33 'is connected.
  • Fig. 20 is the friction gear 136 of form cylinder distant Grub cylinder 33 'only indicated by dashed lines, since it is hidden in this view by the spur gear 167.
  • a rotation of the shaft 176 causes a rotation of the driver 177, which in turn via the crank mechanism an axial stroke of the distribution cylinder 33;
  • the output on the traversing drive 162 can also take place elsewhere on the rotary drive train between the drive motor 128 and the distribution cylinder 33 'or even on the other side of the machine on the other end face of the distribution cylinder 33' located pin 169 to a corresponding traversing gear 162.
  • the traversing drive 162 and the traversing gear 162 is formed as a whole unit with its own housing 181, which can be designed additionally encapsulated.
  • the one the one distribution cylinder 33; 33 'rotatably driving drive motor 128 as a respect to his performance and / or its torque and / or in terms of its speed controllable or controllable electric motor be executed.
  • the drive motor 128 is also operated in speed-controlled manner in pressure-on, then in the region of the inking unit 08 remote from the printing cylinder, problems with regard to different effective roll circumferences still occur.
  • the drive motor 128 is advantageously designed such that it at least during the printing operation with respect. Its power and / or its torque is controlled or regulated. This can basically be done by means of a drive motor 128 designed as a synchronous motor 128 or as an asynchronous motor 128:
  • the drive motor 128 is embodied as an asynchronous motor 128, which has only one frequency (eg in pressure-down of the inking unit 08) and / or one electric drive power or one torque (in FIG Pressure on the inking unit 08) is specified.
  • the applicator rollers 28 are out of rolling contact with the forme cylinder 07, can be brought over the predetermined frequency and / or drive power the inking unit 08 via the second distribution cylinder 33 'to a suitable for the pressure-On-sites peripheral speed at which the peripheral speeds of forme cylinder 07 and applicator rollers 28 only by less than 10%, in particular less than 5%, from each other.
  • a frequency or power specification suitable for this purpose can be empirically and / or computationally determined beforehand and kept either in the drive control itself, a machine control or a control computer.
  • the default value is preferably changeable by the operator, wherein the default value is preferably changeable by the operating personnel (advantageously also applies to the default values mentioned below).
  • the applicator rollers 28 are employed in rolling contact with the forme cylinder 07 and all inking rollers to each other, the rollers 28; 33; 34; 33 ';34; 37 to a part of the forme cylinder 07 via the now produced friction gear between the rollers 28; 33; 34; 33 ';34; 37 rotationally driven. so that the drive motor 128 only in the friction gears with increasing distance from the forme cylinder 07 increasing power loss must bring. That is, the drive motor 128 can be operated with a small drive torque or a small drive power, which only contributes to keep the rear portion of the inking unit 08 at the substantially predetermined by the frictional contact peripheral speed.
  • This drive power can be left constant in a first variant for all production speeds (or rotational speeds of the forme cylinder 07) and either correspond to that specification for starting in pressure-Ab or represent its own constant value for the production.
  • different specifications with regard to the frequency and / or drive power can be predetermined and stored for different production speeds (and possibly also for starting in pressure-off).
  • the specification for the drive motor 128 can then vary.
  • roller locks 257 for setting a force exerted by a roller in a roll strip on an adjacent body rotation pressing force and / or for hiring the roller to the rotating body and / or stopping the roller of this body rotation and the respective control or regulation of these devices received.
  • the applicator roll 28, as in Fig. 9 . 10 and 13 also represented as representative of the other versions of the inking unit 08, has such a roller lock 257 for on / off position.
  • all adjustable rollers 28, 34 of the inking unit 08 and possibly the adjustable rollers 41; 43 of the dampening unit 09 (if present) such an automatic roller lock 257 on.
  • rollers 28, 34, 41, 43 mounted in this way are in each case designed as rollers 28, 34, 41, 43 controllable in their contact pressure.
  • each of these controllable rollers 28; 34; 41 of the inking unit 08 or dampening unit 09 to two adjacent bodies of revolution in a touch contact d. H.
  • each of these rollers 28; 34; 41 is simultaneously employed on two of the rotational bodies provided in this arrangement, so that each of these rollers 28; 34; 41 each on its lateral surface two nip points also called, has substantially axially to the respective roller extending roll strip.
  • Each controllable in its contact force roller presses in their respective roll strip with an adjustable contact force against their adjacent bodies of revolution.
  • this controllable roller z. B. associated with only a single adjacent body of revolution.
  • the width is in the range of a few millimeters and z. B. between 1 mm and 10 mm.
  • actuators 322 are described below as actuators 322 which can be pressurized with a pressure medium, which corresponds to their preferred embodiment, the control of the support bearings 257 and / or their actuators 322 described below is independent of the medium used for the application of the contact pressure becomes.
  • the actuators 322 z. B. also be formed as actuators 322, the respective contact force z. B. exercise due to a hydraulic, electrical, motor or piezoelectric effect.
  • actuated actuators 322 cause the roller retainer 339 with respect to the support bearing 257 in an orthogonal to the axial direction of the controllable roller 28; 34, 41; 43 stationary level is moved eccentrically.
  • the radial stroke can be done on a linear or nonlinear trajectory.
  • the z. B. frame fixedly arranged support bearing 257 permissible radial stroke of the roller mount 339 thus leads to an eccentric adjustment of the roller mount 339 in the preferably designed as a radial bearing support bearing 257th
  • a roller lock 257 exemplified in its structural design.
  • the Fig. 23 shows the roller lock 257 in a parallel to the axis 319 of the roller longitudinal section.
  • the Fig. 24 shows the roller lock 257 of Fig. 23 in a perspective view with a partial longitudinal section in two mutually orthogonal planes. It can be provided that at least all with a forme cylinder 07 directly cooperating rollers 28; 41 each have at least one actuator 322, the independent of the other actuators 322 of the forme cylinder 07 directly interacting rollers 28; 41 is controlled.
  • the housing of the roller lock 257 has a z. B. sleeve-shaped frame holder 323, in the interior of a roller holder 324 is mounted, the actuators 322 act on the roller holder 324 in their operation and the roller holder 324 in a radially formed about the axis 319 gap between the frame holder 323 and Roll holder 324 can move radially.
  • the gap between the frame holder 323 and the roll holder 324 has z. B. a width of 1 mm to 10 mm, preferably of about 2 mm.
  • the actuators 322 are z. B.
  • actuator 322 has a directed onto the roller holder 324 effective surface 338, with which the actuator 322 exerts a surface pressure on the roller holder 324 in its operating state acted upon by a pressure medium.
  • the actuators 322 are preferably arranged rotationally fixed in the housing of the roller lock 257 relative to this housing or at least relative to the frame holder 323.
  • the actuators 322 are z. B. each as a pressurizable with a pressure medium hollow body, for. B. as a pressure hose, formed, wherein the hollow body at least one surface 338 ( Fig. 24 ) comprises a reversibly deformable elastomeric material, said surface 338 z. B. is formed in a further embodiment, not shown, as a membrane, wherein the membrane 338 preferably comes on the pressure medium loading of the hollow body on an outer circumferential surface of the roll holder 324 for support.
  • the reversibly deformable surface 338 therefore at least largely corresponds to the surface 338 which is effective for applying the surface pressure.
  • the actuators 322 have no piston guided in a cylinder, but instead are rodless.
  • the integration of the actuators 322 in the housing of the roller lock 257 leads to an extremely compact design of the roller lock 257.
  • the pressure medium is supplied to the actuators 322 via a pressure medium line 341 ( Fig. 24 ).
  • One of the ends 318 of the roller 28, which can be controlled in its contact force; 34; 41; 43 is in the formed on the roll holder 324 z.
  • the roller mount 339 has a bearing, z. As a rolling bearing or sliding bearing in which the end of the roller is rotatably mounted.
  • the frame holder 323 is z. B. attached to a frame wall 336 of the printing unit 301.
  • the roller lock 257 is sealed at its controllable in its contact force roller face preferably with a particular gap between the frame holder 323 and the roller holder 324 covering the sealing element 337 sealed against dust, moisture and other contaminants, wherein the sealing element 337 z. B. is screwed to the frame holder 323.
  • the sealing element 337 and in particular the actuators 322 are protected from contamination and thus from a disturbance in their mobility.
  • a roll can also be set against its adjacent rotation body or be turned off from it.
  • the roller lock 257 has z. B. a fixing device, the roller holder 324 and thus the rigidly connected to him roller 28; 34; 41; 43 fixed in a first operating position and thus locks against any radial displacement relative to the frame holder 323 or releases in a second operating position for such a shift.
  • the fixing device has z. B. a preferably coaxial, rigid z. B. connected to the roller holder 324 first plate set 326 and also preferably coaxial second plate pack 327, wherein the second plate set 327 engages with its fins between the slats of the first plate set 326.
  • the fixation takes place when meshing the slats preferably frictionally or positively. After loosening the zip or positive locking of the slats, the second disk set 327 in the axial direction of the roller lock 257 is movable.
  • the axial movement of the second disk set 327 comes z. B. by the fact that a pressure medium by a formed in the frame wall 336 channel 328 in a arranged in the roller lock 257 pressure chamber 329 is guided, wherein a arranged in the pressure chamber 329 pressure plate 331 against the force of a spring element 332, a preferably arranged in the roll holder 324 punch 333 moves axially.
  • the second disk set 327 is attached to a punch head 334 of the punch 333 and is also moved in an axial movement of the punch 333, whereby the fins of the disk sets 326; 327 disengaged.
  • each roller lock 257 each four circular about the axis 319 of the roller 28; 34; 41; 43 arranged actuators 322, wherein the actuators 322 preferably at uniform intervals about the axis 319 of the controllable in its contact force roller 28; 34; 41; 43 are distributed.
  • the actuators 322 can be remotely controlled, ie actuated by a control unit, and preferably designed as pneumatic actuators 322.
  • pneumatic actuators 322 As a pressure medium z.
  • a prestressed gas preferably compressed air used.
  • An alternative to the preferred pneumatic actuators 322 are, in particular, hydraulic actuators 322 pressurized with a fluid or electromotively acting actuators 322. As in FIGS Fig.
  • each actuator 322 exerts during its pressure medium application a directed into the interior of its roller lock 257 radial force Fn1; Fn2; Fn3; Fn4 on the connected to the roller lock 257, controllable in its contact force roller 28; 34; 41; 43, wherein the actuators 322 are preferably radially supported on or in the frame holder 323 of the roller lock 257 and by the surface pressure on the frame holder 323 radially displaceably arranged roller holder 324, the radial force Fn1; Fn2; Fn3; Fn4 on the roll holder 324 mounted, controllable in its contact force roller 28; 34; 41; 43 exercise.
  • the controllable by a contact force roller 28; 34; 41; 43 applied in a roll strip on an adjacent body rotation pressing force is then obtained as a vector sum of the simultaneously exerted radial forces Fn1; Fn2; Fn3; Fn4 of actuators 322 of the same roller lock 257 - possibly taking into account one of the controllable roller 28; 34; 41; 43 due to their own mass on the adjacent body of revolution at least partially exerted weight.
  • n in the designation of the radial force Fn1; Fn2; Fn3; Fn4 is a particular roller lock 257 markable and therefore identifiable.
  • each installed in the printing press to a controllable roller 28; 34; 41; 43 associated roller lock 257 assigned in the controller as an address identifier with which the roller lock 257 in the printing press or at least in a printing unit 04 uniquely identifiable and thus selectable in the controller.
  • each actuator belonging to a roller lock 257 is assigned an identifier 322 with which each actuator 322 can be uniquely identified, selected and controlled in one of the roller locks 257 arranged in the printing press or in the respective printing unit 301.
  • each fixing device can be unambiguously identified by the roller locks 257 arranged in the printing press or in the printing unit 301.
  • the respective identifier of the roller locks 257, their actuators 322 and their fixing device is preferably machine-readable and can be stored in the control unit, preferably an electronic, digital data-processing control unit.
  • the actuators 322 are in each roller lock 257 in their preferred pneumatic execution in each case by a pressure medium line 341 with a pressure level having a pressure medium source, for. As a compressor connected.
  • the control unit is z. B. formed as part of a printing press or at least to a printing unit 04 belonging control room or control computer and thus associated with the printing press or the printing unit 04.
  • the actuator 82 or the actuators 82 of the respective bearing units 14 or bearing units 252 (FIG. Fig. 18 ; Fig. 7 ) arranged in a printing unit 04 a printing unit 01 (previous figures) cylinder 06; 07 or rollers 28; 34; 41; 43 preferably identifiable and addressable from the control station or from a central computer and z.
  • controllable with at least one valve 93 by the actuator 82 or the actuators 82 of the respective storage units 14 is also assigned in each case a unique identifier.
  • Fig. 27 schematically a profile for a surface pressure P in the pressure point of the forme cylinder 07 and the transfer cylinder 06 is shown.
  • the surface pressure P extends over an entire region of the contact zone, wherein it reaches a maximum surface pressure P max at standstill at the level of a connecting plane V of the axes of rotation. This shifts in production to the incoming gap side due to the viscous force component.
  • the contact zone and thus the profile has a width B.
  • the maximum surface pressure P max is ultimately responsible for the color transfer and adjust accordingly.
  • the characteristic curve represents the (maximum) surface pressure P as a function of the (maximum) indentation ⁇ Fig. 28
  • some characteristic curves of conventional elevators 23, in particular metal printing blankets 23 with a solid carrier plate 116 and an elastic layer, eg rubber layer 117 are shown.
  • the values are determined on a quasi static bench test bench in the laboratory. They are to be transmitted in a suitable manner to values determined in a different way.
  • a slope dP / d ⁇ of the characteristic determines the fluctuation in the surface pressure P when the indentation ⁇ changes.
  • the magnitude of a fluctuation ⁇ P of the required maximum surface pressure P max in the nip 114 about the average surface pressure is approximately proportional to the slope dP / d ⁇ of the characteristic curve at the position ⁇ . For example, in the case of a lift, a in Fig.
  • An elevator b has a lower pitch.
  • Lifts 23, which as a whole or their rubber layer 117 as such has a large pitch dP / d ⁇ , in particular in the range of the required maximum surface pressure P max in the pressure-relevant area, are referred to here as “hard” (curve a), those with a small pitch dP / d ⁇ is called “soft” (curve b).
  • the elevator 23 or the rubber layer 117 is here designed as a soft elevator b or as a soft layer.
  • a soft elevator a or a hard layer performs a same relative movement of the cylinder 06; 07 at a soft lift b to a smaller change in the surface pressure P and thus to a reduction of Fluctuations in the color transfer.
  • the soft elevator b thus causes a lower sensitivity of the printing process to vibrations and / or deviations at intervals from a desired value. Due to smaller changes in the surface pressure P as a result of relative movements of the cylinder 06; 07 are z.
  • B. vibration strip in the printed product at the same elevators 23 or 23 lifts with soft layer visible only at higher vibration amplitudes.
  • the surface pressure P varies in pressure-on position in an advantageous embodiment at most in a range between 60 and 220 N / cm 2 .
  • fluids e.g. As printing inks, with very different rheological properties, different areas within the above-mentioned area for the surface pressure may be preferred.
  • the range for the wet offset z. B. between 60 and 120 N / cm 2 , in particular from 80 to 100 N / cm 2 , while in the case of dry offset (no dampening solution, only paint on form cylinder) z. B. between 100 to 220 N / cm 2 , in particular 120 to 180 N / cm 2 is.
  • the pressure-relevant area for the surface pressure P max is advantageously between 60 and 220 N / cm 2 .
  • fluids e.g. As printing inks, with very different rheological properties, different areas within the above range for the surface pressure P may be preferred.
  • the range for the wet offset z. B. between 60 and 120 N / cm 2 , in particular from 80 to 120 N / cm 2 (in Fig. 28 shaded), while in the case of dry offset z. B. between 100 and 220 N / cm 2 , in particular from 120 to 180 N / cm 2 varies.
  • a soft elevator 23 at least in the range of 80 to 120 N / cm 2, a slope dP / d ⁇ of z.
  • a pressure-relevant area with 40 - 60 N / cm 2 is selected.
  • the blanket should now at least in this area of the surface pressure P of 40-60 N / cm 2 have a slope less than 350 (N / cm 2 ) / mm, in particular at most 300 (N / cm 2 ) / mm.
  • the characterization of the blanket 23 in this work area can be used alone or in addition to the above characterization in the areas mentioned, so that the blanket is characterized by several support points.
  • the layer 117 a greater strength t or the elevator 23 a greater total thickness T than hitherto customary.
  • the thickness t of the elasticity or compressibility functional layer 117 amounts, for example, to 1.3 to 6.3 mm, especially 1.7 to 5.0 mm, in particular more than 1.9 mm.
  • the strength of one or more u. U. associated with the layer 117 substantially incompressible and inelastic layers on the cylinder base body side facing, which are connected to the layer 117 for the purpose of dimensional and / or dimensional stability (not shown).
  • support layers eg, woven fabrics
  • the carrier layer 116 or support layers which are functionally not functional for the "softness" of the elevator but rather for the dimensional stability can also be arranged between the "soft" layers. It can, for example, be designed as a metal, in particular stainless steel sheet, about 0.1 to 0.3 mm thick. As a fabric, this may be from 0.1 to 0.6 mm, depending on the design of the elevator 23.
  • the specified thickness t of the layer 117 in the case of several layers of layers 117 refers to the sum of the "partial layers” functionally responsible for the above-described characteristic (dependence on surface pressure / indentation) and the elasticity or compressibility.
  • An elevator 23 then has, for example together with carrier layer (s), the total thickness T of 2.0 to 6.5 mm, in particular 2.3 to 5.9 mm.
  • the layer 117 Under the elastic layer 117 or its thickness t, the layer 117, or sum the layers 117 whose material has a modulus of elasticity in the radial direction of less than 50 N / mm 2 .
  • the layers possibly provided for support (fabric) or dimensional stability (support) have significantly greater modulus of elasticity, e.g. B. greater than 70, in particular greater than 100 N / mm 2 or even greater 300 N / mm 2 .
  • At least one sub-layer of the layer 117, referred to here as an elastic layer, is made of porous material in an advantageous embodiment.
  • the elastic layer 117 may include a Fig. 27 not shown cover layer whose modulus of elasticity is less than 50 N / mm 2 in the radial direction.
  • a cover layer serves to form a closed surface and in this case contributes to the formation of "softness".
  • the "soft" elevator is preferably operated with a higher indentation ⁇ compared to conventional indentations ⁇ , ie the transfer cylinder 06 and the forme cylinder 07 are related to their respective effective but undisturbed diameter further hired together.
  • an optimal maximum surface pressure P max is achieved despite a smaller pitch dP / d ⁇ .
  • the design and / or arrangement of the "soft" elevator particularly advantageous if one of the two cooperating cylinders 06; 07 (or both) have at least one interruption influencing disorder.
  • the disturbance may be caused by an axially extending channel 21 for attachment of ends of one or more elevators 23.
  • the channel 21 has the outer surface of the cylinder 06, 07 through an opening with a width s07 or s07, in which the ends of the elevators 23 are guided.
  • the channel 21, 19 may have a device for clamping and / or tensioning the elevator 23 or the elevators 23.
  • the width s06, s07 of the channel 21, 19 is particularly advantageous to select the width s06, s07 of the channel 21, 19 to be smaller than the width B of the contact zone.
  • the width s06, s07 of the channel 21, 19 is particularly advantageous to select the width s06, s07 of the channel 21, 19 to be smaller than the width B of the contact zone.
  • at least always based areas of the cooperating lateral surfaces in the contact zone from each other there is also an attenuation in height and a flatter course (dissemination of the momentum) for the force of the impact excitation.
  • Smoother lifts 23 or softer rubber layers 117 thus lead to a weakening and a lateral extension of the channel strike in the case of narrow openings s06, s07.
  • the adjustment is preferably carried out such that the contact zone resulting from the deformation in a projection perpendicular to a connecting plane V of the axes of rotation of the two cylinders is at least three times as wide as the slot width of the opening on the co-operating form cylinder 07 in the circumferential direction.
  • ends of a metal blanket 23 may be arranged in the channel 19.
  • the rubber layer 117 is applied in this case on the dimensionally stable carrier layer 116, whose bent ends are arranged in the channel 21.
  • the opening s06 of the channel 21 can then extremely narrow in the circumferential direction, z. B. s06 ⁇ 5 mm, in particular ⁇ 3 mm, be executed.
  • the extremely soft and thick rubber blanket 23 allows a significant reduction of the operational surface pressure of 80 to 100 N / cm 2 in the forme cylinder transfer cylinder Nip in the range of 40-60 N / cm 2 (or even 25 to 60 N / cm 2 ), wherein the layer 117 then has a pitch of less than 350 (N / cm 2 ) / mm, in particular at most 300 (N / cm 2 ) / mm. Due to the softness of the elevator 23, the surface wavinesses customary in transfer cylinders 06 do not lead to problems here in the uniformity of the color transfer.
  • Fig. 1 an embodiment of a printing press is shown, wherein a plurality of printing towers are each provided of two printing units 01 arranged one above the other.
  • the funnel assembly 241 is not located between the printing towers related to these funnels 241 with regard to the webs, but at one end of an alignment of the printing towers related to this funnel assembly 241.
  • the webs can be fed to the funnel structure from a same side.
  • the hopper assembly 241 preferably has at least one group of three stacking hoppers arranged side by side. In Fig. 1 are two such groups arranged vertically one above the other.
  • a mixing device 240 which precedes the funnel structure 241, ie a group of web guide rollers arranged above one another via which the webs to be joined at the formers, is not arranged above the funnel structure 241 but spatially next to the funnel structure 241.
  • the mixing device 240 may be located at a smaller machine height, rather than above the hopper assembly 241 as would otherwise be the case.
  • the hopper assembly 241 preferably has at least two hopper levels, each with three side-by-side formers.
EP07712406A 2006-03-03 2007-03-01 Druckwerke einer druckmaschine Not-in-force EP1991419B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07712406A EP1991419B1 (de) 2006-03-03 2007-03-01 Druckwerke einer druckmaschine
EP08163740A EP2014469A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine

Applications Claiming Priority (4)

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EP06110614 2006-03-03
DE102006030290A DE102006030290B3 (de) 2006-03-03 2006-06-30 Druckwerk
PCT/EP2007/051955 WO2007099148A2 (de) 2006-03-03 2007-03-01 Druckwerke einer druckmaschine
EP07712406A EP1991419B1 (de) 2006-03-03 2007-03-01 Druckwerke einer druckmaschine

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EP08163740A Division EP2014469A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine

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EP1991419A2 EP1991419A2 (de) 2008-11-19
EP1991419B1 true EP1991419B1 (de) 2009-07-15

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EP07712405A Not-in-force EP1991421B1 (de) 2006-03-03 2007-03-01 Druckwerke einer druckmaschine
EP07712406A Not-in-force EP1991419B1 (de) 2006-03-03 2007-03-01 Druckwerke einer druckmaschine
EP08163740A Withdrawn EP2014469A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine
EP08165187A Withdrawn EP2006098A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine

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EP08163740A Withdrawn EP2014469A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine
EP08165187A Withdrawn EP2006098A2 (de) 2006-03-03 2007-03-01 Druckwerk einer Druckmaschine

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US (2) US8069785B2 (ja)
EP (4) EP1991421B1 (ja)
JP (1) JP2009528197A (ja)
CN (2) CN101505962B (ja)
BR (1) BRPI0708538A2 (ja)
DE (3) DE102006030290B3 (ja)
RU (2) RU2377130C9 (ja)
WO (1) WO2007099147A2 (ja)

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US20090145315A1 (en) 2009-06-11
US20090078138A1 (en) 2009-03-26
WO2007099147A2 (de) 2007-09-07
DE502007001078D1 (de) 2009-08-27
BRPI0708538A2 (pt) 2011-05-31
RU2008138404A (ru) 2010-04-10
WO2007099147A3 (de) 2008-02-07
EP1991421A2 (de) 2008-11-19
US8069785B2 (en) 2011-12-06
EP1991419A2 (de) 2008-11-19
CN101448645A (zh) 2009-06-03
CN101505962B (zh) 2011-06-01
DE502007001079D1 (de) 2009-08-27
EP2014469A2 (de) 2009-01-14
RU2377130C9 (ru) 2011-03-20
EP2006098A2 (de) 2008-12-24
CN101505962A (zh) 2009-08-12
RU2377130C1 (ru) 2009-12-27
RU2420409C2 (ru) 2011-06-10
JP2009528197A (ja) 2009-08-06
EP1991421B1 (de) 2009-07-15
DE102006030290B3 (de) 2007-10-18

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