EP2906427B1 - Mécanismes d'encrage d'un groupe d'impression, groupe d'impression et procédé permettant de faire fonctionner un groupe d'impression - Google Patents

Mécanismes d'encrage d'un groupe d'impression, groupe d'impression et procédé permettant de faire fonctionner un groupe d'impression Download PDF

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Publication number
EP2906427B1
EP2906427B1 EP13766058.5A EP13766058A EP2906427B1 EP 2906427 B1 EP2906427 B1 EP 2906427B1 EP 13766058 A EP13766058 A EP 13766058A EP 2906427 B1 EP2906427 B1 EP 2906427B1
Authority
EP
European Patent Office
Prior art keywords
roller
inking unit
drive
inking
pressure
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
EP13766058.5A
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German (de)
English (en)
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EP2906427A1 (fr
Inventor
Sebastian Franz
Patrick KRESS
Volkmar Schwitzky
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
Priority claimed from DE201210218417 external-priority patent/DE102012218417A1/de
Priority claimed from DE102012218423.6A external-priority patent/DE102012218423B4/de
Application filed by Koenig and Bauer AG filed Critical Koenig and Bauer AG
Publication of EP2906427A1 publication Critical patent/EP2906427A1/fr
Application granted granted Critical
Publication of EP2906427B1 publication Critical patent/EP2906427B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • 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
    • B41F31/02—Ducts, containers, supply or metering devices
    • B41F31/14—Applications of messenger or other moving transfer rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/0008—Driving devices
    • 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

Definitions

  • the invention relates to inking units of a printing unit, to a printing unit and to a method for operating a printing unit according to the preamble of claims 1, 12 and 13, respectively.
  • the DE 39 35 215 A1 discloses a Schwenkantneb for a lifting roller, wherein an electric motor, which is associated with a speed control, drives a lifting cam gear.
  • EP 1 996 403 B1 is a combined printing unit for the simultaneous two-sided multi-color printing disclosed, wherein the inking units for iris printing are each equipped with two color sources.
  • the DE 195 11 488 A1 relates to a fluid operated oscillating piston engine, wherein the output shaft with an object to be pivoted, z. B. a robot arm to connect. The pivoting takes place between two end positions whose stops for damping z. B. are formed as a shock absorber holder
  • the DE 1 761 394 B discloses a lift inking unit with a squeegee roller drive and a reversing device, which by means of two adjustable timer devices is switchable in order to set the respective investment period and frequency of the Hebertaktung can.
  • the drive mechanism is designed as a double-acting hydraulic cylinder, which is fed via the reversing device from a pressure oil pump.
  • DE 198 28 142 A1 show further examples of the execution of a lift drive with a pressure medium applied drive means for the pivoting movement.
  • the EP-A-1916110 discloses a device according to the preamble of claim 1.
  • the Efindung has the object of providing an inking unit of a printing unit, a printing unit and a method for operating a printing unit with improved color metering.
  • the achievable with the present invention consist in particular that a quality improvement in color dosing is achieved.
  • This is achieved first by a force-based adjustment and by a variability or variation in the force caused by the drive and optionally additional by a variability or variation in timing.
  • a nominal value specification of a drive means causing the pivoting movement is remotely operated and / or variable.
  • the output-side drive force of the drive causing the pivoting movement is remotely actuated and / or modified.
  • a control device acts via a control command on an operator interface and / or by a control program on an actuating means.
  • pivoting drive is for this purpose as a drive means operated by admission with a pressurized fluid linear or rotary drive provided, wherein the pressure level is varied to vary the contact force. This is done by acting on z. B. a remotely stallable valve.
  • the drive means may be embodied as an electric drive which can be operated torque-controlled and / or operated in at least one operating mode with an electric motor, wherein a desired torque input can be preset and / or changed remotely as actuating means designed as a drive controller of the electric drive.
  • Both versions cause the possibility of a variation in the contact force of the pivotable roller.
  • the contact force to the nude cylinder and / or the ductor and thus the color strip width can be adjusted by adjusting or varying the pressure level.
  • This is of particular advantage when different color strip widths are to be set and / or in particular when the effective length of the plant varies by use of cut squeegee rolls, as is the case, for example, in securities printing applications, e.g. B. in iris printing, may occur.
  • the Hebertaktung is hereby mechanically decoupled from the machine speed, even if it can be designed to variably correlated to her.
  • the Hebertaktung is - z. B. within certain limits - freely selectable or changeable. This has particular advantages in the event that little color is to be transferred, as for example in security printing applications, eg. B. when printing numbers or seals with fine lines, may occur.
  • the pressure-medium-based drive solution is a commercially available, preferably double-acting piston-piston chamber system, in particular cylinder-piston system, for use.
  • a commercially available piston-piston chamber system in particular cylinder-piston system, for use.
  • cylinder-piston system for use.
  • Lever lengths can over the Lever lengths also adaptation to be made in the engine room, for example, already available pressure levels.
  • the drive is given by a rotary piston engine. This attacks, for example, with its output member directly in the pivot axis of the lifter roller bearing pivot lever.
  • the electromotive drive solution may be beneficial and be involved in the networked drive system with regard to the transmission of the torque input.
  • a printing unit 01 comprises at least a first imaging printing cylinder 02 (12), z. B. first forme cylinder 02 (12), and one with the forme cylinder 02 (12) to its coloring together acting inking unit 03 (13).
  • the forme cylinder 02 (12) bears on its circumference, for example on a printing form to be fastened on the circumference, a print image original.
  • the printing unit 01 comprises at least a first ink transfer printing cylinder 04 (14) designed as a transfer cylinder 04, which on the one hand has at least one first forme cylinder 02 (12) and on the other hand for printing material 06 with a first transfer cylinder 04 (14) serving as an abutment impression cylinder 14 as a printing cylinder 14 cooperates.
  • the forme cylinder 02 may be associated with a dampening unit 08 for the case of a wet offset pressure described here.
  • a dampening unit 08 for the case of a wet offset pressure described here.
  • a dry offset pressure this can be omitted or at least not operated.
  • the printing unit 01 as a double printing unit 01 for a simultaneous two-sided printing of the impression cylinder 14 is formed as a second transfer cylinder 14, which in turn cooperates with at least one inking unit 13 by a second form cylinder 12 together.
  • a plurality of inking units 03, a forming cylinder and a transfer cylinder 02; 04 comprehensive printing units 01 or for the simultaneous two-sided printing corresponding double printing units 01 be provided in the printing material behind the other.
  • a printing unit 01 designed in this way is preferably designed for double-sided printing on both sides for the security printing.
  • the printing material 06 may be web-shaped or preferably formed as a single sheet.
  • the two collective printing units 09 acting together are also called "Perfecting printing unit” or “Perfecting inking unit” (eg in Fig. 1 left collective printing unit 09) and "perfecting printing unit” or "reverse printing inking unit”.
  • the printed substrate 06, z. B. the printing material 06 leaves the printing area 07 after printing and is transported for example via a correspondingly designed conveyor 11, preferably a gripper system 11 with one or more gripper cylinders or possibly a belt system 11 from the printing unit 01.
  • the inking unit 03, 13 is discontinuous color inking inks 03; 13 formed, as it is particularly advantageous for printing units 01, in which a Reliable dosing and printing should be guaranteed even with the smallest amounts of ink. This comes z.
  • It comprises at the upstream end at least one color source 16 (26), e.g. As an ink fountain 16 (26) or a chamber doctor blade 16 (26), from which printing ink on a (possibly temperature-controlled) first inking roller 17 (27), z. B. a ductor roller 17 (27) or ink fountain roller 17 (27), can be applied.
  • the ductor roller 17 (27) is rotatably positively driven, preferably z. B.
  • Nacktwalze 19 has a hard surface, z. B: with a hardness of at least 60 Shore A, on.
  • Nacktwalze 19 closes downstream in the direction of forme cylinder 02; 12 a exciger or possibly at least partially in several parallel cables dividing compactor 21 with other rollers, which, for example, at least one changeable formed inking roller 22, z. B. Reibwalze 22, and at the formzylindernahen end more with the forme cylinder 02; 12 cooperating inking rollers 23, z. B. applicator rolls includes.
  • a soft-surface inking roller 24 eg, at most 50 Shore A, preferably at most 45 Shore A
  • B. ink transfer roller 24 may be provided.
  • this is with two color sources 16; 26 for parallel color entry in the inking unit 03; 13 formed, wherein the color input from the respective color source 16; 26 ago, z. B. according to the above, in each case from the color source 16; 26 via a ductor roller 17; 27 and a lift roller 18; 28, at a downstream location on a common inking roller 19, in particular on the same Nacktwalze 19 occurs.
  • the lifting rollers 18, 28 have, for example in the axial direction in each case a lateral surface with a profile in Longitudinal direction on which the raised, strip-shaped circumferential portions 29 is interrupted by at least one with respect to the generatrix of the raised portions 29 recessed, strip-shaped circumferential portion 31 (see, for example, schematically oversubscribed in Fig. 3 ).
  • Such in longitudinal sections profiled lifting roller 18; 28 is also referred to as "cut”.
  • the length of the respective sections 29; 31 does not have to be the same, but may, depending on the printing image requirements on the lifter roller 18; 28 and from Heberwalze 18; 28 to lift roller 18; 28 be different.
  • the total proportion of the raised, so supporting portions 29 at the roll length ie the maximum usable bale length in the case of cut lifter rollers 18; 28 depending on the requirements each strong, z. Between 10% and 90%. The ink is thus only in the axial region of the raised portions 29 of the ductor roller 17 forth in the inking unit 03; 13 registered.
  • a self-form cylinder 02; 12 or a same on the forme cylinder 02; 12 provided printing form depending on the overlap of the raised portions 29 and / or depending on the traverse stroke of the at least one rubbing roller 22 with a more or less strongly running in each other color pattern by the same inking unit 03; 13 are colored.
  • pivot drive is particularly advantageous in connection with a security printing, in particular Wertpapieroffsetdruck, and / or the formation of the printing unit 01 as a collective printing 01, in particular as a two-page collective printing 01, and / or the one iris pressure enabling inking 03; 13 with two inking sources 16; 26 and / or the, in particular one with respect to the raised portions variable, cut formation of at least one lifter roller 18; 28th
  • the pivotal movement of the lifting roller 18; 28 causing pivot drive includes z. B. two levers 33 which are pivotally mounted about the pivot axis S and at which, spaced from the pivot axis S, the lifter roller 18; 28 is rotatably mounted frontally.
  • the storage of the lifting roller 18; 28 takes place either as shown by arranged on the levers 33 radial bearing 34, in which pin 36 of the lifting roller 18; 28 are mounted, or by means of a rotationally fixed to the levers 33 arranged through or divided axis, on which on the lifting roller 18; 28 provided radial bearings sit.
  • the two levers 33 are preferably both on a same one or more parts, driven by a pivot drive shaft 39, z. B. a hollow shaft 39, rotatably arranged. This is in the side frames 37; 38 mounted in radial bearings 35 about the pivot axis S pivotally.
  • pivoting the shaft 39 about the pivot axis S is carried on the levers 33 lifter roller 18; 28 with its axis of rotation R on a circular line with the an effective lever length corresponding radius r pivots.
  • a pivoting takes place between a layer A, in which the lifting roller 18; 28 with its lateral surface in the end position on the ductor roller 17; 27 has come to rest, and a layer B, in which the lifting roller 18; 28 has come to rest with its lateral surface in the end position on the Nacktwalze 19.
  • a pivot angle ⁇ of the lever 33 between the two layers A; B is dependent on the geometry of the rollers and their arrangement as well as the lifting length
  • the said geometry and lever length is preferably provided such that the pivot angle ⁇ is in an angular range of only 3 ° to 10 °, in particular from 5 ° to 8 °.
  • a preferred effective lever length between the pivot axis and rotation axis R is, for example, 60 to 70 mm.
  • the respective lever 33 and the two levers 33 together pivoting, and medium or directly on the lever 33 and the levers 33 attacking drive means 32 is adjustable in terms of its output side drive force formed, in particular at least limited in force upwards , As a result, a force-based hiring of the lifting roller 18; 28 possible.
  • a force-based hiring of the lifting roller 18; 28 possible.
  • the stop is then through the lateral surface of the stationary roller 17; 19 formed, against which the lifting roller 18; 28 is turned by the pivot drive.
  • the drive means 32 of the pivot drive as a pressure medium, in particular Druckfuid, ie a fluid under pressure, operated, ie hydraulically or preferably pneumatically operated, drive means 32 running.
  • This drive means 32 preferably engages with its output member 41, which is movable by acting on it; 42 indirectly via at least one transmission element, z. B. via at least one lever 33; 43 and / or possibly a movement-reducing gear, or directly via a non-rotatable or at least torsionally rigid connection, for.
  • a clutch 44 on the shaft 39 to pivot it.
  • the drive means 32 is in this case preferably designed double-acting, that is, that the movement of the output member 41; 42 is actively effected or can be effected along its degree of freedom of movement in both directions by respectively applying pressure to the drive means 32.
  • the principle of the drive means 32 is preferably based on a movement of a piston in a piston chamber caused by the application of pressure medium, the movement of the piston acting on the output member 41; 42, which may possibly also be formed integrally with the piston, is transmitted.
  • the side of the piston chamber, which is acted upon to displace the piston with a pressurized fluid, is also referred to as a pressure chamber.
  • a double-acting piston-piston chamber system accordingly comprises a pressure chamber on each side of the piston.
  • the drive means 32 as a fluid-operated or fluid-operated linear drive 32, for. B. linear motor 32, z. B. as druckstoffbeetzschlagbares cylinder-piston system 32, short as operated with pressure medium working cylinder 32, in particular pneumatic cylinder 32 is formed.
  • This or this comprises a piston chamber limiting housing 46, z. B. cylinder 46, in which axially a piston is movable back and forth, which transmits its movement to a piston rod connected thereto.
  • the latter or an extension connected to it in a tension- and pressure-rigid manner, forms the driven member 41 of the drive means 32 which can be moved by being acted upon.
  • the piston chamber can be acted upon with pressure medium on both sides of the piston.
  • a pressure medium source 47, z. B. a pressure medium supply or a compressor via corresponding lines connectable or connected port 48; 49, z. B. pressure medium connection 48; 49, provided.
  • the two pressure medium connections 48; 49 or supplied thereto piston part spaces are each one of the two by the lifting roller 18; 28 o. G. Plies A; B assigned in such a way that by acting on the respective pressure medium connection 48; 49, the lifter roller 18; 28 a corresponding thereto position A; B of the two o. G. Plies A; B strives to occupy or take aim.
  • pressure medium source 47 and the pressure medium connections 48; 49 is preferably a controllable pressure reducing valve 51, short pressure regulating valve 51, z. B.
  • Proportional pressure control valve provided at the output of a desired pressure level P (P1, P2) can be generated.
  • this pressure regulating valve 51 is adjustable with respect to the pressure level P (P1, P) present at the outlet and comprises a corresponding adjusting means 52.
  • the adjusting means 52 can in principle be manually, adjustably, but preferably as explained below, by a control means 57, e.g. B: via a user interface 49 to a control means 57, be remotely controlled adjustable.
  • the force with which the squeegee roller 18; 28 to the other inking roller 17; 27; 19 and the other rollers 17; 27; 19 is set, and thus the color stripe width in the nip, is set by setting (manually on-site or via an operator station 59 or automated by a control means 57) of the pressure regulating valve 51.
  • This can be z. B. in the context of the initial commissioning of the machine and / or maintenance or inspection of the machine and / or changing pressure conditions.
  • the pressure medium source 47 can now in one embodiment, for example via a than Switching 53 with two outputs trained valve 53, advantageously a z. B. as so-called. 5/2-way valve trained multi-way valve, and corresponding lines with two pressure medium connections 48; 49 connected.
  • the two pressure medium connections 48; 49 or the piston sub-chambers supplied by this are now, depending on the position of the switching valve 53, alternately with pressure medium of the pressure levels P provided by the pressure medium source 47 and the pressure regulating valve 52; P1; P2 acted upon.
  • the setting of the switching valve 53 is carried out by a control means 56 forth automated by controlling a valve 53 associated with the actuating means 54 via corresponding control signals S.
  • the control of the valve 53 causing control means 56 may be formed as a control circuit 56 or program routine 56 and a part of a decentralized or centrally constructed control device 58, z. B. a machine control and / or a control console.
  • the control of the valve 53 is carried out according to the desired lifter stroke T or clock T (cycle length) and the desired clock curve (course of the various clock phases), wherein a complete clock T z. B. includes two switching operations.
  • a clock T comprises a phase ⁇ A of the system of the lifting roller 18; 28 in position A, a phase ⁇ AB of the position change after position B, a phase ⁇ B of the system of the lifting roller 18; 28 in position B, and finally a phase ⁇ BA of the position change again to position A.
  • the predetermined by the control means 53 timing, so the periodically recurring pattern and the repetition frequency for the control of the valve 53, z. B. via an operator interface 59 can be predetermined and / or changed.
  • the timing may correlate with the actual machine speed present, a factor determining the correlation at the operator interface 59 may be changed or automatically selected based on relationships stored in the controller 58.
  • different correlations or factors between lifter clock and. Can be used for productions with mutually different production conditions and / or machine settings Machine speed be deposited.
  • Machine speed be deposited.
  • a correlation of one lifter stroke per five sheets to be delivered by the printing location 07 and for another production a correlation of one lifter cycle per one of five sheets deviating number of sheets to be conveyed by the printing area 07 may be deposited.
  • the factor can vary between 1 bar per 5 beats up to 1 bar per 25 bends.
  • the pressure regulating valve 51 is controlled by a control means 57 (eg control circuit 57 or program routine 57), which e.g. B. may form part of the decentralized or centrally constructed control device 58, be remotely controlled adjustable.
  • a control means 57 eg control circuit 57 or program routine 57
  • the setting of the differing pressure level P1; P2 made by actuation of the actuator 52 via the control means 57.
  • a specification of the respective pressure level P1; P2 can be z. B. via one or the user interface 59 can be specified and / or changed.
  • a Pressure levels P1; P2 automatically be selected based on stored in the controller 58 relationships.
  • a basic setting for the pressure level P1 can be predefined, for example, which can then be changed by the operator at the operator interface 59.
  • Both pressure medium connections 48; 49 and Kolbenteilsammlung alternately supplying switching valve 53 may in a variant, not shown, two individual, z. B. by the control means 57 to each other synchronized controlled switching valves may be provided, which input side z. B. with a particular adjustable pressure control valve 51, z. B. Proportional pressure control valve, are in communication. Although this causes a higher technical effort, but it allows for the two layers A; B different Anstell devis by mutually different pressure levels P1; P2 to realize. The possibly for the two pressure medium connections 48; 49 different pressure levels P1; P2 can additionally in o. G. Way vary depending on the total proportion of the supporting portions 29.
  • the working cylinder 32 and the piston chamber may be dimensioned in its length such that the layers A; B of the squeegee roller 18; 28 are reached when the piston reaches the region of an end position in the cylinder. It may be particularly advantageous if the working cylinder is designed with a cushioning.
  • the trained as a fluid-operated or fluid-operated linear motor 32 as described Drive means 32 engages a lever 33; 43, z. B. on which the lifting roller 18; 28 bearing lever 33 outside of the pivot axis S or on a specially provided for this purpose, with the shaft 39 rotatably connected lever 43 at.
  • the specially provided lever 43 which possibly also by a second arm of the lifting roller 18; 28 bearing lever 33 may be formed, preferably has a larger, z. B. at least twice the lever length, as that of the lifting roller 18; 28 carrying lever 33 and is for example 140 to 180 mm.
  • the drive means 32 as a fluid-operated or fluid-operated rotary drive 32, preferably fluid-operated rotary piston motor 32, in particular pneumatically actuated rotary piston motor 32 is formed.
  • the shaft 42 or a non-rotatably connected to this extension forms the driven by loading driven member 42 of the drive means 32.
  • double-acting design of the piston chamber can be acted upon on both sides of the piston with pressure medium.
  • the rotary drive 32 according to o. G. Version two pressure medium connections 48; 49, which or their piston subspaces in the manner described above for the first embodiment with pressure means of one or more pressure levels P; P1; P2 are supplied.
  • the above-mentioned embodiment of the first embodiment in terms of timing, driving, adjustment and operation is to be applied according to the second embodiment.
  • the oscillating piston motor 32 and its stator is arranged fixed to the frame, z. B. directly or via a holding device 66, for example via studs 66, at least rotatably connected to the side frame 38.
  • both embodiments of the pivot drive in particular at a point of the drive train between the output member 42 of the drive means 32 and the pins 36 of the lifting roller 18; 28 bearing radial bearing 34, biased such that when removed or without resistance switched drive means 32 and output member 41; 42, one of gravity-induced acceleration of the lift roller 18; 28 opposing force, preferably a torque caused by the counteracting torque, in particular substantially canceling torque, is introduced into the drive train.
  • An advantageous bias voltage is designed and adjusted so that when disconnected or without resistance switched drive means 32 and output member 41; 42, the lifting roller 18; 28 not at all or with at most a part, z. B.
  • the biasing device is configured and adjusted such that the lift roller 18; 28 with separate or without resistance switched drive means 32 and output member 41; 42 - z. B. manually - in almost every position between ductor roller 17; 27 and Nacktwalze 19 can be spent or could and would remain there or would remain.
  • This can basically with z. B. an arbitrarily formed and acting at any suitable point in the drive train spring element 62 are effected.
  • a tension or compression spring with its spring force could be counteracted by a torque due to the force of gravity by acting on the lifting roller 18; 28 bearing lever 33 or the torque acting on the shaft 39 lever 43 engages in a suitable manner.
  • the device for biasing comprises a torsion spring 62 designed as spring element 62 which on a frame side, preferably the input side of the shaft 39 opposite frame side, operationally, ie during operation of the machine or the printing unit 01, rotationally fixed in or on the side frame 37; 38 fixed, and in an opposite side frame 38; 37 closer longitudinal section of the shaft 39, z.
  • a torsion spring 62 designed as spring element 62 which on a frame side, preferably the input side of the shaft 39 opposite frame side, operationally, ie during operation of the machine or the printing unit 01, rotationally fixed in or on the side frame 37; 38 fixed, and in an opposite side frame 38; 37 closer longitudinal section of the shaft 39, z.
  • a torsion spring 62 designed as spring element 62 which on a frame side, preferably the input side of the shaft 39 opposite frame side, operationally, ie during operation of the machine or the printing unit 01, rotationally fixed in or on the side frame 37; 38 fixed, and in an opposite side frame 38; 37
  • the determination at the frame-fixed end of the torsion bar spring 62 is preferably designed such that the rotationally fixed connection of the torsion bar spring 62 releasably for adjustment purposes and the torsion bar spring 62 in the region of this end rotatable, and can be fixed again after Verderehen. As a result, the applied to the shaft 39 bias can be adjusted and maintained after setting for further operation.
  • the frame-fixed mounting of the torsion spring 62 is effected for example via a clamping set 63, by means of which the torsion bar spring 62 is releasably fixed in the frame.
  • the torsion spring 62 is preferably mounted such that it in particular runs coaxially-in the shaft 33 designed as a hollow shaft 39.
  • the torsion spring 62 is for example designed such that they are in their elastic, z. B. substantially linear, setting range, but at least in this case the pivotal movement claimed adjustment range, a spring constant of z. B. 15 to 30 Ncm / grad, preferably 21 to 26 Ncm / degree. It takes when pivoting the lifter roller 18; 28 a total stroke over an angle ⁇ , z. B. torsion or torsion angle ⁇ (eg., With ⁇ of 3 ° to 10 °, in particular from 5 ° to 8 °), which corresponds to the pivot angle ⁇ between the layers A and B.
  • the bias of the torsion spring 62 is z. B.
  • the torsion spring 62 about a central position of its deflection around, z. B. around a mean torsion angle ⁇ o around, z. B. in the range of 12 ° to 18 °, in particular from 14 to 16 °, is pivoted, from which they, for example, during pivoting of the lifting roller 18; 28 is deflected on both sides by half the total stroke.
  • the torsion spring 62 is thus upon pivoting of the lifting roller 18; 28 between the layer B and the layer A on its length between the frame-fixed end and the shaft-fixed part by the angle ⁇ between a rotational position b (B) and a rotational position a (A) tortiert.
  • the torque applied by the torsion spring 62 is for the mean torsion angle ⁇ 0, for example between 3000 and 3800 Ncm, preferably between 3200 and 3600 Ncm. Due to the small angular difference in the deflection, the torque varies only slightly.
  • the possibility for applying the bias can also be formed by a spring-elastic in rotation connection between the shaft 42 of the rotary drive 32 and the lever 33 bearing shaft 39.
  • the clutch 44 between its input and output side with respect to.
  • the torque transmission be designed resilient.
  • the drive means 67 of the pivoting drive is designed as an electric drive 67 which can be operated torque-controlled and / or operated in at least one operating mode with an electric motor 68.
  • an electric power P out, adjustable, at least upwards is limited.
  • a torque input M s (or specification of a corresponding variable) can be preset and / or changed remotely operated to a setting means 69 embodied as a drive controller 69 of the electric drive 67.
  • the drive controller 69 or a process implemented there, for example, the control signals S causing the reciprocating motion from a corresponding control means 56 are supplied, which cause here, for example, the clocked change between clockwise and counterclockwise.
  • the control means 57 is connected via a signal connection to the drive controller 69, wherein the control means 57 may be connected via a signal connection with an operator interface 59.

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  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)

Claims (15)

  1. Groupe d'encrage (03 ; 13) d'un groupe d'impression (01) avec au moins un premier rouleau (17 ; 27) de groupe d'encrage, et avec un deuxième rouleau (18 ; 28) de groupe d'encrage pouvant pivoter en va-et-vient entre le premier rouleau (17 ; 27) de groupe d'encrage et un troisième rouleau (19) de groupe d'encrage espacé du premier rouleau (17 ; 27) de groupe d'encrage, un entraînement de pivotement étant prévu pour le pivotement du deuxième rouleau (19) de groupe d'encrage avec un moyen d'entraînement (32) mécaniquement indépendant de la rotation des cylindres (02 ; 04 ; 12 ; 14) de groupe d'impression et des rouleaux (17 ; 18 ; 19 ; 22 ; 23 ; 23 ; 24 ; 27 ; 28) de groupe d'encrage prévus dans le groupe d'impression (01), et la force d'application sur le premier et/ou le troisième rouleaux (17 ; 19) de groupe d'encrage pouvant être réglée, une valeur de consigne relative à la force d'entraînement du moyen d'entraînement (32) pouvant être prescrite et/ou modifiée par commande à distance en agissant sur un organe de réglage (52 ; 69), caractérisé en ce que le moyen d'entraînement (32) est réalisé comme entraînement linéaire ou rotatif (32) actionné ou actionnable par application d'un fluide sous pression et la force d'application sur le premier et/ou sur le troisième rouleaux (17 ; 19) de groupe d'encrage est réglable par ajustement ou variation d'un niveau de pression du moyen d'entraînement (32).
  2. Groupe d'encrage selon la revendication 1, caractérisé en ce que le moyen d'entraînement (32) est réalisé de manière réglable par la prescription de valeur de consigne quant à sa force d'entraînement côté sortie.
  3. Groupe d'encrage selon la revendication 1 ou 2, caractérisé en ce qu'un niveau de pression du fluide sous pression est prescriptible et/ou modifiable en tant que valeur de consigne par commande à distance d'un organe de réglage (52) réalisé comme vanne régulatrice de pression (52).
  4. Groupe d'encrage selon la revendication 1, 2 ou 3, caractérisé en ce que l'entraînement linéaire ou rotatif (32) actionné par fluide sous pression est réalisé comme système à piston et chambre de piston, en particulier comme système à piston et chambre de piston à double action.
  5. Groupe d'encrage selon la revendication 1, 2, 3 ou 4, caractérisé en ce qu'une chambre de pression de l'entraînement linéaire ou rotatif (32) est reliée à une source de fluide sous pression (47) par une vanne de détente de pression (51) pour l'alimentation en fluide sous pression, la vanne de détente de pression (51) étant réalisée de manière réglable par l'organe de réglage (52) quant au niveau de pression présenté à la sortie.
  6. Groupe d'encrage selon la revendication 1, 2, 3, 4 ou 5, caractérisé en ce que, pour son réglage à distance, l'organe de réglage (52) est en liaison technique de signal avec un moyen de commande (57) réalisé comme circuit de commande (57) ou comme programme informatique (57), prévu pour régler l'organe de réglage (52) suite à une instruction provenant d'une routine logicielle du programme informatique (57) ou à une saisie effectuée sur une interface d'opérateur (49) reliée au moyen de commande (57).
  7. Groupe d'encrage selon la revendication 1, 2, 4, 5 ou 6, caractérisé en ce qu'un moyen de commande (56) réalisé comme circuit de commande (56) ou comme programme informatique (56) est prévu, au moyen duquel un organe de réglage (54) d'au moins une vanne (53) est configuré pour la sollicitation cyclique d'au moins une chambre de pression.
  8. Groupe d'encrage selon la revendication 1, 2, 3, 4, 5, 6 ou 7, caractérisé en ce que le moyen d'entraînement (32) est réalisé comme cylindre pneumatique dont l'organe d'entraînement (41) est accouplé par un levier (33 ; 43) à un arbre (39) pivotant sur lequel le deuxième rouleau (18 ; 28) est monté excentriquement à l'axe de pivotement (S).
  9. Groupe d'encrage selon la revendication 1, 2, 3, 4, 5, 6, 7 ou 8, caractérisé en ce que l'entraînement de pivotement est pré-contraint au moyen d'un élément à ressort (62), de telle manière qu'en cas de moyen d'entraînement (32) éloigné ou commuté sans résistance, une force opposée à l'accélération du rouleau preneur (18 ; 28) due à la force de gravité est appliquée dans le train de transmission de l'entraînement de pivotement.
  10. Groupe d'encrage selon la revendication 1, 2, 3, 4, 5, 6, 7, 8 ou 9, caractérisé en ce que deux premiers rouleaux encreurs (17 ; 27) coopérant chacun avec une source d'encrage (16) et deux deuxièmes rouleaux (18 ; 28) de groupe d'encrage pivotants coopérant chacun avec le premier rouleau encreur (17 ; 27) respectif sont prévus dans le train de rouleaux du groupe d'encrage (03 ; 13), et en ce que, pour le pivotement, un moyen d'entraînement (32) propre mécaniquement indépendant est prévu par rouleau (18 ; 28) pivotant.
  11. Groupe d'encrage selon la revendication 1, 2, 3, 4, 5, 6, 7, 8, 9 ou 10, caractérisé en ce que le rouleau (18 ; 28) pivotant est réalisé comme rouleau segmenté (18 ; 28), des segments (29) circonférentiels en forme de bande en saillie étant dans le sens de la longueur interrompus par au moins un segment (31) circonférentiel en forme de bande en creux par rapport à la génératrice des segments (29) en saillie.
  12. Groupe d'impression d'une machine à imprimer pour l'impression simultanée en polychromie avec au moins un cylindre de transfert (04 ; 14), avec plusieurs cylindres porte-cliché (02 ; 12) coopérant avec le cylindre de transfert (04 ; 14) ainsi qu'avec un groupe d'encrage (03 ; 13) par cylindre porte-cliché (02 ; 12) coopérant pour l'encrage de celui-ci, caractérisé par la configuration du groupe d'encrage (03 ; 14) selon l'une ou plusieurs des revendications 1 à 11.
  13. Procédé de fonctionnement d'un groupe d'impression avec au moins un premier rouleau (17 ; 27) de groupe d'encrage, et avec un deuxième rouleau (18 ; 28) de groupe d'encrage pouvant pivoter en va-et-vient entre le premier rouleau (17 ; 27) de groupe d'encrage et un troisième rouleau (19) de groupe d'encrage espacé du premier rouleau (17 ; 27) de groupe d'encrage, le deuxième rouleau (19) de groupe d'encrage étant pivoté au moyen d'un moyen d'entraînement (32}, caractérisé en ce que le deuxième rouleau (19) de groupe d'encrage est pivoté par sollicitation d'un moyen d'entraînement (32) réalisé comme entraînement linéaire ou rotatif (32) actionné par un fluide sous pression, réglable par commande à distance quant à une force d'entraînement côté sortie.
  14. Procédé selon la revendication 13, caractérisé en ce qu'une chambre de pression de l'entraînement linéaire ou rotatif (32) actionné par un fluide sous pression est sollicitée par du fluide sous pression avec un niveau de pression (P ; P1 ; P2) différencié pour deux cycles de production distincts l'un de l'autre.
  15. Procédé selon la revendication 13 ou 14, caractérisé en ce que le niveau de pression (P ; P1 ; P2) du fluide sous pression à appliquer sur l'entraînement linéaire ou rotatif (32) est réglé pour l'ajustement d'un interstice entre rouleaux.
EP13766058.5A 2012-10-10 2013-09-23 Mécanismes d'encrage d'un groupe d'impression, groupe d'impression et procédé permettant de faire fonctionner un groupe d'impression Not-in-force EP2906427B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE201210218417 DE102012218417A1 (de) 2012-10-10 2012-10-10 Farbwerk eines Druckwerks, Druckwerk sowie Verfahren zum Betreiben eines Druckwerks
DE102012218423.6A DE102012218423B4 (de) 2012-10-10 2012-10-10 Farbwerk eines Druckwerks, Druckwerk sowie Verfahren zum Betreiben eines Farbwerks
PCT/EP2013/069687 WO2014056711A1 (fr) 2012-10-10 2013-09-23 Mécanismes d'encrage d'un groupe d'impression, groupe d'impression et procédé permettant de faire fonctionner un groupe d'impression

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EP2906427A1 EP2906427A1 (fr) 2015-08-19
EP2906427B1 true EP2906427B1 (fr) 2016-09-14

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JP2015536256A (ja) 2015-12-21
US9604446B2 (en) 2017-03-28
WO2014056711A1 (fr) 2014-04-17
EP2906427A1 (fr) 2015-08-19
US20150290927A1 (en) 2015-10-15
ES2604760T3 (es) 2017-03-09
CN104781076A (zh) 2015-07-15

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