EP2869993B1 - Dispositif et procédé de transport de feuilles imprimées avec déplacement élastique - Google Patents

Dispositif et procédé de transport de feuilles imprimées avec déplacement élastique Download PDF

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Publication number
EP2869993B1
EP2869993B1 EP13730513.2A EP13730513A EP2869993B1 EP 2869993 B1 EP2869993 B1 EP 2869993B1 EP 13730513 A EP13730513 A EP 13730513A EP 2869993 B1 EP2869993 B1 EP 2869993B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
circulating means
stop
drive
conveying
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.)
Active
Application number
EP13730513.2A
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German (de)
English (en)
Other versions
EP2869993A1 (fr
Inventor
Hans Ehrlich
Stephan Gericke
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.)
KBA Metalprint GmbH and Co KG
Original Assignee
KBA Metalprint GmbH and Co KG
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.)
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Publication date
Application filed by KBA Metalprint GmbH and Co KG filed Critical KBA Metalprint GmbH and Co KG
Publication of EP2869993A1 publication Critical patent/EP2869993A1/fr
Application granted granted Critical
Publication of EP2869993B1 publication Critical patent/EP2869993B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F21/00—Devices for conveying sheets through printing apparatus or machines
    • B41F21/12—Adjusting leading edges, e.g. front stops
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H11/00—Feed tables
    • B65H11/002—Feed tables incorporating transport belts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H9/00—Registering, e.g. orientating, articles; Devices therefor
    • B65H9/14—Retarding or controlling the forward movement of articles as they approach stops
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/60—Damping means, shock absorbers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/20—Belts
    • B65H2404/25—Driving or guiding arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2801/00—Application field
    • B65H2801/03—Image reproduction devices
    • B65H2801/21—Industrial-size printers, e.g. rotary printing press

Definitions

  • the invention relates to a conveying device and a method for conveying printing material according to the features of claim 1 or 11.
  • an apparatus and a method for printing metal plates wherein by feeding means with chain-driven and resiliently arranged thrust elements to be printed metal plate in the nip of a printing unit can be fed.
  • a brand lever is provided with a stop surface on the printing cylinder, which acts together with the leading edge of the path when limiting the metal plate.
  • the brand lever is pivotable in an off-hook area about an axis parallel to the cylinder axis.
  • the pivot axis is located outside the peripheral profile of the cylinder.
  • the pivotable brand lever carries in the region of its free end a stop means, which is fixed in such adjustable manner with respect to its position on the brand lever, so that the effective length of the lever between the pivot axis and stop surface is adjustable.
  • the brand lever is articulated to move between the pivot axis and the stop surface by a lever of a drive mechanism which is driven by cam means correlated to the cylinder rotation.
  • the EP 1 678 066 B1 relates to a gripper cylinder in the folder of a web-fed rotary printing machine with a gripper control, wherein the gripper arm carrying the gripper tip are articulated on two radially spaced levers, which are each driven via a cam gear. To shorten the movement when gripping between retracted and extended position, the axis of the gripper arm is displaced as such in the radial direction by the interaction of the lever. To grasp the leading edge of a printed product, the gripper is first extended below the trailing end of the previous product and pivoted against the direction of rotation over the end to be gripped. Also the EP 0 931 748 A1 relates to a cylinder in the folding apparatus of a web-processing printing press. About the interaction of a control roller with a control curve is first an extension of the gripper and subsequently a movement against the rotational movement of the folding blade cylinder designed as a cylinder.
  • the EP 1 472 164 B3 is a transport system of a sheet metal printing machine or Sheet metal coating machine with a belt system known, the panels should be fed accurately without backing systems. This is achieved in that the panel leading edge is permanently pushed against the application mark by closing the gripper system by a difference in speed between a suction belt and application marks, wherein the Belachtafel is attracted by a clocked activatable vacuum against the suction belt.
  • the EP 1 116 679 A2 discloses a conveyor having a trailing edge of sheets of sheets to be conveyed in the direction of transport, which feed the sheet trays with their leading edges against application marks of a feed drum.
  • the Tafelschübe are z. B. designed as a belt or chains Tafelschubtrum so resiliently attached so that they can collapse against the springing force against the spring when it comes to rest on the landing.
  • GB 000 748 122 A discloses an endlessly revolving chain with a sprung backing, wherein the drive comprises a mechanism by which the drive of the chain of one revolution sequence is temporarily delayed in a defined manner and temporarily accelerated in another revolution sequence.
  • the invention has for its object to provide a conveyor and a method for conveying a printing material sheet.
  • the conveying device has means for limiting the feed of the circulating medium conveying the printing material sheet. This will - at least for a movement phase - a limit of the printing material for the feed causes attacking force. This is particularly advantageous in connection with a friction-based transport, since a jerky release of the static friction force can be prevented.
  • the feed of the printing material sheet frictionally or positively conveying the circulating means at least in the cooperating with the printing material conveyor section against the conveying direction is operationally yielding, z. B. spring-damped and / or limited torque formed.
  • this is realized by the driving means of the circulating means driving the circulating means can deflect even in the case of a resistance increase opposed to the transport direction or is yielding from a threshold value for the resistance.
  • the band or Werverlauf can deflect in the case of the transport direction opposite resistance increase.
  • the "soft" belt conveyor formed in the aforementioned manner cooperates with a downstream stop device whose brand lever, in addition to a radial movement, enables a tangential movement of a stop surface along the transport direction.
  • the stop surface is tunable with respect to the uniform movement of an approaching printing material sheet.
  • bouncing can be avoided or at least reduced.
  • a non-uniform movement projected onto the movement path of the printing material sheet which otherwise results from the superimposition of rotation of the cylinder and pivoting of the brand lever, can be counteracted.
  • the application mark is designed so as to be controllable by the second movement component with respect to the movement path.
  • the system further makes it possible to vary the brand movement along the transport direction so that it substantially covers the area of the first contact before the printing nip Feed rate of the conveyor line and in the region of the Nippstelle substantially corresponds to the peripheral speed of the bearing device bearing cylinder.
  • a guided and continuous braking is possible, whereby a bouncing effect is avoided.
  • this allows the reduction of compression forces on possibly existing sprung thrusts or possibly sprung drive system of the Nippstelle upstream conveying path, z. B. on the funding of a feed frame.
  • a first contact between the investment brand and substrate can early by the investment device, d. H. clearly before the zero position and / or Nippstelle done, z. B. at a time in which the printing cylinder is still at least 20 °, preferably at least 30 ° before its zero position, wherein in the printing unit as a zero position z. B. the situation is to be understood, in which the voltage applied to the investment mark panel leading edge in the theoretical nip line, d. H. which enters the axes of rotation of the pressure point forming cylinder connecting plane.
  • a secure, and more independent of the specific weight of the printing material sheet stiffening of the printing material in the transverse direction is achieved by a kinking guide in conjunction with a deflection assisting means.
  • a stretched course of the leading edge to be brought to a stop device is ensured.
  • the means which presses the conveyed printing material sheet in the region of the deflecting guide against the support surface ensures that the printing material sheet undergoes a deflection in a definable manner, possibly counter to its stiffness in the longitudinal direction.
  • a printing material 01 preferably as a printing material 01 trained substrate sheet 01 machined machine, especially printing and / or varnishing machine, are printing material 01, preferably printing material boards 01, by one or more conveyors 04; 06 transported along a conveying path, on which they by one or more processing units 02; 03 edited on at least one of their pages, z. B. printed and / or painted.
  • a cylinder 07 is located in the conveying path at at least one point; 08 with a device 09 for register-oriented alignment, short stop device 09, one on the conveyor line, in particular by an upstream conveyor 04; 06 promoted,
  • Substrate sheet 01 in particular a Betigstofftafel 01, provided.
  • the conveyor 04; 06 includes at least one substrate sheet 01 promoting means 05, for example circulating means 05 and a circulating, printing material 01 transporting conveyor 05, for example, it comprises a tape system with one or more z. B. as circulating belts 05 trained circulating means 05, on which or which of the printing material 01 arranged in the transport direction by positive engagement with a band 05 or a different, also rotating traction means 05 and acting on the trailing end of the printing material 01 stop 15, z. B. rear thrust 15, or by adhesion (friction) with the belt system by only the weight or supported by friction-increasing measures, eg.
  • Example by a support force and thus the friction increasing means 25, in particular a means 25 for generating a negative pressure P - , for example, designed as a vacuum chamber 25 pressure sink 25, or a magnetic force, such as a magnet 25, in particular electromagnet, is promoted.
  • the effect of the means 25 is variable and / or designed to be activated and deactivated.
  • cylinder 07; 08 upstream conveyor 04; 06 is in Fig. 1 the conveyor 04; 06 schematically as at least one circulating belt 05 with a rear thrust 15 having belt system and in Fig. 2 with a friction or contact force increasing means 25 shown.
  • the printing material sheet 01 or printing material plates 01 machine comprises at least one processing unit 02; 03, z. B. at least one printing unit 02 (eg. Fig. 8 ) and / or at least one coating unit 03 (eg. Fig. 9 ), by which the substrate sheet 01 formed in particular as a printing material 01 is printable or paintable on at least one side. It can be provided in the same processing line of the machine in the conveying direction one behind the other also at least one printing unit 02 and at least one coating unit 03.
  • the cylinder 07; 08 with upstream conveyor 04; 06 can basically be provided one or more times in the conveying path of the machine.
  • the stopper 09 comprehensive cylinder 07; 08 for example, as a corrective on a free conveying path and / or in the input area of a processing unit 03 in the manner of a contact cylinder 08 or a feed drum 08 and / or as a functional part of a processing unit 02 with stop device 09,
  • the abutment device 09 exhibiting cylinder 07, in particular printing cylinder 07 be executed.
  • the to be conveyed and processed by the machine substrate sheet 01 can in principle be used as a paper sheet, z. B. be designed as a sheet of paper or cardboard greater strength, for example, up to at least 1 mm thickness, but are in a preferred embodiment as a rigid substrate sheet 01 or of a rigid material, for example in the form of panels 01, z. B. printing material boards 01, formed.
  • the printing material panels 01 can preferably be formed as metallic panels 01, in particular as metal sheets 01.
  • the printing material sheet 01 or Bedruckstofftafeln 01 in the preferred here sense z. B. in contrast to thin paper sheet, for example, characterized in that they relate to their running in the transport direction longitudinal extent a significantly higher flexural rigidity and / or a higher basis weight of z.
  • B. at least 1 kg / m 2 , in particular 1 to 3 kg / m 2 as thin paper sheets. They are characterized for example by the fact that they are not wound on the curved surfaces of rotating transport cylinders or rollers, but on such rollers and cylinders, possibly with slight deflection and / or possibly a negligible wrap, z. B. less than 20 °, are transported only substantially straight.
  • panels 01 in this sense therefore, in addition to the preferred embodiment as metal panels 01, z. B. metal sheets 01, for example, from tinplate or aluminum sheet, and panels 01 made of more sensitive material such.
  • panels made of plastic, wood, a composite material or cardboard into consideration, in particular if they are z. B. are formed rigid in the above-mentioned sense.
  • the term "printing material sheet” is also understood as meaning one of the special embodiments, in particular as a printing material panel 01 in one of the forms mentioned, preferably made of metal.
  • the cylinder 07; 08 acts with the particular tabular printing material 01 this leading and aligning together, this on the cylinder 07; 08 rolls substantially tangentially on the circumference of the cylinder, in particular does not apply to a significant circumferential area.
  • the stop device 09 ensures the correct, with respect to the transport direction register-oriented system of a leading edge 13 of the conveyor through the upstream conveyor 04; It includes at least one stop means 11 with a stop surface 12, preferably several, z. B.
  • the free end carrying the abutment surface 12 preferably further passes out of the circumferential line of the cylinder 07; 08 out than in the first position, in which it is for example taken up for the most part within the circumferential line.
  • the periodically and / or correlated to the cylinder rotation movable stop means 11, z. B. so-called. Brand lever 11, can basically formed in any way, in the cylinder 07; 08 mounted and driven by a first drive mechanism, provided that in this way the above-mentioned periodic and / or correlated movement of the stop surface 12 bearing free end with at least one radial component of movement between an inner and an outer layer can be realized or realized.
  • the z. B. designated as a brand lever 11 stop means 11 are mounted in a guide and in this guide along a straight line or along a curved path to be movable back and forth, wherein at least one, in particular predominantly radial path or movement component is provided.
  • the stop means 11 is designed as a brand lever 11 in the manner of a pivotable lever, wherein the radial movement of the free, drive side remote end between the first and the second position preferably by pivoting the brand lever 11 about an axis parallel to the cylinder, advantageously located within the circumferential axis axis A. , in particular a cylinder-fixed axis A, takes place.
  • the brand lever 11 or the two brand levers 11 can be rotationally fixed to a shaft 14, in particular a pivotably but cylinder-mounted shaft 14 may be arranged.
  • Exemplary and representative of the possible versions of the cylinder 07; 08 is in Fig. 3 the cylinder 07 in the embodiment shown as a printing cylinder 07.
  • the correlated with the cylinder rotation drive the brand lever 11 and the shaft 14 can in principle be effected via a mechanically independent of the cylinder rotation drive means, wherein the correlation in this case z. B. can be realized by electronic or circuit technology.
  • the correlated with the cylinder rotation drive the brand lever 11 and the shaft 14 via a cam gear 16, which forms, for example, together with the or the brand lever 11 supporting shaft 14 and possibly other intermediate links the first drive mechanism.
  • One to the cylinder 07; 08 to be introduced panel 01 is by the upstream conveyor 04; Promoted 06 so that the leading edge 13 of the panel 01 at least directly before emergence on the cylinder 07; 08, z. B. at least over a distance of at least 5 cm, preferably at least 10 cm, before First touch, along a nearly linear trajectory B T runs, which preferably with a tangent or alternatively with a parallel to the tangent to a few millimeters, z. B. offset by up to 10 mm, secant falls together.
  • the supplied table 01 as early as possible and on a significant, in particular the largest possible stretch of road, z. B. on at least a section of 5 cm or a cylinder movement by at least 20 °, until the emergence of the board 01 on the cylinder 07; 08 to lead to the stop surface 12.
  • a brand lever 11 stop means 11 z. B. in such a multi-part with a stop element 21 and a stop element 21st supporting arm 22, z. B. lever arm 22, formed so that a stop surface 12 comprehensive stop member 21 is not rigid and possibly only adjustable on a movable along the first trajectory lever, along a (second) movement path relatively movable, in particular translationally relatively movable, on the arm 22, z , Lever arm 22, and is forcibly driven by a (second) drive mechanism 23 with respect to its movement relative to the arm 22 periodically and / or in correlation to the movement of the arm 22.
  • the stopper element 21 having brand lever 11 is thus a total of a first drive mechanism with at least one, in particular a predominant, radial component, periodically and / or in correlation to the cylinder rotation movable or moved, in particular pivotable, wherein the stop surface 12 having stop member 21 itself am Brand lever 11, in particular in the region of the free end, mounted relatively movable and by a second drive mechanism 23, preferably periodically and / or in correlation to the movement of the arm 22, forcibly driven or positively driven.
  • the second movement also takes place along a defined second trajectory with at least one with respect to the cylinder 07; 08 tangential movement component, in particular predominant tangential component, between a first and a circumferential direction of the cylinder 07; 08 spaced from the first layer second layer.
  • a movement with a predominantly radial component is to be understood as meaning a movement whose radial stroke is greater than the tangential stroke that possibly takes place at the same time as a result of this movement.
  • a movement with a predominantly tangential component should be understood to mean a movement whose tangential stroke is greater than the radial stroke possibly taking place simultaneously by this movement.
  • the stop surface 12 is thus during the entire cycle of movement of a full rotation of the cylinder 07; 08 operatively not rigidly arranged on the moving stop means 11, but is part of a stop element 21, which in turn is arranged movable relative to the stop means 11 and is also periodically forced or is.
  • the stop element 21 is on the brand lever 11, z. B. on the arm 22, arranged in such a relatively movable and / or is driven or drivable by the second drive mechanism 23 in such a way that it in at least one phase in which it with the edge 13 of a conveyed printing material 01 in Contact occurs, but the printing material 01 preferably still not on the cylinder 07; 08 (24) accumulates, on the brand lever 11 in a direction with at least one component of movement in the direction of rotation of the cylinder 07; 08 (24) and / or along the movement path B T of the printing material sheet 01 is moved or is movable
  • stop means 11 and the drive mechanisms (23) for the arm 22 and the stop element 21 are matched to one another such that the stop element 21 located in contact with the printing material sheet 01 in the circumferential direction of the cylinder 07; 08 (24) viewed in the direction of rotation or in the direction of movement of the printing material 01 moves.
  • the periodic drive of the stop element 21 can in principle also be correlated to the cylinder rotation and possibly coupled directly to it mechanically or electronically. In the case of an electronic or circuit coupling, a separate drive means for the movement of the stop element 21 may be provided.
  • a separate drive means can be omitted by the stop element 21 via the second drive mechanism 23, z. B. via a gear 23, directly to the rotational movement of the cylinder 07; 08 (24) or preferably indirectly via the movement of the stop means 11, in particular of the arm 22, which correlates with the rotational movement, to the rotational movement of the cylinder 07; 08 (24) is coupled.
  • a direct coupling to the rotational movement of the cylinder 07; 08 (24) may be provided in addition to the first operationally fixed space cam 19, a further, not shown, space-tight cam, which forms the second drive mechanism 23 in the manner of a cam gear with a roller and a lever connected to the stop element 21.
  • the forced relative movement of the stop element 21 is not by a space-tight cam, but by the movement of the stop member 21 supporting stop means 11 (brand lever 11) and its arm 22 in conjunction with a cylinder-fixed linkage (eg Coupling 28 or a cam gear 32, see below 4 and FIG. 5 ).
  • the relative movement of the stop element 21 can basically take place along different paths of movement B R , provided that this differs from the direction of movement of the first movement and a (significant) component in the circumferential direction and / or in the tangential direction of the cylinder 07; 08 (24). So a z. B. for the first movement Opposing pivotal movement may be provided to a mark lever fixed pivot axis, which, for example, the og sinusoidal tangential velocity profile counteracts. Likewise, a translational movement may be provided along a guide, which may be curved or at least not formed in a straight line in the entire range of motion. Such a movement path B R for the relative movement can then be adapted concretely to the movement required by the superposition with the first movement.
  • the relative movement of the stop element 21 on the arm 22 takes place along a linear trajectory B R.
  • the rectilinear trajectory B R is preferably oriented on the arm 22 in such a way that it essentially (eg with a maximum deviation of ⁇ 5 °, in particular not more than ⁇ 3 °) is tangential to the cylinder 07; 08 (24) runs when the stop means 11, so the arm 22 together with the stop element 21, is in that position in which the stop surface 12 passes through a zero position L 0 .
  • the coupling between a point of attack of the stop element 21 and the effective for the cylinder-fixed articulation point a fixed (effective) coupling length I on.
  • the coupling is given by a coupling 28, which on the one hand, for example via a pin 29 or a shaft 29 rotatably on the stop element 21, z. B. on a arranged on the stop element 21 support member 35, and on the other hand via a pin 31 or a shaft 31 rotatably on the cylinder 07; 08 is articulated, wherein the axes of the rotatable connection in each case preferably extend parallel to the cylinder axis.
  • the shaft 31 is in this case as an abutment 31 against which the stop member 21 is supported via the coupling 28.
  • the coupling or articulation is provided by a cam gear 32, which on the one hand a rotatable about, for example, a pin 33 or a shaft 33 on the stop element 21, z. B. on the stop element 21 fixed support member 35, arranged Roller 34 includes, which with a via, for example, a pin 31 or otherwise on the cylinder 07; 08 arranged, in particular cylinder-fixed stop member 26 cooperates as an abutment 21, wherein in this embodiment at least the cooperating with the roller 34 during the movement cycle peripheral portion of the stop element 26 has a circular ring-shaped contour.
  • the axis of the rotatable roller 34 and the center of the annular contour are each preferably parallel to the cylinder axis.
  • the center of the annular or annular section-shaped stop element 26 extends at a distance from the cylinder axis and preferably spaced from the pivot axis of the brand lever 11.
  • the coupling is further associated with a spring element 27, for example a compression spring 27, through which the roller 34 experiences a force in the direction of the stop element 26.
  • the spring element 27 attacks this z. B. directly or indirectly on the arm 22 of the stop means 11, and on the other hand on the roller 34 bearing stop member 21 at.
  • a compression spring 27 can be found under consideration of the direction of force and a tension spring application.
  • a bias towards the stop element 26 is applied by the spring element 27.
  • the cylinder-fixed stop element 26 in this case represents - possibly together with the spring element 27 - the abutment, against which the stop element 21 is supported on the roller 34.
  • the stop element 26 in the effective range ie in relevant curve section or segment, not formed with a circular ring-shaped contour, but a deviating contour.
  • This contour of the cam portion of the abutment element 26, which interacts with the roller 34 during a movement cycle, is designed, for example, in irregular curvature such that as a result of the superimposition of the movements of the entire stop means 11 and the movement of the abutment element 26, a desired movement profile can be modeled.
  • the movement line can be influenced, wherein, for example, a substantially rectilinear, possibly tangential movement or a movement inclined to the tangent may be desired and / or generated.
  • a contour of the stop element 26 modeled with regard to the special requirements thus opens up a large margin for optimizing the movement of the stop surface (s) 12 which is effective for the alignment.
  • the stop element 21 is arranged, for example, via a linear guide 38 on the arm 22 in the region of its free end, ie in the head region.
  • the Z. B. designed as a brand lever 11 stop means 11 is z. B. arranged by a clamping connection 39 torsionally rigidly on the shaft 14, wherein the clamping connection 39 by a spring element, for. B. a compression spring, can be biased.
  • the cylinder 07; 08 associated device 09 may be formed as a pure stop device 09 or in an advantageous development as a stop and gripping device 09. In the latter case, preferably on the stop means 11, in particular on the stop element 21, gripping elements 36, z.
  • gripper tips 36 may be provided, which viewed in the tangential direction over the stop surface 12th protrude and press in the phase of lowering the stop member 11 on the voltage applied to the stop surface 12 substrate sheet 01.
  • one or more grippers 37 may be provided, which in contrast to the possibly additionally gripper tips 36 having stop means 11, for. B. does not have an aligning, but only holding function.
  • the function and the movement of the abutment means 11 described above is set out on the basis of a sequence of snapshots in the case of a trained with hook tip 36 stop means 11 and additional gripper 37, wherein at relevant points for possible deviations in the event of training without hook tip 36 as pure Lifting means 11 is pointed.
  • the explanation will be further given by way of example as a cylinder 07 designed as a printing cylinder 07, but is also applied to other arranged in the conveying cylinder 08 with stop device 09.
  • the direction of rotation D of the cylinder 07 (08) is here, such. B. off Fig. 6a seen as being counterclockwise. Also recognizable z. B. the cooperating with the roller 18 cam 19, the stop means 11 supporting shaft 14, a (pure) gripper 37 in the foreground, and partly conceals a designed as a brand lever 11 stop means 11 with the arm 22 and the stop surface 12 having here linearly relatively movable stop element 21 and the cylinder-fixed coupling, here by way of example by articulation against a cylinder-fixed stop element 26 (see, eg. Fig. 6a ).
  • the zero position L 0 is marked at the point where the trajectory B T of the table 01 affects the circumference of the cylinder.
  • the cylinder 07 (08) is in its zero position L 0 when the effective stop surface 12 coincides with the zero position L 0 .
  • the contour of the cam 19 and the coupling of the stop element 21 to the cylinder 07 (08) are coordinated such that in the phase of movement of the cylinder 07 (08) after the delivery of a previous panel 01 and before contact with a first table 01 to be applied Brand lever 11 by the first movement, in particular by pivoting, further out of the cylinder peripheral surface out comes and the stop member 21 is moved by the second movement with a counter to the direction of rotation component in a relative to the cylinder circumference further back lying position.
  • the stop surface 12 is thereby far before the zero position L 0 , z. B. at an angular position ⁇ between 65 ° and 55 ° before zero position L 0 , already spent in the trajectory B T. D. h.,
  • the stop surface 12 occurs z. B.
  • the stop means 11 additionally has a hook tip 36 and is intended to serve as a gripper 37
  • the stop means 11 penetrates with its gripper tip 36 the trajectory B T up to a height above the male table 01 and approaches in the further course, for example on a rectilinear, z. B. by a small angle ⁇ of, for example, 2 ° to 4 ° to the movement path B T of the table 01 inclined, trajectory B G z. B. radially spaced by the thickness of the panel 01 from the cylinder circumference, located in the alignment of the zero position L 0 point.
  • This movement which is inclined to table movement, is likewise achieved by the interaction of the first and second movements. If the stop means 11 is formed without a gripper function, then the inclined movement can be replaced by a rectilinear trajectory parallel to the trajectory B T of the table O1, preferably by a movement in the trajectory B T of the table O1.
  • the two movements of stop means 11 and stop element 21 and the phase and conveying speed of the upstream conveyor 04; 06 designed and matched so that the first contact (L K ) between the stop surface 12 and the leading edge 13 of the printing material 01 possible early, for example already at an angular position ⁇ of the cylinder 07 (08) of z. B. at least 20 °, preferably at least 30 °, in particular between 35 ° and 45 ° (in the example of Fig. 6b 40 °) before the zero position L 0 comes about.
  • At least from the first contact begins the synchronizing phase in which the stop surface 12 effective as a stop on a straight, inclined to the movement path B T of the panel 01 or parallel trajectory with a along the movement path B T of the panel 01 z.
  • the stop surface 12 effective as a stop on a straight, inclined to the movement path B T of the panel 01 or parallel trajectory with a along the movement path B T of the panel 01 z.
  • the zero position L 0 Upon reaching the zero position L 0 through the stop surface 12, it is preferably simultaneously the gripper closure of possibly arranged on the stop means 11 hook tip 36 and / or the or additionally arranged gripper 37.
  • this position ie the zero position L 0 , is the Lifting means 11 together with stop element 21 preferably in a relative position to the cylinder 07 (08) and / or to the trajectory B T of the table 01, so that the rectilinear trajectory B R substantially (eg., With a maximum deviation of ⁇ 5 °, in particular maximum ⁇ 3 °) is tangential to the cylinder 07 (08) and / or runs along the path of movement B T of the panel 01 (see, for example, FIG. Fig. 6d ).
  • FIG. 7 an example of a schematic application diagram for the movements of the stop means 11 and the stop element 21 relative to the cylinder angle position and relative to the movement of a printing material sheet 01 to be applied.
  • the definition of the position of an approaching printing material sheet 01 is defined in such a way that its zero point at the location of the zero position L 0 relative to the cylinder 07; 08 and / or comes to rest in the location of the tangential contact of the conveyed printing material sheet 01, which is all 360 ° in the angular position of the cylinder 07; 08 repeated.
  • the approaching substrate sheet 01 is promoted here, for example, at a constant speed, while the Slings 11 is still in a resting phase P r .
  • the stop means 11 in total in the retracted position and the stop element 21 is in an initial position in which it is on the arm 22 in an extended, the arm 22 z.
  • the stop element 21 is in its rest phase Z r relative to the arm 22 in a first position, from which it -. B. during contact with the leading edge 13 and / or during a later working phase P a - relative to the arm 22 in the direction of rotation D of the cylinder 07; 08 in a second, circumferentially spaced in the direction of rotation D to the first layer position can be brought.
  • the first movement, z. Example, the pivoting of the stop means 11 as a whole, and the second movement, ie the relative movement of the stop member 21 to the arm 22 of the stop means 11, as described in the example can be done simultaneously or temporally or angularly offset from each other.
  • the angular position or at the time (position L 1 , L 2 ) where at least one of the two elements, for. B. as a result of the above-mentioned coupling of the movements at least in the position L 1 , in which the arm 22 is moved by the corresponding drive mechanism from its rest position, the working phase P a of the stop device 09 begins.
  • the initial contact L K between the abutment element 21 and the printing material sheet 01 formed in particular as a printing material board 01 occurs at a specific angular position ⁇ . B. by an appropriately trained conveyor 04; 06 - until at least to reach the zero position L 0 , preferably beyond until a later angle or time, z. B. a release layer L a , maintained. D. h.,
  • the stop member 21 moves with at least one component of movement in the circumferential direction of the cylinder 07; 08 considered on the arm 22 forward and / or relative to the cylinder circumference in the direction of movement of the printing material 01.
  • the contact to the printing material sheet 01 and possibly the gripper closure can be solved in principle directly in reaching the zero position L 0 again by a return pivoting of the brand lever 11 is initiated in the rest position after reaching the zero position L 0 by the first drive mechanism. It can be spent at the same time or offset the investment brand 21 in the starting position.
  • arm 22 and application mark 21 remain after passing through the zero position L 0 for an angular range, z. B. for 10 ° to 40 °, in their occupied in the range of zero position L 0 end position, before being returned to the starting position and they are for the rest of the cylinder rotation to the beginning of the subsequent working phase P a in its rest phase P r ,
  • a stop device 09 exhibiting cylinder 07; 08 one or more times in the conveying path between a feeder, not shown, z. B. a stacking system through which the printing material to be processed 01 of the conveyor line can be fed, and a delivery device to which the processed substrate sheet 01 is output through the conveyor line.
  • the second cylinder 24 may also be designed as a forme cylinder. With the second cylinder 24 acts in the case of an offset printing unit 02, a printing form exhibiting third cylinder 42, z. B.
  • the device 09 can in principle at one of the two pressure point forming printing cylinder 07; 24 provided.
  • the printing unit 01 printed on one side of the printing unit 02 is one of the two pressure point forming printing cylinder 07; 24, z. B. the first cylinder 07 as a pressure cylinder 07 or counter-pressure cylinder 07 is formed, which the other, color-leading printing cylinder 24, z. B. blanket or transfer cylinder 24, serves as an abutment.
  • the device 09 can then be provided in principle on the ink-carrying printing cylinder 24 or the printing cylinder 07. Preferably, it is in the case of one-sided printing unit 02 provided on the printing cylinder 07.
  • the first cylinder 07 represents, for example, a second transfer cylinder 07, which cooperates with a second form cylinder (not shown).
  • the two transfer cylinders 07; 24, preferably arranged below the movement path of the printing material 01 transfer cylinder 07 include the device 09.
  • the provided on a printing cylinder 07 (24) device 09 is preferably designed as a stop and gripping device 09.
  • a on the conveyor, z. B. before or in the entrance area of a processing unit 02; 03 arranged cylinder 08, with an o. G. Stop device 09 is formed.
  • a processing unit 03 designed as a coating unit 03 is provided in front of or in the entry area assigned cylinder 08 as an application cylinder 08 or feed drum 08 with a stop device 09.
  • This application cylinder 08 is z. B. neither itself, nor as an abutment as a functional part of the concrete processing of the printing material 01 involved, but serves the register-oriented orientation and / or feeding into a downstream, for example, downstream processing unit 03 (02).
  • the application cylinder 08 is preferably arranged below the guided on the movement path B T printing substrate 01 and can cooperate in a non-illustrated embodiment on the printing material 01 to their secure support with a roller or rollers as an abutment.
  • the application cylinder 08 comprises at least one in operation on the device 09 subsequent peripheral area friction-increasing measures, eg. Example, by a bearing force and thus the frictional force between the substrate sheet 01 and lateral surface increasing means 43, in particular a means 43 for generating a negative pressure P - or preferably a magnetic force.
  • metallic printing material sheet 01 z.
  • metallic printing material sheet 01 in the preferred case metallic printing material sheet 01, z.
  • metal or metal sheets in the region of the lateral surface, for. B. directly or by a maximum of 45 °, in particular a maximum of 30 ° spaced, designed as a magnetic segment 43 means 43 to the device 09, which extends over a significant peripheral region, for. B. over at least 20 °, preferably at least 30 °.
  • This magnet segment 43 may comprise one or more magnets cooperating directly with the printing material sheet 01 to be conveyed or one or more magnets magnetizing the outer surface of the cylinder 08 in this segment from the inside.
  • a printing material sheet 01 to be conveyed is then used by the magnetic force on the lateral surface.
  • non-magnetizable printing material 01 z.
  • a friction increasing means 43 to the cylinder 08 as a means 43, for example, a device for generating a negative pressure P - provided, in o. G. Circumference z. B. are provided by the device from the inside with negative pressure P - actable openings in the lateral surface.
  • a printing material sheet 01 to be conveyed is then used by the negative pressure P - on the lateral surface.
  • the application cylinder 08 can in an advantageous embodiment or in the entrance area of processing tools, eg. B. a printing cylinder 07; 24 or in particular a cylinder 47, for example a painting cylinder 47, a downstream processing unit 03 (02) be arranged such that it is spaced upstream of this machining tool on the conveying path at most by the length of the printing material 01 from the downstream processing tool.
  • processing tools eg. B. a printing cylinder 07; 24 or in particular a cylinder 47, for example a painting cylinder 47
  • a downstream processing unit 03 (02) be arranged such that it is spaced upstream of this machining tool on the conveying path at most by the length of the printing material 01 from the downstream processing tool.
  • the cylinder 08 is upstream, z. B. in the entrance area of a coating 03.
  • This has z. B. a first cylinder 46, z. B. counter-pressure cylinder 46, which forms an abutment with the second cylinder 47 formed as a varnishing cylinder 47, a nip, in which the printing material to be carried out 01 by the varnishing cylinder 47 is to paint.
  • the z. B. a rubber pad coating cylinder 47 receives the paint to be applied, for example, a co-operating with the painting cylinder 47 applicator roller 48, which in turn z. B. is supplied via a metering roller 49 a paint supply with the required amount of paint.
  • roller 51 Between the contact cylinder 08 and the nip of the coating unit 03 can in the conveying path a roller 51, z. B. guide roller 51, with a bearing force and thus the frictional force between the substrate sheet 01 and lateral surface increasing means 52, in particular a means 52 for generating a negative pressure P - or preferably a magnetic force, be provided.
  • This roller 51 preferably has the means 52 in the entire peripheral area.
  • the roller 51 is arranged downstream of the Anlegzylinder 08 in the conveying path at a distance which is at most the length of the printing material sheet 01 to be processed.
  • the cylinder 08 as a contact cylinder 08 and between two conveyor sections of the machine, without direct structural or be provided functional connection.
  • This guide 44 can serve for the horizontal alignment and support and possibly comprise a device, not shown, for the lateral alignment of the printing material sheet 01.
  • a z. B. at least one printing unit 02 having machine has in one embodiment at least one printing unit 01 with a stop device 09 having printing cylinder 07 (24).
  • an o. G. Trained as an application drum 08 is additionally on the conveying path. Stop device 09 comprehensive cylinder 08 is provided.
  • At least one printing unit 02 having machine is the printing unit 02 in the entrance area an Anlegzylinder 08 upstream with the stop device 09.
  • the Nippstelle forming printing cylinder 07; 24 can then be executed without stop device 09.
  • At least one coating unit 03 having machine has in one embodiment, at least one the coating unit 03 in the entrance area upstream Anlegzylinder 08 with the stopper 09 on.
  • FIGS. 8 and 9 is the respective the stopper 09 comprehensive cylinder 07; 08 upstream conveyor 04; 06 for the sake of simplicity and representative of suitable embodiments of the relevant conveyor 04; 06 shown both with indicated thrusts 15 and dashed lines shown means 25 to increase the bearing force.
  • one of the two measures can be omitted, wherein the application of the bearing force increasing means 25 is preferable.
  • the execution of the stop device 09 with the first movement exporting stop means 11 and the one, in particular translational, relative movement exerting stop member 21 serves a "pre-control" of the leading edge 13 cooperating stop surface 12.
  • the pilot serves the most possible bounce-free and / or create low-acceleration as possible on the stop surface 12 for register-oriented alignment.
  • a defined, z. B. at least in a synchronous phase in the direction of the trajectory B T extending movement of the stop surface 12 given, however, at any time during the interaction with the edge 13 forms a firmly defined "hard” stop.
  • the application of the printing material sheet 01 with its leading edge 13 to the stop surface (s) 12 of the stop device 09 by means of a by the upstream conveyor 04; 06 on the substrate sheet 01 frictionally and / or positively applied thrust.
  • the pre-controllable stop device 09 executed in the aforementioned manner has a stop means 11 which carries a first, predominantly radial, movement in the aforementioned manner and one on this one, in particular predominantly tangential, relative movement exerting stop element 21 and / or of such a stop device 09 comprehensive cylinder 07; 08 (24) and / or such a cylinder 07; 08 (24) comprehensive conveying path of a sheet-processing machine can in principle with an arbitrarily designed, the thrust force on the printing material 01 applying conveyor 04; 06 be provided cooperating.
  • the conveyor 04 described below forms; 06, in particular a conveyor 04; 06 with means for limiting the feed of the circulating means 05, considered in itself a particularly advantageous solution for applying the thrust and can arbitrarily designed in the conveying stroke stop device 09, in particular a randomly configured stop device 09 cylinder 07; 08 (24), be upstream.
  • the conveyor 04; 06 is with means 53; 54; 67; 56; 81; 82; 83; 84; 98 formed, which cause a limitation of the force acting on the printing material 01 for the feed force.
  • these means 53; 54; 67; 56; 81; 82; 83; 84; 98 be realized in different ways.
  • the means 53; 54; 67; 56; 81; 82; 83; 84; 98 is the by the conveyor 04; 06 applied to the substrate sheet 01 opposite to the resistance formed by the stop device 09 feed force at least temporarily, z. B. to a threshold, limited. If the threshold value is exceeded, a reaction of the agent 53; 54; 67; 56; 81; 82; 83; 84; 98 in such a way that the force on the applied to the stop device 09 substrate sheet 01 does not increase further.
  • the strength of the measure can be dosed or metered to limit the feed force in a simple embodiment, that when promoting the printing material 01 from a certain, by running onto the stop means 11 caused resistance set in this way by the strength Threshold of stiction is exceeded.
  • this can again lead to unwanted accelerations and / or displacements.
  • the feed force limitable conveyor 04; 06 is the feed of the printing material 01 or friction-positively conveying circulating means 05, z. B. of the substrate sheet 01 frictionally promoting belt 05 or a rear 15 carrying traction means (eg belt, chain or belt) at least in the cooperating with the printing material 01 conveyor section 55 against the conveying direction operationally yielding, z. B. spring-damped and / or limited torque formed. This can be z. B.
  • the driving means of the circulating means 05 driving the circulating means 05 can spring even in the event of a transport direction T opposing resistance increase or yielding from a threshold value for the resistance or in a second embodiment of the band or circulating means course for the case of the transport direction T opposing resistance increase can spring.
  • the operational compression or yielding must not be able to be done indefinitely by the feed limiting means.
  • the advance of the circulating means 05 limiting means 54; 67; 56; 81; 82; 83; 84; 98 is z. B. such that it allows at least a minimum stroke between the disturbed by resistance increase tape feed and the expected without interference tape feed (non-destructive). This minimum lift is z. B.
  • the operational compression or yielding is then at least by a stroke in the tape feed at least of the printing material 01 cooperating conveyor section 55 as a result by an at least temporary delay of the circulating means 05 of up to several millimeters, z. B. at least 5 mm, relative to the undisturbed movement.
  • the operational too enabling minimum stroke means a non-destructive and not in the range of unwanted permanent material deformations lying yielding.
  • the limitation of the force acting on the printing material 01 for the feed force is thus effected in that, for example, give the drive means of the traction means or Werbachverlauf even in the case of one of the transport direction T opposite resistance increase, z. B. compress or in the case of the drive device z. B. "slipping" can.
  • the conveying device 04 based on frictional engagement between circulating means 05 and printing material sheet 01; 06, the feed of the circulating means 05, z. B. Bandes 05, in the above manner operational yielding, z. B. spring-damped and / or limited torque formed, the static friction between the circulating means 05 and the printing material 01 to be funded is chosen so large in operation that below a spring triggering or effecting force, especially at least within the discoursehubes, still no loosening of Conclusion occurs.
  • the friction increasing measure and the spring force or threshold force of the means 54; 67; 56; 81; 82; 83; 84; 98 adjusted to one another in such a way that the effective against the transport direction T stiction force between the circulating means 05 and the printing material sheet 01 to be funded is greater than the compression or yielding within the technicallyhubes causing force. If the leading edge 13 of the printing material 01 by the conveyor 04; Pressed 06 with a threshold value exceeding force against the subordinate stop in the conveying device 09, so the feed of the circulating means 05 springs accordingly, so that a limitation of the printing material 01 for the feed force is effected. This is a force which between the stop device 09 on the one hand and the frictionally engaging conveyor 04; 06 on the other side on the substrate sheet 01 acts, limited or limited.
  • the rearward thrust 15 is arranged stationary on the circulating means 05 with respect to the circumferential direction or along the transport direction T and is made unyielding.
  • a conveyor 04; 06 with a with respect to the feed on at least the conveying path compliant trained circulating means 05 is in the drive train of the circulating means 05 driving drive means 54; 67; 56 provided for feed limitation of the circulating means 05.
  • z. B. output member 58 is not entirely stiff, but - z. B. in the context of a non-zero minimum spring travel - resilient.
  • This operationally provided minimum spring travel correlates with the minimum lift of the circulating means 05 that results at the conveyor section 55 between undisturbed circulating-medium feed which is disturbed by an increase in resistance.
  • a threshold value for the resilient yielding is preferably provided.
  • a first embodiment of this first embodiment of the first group is based on the fact that in the drive train two in the drive train a rotary motion transmitting members 58; 59 are coupled with respect to the rotation transmission via a yielding in the circumferential direction in the context of the spring travel transmission member 57.
  • the transmission member 57 comprises in this case as a means 54 for feed limitation a resiliently effective element 54, z. B. a spring element 54 or a pneumatically resilient element 54, which z. B. between circumferentially effective stops 61; 62 of the two elastically coupled members 58; 59 is arranged.
  • the torque is then preferably transmitted from the drive side nearer member 58 via the spring-elastic element 54 against the spring force, ie in the manner of a sprung carrier connection, on the abtriebuza artsre member 59.
  • the stiffness or spring constant of the element 54 the "hardness" or compliance of the feed limitation can be influenced.
  • the spring-elastic coupling or the transmission member 57 in a defined zero position L 0 with a non-zero force, which z. B. the threshold for a compression or yielding pretends biased executed.
  • the members 58; 59 further circumferentially effective stops 63; 64 is provided, which counteract the force of the prestressed spring element 54 together.
  • the zero position L 0 is, for example, in the load-free operating state, z. B. at a standstill or especially in the operating phase of the transport, in which there is no beyond the allowable threshold resistance increasing disturbance by the emergence of the leading edge 13 on the stop device 09 with an unacceptably high force.
  • the compression causes the stroke between the actual feed of the circulating means 05 and the expected without disturbance in the same phase of motion feed.
  • the maximum possible stroke in the region of the conveyor section 55 is z. B. over the maximum possible, z. B. by the stops 61; 62; 63; 64 and / or the spring element 54 certain, spring deflection or spring deflection ⁇ of the preferably biased spring element 54 and-ellessgliedes 57 determines.
  • this first embodiment variant is the resilient member 57 on the drive side torsionally rigid with a shaft 66, z. B. a drive shaft 66, connected and between this and a rotatably mounted on the shaft 66 (eg., Via a rolling bearing), preferably the output member 58 forming drive pulley 58 arranged for its entrainment (see, eg Fig. 11 the open representation of the drive wheel 69 from Fig. 10 ).
  • the transmission member 57 between a torsionally rigidly connected to the shaft 66 drive inner ring 59 as a member 59 and the rotatably mounted on the shaft 66 drive pulley 58, wherein the drive pulley 58 together with the drive inner ring 68 and the two links coupling transmission member 57 as rotatably sprung drive wheel 69th may be formed in the manner of a structural unit.
  • the spring element 54 is advantageously designed as a pressure medium cylinder 54, in which compressible fluid, for. As a gas or gas mixture, the spring-elastic action between the cylinder on the one hand and a piston closing the fluid space on the other causes.
  • the circulating means 05 z. B. than with the printing material 01 this promoting together acting band 05 is formed.
  • the conveying in the transport direction T takes place here, for example, not by Schuschübe 15, but based on friction.
  • a vacuum chamber 25 may be provided.
  • the Z. B. as a vacuum chamber 25th trained means 25 may basically be formed attractively in transverse and longitudinal direction at any point in the conveyor section 55 the printing material 01. It can only be provided on a longitudinal section of the conveying path, wherein its distance to the stop device 09 is preferably smaller than the printing material sheet length.
  • the means 25 is arranged in the transverse direction directly below the belt 05, so that the printing material 01 is attracted to the sheet extending between this and the means 25 belt 05.
  • the belt 05 may in this case be advantageously designed as a so-called vacuum belt 05 in the manner of a perforated belt 05, ie have a perforated structure with the belt 05 from below in the direction of the printing material 01 to be conveyed holes 71, which of the 01 to be conveyed opposite side ago by means of z. B. formed as a vacuum chamber 25 means 25 with a negative pressure P - can be acted upon. This is to be applied to a design of the vacuum chamber 05 in moving (see below) as well as frame-resistant design.
  • the conveyor 04; 06 can transversely to the transport direction T spaced several, in particular two the printing material 01 promoting, the defined feed of the printing material 01 via frictional force or form-fitting determining circulating means 05, in particular bands 05 may be provided.
  • This band 05 or these bands 05 run during operation in the conveying region, ie in the area cooperating with the printing material sheet 01, in the transporting direction T, wherein the particularly flat conveying region z. B. by an input side in the transport direction T and an output side, at least partially looped by the circulating means 05 means 81; 82, for example guide member 81; 82, z. B.
  • deflecting 81; 82 in particular deflection roller 81; 82, is limited.
  • tape guide of the circulating means 05 is by these guide rollers 81; 82 a particular planar extending guide section 65 limited, in which the circulating means 05 can interact with the printing material 01 sheet together.
  • further circulation means 72 can be provided for securing the printing material run, which circulate parallel to the at least one circulating means 05 which determines the advance via drive and deflection means which are not further described here.
  • the additional circulating means 72 may also stops 76, z. B. front stops 76 wear. To these can by the conveyor 04; 06 to be conveyed substrate sheet 01 are created. These serve z. B. the front conditioning of the printing material sheet 01, if this from an upstream, for example, also about at least one circulating belt 75 z. B. slightly faster conveying section 74 z. B.
  • the circulating means 05 exhibiting conveyor section 55 are passed. Due to the higher conveying speed of the upstream conveying section 74 and the z. B. to the circulating means 05 synchronously moving front stops 76, the printing material 01 01 for the stop device 09 directly upstream conveyor line in a respect. Their leading edge 13 defined location spent.
  • the drive of the or the feed-determining circulating means 05 can in this or other embodiments or variants, possibly via a coupling (see below), directly to the drive wheel 69 and the drive wheels 69 bearing shaft 66 or as shown via or a plurality of gears 73, z. B. a traction mechanism 73, of the only schematically indicated means 56, z. B. drive means 56, preferably one of the conveyor 04; 06 associated drive motor 56, or possibly be driven by a drive network forth via a corresponding drive connection or be.
  • the circulating means 05 which determines the feed and possibly additional circulating means 72 is / are designed to be endless.
  • the compliance is based on the fact that in the drive train a rotational movement transmitting transmission member 80 even in the manner of a torsion spring in the circumference of a required spring travel (or Einfederwinkels ⁇ ') yielding, ie. With respect to a torsion soft, is formed.
  • resiliently effective transmission member 80 may be formed in the drive train of the drive means arranged shaft 80. This shaft 77 is then formed in the manner of a torsion spring.
  • first embodiment of the first group can further arranged in the drive train transmission member 77, z. B. a traction means 77, respect. Its spatial course be resiliently mounted.
  • at least one compression roller not shown, for. B. a spring-loaded tensioner roller, be provided by which an effective Buchstoffin example of the running strand against the spring force can be extended, and thus at least temporarily an o. G. Hub in Switzerlandstoffvorschub can be reached.
  • a corresponding compression roller is provided or vice versa.
  • a threshold can be limited. It is here z. B. even with increasing resistance, which originates, for example, from a run-up of the leading edge 13 on the stop device 09, a torque corresponding to the threshold registered in the drive train of the circulating means 05 and / or transmitted in this drive train to the circulating means 05.
  • first embodiment of the second embodiment of the first group (see z. B. Fig. 12 ) is provided in the drive train between the drive means 56 and the circulating means 05 to the drive together acting output member 58 designed as a clutch 67 transmission member 67 whose maximum torque to be transmitted limited to a threshold or limited.
  • the thus formed coupling 67 is in this case in the above sense as a means 67 for limiting the feed of the circulating means 05 effective.
  • the clutch 67 is preferably adjustable with respect to the height of the threshold value, in particular at least within a control range, preferably designed gradios adjustable.
  • the threshold value for the torque is set for the execution of the (pure) frictional transport in such a way in relation to - with or without friction-increasing measures - present between Abruckstoffbogen 01 and 05 circulating means static friction, that by running the leading edge 13 on the Stop device 09 reaching this yielding the Umlaufstoffvortriebes triggering threshold already takes place before by the emergence of the static friction resistance, ie the limit to the "demolition" of static friction is reached.
  • the coupling 67 can basically be designed arbitrarily with regard to its underlying principle of action, provided that it defines a defined torque transmission. In an advantageous embodiment, it is designed as a magnetic coupling 67, in particular as a magnetic particle clutch. In an alternative embodiment, a coupling 67 designed as a compressed air coupling 67 can also be used for this purpose.
  • a second embodiment variant of the second embodiment from the first group is designed as a drive motor 56 drive means 56 with respect to.
  • the provided by the drive motor 56 drive torque limited executed.
  • the drive motor 56 designed in this way is effective in the above sense as a means 56 for limiting the feed of the circulating means 05.
  • the drive motor 56 is designed as a.
  • the torque limiter in particular adjustable servo motor 56.
  • For setting a torque limiting threshold or a setpoint value predetermining the drive torque is valid in the same way as above for the threshold value.
  • the spatial circulation means or the circulation means guide is designed so resilient that at least one the Buchmlttel entry in co-determining mitbemdes guide member 81; 82; 83; 84; 98, preferably two such guide elements 81; 82; 83; 84; 98, as a result of one of the transport direction T opposite z. B. by accumulating the printing material 01 on the stop device 09 caused resistance increase in a radial direction can or can, and hereby at least temporarily causes a feed limit of the circulating means 05 in the guide section 65 of the conveyor section 55 or cause.
  • the feed limit of the circulating means 05 ie the resistance-related reduction of the present in the conveyor region or in the corresponding guide section 65 belt speed, in a first embodiment of the second group by deflection only of guiding or deflecting elements 83; 84, which leaves the circulating medium or strip course present in the guide section 65 of the conveying region of the circulating means 05, ie in the region cooperating with the printing material sheet 01, unaffected.
  • the feed limitation is unchanged Length and position of the guide portion 65 by reducing the present on this section Umlaufstoff- or belt speed, said reduction is effected at other, lying outside the conveying area of the Umlaufstoffverlaufs by deflection.
  • a guide element 83 in the guide portion 86 between the output side guide roller 81 and the location of the tape drive, for. B. the drive wheel 69, and a guide member 84 in the guide portion 87 between the location of the tape drive, for. B. the drive wheel 69, and the input-side guide roller 82 is provided.
  • one of the guide portions 86; 87, in particular with respect to the drive wheel 69 leading guide section 86 shortened by compression and at the same time the other are extended by the corresponding length.
  • the drive section upstream guide section 86 is thus compliant with respect to the route length.
  • the conveying takes place by the drive does not affect, or at least not fully on the feed of the circulating means 05 in the conveying region, but is at least partially by the yielding in particular leading to the drive guide portion 86; 87 recorded.
  • this first embodiment of the second group (see, for example, FIG. Fig. 14 , in which only exemplary course and leadership of the circulating means 05 with guide elements 81; 82; 83; 84 and the indicated drive wheel 69 are shown) are the upstream in the drive gear 69 and the drive wheel 69 downstream guide portion 86; 87 yielding or resiliently mounted deflecting elements 83; 84, z. B. pulleys 83; 84 with respect to a radial direction linearly movable.
  • they may be on a common support 88, z. B. a carriage 88, rotatably mounted, which in turn is disposed linearly movable relative to a frame-fixed guide.
  • the carriage 88 is biased by a not shown here spring element against a frame-fixed point in such a way that the guide roller 86 together with the leading guide roller 81 this guide portion 86 against a possible deflects shorter course to a longer course out and vice versa shortened together with the trailing guide portion 87 deflecting roller 82 shortens the trailing guide portion 87 against a possible longer course.
  • a linear movement against the spring force limiting stop is provided by which the spring element already in zero position L 0 of the carriage 88 unfolds a spring force and thus defines a nonzero threshold for the deflection caused by a resistance increase.
  • the two deflection rollers 83; 84 also independently of each other in the manner mentioned in the guide sections 86; 87 are each stored linearly movable.
  • a deflection roller 81 cooperating with the leading guide section 86 is mounted on a pivotable lever 89 such that it guides this guide section 86 in the unloaded state towards a shorter path to a longer course deflects. If the resistance is increased, for example, by emergence of the printing material sheet 01, then the lever 89 against the force of an acting on the lever 89 spring element 94, z. As a compression or tension spring or a pneumatically acting cylinder moves into a conveying section 86 shortening position.
  • a deflection roller 83 is resiliently mounted in such a way that it lengthens the length of the trailing conveyor section according to the circulating means or belt length released from the advancing conveyor section 86 by deflection of the lever 89.
  • the pivotal movement of the lever 89 against the spring force limiting stop 96 is provided by which the spring element 94 already in zero position L 0 of the lever 89 unfolds a non-zero spring force and thus a non-zero threshold for defines the deflection caused by a resistance increase.
  • the deflecting roller 84 which is arranged resiliently in the trailing guide section 87, can be designed in the manner of a sprung belt tensioner.
  • the deflection of the circulating means guide is effected by at least one guiding or deflecting elements 81; 82, which determines the length and / or position of the conveying section relevant to the guide section 65.
  • at least the output-side guide roller 81 with at least one along the transport direction T extending component is movable, in particular against the transport direction T against the spring force of a spring element yielding or resiliently mounted.
  • the output-side guide roller 81 is resiliently mounted in the aforementioned manner by being mounted eccentrically on a pivotable about a pivot axis 92 lever 93.
  • the lever 93 is pivotable against the force of a spring element 94 from a zero position L 0 in a position in which the guide roller 81 comes to rest in a relation to the zero position L 0 closer to the input side guide roller 82. Due to the compression, the entire length of the conveying region and the drive forward flow guide sections 65; 86, which at least temporarily reduces the effective speed in the conveyor area.
  • a preload may be applied to the spring element 94, thereby providing a triggering threshold.
  • a deflecting roller 84 which is comparable to the abovementioned examples, is again provided which is resiliently displaced by the movement of the trailing guide section 87 by the excess length.
  • the circulating means 05 to achieve the required compression force between the output side guide roller 81 and drive wheel 69 via one or more stationary arranged guide or deflection 95, z. B. pulleys 95, be performed.
  • the output-side guide roller 81 is in contrast to the preceding variant on a lever arm of a two-armed pivotable about the pivot axis 92 lever 97, wherein the second lever arm is provided a further, partially wrapped by the circulating means deflection roller 98.
  • the lever 97 By pivoting the lever 97 as above, the total length of the conveying region and the drive forward flow guide sections 65; 86 shortened, but with the S guide to the two pulleys 81; 98 at a comparable way the output side pulley 81 a greater reduction of the total length is made possible.
  • a stop 96 and arranged in the trailing guide portion 87 guide roller 84 applies the above.
  • the output-side guide roller 81 is linearly movable, in particular parallel to the transport direction T, stored.
  • frame-fixed guide elements 101, z. B. guide pin 101 with guide elements 102 of a carriage 103, z. B. provided in the carriage 103 slots 102, in such a way that they allow a parallel to the transport direction T extending movement of the output-side guide roller 81 supporting carriage 103.
  • the carriage 103 is again against the force of a spring element 104, here z. B. a compression spring, einfederbar, wherein the spring element 104 is supported on a frame-fixed stop 106.
  • z. B. acting as a vacuum chamber 25 friction increasing means 25.
  • friction increasing means 25 with negative pressure P - can be provided fixed to the frame connection piece 107 which, for example, contactless or via a sliding contact with a suction-side opening 108 of the vacuum chamber 25 cooperates.
  • a sealing element 109, z. B. a sealing plate 109 may be provided at the connecting piece 107 and / or in the region of the opening 108.
  • the connecting piece 103 is arranged in such a coincidence with the opening 108 that in each of the operating positions of the carriage 103 at least one overlap exists.
  • the connecting piece 107 is connected via a line 99, z. B. a fluid of a relation to the environment lower pressure leading suction line 99, with a means, not shown, for providing a relation to the environment lower negative pressure P - , z.
  • a pump a turbine or a fan connected.
  • the P - port of the movable vacuum chamber 25 may be fixedly connected to a flexible hose, so that the movement of the suction chamber is almost not hindered (not shown).
  • FIG. 18 are schematically for different operating situations and associated load conditions, the positions of the carriage 103 of the third embodiment with reference to the relative position of the cooperating guide elements 101; 102 shown:
  • P active means 25
  • the output-side deflection roller 81 unlike the first two variants, likewise can not be pivoted but is linearly movable, in particular linearly movable parallel to the transport direction T.
  • this differs functionally only in that the friction-increasing means 25, z. B. the vacuum chamber 25 is arranged fixed to the frame.
  • the mentioned to the spring element 104, a possibly according to the second variant to be provided stop 96 and the spring-mounted guide roller 84 in the trailing guide section 87 mentioned is applied accordingly.
  • this has at least one opening 91, for example, on the side to be transported to the printing material 01 and / or the circulating means 05 side.
  • B. a large opening 91 or more spaced apart openings 91, z.
  • a negative pressure P prevailing in the vacuum chamber 25 acts - attracting the conveyed printing material sheet 01 to the circulating means 05.
  • the opening 91 or openings may or may advantageously be arranged directly beneath the circulating means 05, which is designed here as a perforated belt 05, for example.
  • the or, for example, slit-shaped opening (s) 91 can be arranged to cooperate directly with holes 112 of the hole band (s) 91 that otherwise substantially cover the perforated strip 05, so that the printing material sheet passes through the holes 112 01 is pulled against the perforated belt 05.
  • the function and integration of the vacuum chamber 25 is to be applied both to a construction of the vacuum chamber 25 in frame-resistant design (ie without movable carriage 103 and eg with a firmly connected or connectable connecting piece 107) as well as to the embodiment with a movable carriage 103 ,

Landscapes

  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)

Claims (15)

  1. Système de transport pour le convoyage de feuilles à imprimer (01) dans une machine à vernir et/ou à imprimer, comprenant un dispositif de transport (04 ; 06) pourvu d'un moyen de circulation sans fin (05), où ledit moyen de circulation sans fin (05) est réalisé sous forme de bande (05) convoyant par friction les feuilles à imprimer (01) ou de moyen de traction (05) supportant un poussoir arrière (15), lequel est réalisé comme bande supportant le poussoir arrière (15), comme chaîne supportant le poussoir arrière (15) ou comme courroie supportant le poussoir arrière (15), où une feuille à imprimer (01) est déplaçable par le moyen de circulation (05), par complémentarité de forme ou par friction, vers une surface de butée (12) d'un dispositif de butée (09) prévu en aval, caractérisé en ce que le guidage du moyen de circulation sans fin (05) convoyant la feuille à imprimer (01) par complémentarité de forme ou par friction et/ou le dispositif d'entraînement comprenant un moyen d'entraînement (56) du moyen de circulation sans fin (05) convoyant la feuille à imprimer (01) par complémentarité de forme ou par friction sont conçus avec un amortissement par ressort et/ou avec limitation de couple, de telle sorte que l'avance du moyen de circulation sans fin (05) sur au moins un segment de transport (55) coopérant avec la feuille à imprimer (01) est fonctionnellement réalisée de manière flexible par rapport à un déplacement non perturbé du moyen de circulation sans fin (05), du fait d'une augmentation de la résistance due au contact de la feuille à imprimer (01) contre le dispositif de butée (09).
  2. Système de transport selon la revendication 1, caractérisé en ce que le guidage du moyen de circulation sans fin (05) comprend sur un segment de guidage (86) un moyen (81 ; 82 ; 83 ; 84 ; 98) réalisé comme élément de guidage (81 ; 82 ; 83 ; 84 ; 98), lequel est monté de manière élastique dans la direction radiale.
  3. Système de transport selon la revendication 2, caractérisé en ce que l'élément de guidage (83 ; 98) monté de manière élastique dans la direction radiale est prévu dans le guidage du moyen de circulation (05) sur un segment de guidage (86) entre un élément de guidage (81) déviant le moyen de circulation (05) à une extrémité côté sortie du segment de transport (55) et une roue d'entraînement (69) entraînant le moyen de circulation (05).
  4. Système de transport selon la revendication 2, caractérisé en ce que l'élément de guidage (81) déviant le moyen de circulation (05) à une extrémité côté sortie du segment de transport (55) est réalisé de manière flexible dans la direction radiale.
  5. Système de transport selon la revendication 3 ou la revendication 4, caractérisé en ce que l'élément de guidage (81 ; 83 ; 98) réalisé de manière flexible dans la direction radiale est monté sur un levier (93 ; 97) de manière pivotante contre une force de ressort ou mobile linéairement, en particulier sur un chariot (88 ; 103) déplaçable linéairement contre une force de ressort.
  6. Système de transport selon la revendication 1, caractérisé en ce que le dispositif d'entraînement entraînant le moyen de circulation (05) comporte un moyen (54 ; 67) provoquant ou pouvant provoquer un débattement de la liaison d'entraînement à l'opposé de la direction d'entraînement ou une limitation du couple à transmettre.
  7. Système de transport selon la revendication 6, caractérisé en ce que la transmission est réalisée avec une élasticité de ressort dans au moins un organe de transmission (57) transmettant le couple entre un moyen d'entraînement (56) et un organe de sortie (58) coopérant avec le moyen de circulation (05) pour l'avance de celui-ci.
  8. Système de transport selon la revendication 6, caractérisé en ce que le moyen d'entraînement (56) entraînant le moyen de circulation (05) et/ou un organe de transmission (67) transmettant le couple d'entraînement dans la transmission sont réalisés de manière flexible et/ou limitable quant à leur couple à appliquer ou à transmettre.
  9. Système de transport selon la revendication 1, 2, 3, 4, 5, 6, 7 ou 8, caractérisé en ce qu'il est prévu un moyen (25) d'élévation, en état d'activation, de la friction entre la feuille à imprimer (01) à transporter et le moyen de circulation (05).
  10. Système de transport selon la revendication 1, 2, 3, 4, 5, 6, 7, 8 ou 9, caractérisé en ce que le dispositif de butée (09) est prévu sur un cylindre (07 ; 08 ; 24) et comprend un levier de repère (11) exécutant un premier déplacement essentiellement radial ainsi qu'un repère de marge (21) à déplacement relatif disposé sur un bras (22) du levier de repère (11) et présentant la surface de butée (12).
  11. Procédé de transport d'une feuille à imprimer (01) dans une machine à vernir et/ou à imprimer sur un dispositif de transport (04 ; 06) comprenant un moyen de circulation sans fin (05), où la feuille à imprimer (01) est convoyée par le moyen de circulation sans fin (05), réalisé sous forme de bande (05) convoyant par friction les feuilles à imprimer (01) ou de moyen de traction supportant un poussoir arrière (15), par complémentarité de forme ou par friction vers une surface de butée (12) d'un dispositif de butée (09) prévu en aval, caractérisé en ce qu'un retardement de l'avance du moyen de circulation sans fin (05) est généré sur au moins un segment de transport (65) coopérant avec la feuille à imprimer (01), du fait d'une augmentation de la résistance due au contact de la feuille à imprimer (01) contre la surface de butée (12), et se transmettant par la liaison à complémentarité de forme ou à friction au moyen de circulation sans fin (05) réalisé comme bande ou comme moyen de traction.
  12. Procédé selon la revendication 11, caractérisé en ce que le retardement est généré par un déplacement radial d'un élément de guidage (81 ; 82 ; 83 ; 84 ; 98) déterminant conjointement la course de guidage du moyen de circulation (05).
  13. Procédé selon la revendication 11, caractérisé en ce que le retardement est généré par un débattement d'un organe de transmission réalisé avec élasticité de ressort dans la transmission entraînant le moyen de circulation (05), ou par application d'une limitation de couple d'un moyen d'entraînement (56) entraînant le moyen de circulation (05) ou d'un organe de transmission (67) transmettant le couple dans la transmission.
  14. Procédé de transport selon une ou plusieurs des revendications 11 à 13, caractérisé en ce qu'un moyen (25) d'élévation de la friction est mis en service de manière à générer un relâchement ou un retardement dû à l'augmentation de la résistance par débattement ou diminution du couple d'entraînement appliqué, avant que soit atteinte une force provoquant la rupture de l'adhérence.
  15. Procédé d'utilisation du système selon la revendication 9, caractérisé en ce que le moyen (25) d'élévation de la friction est mis en service de manière à générer un débattement ou une diminution du couple d'entraînement appliqué, avant que soit atteinte une force provoquant la rupture de l'adhérence.
EP13730513.2A 2012-07-06 2013-06-12 Dispositif et procédé de transport de feuilles imprimées avec déplacement élastique Active EP2869993B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012211784.9A DE102012211784A1 (de) 2012-07-06 2012-07-06 Fördervorrichtung und ein Verfahren zum Fördern von Bedruckstoffbogen
PCT/EP2013/062125 WO2014005812A1 (fr) 2012-07-06 2013-06-12 Dispositif de transport et procédé destinés à transporter des feuilles en matière imprimée en assurant un mouvement d'avance souple

Publications (2)

Publication Number Publication Date
EP2869993A1 EP2869993A1 (fr) 2015-05-13
EP2869993B1 true EP2869993B1 (fr) 2016-11-09

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13730513.2A Active EP2869993B1 (fr) 2012-07-06 2013-06-12 Dispositif et procédé de transport de feuilles imprimées avec déplacement élastique

Country Status (5)

Country Link
EP (1) EP2869993B1 (fr)
CN (1) CN104487250B (fr)
DE (1) DE102012211784A1 (fr)
ES (1) ES2612348T3 (fr)
WO (1) WO2014005812A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209116A1 (de) * 2016-05-25 2017-11-30 Koenig & Bauer Ag Bogenleitvorrichtung für eine bogenverarbeitende Maschine sowie Verfahren zum Betrieb einer Auslagevorrichtung
WO2019072649A1 (fr) * 2017-10-13 2019-04-18 Koenig & Bauer Ag Machine de traitement de feuilles dotée d'un dispositif de transport de feuilles et procédé de transport de feuilles d'un cylindre de guidage de feuilles vers un système de transport de feuilles
DE102019122494B4 (de) * 2019-08-21 2021-09-09 Koenig & Bauer Ag Vorrichtung zum Zuführen von Bogen
DE102020102451B4 (de) 2020-01-31 2023-11-16 Koenig & Bauer Ag Bearbeitungsmaschine zur Bearbeitung eines bogenförmigen Substrats

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB268388A (en) * 1926-03-26 1928-01-05 Marinoni Machines Et Materiel Improved apparatus for feeding sheets to printing or like machines
US2699941A (en) 1949-12-15 1955-01-18 Huck Company Registering and gripper means for sheet-fed printing presses
GB748122A (en) * 1951-07-16 1956-04-25 John Ratcliff & Sons Ltd Improvements in or relating to means for feeding sheets to printing or other machines
DE944925C (de) * 1953-03-28 1956-06-28 J A Schmalbach Blechwarenwerke Vorrichtung zum Ausrichten von Blechtafeln an Lackiermaschinen
CH641114A5 (de) * 1979-10-17 1984-02-15 Grapha Holding Ag Bogenanleger.
JPS6112552A (ja) * 1984-06-29 1986-01-20 Fuji Xerox Co Ltd ベルト保持機構
GB8918175D0 (en) 1989-08-09 1989-09-20 Crabtree Gateshead Ltd A method of and apparatus for printing on metal sheets
FR2774023B1 (fr) 1998-01-27 2000-04-14 Heidelberger Druckmasch Ag Plieuse sans pointure pour machines rotatives a imprimer
FR2774024B1 (fr) 1998-01-27 2000-04-14 Heidelberger Druckmasch Ag Plieuse d'une machine rotative a imprimer
DE20000247U1 (de) * 2000-01-12 2000-03-02 Ltg Mailaender Gmbh Vorderkantenanschlagvorrichtung
DE10205488A1 (de) 2002-02-09 2003-08-21 Peter Weiss Saugriementransportsystem
DE10312153A1 (de) * 2003-03-17 2004-10-07 Ebe Hesterman Maschine für den Bogenrotationsdruck oder Bogenbeschichtung
DE10344950A1 (de) 2003-09-27 2005-04-28 Koenig & Bauer Ag Zylinder mit einem Zylinderkörper und wenigstens einem Greifer
DE102005037128B4 (de) * 2005-08-06 2009-04-23 LTG Mailänder GmbH & Co. KG Transportsystem einer Blechdruck- oder Blechlackiermaschine

Also Published As

Publication number Publication date
EP2869993A1 (fr) 2015-05-13
WO2014005812A1 (fr) 2014-01-09
DE102012211784A1 (de) 2014-01-09
ES2612348T3 (es) 2017-05-16
CN104487250A (zh) 2015-04-01
CN104487250B (zh) 2016-03-16

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