EP2869991A1 - Dispositif transporteur et procédé pour le transport de feuilles à imprimer, en particulier de panneaux rigides - Google Patents

Dispositif transporteur et procédé pour le transport de feuilles à imprimer, en particulier de panneaux rigides

Info

Publication number
EP2869991A1
EP2869991A1 EP13729936.8A EP13729936A EP2869991A1 EP 2869991 A1 EP2869991 A1 EP 2869991A1 EP 13729936 A EP13729936 A EP 13729936A EP 2869991 A1 EP2869991 A1 EP 2869991A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
stop
movement
printing material
arm
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.)
Granted
Application number
EP13729936.8A
Other languages
German (de)
English (en)
Other versions
EP2869991B1 (fr
Inventor
Stephan Gericke
Joachim Löffler
Andreas Vollmann
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.)
Filing date
Publication date
Application filed by KBA Metalprint GmbH and Co KG filed Critical KBA Metalprint GmbH and Co KG
Publication of EP2869991A1 publication Critical patent/EP2869991A1/fr
Application granted granted Critical
Publication of EP2869991B1 publication Critical patent/EP2869991B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F7/00—Rotary lithographic machines
    • B41F7/16—Rotary lithographic machines for printing on non-deformable material, e.g. sheet metal
    • 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
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F23/00—Devices for treating the surfaces of sheets, webs, or other articles in connection with printing
    • B41F23/08—Print finishing devices, e.g. for glossing prints
    • 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
    • B65H9/10—Pusher and like movable registers; Pusher or gripper devices which move articles into registered position
    • B65H9/101—Pusher and like movable registers; Pusher or gripper devices which move articles into registered position acting on the edge of the article
    • 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
    • B65H2404/26—Particular arrangement of belt, or belts
    • B65H2404/264—Arrangement of side-by-side 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
    • 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 according to the preamble of claim 1 or a method for conveying printing material, in particular a printing material, according to the features of claim 12.
  • EP 0 412 720 B1 discloses a device and a method for printing metal plates, wherein a metal plate to be printed can be fed into the nip point of a printing unit by feed means. In order to guide the metal plate with respect to position relative to the printing cylinders in register through the nip, is on
  • Pressure cylinder provided a brand lever with a stop surface, 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.
  • 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.
  • pivotable lever at two spaced in the longitudinal direction of the brand lever Points is articulated. These levers are each correlated via cam means to
  • the cam means and the shape and articulation of the brand lever are designed such that the abutment surface substantially on a
  • EP 1 678 066 B1 relates to a gripper cylinder in the folder of a
  • EP 0 931 748 A1 also 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.
  • a drive of gripper elements of a cylinder in the folder of a printing machine is also known, wherein the gripper elements are mounted radially movable on a pivotable carrier via a sliding or slide guide.
  • a sliding or slide guide is about the guide.
  • the entry and exit movement and the pivoting movement are each controlled by control cams.
  • 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 by the fact that due to a difference in speed between a suction belt and application marks the panel leading edge until closing the gripper system permanently against the
  • a printing machine for sheet material being provided on a counter-pressure cylinder a brand lever with stop means for the leading edge of the printing material sheet.
  • the stop means are to adjust the correct relative position of the sheet on the brand lever along the
  • Direction of movement of the sheet can be positioned by means of a motor.
  • the setting of the stop means can also take place during the printing operation.
  • US 2,699,941 A relates to a printing machine for printing rigid sheet-like substrates, wherein a printing cylinder comprises register elements.
  • the register elements are designed claw-like at their end acting together with the printing material, projecting out of the cylinder circumference.
  • the gripper-shaped end In order for the gripper-shaped end to carry out a tangential movement component in addition to a pure up / down movement, it is pivotably mounted on two circumferentially spaced locations on couplings, wherein one of the couplers is positively driven in rotation via a cam gear for cylinder rotation.
  • the invention is based on the object, a conveyor device and a method for Conveying of substrate to create, in particular a Beyakstofftafel.
  • the advantages which can be achieved with the invention are, in particular, that low acceleration values when a printing material sheet, in particular a printing material panel, is applied to the registration mark and thus a particularly smooth running, are made possible.
  • Circumferential speed of the bearing device bearing cylinder corresponds.
  • a guided and continuous braking is possible, whereby a bouncing effect is avoided.
  • this allows the reduction of jounce 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.
  • substrate material in particular printing material panels, also less rigid panels, in particular, in addition to thicker metal panels (eg> 0.1 mm or even greater than 0.3 mm) also metal panels of low thickness, eg. B. sheets with a thickness of, for example, ⁇ 0.1 mm) or sheets of other sensitive material (such as plastic, wood or cardboard boards) without damage aligned on the system and the processing unit, eg. B. a printing or coating unit, be supplied.
  • An early “clamping" of the incoming sheets between a pushing force exerted by the conveyor line, for example spring-loaded drawers and / or frictional forces applied by magnets or negative pressure, and mark leads to a calming of the sheet or board run.
  • the stop device is formed with a moving, but "hard”, stop defined with respect to the longitudinal register in an advantageous development, this stop device cooperates with a conveyor having means which - at least for a limited movement phase Limit the force acting on the substrate for the feed force. Although for the leading edge 13 expediently a respect.
  • the register "hard” stop is provided by the at least within certain limits “soft” feed from the side of the conveyor the risk of bouncing or even a deformation of the printing material sheet is reduced.
  • 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.
  • Fig. 1 a stop device having a cylinder with upstream
  • Fig. 2 is a stop device having a cylinder with upstream
  • 3 shows an embodiment of a cylinder with a stop device
  • 4 shows a first embodiment for the coupling of the movement of an application mark to the movement of the brand lever.
  • Fig. 5 shows a second embodiment for coupling the movement of an application mark to the movement of the mark lever
  • FIG. 6 shows a sequence of snapshots a) to d) for the movement of the
  • Fig. 7 is an application diagram for the movements of the brand lever and the
  • FIG. 8 shows a printing unit with stop device and upstream conveyor
  • Fig. 1 1 is a detail view of the conveyor of FIG. 10;
  • FIG. 12 shows an embodiment variant for a conveying device with feed limitation of the circulating medium by torque limitation
  • Fig. 13 shows a further embodiment for a conveyor with
  • Fig. 14 shows a variant for a conveyor with feed limitation of the circulating means by deflection of the traction means course
  • Fig. 15 shows a further embodiment for a conveyor with feed limitation of the circulating means by deflection of the
  • Fig. 16 shows a further embodiment for a conveyor with
  • Fig. 17 shows a further embodiment of a conveyor with
  • Fig. 19 is a schematic sectional view of a cooperating with a perforated belt vacuum chamber.
  • a printing material 01 preferably as a printing material 01 formed substrate sheet 01 machined machine, in particular pressure and / or
  • Varnishing machine substrate sheet 01, preferably printing material panels 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 Bedruckstofftafel 01, provided.
  • Stop device 09 pressed.
  • the conveyor 04; 06 comprises at least one printing material 01 conveying 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.
  • circulating belts 05 formed circulating means 05, on which or which of the printing material 01 in the transport direction by positive engagement with a band 05 or one different, also circulating
  • Traction means arranged and acting on the trailing end of the printing material 01 stop 15, z. B. rear thrust 15, or by adhesion (friction) with the band system by only the weight or supported by
  • 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.
  • Stop device 09 having cylinder 07; 08 working together
  • Conveyor 04; 06 preferably 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 the feed force on the printing material sheet 01 limiting means can -. B. depending on the nature of the funding - in principle be realized in different ways (see also below to Fig. 10 to Fig. 18).
  • 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 exhibiting tape system and in Fig. 2 with a the 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), through which the substrate sheet 01 formed in particular as substrate sheet 01 on at least one side can be printed or painted is. It can in a 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 may be provided.
  • 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 conveyor line and / or in the entrance area of a processing unit 03 in the manner of a contact cylinder 08 and a feed drum 08 and / or as
  • Function part of a processing unit 02 with stop device 09 For example, as 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.
  • Bescherstofftafeln 01 in the preferred here sense are z. B. in contrast to thin sheets of paper, for example, characterized in that they are based on their in
  • Transport direction extending longitudinal extent a significantly higher flexural rigidity and / or a higher basis weight of z.
  • metal sheets 01 for example, from Weisblech 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. in o. G. Are formed bending stiff.
  • 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 am
  • 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 1 1 with a stop surface 12, preferably several, z. B. two, axially from each other
  • Movement component between a first and a radially spaced from the first layer second layer is movable. In the second situation that occurs
  • Stop surface 12 bearing free end preferably further from 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 1 1, z. B. so-called. Brand lever 1 1, can basically be formed in any way, in
  • Stop surface 12 bearing free end with at least one radial
  • Movement component between an inner and an outer layer can be realized or realized.
  • the z. B. designated as a brand lever 1 1
  • Supporting means 1 1 mounted in a guide and be movable in this guide along a straight line or along a curved path back and forth, wherein at least one, in particular predominant, radial path or
  • the stop means 1 1 is designed as a brand lever 1 1 in the manner of a pivotable lever, wherein the radial movement of the free,
  • the correlated with the cylinder rotation drive the brand lever 1 1 and the shaft 14 can in principle via a mechanically independent of the cylinder rotation
  • the correlated with the cylinder rotation drive the brand lever 1 1 and the shaft 14 but via a cam gear 16, which, for example, together with the or the brand lever 1 1 supporting shaft 14 and possibly further
  • Pillars forms the first drive mechanism. This rolls z. B. a at the free end of a shaft 14 rotatably connected to the lever 17 arranged roller 18 on a spatially fixed cam 19 from whose shape during rotation of the cylinder 07; 08 on the roller 18, the lever 17 and the shaft 14, the up and down movement of the brand lever 1 1 specifies.
  • 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.
  • lever 1 1 stop means 1 1 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 , B. lever arm 22, and arranged by a (second)
  • Drive mechanism 23 is forcibly drivable with respect to its movement relative to arm 22 periodically and / or in correlation to the movement of arm 22.
  • the stopper element 21 having brand lever 1 1 is thus a total of a first drive mechanism with at least one, in particular one
  • 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 1 1, but is part of a stop element 21, which in turn is arranged movable relative to the stop means 1 1 and also periodically
  • the stop element 21 is on the brand lever 1 1, z. B. on the arm 22, arranged so relatively movable and / or is or is by the second
  • Drive mechanism 23 driven in such a way or drivable formed that it in at least one phase, in which it with the edge 13 of a conveyed
  • Substrate sheet 01 comes into contact, but the printing material 01 preferably still not on the cylinder 07; 08 (24) accumulated, the brand lever 1 1 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 1 1 and the drive mechanisms (23) for the arm 22 and the stop element 21 are coordinated with one another such that the stop element 21 located in contact with the printing material sheet 01 is in
  • Movement direction of the printing material 01 moves.
  • Theden stop element 21 is hereinafter also referred to as vor putbare or vor putnde stop device 09.
  • the periodic drive of the stop element 21 can in principle also for Cylinder rotation correlated and, if necessary, be 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
  • Cam gear with a roller and a lever connected to the stop element 21 forms the second drive mechanism 23.
  • 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 1 1 (brand lever 1 1) and its arm 22 in conjunction with a cylinder-fixed linkage (eg. via a coupling 28 or a cam gear 32, see below to Fig. 4 and Fig. 5) causes.
  • the relative movement of the stop element 21 can basically along
  • Movement direction of the first movement is different and a (significant)
  • a z. B. for the first movement counter-rotating pivoting movement about a mark lever fixed pivot axis may be provided, which counteracts, for example, the above-mentioned sinusoidal tangential velocity profile.
  • a Translation 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 1 1, 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 is given by a coupling 28, which on the one hand via, for example, 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 element 21 is supported via the coupling 28.
  • roller 34 includes, which with a via, for example, a pin 31 or in other Way at 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 1 1.
  • the coupling is further a spring element 27, for example a
  • Stop element 26 experiences.
  • the spring element 27 attacks this z. B. directly or indirectly on the arm 22 of the stop means 1 1, 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.
  • 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.
  • Embodiment represents, the stop element 26 in the effective range, ie in the relevant curve section or segment, not with a circular ring portion-shaped Contour, but one of these deviating contour formed. This contour of cooperating with the roller 34 during a cycle of motion
  • Curve portion of the stop member 26 is formed, for example, in the manner of irregular curvature that as a result of the superposition of
  • Stop element 26 a desired motion profile is modeled.
  • a movement with respect to the tangential direction can be constant
  • Movement with at least partially decreasing speed required and / be generated 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.
  • Brand lever 1 1 trained stop means 1 1 is z. B. arranged by a clamping connection 39 torsionally rigidly on the shaft 14, wherein the clamping connection 39 by a
  • Spring element z. 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.
  • gripping elements 36, z As gripper tips 36, be provided, which protrude in the tangential direction beyond the stop surface 12 and in the phase of lowering of the stop element 1 1 on the at the Press stop surface 12 adjoining substrate sheet 01.
  • grippers 37 may be provided, which in contrast to the possibly additionally gripper tips 36 having stop means 1 1, z. B. does not have an aligning, but only holding function.
  • the direction of rotation D of the cylinder 07 (08) is here, such. B. from Fig. 6a, as assumed counterclockwise. Also recognizable z. B. the cooperating with the roller 18 cam 19, the stop means 1 1 bearing shaft 14, a (pure) gripper 37 in the foreground, and partly conceals a designed as a brand lever 1 1 stop means 1 1 with the arm 22 and the stop surface 12 having, here rectilinearly movable stop member 21 and the cylinder-fixed coupling, here by way of example to a cylinder-fixed
  • Stop element 26 (see, for example, 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 Cylinders 07 (08) are matched to one another such that in the movement phase of the cylinder 07 (08) after the delivery of a previous panel 01 and before contact with a panel 01 to be applied first, the brand lever 1 1 by the first movement, in particular by pivoting, a total of continues to emerge from the cylinder peripheral surface 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.
  • the stop surface 12 occurs z. B. already in an angular position ⁇ between 65 ° and 55 ° in the trajectory B T of the panel 01 (see, for example, Fig. 6a).
  • the stop means 1 1 additionally has a hook tip 36 and should serve as a gripper 37, penetrates the stop means 1 1 with your hook tip 36, the trajectory B T to a height above the male 01 and to be taken in the course, for example on a straightforward, 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.
  • the inclined movement can be replaced by a linear trajectory parallel to the trajectory B T of the table O1, preferably by a movement in the trajectory B T of the table O1.
  • Movements of stop means 1 1 and stop member 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 ß of the cylinder 07 (08) of z. At least 20 °, preferably at least 30 °, in particular between 35 ° and 45 ° (in the example of Fig. 6b about 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. B. substantially one of the peripheral speed of the cylinder 07 (08) corresponding speed moves.
  • the stop means 1 1 Upon reaching the zero position L 0 through the stop surface 12, it is preferably the same time to gripper closure of possibly arranged on the stop means 1 1 hook tip 36 and / or the or additionally arranged gripper 37.
  • this position ie the zero position L 0 , is located the stop means 1 1 together with the 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 is substantially (eg with a maximum deviation of ⁇ 5 °, in particular at most ⁇ 3 °) runs tangentially to the cylinder 07 (08) and / or along the path of movement B T of the panel 01 (see eg Fig. 6d).
  • FIG. 7 To illustrate the mechanism and its function is shown in FIG. 7 by way of example a schematic application diagram for the movements of the stop means 1 1 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 in the place of tangential contact of the promoted
  • Substrate sheet 01 comes to rest, which are all 360 ° in the angular position of the cylinder 07; 08 repeated.
  • the approaching printing material sheet 01 is promoted here, for example, at a constant speed, while the stop means 1 1 is still in a rest phase P r .
  • the stop means 1 1 In this angular range of Cylinder 07; 08 is the stop means 1 1 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. B. extending and / or with respect to the pivot axis remote location.
  • the stop element 21 is in its rest phase Z r relative to the arm 22 in a first position, from which it -. B.
  • the first movement, z. As the pivoting of the stop means 1 1 as a whole, and the second movement, ie the relative movement of the stop member 21 to the arm 22 of the stop means 1 1, as described in the example, simultaneously or temporally or angularly offset from each other.
  • position Li; L 2 In the angular position or at the time (position Li; L 2 ), where at least one of the two elements, for. B. due to the above-mentioned coupling of the movements at least in the situation Li, in which the arm 22, through the
  • Rotationsachsfernfernere, second location spent.
  • 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 after reaching the zero position L 0 by the first drive mechanism pivoting back of the
  • Brand lever 1 1 is initiated in the rest position. 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. 10 ° to 40 °, in their occupied in the zero position L 0 end position before being returned to the starting position and they are for the rest of the cylinder revolution to the beginning of
  • a stop device 09 exhibiting cylinder 07; 08 one or more times in the conveying path between a feeder, not shown, for. B. a stacking system, through which the to be processed substrate sheet 01 of Conveyor line can be fed, and a delivery device to which the processed printing material 01 is discharged through the conveyor line.
  • At least one printing cylinder 07 (24) forming the nip is at least one printing unit 02, in particular an offset printing unit 02, as a cylinder 07 (24) with an o. G. Stop device 09, z. B. a stop and gripping device 09 is formed. This acts with the other nip forming the cylinder 24 (07), which z. B. for the advantageous case of
  • Offset printing as a blanket cylinder 24, in particular as a blanket cylinder 24, is formed, forming the effective nip pressure point together.
  • 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. form cylinder 42, in particular
  • Plate cylinder 42 together (see eg Fig. 8). With the forme cylinder 42 acts in a conventional manner, not shown here paint applicator, z. B. an inking, together. In the case of wet offset acts with the forme cylinder 42 and a fountain solution applicator, z. As a dampening together. Blanket cylinder 24 and forme cylinder 42 are located in the color path and thus provide color leading
  • 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
  • Impression cylinder 07 is formed, which the other, ink-carrying
  • 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.
  • the first cylinder 07 represents, for example, a second transfer cylinder 07, which cooperates with a second form cylinder (not shown).
  • one of 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
  • the application cylinder 08 comprises friction-increasing in at least one circumferential region following the device 09 during operation Measures, eg. B. by a bearing force and thus the frictional force between
  • 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 can have one or more directly with the printing material sheet 01 to be conveyed
  • a printing material sheet 01 to be conveyed is then applied to the lateral surface by the magnetic force
  • non-magnetizable printing material 01 z. B. plastic, wood, cardboard or paper sheet to be pulled by a friction-increasing means 43 to the cylinder 08, as a means 43, for example, a
  • 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 be in an advantageous embodiment before or in Entrance area of editing 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.
  • editing 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, too. 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.
  • 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 can be provided as an application cylinder 08 between two conveyor sections of the machine, without direct structural or functional connection.
  • Between the respective conveyor 04; 06 and the stop or stop and gripping device 09 having cylinder 07; 08 (24) is for example a z. B. frame-fixed (in Fig. 1 and Fig. 2 and in Fig. 12 and Fig. 13), although not shown, but also here each predictable guide 44, z. B. a one or more parts guide member 45, z. B. sliding plate 45 comprehensive guide device 44, provided over which or which of the printing material 01 by the
  • Conveyor 04; 06 the cylinder 07; 08 (24) is supplied (see, for example, Fig. 8 and Fig. 9).
  • 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 printing unit 02 with a stop device 09 can each have a further development Printing cylinder 07 (24) and at least one coating unit 03 may be provided with an above-mentioned Anlegzylinder 08.
  • 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 precontrol serves the most possible impact-free and / or possible low-acceleration apply to the stop surface 12 for register-oriented alignment defined, eg at least in one
  • Stop surface 12 given, however, at any time during the
  • edge 13 forms a firmly defined "hard” stop
  • the pre-controllable stop device 09 designed in the above-mentioned manner has a stop means 1 1 which carries out a first, predominantly radial movement, and a relative movement, in particular a predominantly tangential, acting on it performing stop element 21 and / or the comprehensive such a stop device 09 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 stop device 09 and the cylinder 07 comprising them; 08 (24) but with an embodiment of the conveyor 04 described below; 06 cooperating provided, which comprises means for limiting the force acting on the printing sheet 01 for the feed.
  • 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 be configured as desired in the conveyor travel stop device 09, in particular an arbitrarily configured stop device 09
  • 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 against the resistance formed by the stop device 09 feed force at least temporarily, z. B. to a threshold, limited. When exceeded the threshold value sets a response of the agent 53; 54; 67; 56; 81; 82; 83; 84; 98 in such a way that the force applied to the on the stop device 09
  • Substrate sheet 01 does not rise any further.
  • the strength of the measure be dosed or metered so that when promoting the printing material 01 from a certain, caused by emergence of the stop means 1 1 resistance of the threshold set in this way by the strength of the static friction is exceeded.
  • this can be the point of Overcoming the stiction due to the spontaneously changing
  • Friction coefficient again lead to unwanted acceleration and / or displacements.
  • the feed force limitable conveyor 04; 06 is the feed of the substrate sheet 01 frictionally or positively promoting 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.
  • traction means eg belt, chain or belt
  • the Drive means of the circulating means 05 can deflect even for the case of a transport direction T opposite resistance increase or from a threshold value for the resistance is yielding or in a second embodiment of the Band standing. Circulating agent 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. designed such that there is at least a plausiblehub between the disturbed by resistance increase tape feed and without interference too
  • This minimum lift is z. B. several millimeters, in particular at least 2 mm, preferably at least 5 mm.
  • the operational compression or yielding is then carried out at least by a stroke in the tape feed at least the the printing material 01
  • the operationally allowable minimum stroke means a non-destructive and not in the area unintentionally permanent Material deformations lying yielding.
  • the limitation of the printing substrate 01 for the feed attacking force is thus effected in that, for example, give the drive means of the traction means or Werbachverlauf even in the case of the transport direction T opposite resistance increase, z. B. compress or in the case of the drive device z. B. "slipping" can.
  • 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 high-friction 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. In a preferred embodiment for the form-fitting based
  • the rearward thrust 15 is arranged stationary on the revolving means 05 with respect to the direction of rotation or along the direction of transport T and is made unyielding. 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 form-fitting attacking conveyor 04; 06 on the other side on the substrate sheet 01 acts, limited or limited.
  • Feed force limitable conveyor 04; 06 set out, in which the feed of the printing material 01 or friction-positively conveying circulating means 05 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 is formed.
  • Substrate sheet 01 are presented, these are equally on conveyors 04; 06 with positive force application between a on the circulating means 05th
  • Frictional-based force application between circulating means 05 and printing material sheet 01 may advantageously be provided friction-increasing means 25 or possibly -.
  • a high surface density such as metal, z.
  • metal a thickness of at least 0.5 mm - also omitted.
  • 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.
  • a drive means 56, z. B. a drive motor 56, and a cooperating with the circulating means 05 to the feed member 58, z. B. output member 58 is not entirely stiff, but - z. B. in the context of a non-zero minimum spring travel - resilient
  • a first embodiment of this first embodiment of the first group is based in 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.
  • a resilient element 54 for example, has a resiliently elastic element 54.
  • the torque is then preferably from the drive side closer link
  • the "hardness" or resilience of the feed limitation can be influenced by the choice of the stiffness or spring constant of the element 54.
  • the spring-elastic coupling or the transmission element 57 is in a defined zero position L 0 with a non-zero force, which z
  • further stops 63, 64 which are effective in the circumferential direction, are provided on the links 58, 59 and counteract the force of the prestressed spring element 54 exchangeable against a spring element 54 of other spring hardness and / or with respect to the spring characteristic variable and / or the relative position between the zero position L 0 forming stops 63; 64 variable, so can the threshold for the deflection of the drive device and thereby the threshold for the compression the feed limit of the circulating means 05 vary
  • the zero position L 0 is, for example, in the load-free operating state, for. B.
  • the spring element 54 springs.
  • 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 versus.- transmission member 57 determines.
  • the resilient member 57 is on the drive side torsionally rigid with a shaft 66, z. B. a drive shaft 66, 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, for example, in Fig. 1 the open view of the drive wheel 69 of FIG. 10).
  • the resilient member 57 is on the drive side torsionally rigid with a shaft 66, z. B. a drive shaft 66, 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, for example, in Fig. 1 the open view of the drive wheel 69 of FIG. 10).
  • a shaft 66 z. B. a drive shaft 66, and between this and a rotatably mounted on the
  • 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. as with the
  • Substrate sheet 01 this promotional cooperating band 05 formed.
  • the conveying in the transport direction T takes place here, for example, not by Schuschübe 15, but based on friction. To increase the friction, an o. G.
  • Frictional force increasing agent 25, z. As a magnet 25 or as shown advantageous a vacuum chamber 25 may be provided.
  • trained means 25 can basically in the transverse and longitudinal directions at any point be formed in the conveying section 55 the printing material sheet 01 attractive. It may be provided only on a longitudinal section of the conveyor line, wherein the distance to the stop device 09 is preferably smaller than that
  • Substrate sheet 01 is attracted to the extending between this and the means 25 belt 05.
  • the belt 05 can be advantageously designed as a so-called.
  • Vacuum belt 05 in the manner of a perforated belt 05, d. H. have a hole structure with the band 05 from below in the direction of the printing material to be conveyed sheet 01 passing holes 71, which from the the printing material to be conveyed 01 opposite side by means of z. B. formed as a vacuum chamber 25 means 25 with a negative pressure P - can be acted upon. This is due to an education of
  • 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 area, d. H. im with the
  • Substrate sheet 01 together acting area, in the transport direction T, wherein the particular flat conveyor 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
  • 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 drive means and deflection means not described in more detail here parallel to the at least one feed
  • the additional circulating means 72 may also stops 76, z. B. front stops 76 wear. 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 same conveyor 04; 06 or one of these different upstream conveyor to the stop device 09 directly upstream, the circulating means 05 exhibiting
  • Conveyor section 55 are handed over. 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 are the printing material 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 of a
  • Drive network be driven forth via a corresponding drive connection or be.
  • Circulating means 72 is or are designed to be endless.
  • the compliance is based on that in the drive train a the Rotary 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 respect.
  • 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.
  • an effective Switzerland example of the running strand against the spring force
  • a threshold can be limited. It is here z. B. even with increasing resistance, the example of a
  • first embodiment of the second embodiment of the first group (see, for example, Fig. 12) is in the drive train between the drive means 56 and the with the Circulating means 05 to the drive together acting output member 58 designed as a coupling 67 transmission member 67 is provided, the 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 coupling 67 is preferably with respect to the height of the
  • Threshold adjustable in particular at least within a control range preferably designed to be infinitely 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 - between substrate sheet 01 and circulating means 05 present static friction or selected that by running the leading edge 13 on the abutment device 09 has already reached this threshold value, which triggers the recirculation means drive, before the static friction resistance, d. H. the limit to the "demolition" of stiction, 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 used as a magnetic coupling 67, in particular as
  • Magnetic powder clutch formed.
  • a coupling 67 designed as a compressed air coupling 67 can also be used for this purpose.
  • the drive means 56 designed as a drive motor 56 can be limited in terms of the drive torque provided by the drive motor 56.
  • 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.
  • Resistance increase can spring in a radial direction or can, and hereby at least temporarily a feed limit of the circulating means 05 in
  • Guide section 65 of the conveyor section 55 causes or effect.
  • Circulation medium course is caused by deflection.
  • Guide portion 86 is thus compliant with respect to the route length. As a result of the shortening 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.
  • downstream guide section 86; 87 yielding or spring-mounted
  • Deflecting elements 83; 84, z. B. pulleys 83; 84 with respect to a radial direction linearly movable 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 deflects this guide portion 86 against a possible shorter course to a longer course out and vice versa with the trailing guide portion 87 cooperating pulley 82 shortens the trailing guide portion 87 against a possible longer course.
  • Spring force limiting stop provided by which the spring element already unfolds a spring force in zero position L 0 of the carriage 88 and thus defines a non-zero 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. Corresponding to this is in the trailing
  • Conveyor section 86 by means of deflection of the lever 89 freed Umlaufsch- or strip length extended.
  • the pivotal movement of the lever 89 against the spring force limiting stop 96 is provided by which the spring element 94 already unfolds in zero position L 0 of the lever 89 a non-zero spring force and thus caused a non-zero threshold for the caused by an increase in resistance Deflection is defined.
  • the in the trailing Guide portion 87 resiliently arranged guide roller 84 may be formed in the manner of a spring-loaded belt tensioner.
  • Circulation means guide by at least one guide or deflecting elements 81; 82, which relates to the length and / or location of the conveyor area
  • At least the output-side deflection roller 81 is running with at least one along the transport direction T.
  • the output-side guide roller 81 is resiliently mounted in the aforementioned manner by being mounted eccentrically on a lever 93 pivotable about a pivot axis 92.
  • 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.
  • Drive forward relevant guide portions 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 Einfederkraft between the output side guide roller 81 and drive wheel 69 via one or more fixedly arranged guide or deflecting elements 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 circulation means deflection roller 98.
  • pivoting the lever 97 is as above the total length of the
  • the output-side guide roller 81 is linearly movable, in particular parallel to the transport direction T, stored. For example, fixed to the frame
  • 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.
  • Actuation of the designed as a vacuum chamber 25 friction increasing means 25 with negative pressure P ⁇ can a frame fixedly arranged connection piece 107th
  • 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.
  • An opening 1 1 1, z. B. nozzle opening 1 1 1, 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.
  • the suction side of a pump a turbine or a fan connected.
  • the P connection of the movable vacuum chamber 25 may be fixedly connected to a flexible hose, so that the movement of the
  • Fig. 18 are schematically for different operating situations and associated load conditions, the positions of the carriage 103 from the third
  • 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. Compared to the third embodiment, this differs functionally only in that the friction-increasing means 25, z. B. the vacuum chamber 25 is arranged fixed to the frame.
  • the stopper 96 to be provided for the spring element 104, a stop 96, which may be provided according to the second variant, and the trailing roller 84, which is mounted in the drive, are trailing in the drive
  • a vacuum chamber 25 has at least one opening 91, for example, on the side to be transported to the printing material sheet 01 and / or the circulating means 05.
  • a negative pressure P prevailing in the vacuum chamber 25 - acts on the supported printing material sheet 01 on the
  • Circulating means 05 attractive.
  • 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.
  • Substrate sheet 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 , LIST OF REFERENCE NUMBERS

Abstract

L'invention concerne un dispositif transporteur pour le transport de feuilles à imprimer (01) dans un vernisseur (03) - et/ou une machine d'impression (02), comprenant un cylindre (07, 08, 24) présentant un moyen d'arrêt (11), et un dispositif transporteur (04) présentant un moyen rotatif (05), monté en amont du cylindre, dans la trajectoire de transport, le moyen d'arrêt (11) pouvant être entraîné de façon forcée, montant et descendant, par un premier mécanisme d'entraînement (16), en corrélation avec la rotation du cylindre (D), par au moins son extrémité éloignée du côté entraînement, radialement entre une première position rétractée, et une seconde position, différente radialement de la première position, le moyen d'arrêt (11) portant, dans la zone de son extrémité éloignée du côté entraînement, un élément d'arrêt (21) comprenant une surface d'arrêt (12), qui est monté, déplaçable, sur un bras (22) dudit moyen d'arrêt (11). L'élément d'arrêt (21) est configuré de manière à pouvoir être entraîné, de façon forcée, par un second mécanisme d'entraînement (23), en corrélation avec la rotation du cylindre (D) et/ou avec le mouvement du bras (22), de façon relativement mobile sur le bras (22).
EP13729936.8A 2012-07-06 2013-06-12 Dispositif de transport et procédé de transport de feuilles imprimées, notamment de feuilles rigides Not-in-force EP2869991B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012211783.0A DE102012211783A1 (de) 2012-07-06 2012-07-06 Fördervorrichtung und ein Verfahren zum Fördern von Bedruckstoffbogen
PCT/EP2013/062120 WO2014005811A1 (fr) 2012-07-06 2013-06-12 Dispositif transporteur et procédé pour le transport de feuilles à imprimer, en particulier de panneaux rigides

Publications (2)

Publication Number Publication Date
EP2869991A1 true EP2869991A1 (fr) 2015-05-13
EP2869991B1 EP2869991B1 (fr) 2016-11-09

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EP13729936.8A Not-in-force EP2869991B1 (fr) 2012-07-06 2013-06-12 Dispositif de transport et procédé de transport de feuilles imprimées, notamment de feuilles rigides

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EP (1) EP2869991B1 (fr)
JP (1) JP5866069B2 (fr)
CN (1) CN104703799B (fr)
DE (1) DE102012211783A1 (fr)
ES (1) ES2612346T3 (fr)
WO (1) WO2014005811A1 (fr)

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CN107323079B (zh) * 2017-08-14 2023-02-17 上海瑞源印刷设备有限公司 印铁机铁板等牙调节定位装置
DE102017222316A1 (de) * 2017-12-08 2019-06-13 Koenig & Bauer Ag Substratzufuhreinrichtung
DE102018126049B4 (de) 2018-10-19 2020-08-27 Koenig & Bauer Ag Tafelförmiges Substrat verarbeitende Maschine mit einer Anlage, Verfahren zum Einrichten und Verfahren zum Betreiben einer Anlage
DE102018130149B4 (de) 2018-11-28 2020-08-27 Koenig & Bauer Ag Anlage für eine tafelförmiges Substrat verarbeitende Maschine und Verfahren zum Betreiben einer Anlage
DE102020111752A1 (de) 2020-04-30 2021-11-04 Koenig & Bauer Ag Vorrichtung und Verfahren zum Zuführen von flächenförmigen Gütern zu einer Bearbeitungseinheit
DE102021105082B4 (de) 2021-03-03 2024-01-04 Koenig & Bauer Ag Vorrichtungen und Verfahren zum Zuführen von flächenförmigen Gütern zu einer Bearbeitungseinheit
DE102021117587A1 (de) * 2021-07-07 2023-01-12 Focke & Co. (Gmbh & Co. Kg) Verfahren und Vorrichtung zur Handhabung von Zuschnitten aus Verpackungsmaterial
CN114280465B (zh) * 2022-03-04 2022-05-13 武汉普赛斯电子技术有限公司 一种应用于芯片测试设备的平台移动装置

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Publication number Publication date
EP2869991B1 (fr) 2016-11-09
DE102012211783A1 (de) 2014-01-09
WO2014005811A1 (fr) 2014-01-09
JP2015522453A (ja) 2015-08-06
JP5866069B2 (ja) 2016-02-17
ES2612346T3 (es) 2017-05-16
CN104703799A (zh) 2015-06-10
CN104703799B (zh) 2016-09-28

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