EP2869991A1 - Conveying device and method for conveying printed sheets, in particular rigid panels - Google Patents

Abstract

The invention relates to a conveying device for conveying printed sheets (01) in a coating machine (03) and/or printing machine (02), comprising a cylinder (07, 08, 24) which has stop means (11) and comprising a conveying device (04) which is arranged upstream of the cylinder in the conveying path and which has circulating means (05). A first drive mechanism (16) correlated with the cylinder rotation (D) can forcibly drive at least one stop means (11) end, which is remote from the drive side, up and down in a radial manner between a first retracted position and a second position which is radially different from the first position. The stop means (11) has a stop element (21) comprising a stop surface (12) in the region of the stop means end remote from the drive side, said stop element being mounted on an arm (22) of the stop means (11) such that the position of the stop element can be changed. The stop element (21) is designed to be forcibly drivable on the arm (22) so as to be relatively movable by a second drive mechanism (23) correlated with the cylinder rotation (D) and/or the movement of the arm (22).

Description

 description

CONVEYING DEVICE AND A METHOD FOR PROMOTING PRESENTING ARC, IN PARTICULAR STEEL TABLE

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. To counteract the adverse effect resulting from the superposition of the rotation of the cylinder and the phase-wise opposite

Component of pivotal movement of the brand lever results, the pivot axis is located outside the peripheral profile of the cylinder. The swiveling

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.

In US 2,699,941 A a stop device is disclosed with a brand lever, which is not pivotable about a cylinder-fixed axis, but over two

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

Cylinder rotation driven and cause a different from a pure pivoting movement of the provided at the free end of the brand lever

Stop. The cam means and the shape and articulation of the brand lever are designed such that the abutment surface substantially on a

involute path moves.

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 is

Collaboration of the lever, the axis of the gripper arm as such shifted in the radial direction. 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. 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.

From DE 198 57 507 A1 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. About the guide is a retraction and extension of the gripper elements carrying carrier. The entry and exit movement and the pivoting movement are each controlled by control cams.

From 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

Positioning is pushed, the Belachtafel is attracted by a clocked activated vacuum against the suction belt.

From a brochure of the company. KBA MetalPrint GmbH from 201 1 to a metal stamping machine of the type MAILÄNDER 222 a conveying path in a printing unit is known, which comprises a relative to the upstream conveying direction inclined conveyor section.

By the US 5,253,583 A a printing machine for sheet material is known, 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. 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 Bedruckstofftafel.

The object is achieved by the features of claim 1 and 12, respectively.

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.

In the case of a relation to the peripheral speed of the cylinder greater feed rate of the conveyor line, it is also possible by the conditioning device in development, which extends along the transport direction

Brand movement on their way to vary so that they are essentially the feed speed of the conveyor line and in the region of the Nippstelle essentially the. For the area of the first contact lying before the nip

Circumferential speed of the bearing device bearing cylinder corresponds. As a result, a guided and continuous braking is possible, whereby a bouncing effect is avoided. At initial contact or at the O-point (eg at gripper closure) 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.

By avoiding abrupt deceleration, it is possible to use as 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.

In a particularly advantageous embodiment, a first contact between investment brand and substrate early, d. H. clearly before the zero position and / or Nippstelle done, z. B. to a second point 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. 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.

Bouncing effects, d. H. shock-like touches between brands and Hinterschüben and possibly side thrusts are greatly reduced in this way, which is beneficial to the

Registration accuracy and production safety. An otherwise possibly necessary precontrol of rear thrusts on the funding of the upstream funding, z. B. a feed frame, can be omitted. Instead, only a simple feedback control of possibly provided thrusts can be provided, the z. B. after the gripper closure, d. H. after fixation of the sheet or the panel by additionally provided gripper and / or by simultaneously executed as a gripper brand lever, provides for a distance between any existing thrusts and the panel trailing edge.

Although 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.

In a development, 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. As a result of the stiffening in the transverse direction at the same time 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.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below.

Show it:

Fig. 1 a stop device having a cylinder with upstream

 Conveyor of a first embodiment;

Fig. 2 is a stop device having a cylinder with upstream

 Conveyor of a second embodiment;

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;

6 shows a sequence of snapshots a) to d) for the movement of the

 Brand levers and the application mark;

Fig. 7 is an application diagram for the movements of the brand lever and the

 Registration mark;

8 shows a printing unit with stop device and upstream conveyor;

9 shows a coating unit with feed drum and upstream conveyor;

10 shows a variant for a conveyor with feed limitation of the circulating means by a spring-loaded drive device;

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.

Fig. 13 shows a further embodiment for a conveyor with

 Feed limit of the circulating medium by torque limitation;

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

 Zugmittelverlaufs;

Fig. 16 shows a further embodiment for a conveyor with

 Feed limitation of the circulating medium by deflection of the

 Zugmittelverlaufs;

Fig. 17 shows a further embodiment of a conveyor with

 Feed limitation of the circulating medium by deflection of the

 Zugmittelverlaufs;

18 is a schematic representation of different operating situations for the

 Laying a carriage from the embodiment of FIG. 17;

Fig. 19 is a schematic sectional view of a cooperating with a perforated belt vacuum chamber.

In 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. In order to ensure register-related processing with respect to the longitudinal register, 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.

By interaction of the printing material 01 promoting conveyor 04; 06 with the stop device 09 of the printing material 01 is the latter

created in accordance with the register and, if necessary, aligned correctly in the event of an inclination. For this purpose, or is the cylinder 07; 08 directly upstream conveyor 04; 06 preferably at least temporarily with respect to the peripheral speed of the cylinder 07; 08 operated higher feed or conveying speed. By, for. B. at least temporarily, higher feed rate is a leading edge 13 of the printing material 01 at least one stop means 1 1 of

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. B. 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

friction-increasing measures, eg. B. by a bearing 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. Preferably, the effect of the means 25 is variable and / or designed to be activated and deactivated.

To after the initial contact, a deformation of the printing material 01 by the To avoid divergent speeds is the with the

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).

By way of example and representative of possible embodiments of the 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.

As already explained, 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. Thus, such a, 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. The substrate sheet 01 or

Bedruckstofftafeln 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. 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 over such rollers and cylinders, possibly under

slight deflection and / or possibly a negligible wrap, z. B. less than 20 °, are transported only substantially straight. As panels 01 in this sense, therefore, in addition to the preferred embodiment as metal panels 01, z. B. metal sheets 01, for example, from Weisblech or aluminum sheet, and panels 01 made of more sensitive material such. As 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. Where not explicitly differentiated below, 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

Cylinder circumference substantially tangentially rolls, in particular does not apply to a significant peripheral 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 1 1 with a stop surface 12, preferably several, z. B. two, axially from each other

spaced stop means 1 1, which in the manner by a first

Drive mechanism periodically and / or correlated to the cylinder rotation are movable, so that a stop surface 12 carrying end along a defined first trajectory with at least one with respect to the cylinder 07; 08 radial

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

Cylinder 07; 08 and driven by a first drive mechanism, provided that the o. G. periodic and / or correlated movement of the

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. For example, 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

Movement component is provided. Preferably, 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,

Drive side distant Endes between the first and the second position preferably by pivoting the brand lever 1 1 to a parallel to the cylinder axis, advantageously lying within the circumferential axis axis A, in particular a cylinder-fixed axis A, takes place. For this purpose, the brand lever 1 1 or the two brand lever 1 1 can be rotationally fixed to a shaft 14, in particular a pivotally mounted but cylinder-mounted shaft 14 may be arranged. Exemplary and representative of the possible versions of the cylinder 07; 08 (24, see below) is in Fig. 3, the cylinder 07 in the

Version shown as a printing cylinder 07.

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

Drive means done, the correlation here then z. B. can be realized by electronic or circuit technology.

However, 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.

As a result of the sinusoidal velocity profile of the image projected on the trajectory B _T motion of a rotating with constant circumferential speed cylindrical fixed cylinder jacket point on the one hand, and the superimposed a constant cylinder rotation movement of the free end of the along the first path of movement (e.g., pivoting movement.) Relative to the cylinder 07; 08 moving stop means 1 1 on the other hand, learns the free end, and with this the stop surface 12, without further measures a projected onto the trajectory B _T non-uniform movement. The resulting negative influences on the conveying behavior of panel 01 can only be reduced under these conditions by reducing contact between abutment surface 12 and leading edge 13 over as short a route as possible, preferably to the area of the contact point with a tangential trajectory B _T.

However, this is contrary to a goal pursued here, the table 01 to be supplied as early as possible and on a significant, in particular as large as possible

Track section, 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. In this case, should be moved at a substantially constant speed along the movement path B _T or be on this section of the current effective part of the stop surface 12, which preferably the peripheral speed of the cylinder 07; 08 corresponds.

In order to make this possible or at least to come as close as possible to this goal according to the invention, in particular designed as a brand 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

predominantly, radial component, periodically and / or in correlation to

Cylinder rotation movable or moved, in particular pivotable, wherein the stop surface 21 having stop member 21 itself on the brand lever 1 1, in particular in the region of the free end, relatively movably supported 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.

In the present context, 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. Conversely, 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

is forced or is.

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

The formation of the 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

Circumferential direction of the cylinder 07; 08 (24) considered in the direction of rotation or in

Movement direction of the printing material 01 moves.

An inventively executed stop device 09 with a type mentioned in a first, predominantly radial movement exporting stop means 1 1 and one on this one, in particular predominantly tangential, relative movement ausübenden stop element 21 is hereinafter also referred to as vorsteuerbare or vorsteuernde 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.

Preferably, however, 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 1 1, in particular of the arm 22, which correlates with the rotational movement, to the rotational movement of the cylinder 07; 08 (24) is coupled.

In the case of 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 spatially fixed cam, which in the manner of

Cam gear with a roller and a lever connected to the stop element 21 forms the second drive mechanism 23. In a preferred embodiment, however, 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

different trajectories B _R take place, provided that this of the

Movement direction of the first movement is different 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 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. Likewise, 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.

In an illustrated and preferred embodiment, 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 .

Under the zero position L ₀ is on the axis of rotation of the cylinder 07; 08 (24) related angular position to understand, to which the radius of the cylinder 07; 08 (24) and the transport direction T _{0 of} the panel 01 at the contact point (or the axially extending contact line) with the cylinder 07; 08 (24) are perpendicular to each other. In the event that the panel 01 does not touch the cylinder approximately on a line of contact, but by elastic and / or compressible deformation of the cylinder surface and / or by slight deflection of the panel 01 in a small angular range, as a zero position L ₀ which halves this angular range Location to be understood. In the event that the first cylinder 07 with another cylinder 24, z. B. a printing cylinder 24, forms a Nippstelle on the printing material to be funded 01 or Table 01, the zero position L _0, for example, with the axes of rotation of the two cylinders 07; 24 connecting line together.

Basically, regardless of the specific expression of the second trajectory B _R , but preferably in conjunction with their rectilinear expression includes the relative movement of the stop element 21 inducing gear 23 and der second drive mechanism 23, which takes place via a single or multi-member connection articulation of the stop element 21 to a cylinder-fixed abutment 26; 31, so that upon movement of the stop member 21 supporting stop means 1 1, the stopper member 21 on the cylinder-fixed abutment 26; 31 is supported.

In a first embodiment, the coupling between a point of the

Stop element 21 and the effective for the cylinder-fixed articulation point a fixed (effective) coupling length I on.

In a respect to a mechanically little expensive advantageous first

Embodiment of this first embodiment, 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 cylinder-fixed axis of rotation, d. H. the center of the pin 31 and the shaft 31, spaced from the cylinder axis and spaced from the pivot axis of the brand lever 1 1. The shaft 31 is in this case as an abutment 31 against which the stop element 21 is supported via the coupling 28. By moving, in particular pivoting of the entire stop means 1 1, in particular the brand lever 1 1, or its arm 22 z. B. spaced from the pivot axis of the brand lever 1 1 hinged stop element 21 by the coupling to the o. G. Forced relative movement.

In an alternative embodiment of the first embodiment, the coupling or

Linkage given by a cam gear 32, which on the one hand an over

For example, a pin 33 or a shaft 33 rotatably 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 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. By the radii of the roller 34 and the annular ring (section) shaped stop element 26 is given an effective coupling length I. In order to achieve a mutual effect of the coupling, the coupling is further a spring element 27, for example a

Compression spring 27, assigned by which the roller 34 is a force in the direction

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. Instead of a compression spring 27 can be found under consideration of the direction of force and a tension spring application. Preferably, 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. By moving, in particular pivoting of the entire stop means 1 1, in particular the brand lever 1 1, or its arm 22 z. B. spaced from the pivot axis of the brand lever 1 1 hinged stop member 21 formed by the biased cam gear 32 coupling to the o. G. Forced relative movement.

In a second, not explicitly illustrated embodiment, which, for example, an advantageous development of the second embodiment of the first

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

Movements of the entire lifting means 1 1 and the movement of the

Stop element 26 a desired motion profile is modeled. For example, a movement with respect to the tangential direction can be constant

Movement of the abutment element 21 located stop surface 12 or a

Movement with at least partially decreasing speed required and / be generated. On the other hand, 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.

In the embodiment of the relative movement along a rectilinear trajectory B _R , 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. as

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. In the latter case, preferably on the stop means 1 1, in particular on the stop element 21, 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. Instead or in addition, however, axially spaced on the same shaft 14 or on a separately provided and similarly forcibly driven shaft one or more 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.

In the following (see, for example, Fig. 6a to d), the function and the movement of the above-described stop means 1 1 based on a sequence of snapshots for the case of a trained with hook tip 36 stop means 1 1 and additional gripper 37 set forth, wherein relevant bodies for possible deviations in the case of training without gripper tip 36 is referred to as a pure sling 1 1. The explanation will further be made using the example of a printing cylinder 07

trained cylinder 07, but is also applied to other arranged in the conveying cylinder 08 with stop device 09 apply.

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 α 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. already in an angular position α between 65 ° and 55 ° in the trajectory B _{T of} the panel 01 (see, for example, Fig. 6a). In the event that 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 δ 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 1 1 is formed without a gripper function, 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.

To ensure a good and quiet guidance of Table 01, the two are

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.

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. In 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).

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.

For the example, 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 . 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. 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. 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. 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

corresponding drive mechanism is moved from its rest position, the working phase P _{a of} the stop device 09 begins. In this is the particular as

Brand lever 1 1 trained stop means 1 1 from a in the rest position

withdrawn, d. H. with its free end rotation axis closer, first position by the first, caused by the first drive mechanism first movement in an extended, d. H. with its free end with respect to the cylinder 07; 08

Rotationsachsfernfernere, second location spent. At the same time or this offset the particular designed as a landing mark 21 stop element 21 from a z. B. extended in the rest position, d. H. with its free end schwenkachsferneren, first position by the second, effected by means of the second drive mechanism 23 second movement, in particular linear movement, in a respect to the arm 22nd

retracted and / or spent in a respect to the circumferential direction in the direction of rotation D further forward and / or pivot axis closer, second position. During the working phase P _a , it comes in a certain angular position ß

Initial contact L _K between the stop element 21 and the particular as

Bedruckstofftafel 01 trained substrate sheet 01. This contact is -. 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., In at least part of the working phase P _a , in particular during contact with the printing material 01, 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.

In the event that the stop element 1 1 has a hook tip 36 and / or that an additional gripper 37 is provided, this closes at the latest when reaching the zero position L ₀ .

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. In a variant shown 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

subsequent working phase P _{a are} in their resting phase P _r .

As already indicated, 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.

In a particularly advantageous embodiment, 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. In the case of direct printing, 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

Printing cylinder 24; 42 dar.

The device 09 can in principle at one of the two pressure point forming printing cylinder 07; 24 provided. In the case of 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. Preferably, it is provided in the case of the single-sided printing unit 02 on the printing cylinder 07. For the case of a printing unit 02 printed on both sides of the printing material sheet 01, the first cylinder 07 represents, for example, a second transfer cylinder 07, which cooperates with a second form cylinder (not shown). Here, 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.

In another advantageous embodiment, 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. Preferably, 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 material 01 and can in an embodiment, not shown on the printing material 01 to their secure support with a roller or rollers as abutment

interact.

In an embodiment set forth here, 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.

For example, in the preferred case metallic printing material sheet 01, z. As 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

cooperating magnets or one or more of the lateral surface of the cylinder 08 in this segment of magnetizing inside magnets. A printing material sheet 01 to be conveyed is then applied to the lateral surface by the magnetic force

used.

In an alternative embodiment, in which also 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

Device for generating a negative pressure P - provided, wherein 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.

Although in the aforementioned embodiments with a frictional force between the substrate sheet 01 and lateral surface increasing means 43 does not have, but can basically a o. additional pressure roller or roller may be provided.

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.

In z. B. embodiment shown in Fig. 9, 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.

Between the contact cylinder 08 and the nip of the coating 03 can in

Conveyor 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. Preferably, 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.

In a third embodiment, not shown, 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). In a further development, an o. G. Trained as an application drum 08 is additionally on the conveying path. Stop device 09 comprehensive cylinder 08 is provided.

In an alternative embodiment of a z. B. 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.

A z. B. at least one coating unit 03 having machine has in one

Execution at least one of the coating 03 in the entrance area upstream Anlegzylinder 08 with the stopper 09 on.

In a processing line of a machine, 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.

In the examples of FIGS. 8 and 9, the cylinder 07 which in each case encloses the stop device 09 is shown in FIG. 08 upstream conveyor 04; 06 for the sake of simplicity and representative of suitable embodiments of the subject

Conveyor 04; 06 shown both with indicated thrusts 15 and dashed lines shown means 25 to increase the bearing force. Preferably, 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 a first movement exporting stop means 1 1 and the one on this one, in particular translational,

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

Synchronous phase in the direction of the trajectory B _T running movement of the

Stop surface 12 given, however, at any time during the

Cooperation of the edge 13 forms a firmly defined "hard" stop The application of the printing material 01 with its leading edge 13 to the stop surface (s) 12 of the stop device 09 by means of a through the upstream conveyor 04; 06 on the substrate 01 friction - and / or positively applied thrust.

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.

In a particularly advantageous embodiment, 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. Conversely, 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

having cylinder 07; 08 (24), be upstream. However, it is in an advantageous embodiment of a cylinder 07; 08 (24) with an abovementioned stop device 09 with a known type a first movement exporting stop element 1 1 and a stopper 21 performing on this a relative movement.

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. Depending on the expression of the conveyor 04; 06 and / or the manner of applying the thrust, these means 53; 54; 67; 56; 81; 82; 83; 84; 98 be realized in different ways. By 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.

In the form-fitting based execution of the conveyor 04; 06 arranged on the circulating means 05, at the trailing end of the printing material 01 attacking attacks 15, z. B. Hinterschüben 15, these can be used to limit the feed force in a simple embodiment of the corresponding traction means, z. B. on the belt 05 itself or the rear thrusters 15 also carrying circumferential belt or chain, against the on the conveyor 04; 06 present transport direction T be resiliently mounted. As the thrust limiting agent 53 may be z. B. a (in Fig. 1 by way of example only indicated) spring element 53, z. B. a compression spring 53 may be provided by which the back thrust 15 relative to the limitation of the feed force relative to the tape against the transport direction T be resiliently mounted. The same applies to a trained as a tension spring spring element 53 in accordance with the reverse arrangement. However, in this embodiment of the force limitation by relative movement between the further conveyed belt 05 and the einfedernden printing material 01 when "tearing" the stiction come to unwanted accelerations.

In one embodiment of the conveyor 04; 06 with only friction or adhesion between the means of circulation 05 and substrate sheet 01 based transport using (in Fig. 2 by way of example only indicated) friction-increasing measures, eg. B. with means 25 for applying a negative pressure P ^~ or a

Magnetic force, can limit the feed force in a simple

Embodiment variant, 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. However, this can be the point of Overcoming the stiction due to the spontaneously changing

Friction coefficient again lead to unwanted acceleration and / or displacements.

In a preferred embodiment, with regard to 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.

spring-damped and / or torque-limited trained. This can be z. B. be realized by the circulating means 05 driving in a first embodiment

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 Bandbzw. 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 Mindesthub between the disturbed by resistance increase tape feed and without interference too

expected tape feed (non-destructive) allows. 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

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 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 Zugmittelverlauf 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.

In a preferred embodiment of the friction between Umlaufmittel 05 and substrate 01 based conveyor 04; 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 Mindesthubes, still no loosening of Conclusion occurs. In other words, 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 Mindesthubes 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

Conveyor 04; 06 arranged on the circulating means 05, at the trailing end of the printing material 01 attacking attacks 15, z. B. thrusts 15, the feed of the at least one rear thrust 15 having circulating means 05 in o. G. Way operationally compliant, z. B. spring-damped and / or

be formed limited torque. 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.

Hereinafter, advantageous embodiments of the in terms of

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. Although the examples of the with respect to the advancement of the circulating means 05 yielding training on the basis of a preferred embodiment with frictional-based force attack between circulating means 05 and

Substrate sheet 01 are presented, these are equally on conveyors 04; 06 with positive force application between a on the circulating means 05th

arranged stop 15 and the substrate sheet 01 apply. In this case, a frictional force increasing means can be omitted. In the versions with

Frictional-based force application between circulating means 05 and printing material sheet 01 may advantageously be provided friction-increasing means 25 or possibly -. B. in the case of substrate sheet 01 a high surface density such as metal, z. As metal a thickness of at least 0.5 mm - also omitted.

In a first group of embodiments of 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.

In a first embodiment of the first group of the drive train in at least one transmission member 57 of the drive torque between 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

educated. 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. In the (purely) friction-based design of the conveyor 04; 06 is preferably provided a threshold value for the resilient yielding. This is set for the execution of the (pure) frictional transport in the manner in relation to - with or without friction-enhancing measures - present between Abruckstoffbogen 01 and 05 circulating means static friction or chosen that by running the leading edge 13 on the stop device 09 reaching this yielding the Umlaufmittelvortriebes triggering threshold already takes place before by the emergence of the static friction resistance, d. H. the limit to the "demolition" of stiction, is reached.

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. The transmission link

In this case, as a means 54 for limiting the feed, a resilient element 54, for example, has a resiliently elastic element 54. 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. In the operating direction of rotation, the torque is then preferably from the drive side closer link

58 via the spring-elastic element 54 against the spring force, ie transmitted in the manner of a spring-loaded dog connection on the output side nearer member 59. The "hardness" or resilience of the feed limitation can be influenced by the choice of the stiffness or spring constant of the element 54. Preferably, the spring-elastic coupling or the transmission element 57 is in a defined zero position L ₀ with a non-zero force, which z For this purpose, 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. 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. Is this by the spring element 54 and the spring member 54 comprehensive transmission member 57 certain threshold in the contact force

exceeded, so 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 ε of the preferably biased spring element 54 bzw.- transmission member 57 determines.

In an advantageous embodiment of this first embodiment (see, for example, Fig. 10, Fig. 1 1), 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). Preferably that is

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 arranged drive pulley 58, wherein the drive pulley 58 may be formed together with the drive inner ring 68 and the two members coupling transfer member 57 as rotatably sprung drive wheel 69 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.

In the first embodiment, 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 Hinterschübe 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. The Z. B. as a vacuum chamber 25th

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

Bedruckstoffbogenlänge. In an advantageous embodiment, the means 25 in

Viewed transversely, located directly below the belt 05, so that the

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

Use vacuum chamber 05 in moving (see below) as well as frame-resistant design.

In this, in one, in several or in all subsequent embodiments and variants 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

in particular deflection roller 81; 82, is limited. With regard to the 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. In addition to these circulation means 05, 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

circulating circulating means 05. 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. The feed rate determining circulating means 05 and possibly additional

Circulating means 72 is or are designed to be endless.

In a second, not explicitly shown embodiment of the first embodiment of the first group, 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 ε ') yielding, ie respect. A torsion soft, is formed. As in this way 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.

In a third, also not explicitly set forth embodiment of the 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. Here, for example, between the drive side and output side, d. H. in Zugmittelumlauf between a Eintriebsrad 78 and a driven gear 79, at least one compression roller, not shown, for. B. a spring-loaded tensioner roller, be provided by which an effective Zugmittellänge example of the running strand against the spring force can be extended, and thus at least temporarily an o. G. Hub in Zugmittelvorschub can be reached. In the returning strand is

preferably provided a corresponding Einfederungsrolle or vice versa.

In a second embodiment of the first group of the feed of the circulating means 05 is characterized compliant that the introduced into the drive train by the drive means 56 on the input side and / or in the drive train by z. B. at least one transmission member 67 transmitted driving force, in particular in the form of on and / or transmitted torque, with respect to z. B. a threshold can be limited. It is here z. B. even with increasing resistance, the example of a

Running up 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 transferred to the circulation means 05 in this drive train.

In 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. In an alternative embodiment, a coupling 67 designed as a compressed air coupling 67 can also be used for this purpose.

In a second embodiment variant of the second embodiment from the first group (see, eg, FIG. 13), 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. Preferably, the drive motor 56 is designed as a. With respect to the torque limiter, in particular adjustable servo motor 56. For the setting of a torque limiting threshold or a drive torque predetermining setpoint, the above applies to the threshold executed in the same way.

In a second group of embodiments of a conveyor 04; 06 with a on at least the conveyor section 55 with respect to the feed compliant trained circulating means 05 is the spatial circulation means course or the

Umlaufmittelführung formed so resilient that at least one

Zugmittelführung in space mitbestimmendes guide element 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 emergence of the

Substrate sheet 01 on the stop device 09 caused

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. The resiliently arranged in this way or resiliently in the circulation means guide member 81; 82; 83; 84; 98 (possibly together with an associated spring element 94, 104) in the above sense as a feed, in particular tape feed limiting means 81; 82; 83; 84; 98 effective. By the compression of the feed of the circulating means 05 is temporarily inhibited in the associated with the printing material 01 conveyor section 55 and in the conveyor section 55 associated guide section 65 or even brought to a standstill.

The feed limit of the circulating means 05, d. H. 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 guide or deflecting elements 83; 84 take place, which in the guide section 65 of the conveying region of the circulating means 05, ie in the cooperating with the printing material 01 area, present Umlaufmittelbzw. Band history leaves unaffected. The feed limitation is carried out at unchanged length and position of the guide portion 65 by a reduction in this Section present Umlaufmittel- or belt speed, this

Reduction at another point outside the scope of the program

Circulation medium course is caused by deflection. Preferably, in each case 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. of

Drive wheel 69, and the input-side guide roller 82 is provided. As a result, 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 upstream of the drive

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.

In a first embodiment variant of this first embodiment of the second group (see, for example, FIG. 14, in which only the course and guidance of the circulating means 05 with guide elements 81, 82, 83, 84 and the indicated drive wheel 69 are shown by way of example) are shown in FIG the drive gear 69 upstream and the drive wheel 69th

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. In particular, 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. Preferably, 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. In an advantageous embodiment, the linear movement against the one

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.

In principle, 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.

In a second variant of this first embodiment of the second group, not shown, 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

Guide portion 87, a guide roller 83 so resiliently mounted so that it corresponds to the length of the trailing feed gate corresponding to that from the leading

Conveyor section 86 by means of deflection of the lever 89 freed Umlaufmittel- or strip length extended. In an advantageous embodiment, 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.

In a second embodiment of the second group, the deflection of the

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

Guide section 65 co-determined. Preferably, at least the output-side deflection roller 81 is running with at least one along the transport direction T.

Component movable, in particular against the transport direction T against the spring force of a spring element yielding or resiliently mounted.

In a first embodiment of this second embodiment of the second group (see, for example, Fig. 15), 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. By compression, the entire length of the conveyor area and the

Drive forward relevant guide portions 65; 86, which at least temporarily reduces the effective speed in the conveyor area. As above, by biasing the abutment 96, a preload may be applied to the spring element 94, thereby providing a triggering threshold. In the trailing guide section 87, 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. Depending on the position of the drive wheel 69, 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. In a second embodiment of this second embodiment, 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. By pivoting the lever 97 is as above the total length of the

Conveying region and the drive forward relevant 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. For the spring element 94, a stop 96 and arranged in the trailing guide portion 87 guide roller 84 applies the above.

In a z. B. in Fig. 17 illustrated third embodiment of this second

Execution, 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. With the movement of the carriage 103 moves accordingly

output side pulley 81 and also connected to the carriage 103, z. B. designed as a vacuum chamber 25 friction increasing means 25. Zur

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

be provided, which, for example, contactless or via a sliding contact with a suction-side opening 108 of the vacuum chamber 25 together. At the Connecting piece 107 and / or in the region of the opening 108, a sealing element 109, z. B. a sealing plate 109 may be provided. 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. As the suction side of a pump, a turbine or a fan connected. Alternatively, the P connection 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 obstructed (not shown)

In Fig. 18 are schematically for different operating situations and associated load conditions, the positions of the carriage 103 from the third

Embodiment based on the relative position of cooperating

Guide elements 101; 102 shown: A first relative position (a), wherein the carriage 103 and the output-side guide roller 81 is spent in one of the input-side guide roller 82 closer position is z. B. taken in the event that alone the

Belt tension, so the voltage of the unloaded circulating means 05 without active friction increasing means 25, is applied. If a printing material sheet 01 is conveyed using negative pressure P (active means 25), then, as a result of the entrainment of the means 25 in the transporting direction T, a position (b) located farther away from the input-side deflection roller 82 is established. Now, if an increased resistance by the emergence of an edge 13 via the frictional connection to the circulating means 05 and from there by increasing the tension in the circulating means 05 on the deflecting deflecting roller 81, by the carriage 103, for example, again one of the input side guide roller 82 closer position taken (c). If there is neither a belt tension nor any other load, the carriage 103 becomes

For example, spent on its input side remote end position (d). In a fourth embodiment variant of this second embodiment, which is not specifically shown, 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

Guide section 87 The above should be applied accordingly.

As shown by way of example in FIG. 19 for the embodiments of a vacuum chamber 25, it 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. B. a large opening 91 or more spaced apart openings 91, z. B. suction openings 91, on. By means of this suction opening (s) 91, 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. Here, the or, for example, the slot-shaped (s) 91 (opening) 91 directly with holes 1 12 of the opening (s) 91 in the other substantially covering the perforated belt 05 acting together so arranged to pass through the holes 1 12th of the

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

01 substrate sheet, blackboard, substrate board, metal sheet, metal sheet

02 Processing unit, printing unit, offset printing unit

 03 Processing unit, coating unit

 04 conveyor

 05 Medium, circulating means, conveyor, belt, vacuum belt, perforated belt

06 conveyor

 07 cylinder, first, printing cylinder, impression cylinder, impression cylinder, transfer cylinder

 08 Cylinder, application cylinder, feed drum

 09 Device, stop device, stop and gripping device

10 -

1 1 lifting gear, brand lever

 12 stop surface

 13 edge, leading

 14 wave

 15 stop, rear thrust

 16 cam gear

 17 levers

 18 roll

 19 cam

 20 -

21 stop element, application mark

 22 arm, lever arm

 23 drive mechanism, gearbox

 24 cylinders, printing cylinder, blanket cylinder, blanket cylinder, transfer cylinder

25 medium, friction force increasing, pressure sink, vacuum chamber, magnet Abutment, stop element

Spring element, compression spring

paddock

Tang, shaft

- abutment, tenon, shaft

cam gear

Tang, shaft

role

supporting member

Gripper element, hook tip

grab

linear guide

clamp connection

- - Cylinder, forme cylinder, plate cylinder, printing cylinder

Medium, friction force increasing, magnet segment

Guide, guide device

Guide element, sliding plate

Cylinder, impression cylinder

Cylinder, painting cylinder

applicator roll

metering

- Roller, guide roller

Medium, frictional increasing

Means for pushing force limitation, spring element, compression spring

Feed limiting means, element, spring element, Druckmittelzylin conveyor section

Means, drive means, drive motor, servomotor

Transmission member

Link, output member, drive pulley

Link, drive inner ring

- Attack

attack

attack

attack

guide section

Shaft, drive shaft

Feed limiting means, transmission element, coupling, magnetic coupling, compressed air coupling

- Drive wheel

- hole

working capital

Transmission, traction mechanism

conveyor section

tape

Stop, front stop

Transmission link, shaft, traction means

Eintriebsrad

output gear

transmission member

Means, guide element, deflection element, deflection roller, front

Center, guide element, deflection element, deflection roller, rear Means, guide element, deflecting element, deflection roller means, guide element, deflecting element, deflection roller guide section

guide section

Carrier, sled

lever

- Opening, suction opening

swivel axis

lever

spring element

Guide or deflection element, deflection roller

attack

lever

Middle, guide element, pulley

Line, suction line

- Guide element, guide pin

Guide element, oblong hole

carriage

spring element

- Attack

spigot

opening

Sealing element, sealing plate

- Opening, neck opening 1 12 hole (05)

A axis

 D direction of rotation

 S cutting line

 T transport direction

B _G movement path (36)

B _R trajectory (21)

B _T movement path (01)

L ₀ zero position

L ₂ location

L _K first contact

P ^_ negative pressure

P _a working phase

P _r rest phase (1 1)

T ₀ transport direction (zero position)

_Rest phase (21) α Angular position

ß angular position

δ angle

ε spring deflection angle

Claims

claims

1 . Conveyor for conveying printing material (01) in a painting and / or printing machine with a stop means (1 1) having cylinder (07, 08, 24) and with a cylinder (07, 08, 24) upstream in the conveying, a circulating means (05) conveying device (04; 06),

 wherein the stop means (1 1) by a first drive mechanism correlated to the cylinder rotation with at least its drive side remote end radially between a first, retracted position and a radially different from the first layer second position is zwangsantreibbar up and down, and wherein the stop means (1 1) in the region of its end remote from the drive side, a stop element (21) which comprises a stop surface (12) and which is mounted so as to be movable on an arm (22) of the stop means (11),

 characterized in that the abutment member (21) is positively driven by a second drive mechanism (23) correlated to cylinder rotation and / or movement of the arm (22) relative to the arm (22).

2. Conveyor device according to claim 1, characterized in that the

 Stop means (1 1) on the cylinder (07, 08) pivotally mounted about an axis parallel to the cylinder axis (A) and / or the first, the stop means (1 1) driving a total drive mechanism comprises a cam gear (16).

3. Conveyor device according to claim 1 or 2, characterized in that the

Stop element (21) is arranged in such a way that it can move relative to the arm (22) of the stop means (11) and is driven by the second drive mechanism (23) in such a way that it is located upstream of the movement path (B _T ), at which it comes into contact with the edge (13) of a printing material sheet (01) to be conveyed, on the stop means (11) in one direction at least one movement component in the direction of rotation of the cylinder (07; 08; 24) and / or along the direction of movement (B _T ) of the printing material sheet (01) is movable.

4. Conveying device according to claim 1, 2 or 3, characterized in that the stop element (21) zwangsantreibende second drive mechanism (23) on the drive side to the forced by the first drive mechanism movement of the stop means (1 1) is coupled.

5. Conveying device according to claim 4, characterized in that the coupling of the second drive mechanism (23) to the movement of the stop means (1 1) a cylinder-fixed linkage, d. H. a single or multi-membered connection of the stop element (21) to a cylinder-fixed abutment (26, 31).

6. Conveying device according to claim 5, characterized in that the articulation via a cam gear (32) is given, which rotatably on

 Stop element (21) arranged roller (34) which cooperates with a on the cylinder (07, 08) arranged stop element (26), supporting on this.

7. Conveying device according to claim 5, characterized in that the articulation via a coupling (28) is given, which on the one hand rotatably on

 Stop element (21) and on the other hand rotatably articulated on the cylinder (07, 08) is articulated.

8. Conveyor device according to claim 1, 2, 3, 4, 5, 6 or 7, characterized in that the stop element (21) is mounted in a linear guide (38) on the stop means (1 1) movable.

9. Conveying device according to claim 8, characterized in that the

Linear guide (38) on the stop means (1 1) is arranged and oriented so that it defines a trajectory (B _R ) for the stop element (21) on the located in the first position stop means (1 1) with respect to the cylinder (07; 08; 24) predominantly tangential component of motion.

10. Conveyor device according to claim 1, 2, 3, 4, 5, 6, 7, 8 or 9, characterized

 in that the conveying device (04; 06) arranged upstream of the cylinder (07; 08; 24) comprises a means (53; 54; 67; 56; 81; 82; 83; 84; 98), by means of which the conveying device (4; 04, 06) on the printing material (01) against the resistance formed by the stop device (09) to be applied feed force is at least temporarily limited.

1 1. A conveying device according to claim 10, characterized in that the feed of the circulating means (05) by the means (53; 54; 67; 56; 81; 82; 83; 84; 98) in at least one with the printing material sheet (01) cooperating

 Conveying section (55) as a result of a by the emergence of the printing material (01) against the stop device (09) conditional resistance increase operationally against an undisturbed movement of the circulating means (05) is yielding.

12. A method for conveying printing material sheet (01) along a conveying path of a painting and / or printing machine, wherein

a printing material sheet (01) by a conveyor (04, 06) along a movement path (B _T ) to a stop means (1 1) with a

Before abutting the conveyed printing material sheet (01) on the cylinder (07, 08, 24), the stop means (11) on the rotating cylinder (07, 08, 24) is brought into contact with the stop surface (12) ) with at least its stop near the end of a first layer in one second, radially further outward position in the movement path (B _T ) of the printing material sheet (01) is spent,

 in at least one movement phase of the cylinder (07, 08, 24) and printing material sheet (01), in which a leading edge (13) has already come into contact with the stop surface (12), a stop element (21) having the stop surface (12) on an arm (22) of the stop means (11) relative to the arm (22) is moved periodically and in correlation to the movement of the arm (22) such that the stop surface (12) moves with a predominantly tangential component of movement relative to the cylinder (12). 07, 08, 24) in its direction of rotation (D).

13. The method according to claim 12, characterized in that the stop means (1 1) is correlated by a first drive mechanism for cylinder rotation between the first, retracted position and radially different from the first position second position is moved, and that the stop surface (12 ) having a second drive mechanism (23) correlated to the cylinder rotation and / or movement of the arm (22) relative to the arm (22) is forcibly driven.

14. The method according to claim 12 or 13, characterized in that the

 Relative movement of the stop element (21) on the arm (22) is rectilinear.

15. The method of claim 12, 13 or 14, characterized in that in a movement phase of cylinder (07; 08; 24) and printing material sheet (01), in which the leading edge (13) already with the stop surface (12) in contact the stop means (1 1) on the rotating cylinder (07; 08; 24) is moved from a radially further outward position into a further inner position with at least its stop surface near end, while at the same time the stop element comprising the stop surface (12) (21) a movement with a predominantly tangential component of motion relative to the cylinder (07; 08; 24) in its direction of rotation (D).

16. The method of claim 12, 13, 14 or 15, characterized in that the movement of the stop element (21) by the movement of the stop means (1 1), in particular by the movement of the arm (22), is enforced.

17. Conveying device according to one or more of claims 1 to 1 1 or

 Method for conveying according to one or more of Claims 12 to 16, characterized in that the printing material sheet (01) to be conveyed is designed as a printing material panel (01), in particular as a metal sheet (01).