EP0639454A1 - Device with a retractable hook for holding a printing plate on a plate cylinder in a rotary printing machine and rotary printing machine with such a device - Google Patents

Abstract

The invention relates to a device for holding a printing plate on a plate cylinder in a printing machine and to a printing machine containing such a device. The printing plate (9), which is held by a front edge (end edge 24) on the outer circumferential surface (8) of the plate cylinder (1), is otherwise held by means of a rear end fold (26) being hooked onto a hook (165) which can be moved relative to the plate cylinder (1) between a front end position in which it forms a projection on the outer circumferential surface (8) to allow the rear end fold (26) to be hooked on or unhooked, and a retracted position in which it is retracted relative to said outer circumferential surface (8) and holds the printing plate (9) under stress in a state wrapped over the outer circumferential surface (8). This facilitates assembly and demounting of a printing plate. Gaps in printing are reduced to a minimum. <IMAGE>

Description

• hakenbildende Mittel mit wenigstens einem radial zur Drehachse des Tragzylinders äußeren und entgegen der Drehrichtung weisenden Haken,
• Mittel zum Betätigen der hakenbildenden Mittel, die wenigstens teilweise in der Bohrung des Tragzylinders angeordnet sind und die geeignet sind, den Haken in gesteuerter Weise hinund herzubewegen zwischen einer in bezug auf den Drehsinn des Tragzylinders vorderen Endposition zum Ermöglichen des Einhakens oder Aushakens der hinteren Endfalte an dem Haken und einer in bezug auf den Drehsinn des Tragzylinders hinteren Endposition um auf die hintere, auf den Haken gehakte Endfalte eine Zugkraft entgegen dem Drehsinn des Tragzylinders auszuüben, wobei die Haken dann in das Innere des Schlitzes bezüglich der äußeren Umfangsfläche des Tragzylinders zurückgezogen ist.

The present invention relates to a device for holding a printing plate on a support cylinder in a rotary printing press, the support cylinder having an outer circumferential surface cylindrical to an axis of rotation of the support cylinder and containing at least one longitudinal bore inside, which opens into the outer circumferential surface by means of a longitudinal slot, with means for Retaining in particular the rear end fold of the plate in the slot, which is otherwise held with respect to the support cylinder with a front edge with respect to a predetermined direction of rotation of the support cylinder about its axis of rotation, by tensioning the plate in the wound state on the outer peripheral surface of the support cylinder, the Means for retaining the rear end fold include:

• hook-forming means with at least one hook pointing radially to the axis of rotation of the support cylinder and pointing counter to the direction of rotation,
• Means for actuating the hook-forming means, which are arranged at least partially in the bore of the support cylinder and which are suitable for moving the hook back and forth in a controlled manner between an end position which is forward with respect to the direction of rotation of the support cylinder, in order to enable the rear end fold to be hooked in or unhooked the hook and a rear end position with respect to the direction of rotation of the support cylinder in order to exert a tensile force against the direction of rotation of the support cylinder on the rear end hook hooked on the hook, the hook then being retracted into the interior of the slot with respect to the outer peripheral surface of the support cylinder.

Such a device is described in DE-A 2 235 119 in an embodiment in which the hook between its front and its rear end position describes a path approximately cylindrical to the longitudinal axis defined by the bore, the bore itself being a cylindrical path to this axis Has a shape to constantly receive the hook, which at no time moves out of the slot. The hooking of the rear end fold of the plate with the hook must therefore take place relatively far away from the outer peripheral surface of the support cylinder through the slot which connects the bore to the peripheral surface. This makes hooking work long and difficult, which could certainly be facilitated by the provision of a relatively wide slot, but at the cost of a correspondingly larger gap in printing. In addition, the plate between the mouth of the slot and the outer circumferential surface of the support cylinder and the rear end fold which can be brought into engagement with the hook has an edge region which cannot be used for printing and which is relatively large, which leads to an oversizing of the plate with respect to the predetermined print format leads.

The object of the present invention is to avoid these disadvantages. To this end, the present invention proposes a device of the type specified in the preamble, which is further characterized in that the hook-forming means are embedded in the slot and the hook protrudes beyond the outer circumferential surface of the support cylinder, and that the actuating means are suitable to cause the hook to retract into the slot during the movement from the front end position to the rear end position and to cause the hook to protrude with respect to the outer peripheral surface of the support cylinder during the movement from the rear end position to the front end position.

One skilled in the art will readily understand that the fact that the hook projects beyond the outer peripheral surface of the support cylinder in its forward end position, in which the rear end fold of the plate is hooked or unhooked, greatly facilitates this hooking or unhooking because the hook is directly accessible . There is no need to oversize the slot for this purpose, which allows the printing gap to be minimized. It is also possible to minimize the edge zone of the plate which is not usable for printing, since the rear end fold of the plate can practically directly adjoin the zone which can be used for printing.

These advantages are obtained without complicating the device over that described, for example, in the cited document.

In particular, as provided in the case of this document, the actuating means may include a longitudinal tension rod which is arranged in a bore of the support cylinder and which is rotatably guided about a longitudinal axis which is arranged between the axis of rotation of the support cylinder and the slot, and drive means, around the tension rod to reciprocate the axis of rotation with respect to the support cylinder between two end orientations corresponding to the front and rear end positions of the hook, and in that the hook-forming means include at least one longitudinal blade having a first end portion radially inner with respect to the axis of rotation of the support cylinder , which is fixedly connected to the tension rod inside the bore, and a second, longitudinal end region which is radially outside with respect to the axis of rotation of the support cylinder and which forms the hook, the blade between its first end region and its second end region ch is elastically deformable.

The drive means for the tension rod can be of any type, i.e. mechanical, electrical, hydraulic or pneumatic. According to a preferred embodiment, they contain means for elastically loading the tension rod in the direction of its end orientation corresponding to the rear end position of the hook, for example in the form of an inexpensive, particularly strong and easily adjustable torsion bar coaxial with the tension rod, and means which form a simple actuator, that loads the tension rod in a controlled manner towards its end orientation according to the front end position of the hook. In this regard, pneumatic means are preferred to the extent that they provide particularly simple, easy and reliable implementation, as will become clear below.

Moving the hook from its front end position, in which it projects beyond the outer circumferential surface of the support cylinder, to its rear end position, in which it is retracted into the interior of the slot, and at the same time the holding and tensioning of the pressure plate wound on the outer circumferential surface of the support cylinder causes can be carried out in a manner of operation which is comparable to winding the sheet onto the tension rod, with a small amplitude of the displacement of the hook in the circumferential direction of the support cylinder, ie for a small size of the slot. For this purpose, it is advantageously provided that the blade is behind the tensioning rod in the sense of the rotation of the support cylinder and along this between its first and its second edge zone. It is preferably further provided that the tension rod has a longitudinal nose which is arranged between its axis of rotation and the slot and which is supported freely with respect to the direction of rotation of the support cylinder on the sheet between its first edge zone and its second edge zone, which allowed the bending of the sheet between its first edge zone and its second edge zone and thereby the resulting on the outer peripheral surface of the support cylinder to amplify the resulting resulting tension, with a predetermined angle of rotation of the tension rod about the axis of rotation inside the bore, ie to obtain the generation of a predetermined tension with a small angle of rotation. This allows the use of technically simpler and less complex drive means than those required by the device described in DE-A 22 35 119. The assembly of the hook known from this document is necessarily associated with rotations of the tension rod over a large angle between its orientations corresponding to the respective front end position and rear end position of the hook. It is also preferably provided that the second end region is offset with respect to the direction of rotation of the support cylinder in relation to the first edge zone, which makes it possible to ensure that the plate is energized by a work which is not only bending but also simultaneous pulling, whereby much more favorable conditions are obtained than the working conditions of the sheet of the device described in DE-A 22 35 119, which are based exclusively on bending.

The movement of the hook from its rear end position, which is retracted into the interior of the slot, into its front end position, which protrudes beyond the outer circumferential surface of the support cylinder, is comparable to an unwinding of the sheet from the tensioning rod. For this purpose, the slot is advantageously designed in such a way that it offers a forward support of the hook with respect to the direction of rotation of the support cylinder. In this regard, a preferred embodiment is characterized in that the slot is limited forwards with respect to the direction of rotation of the support cylinder with a front, longitudinal flank which is oriented with respect to the outer circumferential surface of the support cylinder in such a way that it adjoins the outer circumferential surface with respect to the direction of rotation of the support cylinder of the support cylinder before it is connected to the bore of the support cylinder.

In a manner known per se, the slot can also be limited rearward with respect to the direction of rotation of the support cylinder with a longitudinal rear flange which is inclined with respect to the outer circumferential surface of the support cylinder in such a way that it adjoins this outer circumferential surface in the direction of rotation of the support cylinder before it is connected connects the bore of the support cylinder. This allows the front end fold of the plate to be hooked directly onto the transfer of the slot to the outer peripheral surface of the support cylinder.

It is also possible to provide that the leading flank and the trailing flank are at least approximately parallel to each other, which allows the width of the slot and consequently the resulting printing gap to be minimized.

The device according to the invention, as it is described, offers a common use with conventional devices which are provided in order to facilitate the winding of a printing plate on the outer circumferential surface of a carrying cylinder. These devices usually contain a longitudinal, elastically compressible or elastically loaded to the outer circumferential surface of the support cylinder, which rests with the interposition of the pressure plate during winding on the outer circumferential surface of the support cylinder. In a manner easily derivable from known techniques, this roller causes the retraction of the hook originally protruding with respect to the outer circumferential surface of the support cylinder around the front end fold of the plate, which, moreover, is, for example, hung by a front end fold on the rear flank of the slot when the Preferred shape of the slot described below is referenced. This happens the moment the slot is in the immediate vicinity of the roll.

• Gleichzeitig das Bewegen des Druckelementes von seiner zurückgezogenen Position zu seiner elastischen Abstützposition um die hintere Endfalte der Druckplatte während des Aufwickelns hinter einen Haken, der sich in bezug auf den Drehsinn in seiner vorderen Endposition befindet, und das Bewegen des Hakens von seiner vorderen Endposition in seine hintere Endposition um das gegenseitige Verhalken der hinteren Endfalte und des Hakens zu bewirken und um die Druckplatte auf der äußeren Umfangsfläche des Tragzylinders zu spannen, wenn der Schlitz sich gegenüber dem Druckelement befindet, und
• dann die Rückbewegung des Druckelementes von seiner elastischen Abstützposition in seine zurückgezogene Position, wonach der Haken in seiner hinteren Endposition bleibt.

Other arrangements can also be provided, and in particular, the present invention proposes a printing press that includes a housing and a support cylinder that has an outer circumferential surface cylindrical to its longitudinal axis of rotation and at least one longitudinal bore on the inside that overlaps in the outer circumferential surface Longitudinal slot opens, which is characterized in that it contains a device according to the invention for holding a pressure plate, a longitudinal pressure element lying opposite the outer circumferential surface of the support cylinder and means for holding the pressure element on the housing, which hold the pressure element movably between a support position elastic to the axis of rotation on a pressure plate held with its front edge and in a retracted position displaced with respect to the elastic support position in the direction away from the axis of rotation, the actuating means containing means n that are capable of causing the following during rotation of the support cylinder:

• Simultaneously moving the pressure element from its retracted position to its elastic support position around the rear end fold of the pressure plate during winding behind a hook which is in its front end position with respect to the direction of rotation, and moving the hook from its front end position to its rear end position to cause the rear end fold and hook to hook together and to tension the pressure plate on the outer peripheral surface of the support cylinder when the slot is opposite the pressure element, and
• then the return movement of the pressure element from its elastic support position to its retracted position, after which the hook remains in its rear end position.

Further features and advantages of a device according to the invention for holding a printing plate on a support cylinder and of a printing press according to the invention with such a device result from the following description of a non-limiting exemplary embodiment as well as from the accompanying drawings which form an integrated part of this description.

Fig. 1 shows a cross section along a plane II shown in Fig. 2 of a device embodying the invention to hold the rear edge of a printing plate which is wound in a tensioned state on the outer peripheral surface of a support cylinder, the hook being its rear end position in the absence of the printing plate.

Fig. 2 shows a partial section of the same device according to a longitudinal plane, which includes the axis of the tension rod and which is shown by II-II in Fig. 1.

FIGS. 3A and 3B represent two successive phases of the assembly of an elastic, hook-forming sheet on the tensioning rod in a view in the direction of arrow III in FIG. 1 and in a view corresponding to that in FIG. 1.

Fig. 4 shows a perspective view of a tool for dismantling this sheet.

5 to 7 illustrate the use of the tool for dismantling the blade in the views corresponding to FIGS. 1 to 3.

8A and 8B show, in sections along the longitudinal axis of the support cylinder, two states of a device which replaces a rotary coupling and which is provided in order to temporarily secure the supply of a pressure fluid, in practice compressed air, to pneumatic drive means of the tension rod, at times to bring them into alignment with the front end position of the hook.

Fig. 9 shows, in a partial section through the support cylinder, the pneumatic circuit which is provided within it for this purpose.

9A and 9B show in detail from FIG. 9 two states of a device which is provided in this circuit, both to temporarily ensure the supply of the pneumatic drive means with pressurized fluid and to allow the fluid to escape from the pneumatic means allow.

Fig. 10 shows in a view in a longitudinal direction indicated by X in Fig. 2 the beginning of a winding process of a printing plate on the outer peripheral surface of the support cylinder, on which the printing plate is already hooked with a front end fold at the beginning.

Fig. 11 shows in a view corresponding to that of Figs. 1, 3, 5 to 7 a phase immediately before hooking the rear edge of the plate on the hook, which therefore assumes its front end position, in which it has a slight projection, for example in the Forms magnitude of one to several millimeters with respect to the outer peripheral surface of the support cylinder.

Fig. 12 is a partial view of Fig. 11 showing successive portions of the hooking of the rear edge of the plate on the hook as it moves from its front end position to its rear end position in which it is retracted with respect to the outer peripheral surface of the support cylinder.

Fig. 13 shows in a view corresponding to the views of Figs. 1, 3, 5 to 7, 11 the final state of hooking before the plate is tensioned, the hook occupying an intermediate position between its front and rear end position.

Fig. 14 shows, in a view corresponding to the views of Figs. 1, 3, 5 to 7, 11, 13, the tensioning of the plate by bending the sheet forming the hook, which tries to assume its rear end position, but due to its hooking into the rear fold of the pressure plate is retained.

Fig. 15 shows a perspective view of simple, pneumatic drive means by which those shown in Figs. 1, 2, 9, 9A, 9B, 11, 13 can be replaced to temporarily adjust the tension rod in its orientation according to to hold the front end position of the hook due to the temporary supply of a pressure fluid, in practice compressed air.

16 shows a longitudinal section of these means, on the left when there is no supply of a pressurized fluid and on the right when they are supplied with compressed air.

16A and 16B illustrate the same means in a transverse plane corresponding to XVIA-XVIA and XVIB-XVIB of Fig. 16, respectively in the absence of supply of pressure fluid and in the case of supply of pressure fluid.

17A shows in a cross section the interaction of the support cylinder and the pressure plate, which is already hooked onto it with its front edge, during hooking with the rear edge after winding up into a phase which corresponds to that of that shown in FIG. 13, by means of a pressure element which facilitates this hooking operation, the section being taken along a plane identified by XVIIA-XVIIA in FIG. 17B.

FIG. 17B shows a partial section of this arrangement in the radial direction with respect to the axis of the support cylinder, which is indicated by XVIIB in FIG. 17A.

In the drawings, (1) denotes a support cylinder, which is rotatable about a horizontal longitudinal axis (2) in a housing (3)
Rotationsdsdruckmaschine is arranged. The support cylinder (1) is delimited by two essentially flat transverse surfaces (4, 5), each of which is provided in the axis (2) with a longitudinal bearing journal (6, 7), which is in each case in a bearing of the housing (3) is recorded, for example a warehouse (188). Between the transverse surfaces (4, 5), the support cylinder is provided by means of an outer, longitudinally directed, substantially with respect to the axis (2) cylindrical peripheral surface which is intended to receive and hold a pressure plate (9) which is coaxially wound and in Is stretched in the circumferential direction in the wound state, according to the features that are described below. Drive means (not shown) are provided in order to rotate the support cylinder (1) and with it the pressure plate (9) about the axis (2) with respect to the housing (3) in a sense indicated by (10), on the one hand to wind up the pressure plate (9) on the outer peripheral surface (8) of the support cylinder (1) before the printing work and on the other hand during printing by means of the printing plate in question (9).

The direction (10) serves in the following as a reference for the designations front and rear, upstream and downstream and for the front and rear identification.

In the immediate vicinity of the outer circumferential surface (8) of the support cylinder (1), two longitudinal bores (11 and 12) which are offset from one another in the direction (10) and both of which are delimited about axes (15, 16) by cylindrical rotating surfaces (13, 14). The two bores (11, 12) extend at least over the major part of the longitudinal dimension of the outer peripheral surface (8) of the support cylinder (9). Their diameter, which is, for example, identical, is small with respect to the diameter of the peripheral surface (8) in such a way that their inner peripheral surfaces (13, 14) do not disturb the outer peripheral surface and that the position of the axes (15, 16) between the axis (2) and the
outer peripheral surface is closer to the outer peripheral surface than to the axis (2).

The inner peripheral surface (14) of the downstream bore (12) is continuous. The inner peripheral surface (13) of the upstream bore (11) has an interruption over a few angular straight lines with respect to the axis (15), which is between the axis (15) and the outer peripheral surface (8) of the support cylinder (1) in a common central longitudinal plane (17) of the axes (2 and 15) is arranged. This interruption forms in the inner peripheral surface (13) of the bore (11) the mouth (18) of a slot (19) which connects the inner peripheral surface (13) with the outer peripheral surface (8) of the support cylinder (1), in which the latter Slot (19) has a mouth (20) which is offset forward with respect to the mouth (18) so that the slot is inclined with respect to the central plane (17) such that it extends from the central plane with respect to the axis (2) or removed with respect to the axis (15). Between the mouths (18 and 20), the slot (19) is delimited with two flat, mutually parallel flanks which have a corresponding inclination with respect to the plane (17), ie an upstream or rear flank (21) and a downstream or front flank Form (22), which are at a small distance from one another in comparison to the diameter of the inner peripheral surface (13) of the bore (11), ie in the order of a few millimeters in practice.

Due to its inclination with respect to the plane (17), the upstream flank (21) of the slot (19) with the outer circumferential surface (8) of the support cylinder defines a nose (23) on which a front longitudinal end fold () 24) hooks the pressure plate (9). This fold is formed by deforming an outer front longitudinal edge (25) of the plate (9), which forms a hook with the immediately adjacent zones of the pressure plate (9) and which lies flat against the upstream flank (21) of the slot (9).

The pressure plate (9) also has a rear, longitudinal end fold (26), which is formed by an outer, flat, longitudinal edge, which is folded like a hook with respect to the immediately adjacent areas of the pressure plate (9), in a position that the rear end fold (26) coincides with the mouth (20) of the slot (19) so that the outer edge (27) enters it, but without contact with the flanks (21 and 22) when the pressure plate (9) in tensioned state is wound on the outer circumferential surface (8) of the support cylinder in order to hold it by means which are partially arranged within the slot (19) and in the bores (11, 12) and which will be described.

It is pointed out that according to an arrangement known per se to a person skilled in the art, not shown, the means can be arranged in several designs at angular intervals around the axis (2) of the support cylinder (1), in the same arrangement corresponding to the support cylinder, whereby a bore (11), a bore (12) and a slot (19) are arranged in the manner described such that each slot corresponding to the slot (19) has a rear end fold corresponding to the fold (24) of a pressure plate and a front end fold the fold (26) receives a further pressure plate, these pressure plates corresponding to the plate (9) in the circumferential direction on the outer circumferential surface (8) follow the support cylinder (1). The design of these repetitive means corresponds to that which will be described later.

1, 2, 3A it can be seen that in the interior of the bore (11) a longitudinal tensioning rod (28) which is rotatable about the axis (15) with respect to the supporting cylinder (1) is arranged and guided and extends to a circumference is of the order of magnitude of 240 ° with respect to the axis (15) and has an outer circumferential surface (29) which is cylindrical with respect to the axis (15) and whose diameter is substantially identical to the inner circumferential surface (13) of the bore (11), so that a leading sliding contact for relative rotation about the axis (15) is established between the surfaces (13 and 29). The tensioning rod (28) is otherwise provided with a flattened portion (30) extending in the longitudinal direction over approximately 120 °, the shape of which will be described in detail below, and approximately in all possible orientations that the rod has in the interior of the bore (11 ) can take under normal conditions of use by turning about the axis (15), extended approximately the slot (19).

The tension rod (28) extends over the entire longitudinal dimension of the support cylinder (1) and has an inner, longitudinal recess (31) in the region of the axis (15) with a rectangular cross section over its entire longitudinal dimension, in which a longitudinal torsion rod (32) coaxially is recorded, the cross section of which is also rectangular and the two ends of which are held in the region of the transverse surfaces (4 and 5) of the supporting cylinder (1) by means of bearings (33) which are fixedly mounted on the relevant transverse surfaces of the supporting cylinder. The arrangement of the torsion bar (32) is such that it elastically loads the tensioning bar (28) for rotation about the axis (15) relative to the support cylinder (1) in a direction (34) which is in the immediate vicinity of the mouth (18) the slot (19) the direction (10) is opposite with respect to each rotation the tension rod (28) about the axis (15) inside the bore (11) under the conditions of normal use.

Between each bearing (33) of the torsion bar (32) and the relevant transverse surface (4, 5) of the support cylinder (1), the tensioning rod (28) is provided with one end, with which it each has a lever (35, 36) in rigid connection. wearing.

The two levers (35, 36) are aligned radially with respect to the axis (15), parallel to one another and in any orientation of the tension rod (28) given in normal conditions of use approximately perpendicular to the plane (17), such that they each have one end in the Have longitudinal extension of the bore (12), each with respect to the transverse surface (4) and the transverse surface (5) of the support cylinder (1). Adjustable stops (37), which are arranged on the transverse surfaces (4, 5) of the support cylinder (1) immediately downstream of the slot (19), work together with the levers (35, 36) in order to prevent the clamping rod (28 ) to give an adjustable limit to the axis (15) inside the bore (11) in the direction (34), which corresponds to a position of a longitudinal, straight stop (38) which the end of the outer peripheral surface (29) in the direction ( 34) to the mouth (18) of the slot (19) in the bore (11), ie between the transitions of the upstream flank and the downstream flank of the slot (19) with the inner circumference (13) of the bore (11) such that a zone of the outer circumferential surface (29) which is immediately adjacent to this stop (38) opposite the Slit is arranged as shown in Fig. 1. This position also results from FIG. 14.

From this end orientation, the tension rod (28) can rotate about the axis (15) in a direction opposite to the direction (34) inside the bore (11), which releases the levers (35, 36) from the stops (37), and in the direction of the axis (2) of Support cylinder (1), which causes an increase in the tension of the torsion bar (32).

Limitation of the rotation of the tension rod (28) inside the bore (11) against the direction (34) is effected by means of a longitudinal, profiled rod (39) which is arranged in the interior of the bore (12) and which in the longitudinal direction supports the support cylinder (1) penetrates from one to the other of the transverse surfaces (4, 5) in such a way that the profiled rod (39) is firmly connected to the levers (35, 36) in the region of the transverse surfaces (4, 5).

In Fig. 11, which shows the rod (39) against the direction (34) in a stop position against the inner peripheral surface (14) of the bore (12), you can see that this rod (39) against the direction (34) by means of an outer circumferential surface (40) which is cylindrical to a longitudinal axis (41) and which, in the position shown in FIG. 1, is arranged on the same side as the slot (19) with respect to a longitudinal plane (42) which is perpendicular to the plane ( 17) and which is defined by the axes (14 and 16), so that this axis (41) coincides with the axis (16) in the end position shown in FIG. 11. With respect to this axis (41), the outer circumferential surface (40) has a diameter identical to the diameter of the inner circumferential surface (14) of the bore (12) with respect to the axis (16) with an angular extent of the order of 100 °, which is uniform is distributed on both sides of a longitudinal plane of symmetry (47) of the profiled rod (39), which runs through the axis (41) and is located in a longitudinal plane (43) parallel to the plane (17) and which is represented by the axis (16) in FIG 11 shown position of the profiled rod (39).

The profiled rod (39) can be rotated about the axis (15) inside the bore (12) in a manner guided by the tension rod (28) between the one shown in FIG. 1 by striking the lever (35 and 36) against the adjustable stops (37) in the direction (34) limited position and the position shown in Fig. 11 to and fro, in which the axis (41) coincides with the axis (16) and the the outer circumferential surface (40) is supported against the direction (34) on the inner circumferential surface (14) of the bore by lying locally against this inner circumferential surface (14), which means that the tension rod (28) has a different end orientation with respect to the axis ( 15) corresponds to the inside of the bore (11). The two end orientations of the tension rod (28) defined in this way are angularly offset from one another only by a few degrees with respect to the axis (15), for example in the order of magnitude of 10 °.

The profiled rod (39) is delimited in the direction (34) with three outer, flat surfaces (44, 45, 46). The surface (45) which is symmetrical with respect to the plane (47) merges into the surfaces (44 and 46) which are arranged symmetrically to the plane (47) and which, moreover, adjoin the outer peripheral surface (40).

The surfaces (44, 45, 46) are dimensioned in a manner that can be easily determined by a person skilled in the art in such a way that a gap (48) with a constant cross section exists between them and the inner peripheral surface (14) of the bore (11) in direction (34) which extends over the entire longitudinal extent of the support cylinder (1) between the transverse surfaces (4 and 5).

The gap (48) contains an inflatable bellows (49) which extends practically over the entire length of the support cylinder (1) between the transverse surfaces (4 and 5) and which is anchored on the profiled rod (39), for example by engagement of one on the outside of the bellows (49) attached longitudinal rib (50) which engages in a in the surface (45) of the profiled rod (39) along the plane of symmetry (47) longitudinal groove (51), the plane of symmetry in the same way a plane of symmetry for forms the gap (48) and the bellows (49). The anchoring The longitudinal rib (50) in the longitudinal groove (51) is ensured by a suitable design of its cross sections, which is comparable to a dovetail cross section. Of course, other types of fastening of the bellows to the profiled rod (39) can also be selected, in particular gluing.

The bellows (49) forms a simple drive means, which makes it possible to transfer the tension rod (28) from its orientation shown in FIG. 1 by means of inflation with a fluid which is under overpressure with respect to the ambient pressure, in particular by means of compressed air. This results in an increase in the elastic stress on the torsion bar (32), which tends to return the tensioning bar (28) in the orientation shown in FIG. 1, causing the bellows to be emptied if there is nothing to prevent it.

In order to bring about a temporary supply of pressure fluid, in particular compressed air, to the bellows (49) and to provide the atmospheric pressure in the bellows (49) for the remainder of the time, means are provided which in conjunction with FIGS. 8A, 8B, 9 , 9A, 9B, of which Fig. 9 is a view showing the structure of a pneumatic circuit.

(52) denotes a source of pressure fluid which is received by the housing (3) of the machine, in the exemplary embodiment an air compressor which is equipped with a compressed air reservoir, as is known to the person skilled in the art. The source (52) is suitable for supplying compressed air to a line (53) which leads to a supply connection (54) which is also carried by the housing (3) of the machine and which is coaxial in the longitudinal direction with respect to the bearing journal (7) of the support cylinder (1) is arranged. A valve (55) is arranged in the line (53), which, in an alternatively controlled manner, allows the line (35) to be connected either to the source (52) of a pressure fluid or to an outlet (56) which is in the ambient air opens when the pressure fluid is compressed air, as shown.

The design of the supply connection (54) and its interaction with the bearing journal (7) result in further details from FIGS. 8A and 8B, which show that instead of connecting a rotary coupling to the bearing journal (7), which ensures a fluid permanent connection , as is common when a fixed axis rotating device is powered from a stationary source, the supply port (54) is telescopic and only provides a tight fluidic connection to the trunnion (7) when needed to Supply pressure fluid, in particular compressed air, to the bellows (49) arranged in the bore (12).

As is shown in particular in FIGS. 8A and 8B, the supply connection (54) is designed as a simple actuator.

It has a tubular body (57) which is arranged along the axis (2) opposite the bearing journal (7) of the support cylinder (1) and which is fixedly attached to the housing (3) of the machine, for example by one end a line (58) coaxial screw connection, which delimits the line (53) in the immediate vicinity of the connection (54).

With any external shape, the tubular body (57) has an inner circumferential surface (59) which is cylindrical with respect to the axis (2) and which extends on the one hand in the longitudinal direction in the direction of the tube (58) and with the interposition of a coaxial chamber (60) on a coaxial one Thread (61), which can be screwed onto the tube (58), and on the other hand in the longitudinal direction with respect to this tube (58) via a ring shoulder (62) coaxial to the axis (2) and facing the line (58) to a further inner, connected to the axis (2) cylindrical peripheral surface, which has a smaller Has diameter than the inner peripheral surface (59) and which opens towards the bearing pin (7) to the ambient air.

A tubular piston (64) is arranged in the interior of the body (57) and is penetrated completely along the axis (2) by a channel (65) which forms a permanent fluidic connection with the line (53) and which, for example, is one for Axis (2) has a cylindrical inner peripheral surface (66) with a smaller diameter than the diameter of the inner peripheral surface (63).

Both on the side facing the tube (58) and on the side facing away, the inner circumferential surface (66) ends in flat end faces (67, 68) which run in a ring shape with respect to the axis (2). The two end faces (67 and 68) are mutually spaced apart by a length which is greater than the summed length of the inner peripheral surfaces (59 and 63) of the body (57) and which is suitable for permitting the function which will be described below.

Each of the end faces (67, 68) connects the inner circumferential surface (66) to an outer circumferential surface (69, 70) which is cylindrical with respect to the axis (2). The outer peripheral surface (69) which delimits the piston (64) in the direction of removal from the axis (2) in the region facing the tube (58) has a diameter which is slightly smaller than that of the inner peripheral surface (59) of the Body (57) with which it is tightly connected via a seal (21) annular to the axis (2). The outer circumferential surface (70) has a diameter which is slightly smaller than that of the inner circumferential surface (63), but in the vicinity thereof, in such a way that a mutual sliding guide along the axis (2) is established, which on the one hand between the surfaces (69 and 59) has a sealing function with the aid of the seal (71) and, on the other hand, has no sealing function between the surfaces (70 and 63).

The outer circumferential surfaces (69 and 70) are connected to one another inside the body (57) by means of a flat shoulder (72) which is annular to the axis (2) and which is opposed in the longitudinal direction to the shoulder (62) of the body (57) such that a constant longitudinal distance remains under the normal functional conditions, on the one hand because the outer circumferential surface (69) has a longitudinal dimension that is significantly smaller than the longitudinal dimension of the inner circumferential surface (59), and on the other hand because a coil spring (73) coaxial with the axis (2) is present, which is wound around the outer peripheral surface (70) between this and the inner peripheral surface (59) and which is compressible in the longitudinal direction between the shoulders (72 and 62).

In the absence of compression of the spring (73), as shown in Fig. 8A, the end face (67) of the piston (64) is flush with the chamber (60) and at maximum elastic compression of the spring (73), as is the case 8B, the end face (67) is longitudinally offset in the direction from the tube (58) and the chamber (60), which on the one hand results in a retracted rest position of the body (64) in the body (57) and on the other hand corresponds to an active, projecting position of the piston (64) out of the body in the direction of the bearing journal (7), with which a tight contact then occurs with the aid of an annular seal (74) which is coaxial with the axis (2) and which firmly attaches the end face (68) is attached.

A person skilled in the art will easily understand that when the line (53) is under atmospheric pressure, the piston (64), which is exposed to atmospheric pressure on the one hand in the area of the end face (67) and on the other hand in the area of the end face (68) and its shoulder (72), however, is loaded with the spring (73), assumes its retracted position, but, if the spring (73) is suitably designed, reaches its projecting position when the line (73) is supplied with compressed air from the Source (52) is supplied, which acts on the end face (67), while the atmospheric pressure continues to act on the end face (68) and the shoulder (72). It will therefore maintain this position as long as the pressure of the compressed air from the source (52) acts. The atmospheric pressure on the area of the end face (68) surrounded by the seal (74) is replaced due to the fluidic connection to the inside of the line (63), while the atmospheric pressure continues on the rest of the end face (68) and the shoulder (72 ) is effective. The piston (64) returns to its retracted position when the atmospheric pressure in the line (53) is restored.

In the longitudinal direction with respect to the connection (54), i.e. more precisely the end face (68) provided with the seal (74), the bearing journal (7) has a flat annular surface (75) which is coaxial with the axis (2) and which adjoins an opening (76) of a line (77) which runs along the axis (2) is provided in the bearing journal (7) and is limited, for example, on the inside by a circumferential surface which is cylindrical to the axis (2) and whose diameter is slightly smaller than that of the inner circumferential surface (66) of the piston, the diameter of which is itself such that their cross section is slightly smaller than the cross section of the line (53).

The lines (53 and 77) have thus been brought into fluid communication so that the line (77) is supplied with compressed air which comes from the source (52) when the piston (64) assumes its projecting position, which in Fig. 8B is shown, wherein the seal (74) fits tightly against the surface (75) of the journal (7) around the mouth (76) of the line (77). As will become clear later, this sealing relationship arises due to a suitable actuation of the valve (55) when the carrying cylinder (1) stops or during a short phase of its rotation in the direction (10) about the axis (2) at reduced speed when a pressure plate on the peripheral surface (8) of the support cylinder (1) (9) is attached. The rotation of the support cylinder (1) thus causes the seal (74) to slide on the surface (75) of the bearing journal (7), the tight relationship between them being maintained. However, the piston (64) assumes its retracted position shown in Fig. 8A controlled by an appropriate position of the valve (55) when the support cylinder (1) rotates to print. The line (77) is then open between the seal (74) and the frontal surface (75) directly to the ambient air.

As shown in FIG. 9, the line (77) extends into the interior of the support cylinder (1) and connects there tightly to a line (79) which runs essentially radially with respect to the axis (2) and which has a cross section, which corresponds to the cross section of the line (77) or is slightly less than this.

This line (79) opens in the longitudinal direction via a right-angled connection in a cavity (80) of a transverse flange (81). The transverse flange (81), which is firmly connected to the transverse surface (5) of the support cylinder (1) between the latter and the bearing (188) for the housing (3), surrounds the axis (2) in a ring around the bearing journal (7) and carries one of the bearings of the torsion bar (32) in a fixed but adjustable manner. The bearing journal (6) is surrounded in the same way with a transverse flange (82), which likewise has a ring shape which is essentially coaxial with the axis (2) and which is fixedly attached to the opposite transverse surface (4) of the supporting cylinder (1) and which likewise the other bearing (33) of the torsion bar (32) is fixed but adjustable. Each of the flanges (81, 82) defines, with the associated transverse surface (4, 5) of the support cylinder (1), a receptacle (83, 84) for each of the levers (35, 36) that hold the tension rod (28) and the rod Connect (39) between the two holes (11, 12).

9A and 9B show, the cavity (80) surrounds a longitudinal axis (85) which at least approximately coincides with the axis (16) of the bore (12). It opens in the direction of the transverse surface (5) of the support cylinder (1) in a transverse surface (86) of the receptacle (83), which is arranged with respect to the lever (36) opposite the transverse surface (5). In the direction away from the axis (85) it is delimited by an inner circumferential surface (87) which is cylindrical to the axis (85) and has a diameter which is significantly larger than the diameter of the bore (12). The surface (87) connects to the surface (86) a transverse, flat bottom surface (88) in which the curved line (79) opens at least approximately in the axis (85).

The cavity (80) thus forms a longitudinal cylinder, inside which a piston (89) can move in order to form a telescopic supply connection (95) which has great analogies with the supply connection (54) with which it is connected by means of the lines (77 and 79) is connected in series to ensure compressed air supply to the bellows (49) when the piston (64) is in its projecting position, which is shown in Fig. 8B.

The piston (89) is bounded in the direction away from the axis (85) with an outer circumferential surface (90) which is cylindrical to the axis (85) and has a diameter which is smaller than the inner diameter (87) but is sufficiently adjacent to it to form a mutual guide contact by means of a sealing ring (91) which is fixedly attached to the outer peripheral surface (90). The piston (89) is bounded to the bottom (88) of the cavity (80) and to the opposite side by two flat transverse surfaces (92, 93) which are at a mutual distance which is less than the longitudinal dimension of the inner peripheral surface (87) of the Cavity (80).

Each of the surfaces (92 and 93) connects the outer peripheral surface (90) of the piston (89) to an inner peripheral surface (94) of the piston (89), which is cylindrical with respect to the axis (85) and has a diameter which is equal to or substantially the same as the diameter of the inner peripheral surface (78) of the line, around a line (102) penetrating the piston (89) ) along the axis (85) which is closely related to the lines (77 and 79).

One skilled in the art will readily understand that introducing compressed air from the source (52) into the cavity (80) will longitudinally drive the piston (89) into an active position from this cavity (80) when the surface (93) initially Is exposed to atmospheric pressure. As soon as the cavity (80) is exposed to atmospheric pressure by means of the lines (77 and 79), in particular when the supply connection (54) is in the position shown in FIG. 8A, the piston (89) is in a rest position for a withdrawal movement released inside the cavity (80), since its surface (93) is loaded with a pressure above atmospheric pressure - first only in the middle and then overall - due to the conditions to be described.

In order to temporarily cooperate with the telescopic supply connection (95) which is formed by means of the cavity (80) of the flange (81) and the piston (89), the bellows (49) is provided with a connection (96) which is made up of a part is formed, which is arranged in the axis (41) fixed on the lever (36), which otherwise rigidly supports the profiled rod (39) and with the help of the bellows (49).

The connection (96) opposite the surface (93) of the piston (89) has a flat transverse surface (97) which is annular to the axis (41) and merges into an inner peripheral surface (98) which is cylindrical to the axis (41) and the connection (96) penetrates in order to receive a pipe (100) for inflating and deflating the bellows, which has a passage cross section, with a mutual seal, for example a sealing ring (99) coaxial with the axis (41) which is substantially identical to that of the line (102). All suitable passages are provided in the interior of the profiled rod (39) in order to receive the tube (100) in a manner which is not shown but which is easy for a person skilled in the art to understand.

In the direction away from the axis (41), the surface (97) of the connection (96) adjoins an edge (101) projecting over the surface (97), which has an annular shape with respect to the axis (41) and whose diameter is such that regardless of the position of the profiled rod (39) in the interior of the bore during normal operating conditions, the line (102) of the piston opens within the rim (101). A suitable dimension of the edge (101) for this function is within the normal skill of a person skilled in the art.

In the direction of the surface (93), the edge (101) is delimited by a flat edge (103) against which the surface (93) of the piston lies flat and in a sealing manner when compressed air coming from the source (52) pushes the piston ( 89) from the cavity (80). The edge (101) thus simultaneously forms a seal and a stop which opposes the piston (89) so that it cannot be driven out of the cavity (80) to the extent that its seal is lost with the aid of the sealing ring (91) , whereby a continuous transfer of compressed air from the source (52) is achieved with the aid of the supply connection (54) then taking its state according to FIG. 8B and the supply connection (95) then taking its position according to FIG. 9A, so that the bellows ( 49) is inflated. The piston (89) is exposed to the pressure of the compressed air coming from the source (52) over its entire surface (92) and on the part of its surface (93) lying inside the edge (101), while that outside the edge (101 ) lying part of the surface (93) remains exposed to atmospheric pressure, so that the position of the piston (89) is maintained during inflation. The inflation is with a certain shift the profiled rod (39) accompanies inside the bore (12), but since the edge with its edge (103) slides on the surface (93) of the piston (89), the mutual tightness is maintained, the fluidic connection between the internal line (102) of the piston (89) and the tube (100) of the bellows (49) due to the dimensioning of the edge (101) already mentioned remains.

When the connection between the line (53) and the source (52) is interrupted and the line (53) is then connected to the outlet (56), the supply connection (54) takes its position shown in FIG. 8A under the action of the spring (73) so that the cavity (80) is connected to the free air, ie surface (92) of piston (89) is exposed to atmospheric pressure. Its surface (93), on the other hand, which is also exposed to atmospheric pressure in the zone outside the edge (101), is exposed inside the edge (101) to the excess pressure generated inside the bellows (49) during the previous inflation. This overpressure drives the piston (89) into the interior of the cavity (80), so that a gap (104) is formed between the edge (103) of the edge (101) and the surface (93), which prevents the escape of in the bellows ( 49) contained compressed air to the interior of the receptacle (83) enables the outlet openings, not shown, to connect to the atmosphere. The bellows (49) thus empties as far as the torsion bar (32), which acts in the direction (34) on the tensioning bar (28) via the levers (35, 36), tries the profiled bar (39) in the sense of a Compress the bellows (49) inside the bore (12).

The telescopic supply connections (54 and 95) are particularly suitable for a temporary supply of compressed air to the bellows (49). You can also find other applications, particularly in the case of fluids other than compressed air, the nature of which fluids could include leaking into a reservoir rather than the ambient air low pressure takes place, from which the source (52) for the pressure medium could be supplied.

In the device described, the temporary inflation of the bellows (49) has the purpose of allowing the rear end fold (26) to be hooked in or unhooked to a pressure plate (9) which is otherwise held on a nose by its front end fold (24) The venting of the bellows (49) ensures that the wound printing plate (9) is held in a tensioned state on the outer surface (8) of the support cylinder (1), in particular during the printing process.

However, other means could be used for this purpose, one embodiment of which has been illustrated in Figures 15, 16, 16A, 16B.

These figures represent an actuator (105) which is intended to replace the assembly formed by the profiled rod (39) and the bellows (49).

This actuator (105) contains a rigid body (106) which is intended to be arranged in a longitudinal extension in the bore (12) and to be connected to the levers (35 and 36) in order to secure the latter to one another by means not shown but rigidly interconnect means which are easily implementable by a person skilled in the art.

The body (106) is tubular and has inner and outer peripheral surfaces (107 and 108) cylindrical to the axis (41) when referring to its mounting position with respect to the levers (35 and 36). The outer circumferential surface (108) has a smaller diameter than the inner circumferential surface (14) of the bore (12) in order to maintain the possibilities of sliding inside which have been described in relation to the profiled rod (39) and that of a rotation around the axis (15) of the rod (28), the profiled rod (39) and corresponds to the two levers (35, 36) connecting them to one another.

With its inner circumferential surface (107), the body (106) delimits a longitudinal recess (109) which encloses an inflatable bellows (110) which is comparable overall to the bellows (49). This bellows (110) is closed at one end in the immediate vicinity of the lever (35), not shown in the drawing, by means of a plug (111) screwed into the body (106), while its other end is tightly connected to a part (112) , which is screwed into the other end of the tubular body (106) in the region of the lever (36) and which firmly receives the connection (96), which may be for this purpose in its parts facing the bore (12) in one for the person skilled in the art is easily imaginable modified.

The body is on the same side with a plurality of elongated windows (113), which is oriented in the direction (34) with respect to the axis (15), along a central plane which is aligned in accordance with the previously described central plane (47) and for which the reference number 47 has been retained ) perforated, which are identical to each other and distributed at equal longitudinal distances. Six such windows (113) are shown as an example, but it should be noted that a different number can also be implemented.

In each of these windows (113) an insert (114) is arranged to slide radially to the axis (41) and is supported on the inflatable bellows (110) inside the tubular body (106).

One skilled in the art will readily understand that when the bellows (110) is inflated under the identical conditions to inflate the bellows (49), the inserts (114) are expelled out of the body (106) as shown in FIG. 16B. This shifts the body (106) inside the Bore (12) and causes rotation of the tension rod (28) against the direction (34) with an increase in the load on the torsion bar (32) until the body (106) against the direction (34) on the inside of the bore (12 ) supports. Thereafter, under the same conditions described in connection with the bellows (49), the bellows (110) is vented, as shown in Fig. 16A. The torsion bar (32), which causes the tensioning bar (28) to rotate in the direction (34) inside the bore (11), causes the inserts (114) to pull back against the inner peripheral surface (14) of the bore (12 ) into the body (106) until the levers (35 and 36) rest against the adjustable stops (37).

Of course, all other actuators, in particular, but not exclusively, simple pneumatic actuators carried by the supporting cylinder (1) in connection with a second supply of pressure medium, for example compressed air, can also be used with the means already described in order to alternatively place the tension rod in a Alignment according to the possibility of hooking or unhooking the rear end fold of a pressure plate, or an orientation which holds this wound pressure plate in a tensioned state on the outer circumferential surface (8) of the support cylinder (1). This can be done with the aid of means carried by the tension rod (28), which are described in particular with reference to FIGS. 1, 2, 3A, their function being that with reference to FIGS. 3B, 4 to 7, 10 to 14 and in a variant will be described with reference to FIGS. 17A, 17B.

These means are partially fixed and partially releasably attached to the longitudinal flattened portion (30) of the tensioning rod (28) and in particular contain a plurality of flat, elongated leaf springs (115) which are identical and evenly distributed over the length of the tensioning rod (28) and which are detachable are held on the flattened portion (30) of the tensioning rod (28).

The flattened portion (30) is arranged in the direction (10) in front of the axis (15) and points in all orientations of the tension rod (28) against the direction (10) in front of the axis (15) under normal operating conditions, in particular in the end orientations. . The flat (30) has two flat, identically aligned parts between which the receptacle (31) of the torsion bar (32) opens, i.e. a part (116) lies on the same side as the stop (38) with respect to the receptacle (31), to which the part (116) is set back in the direction of the axis (15). The part (116) is connected to this stop (38) by means of a flat longitudinal shoulder (117). A part (118) of the flattening is arranged between the receptacle (31) and a further longitudinal shoulder (119) which connects this part (118) to a longitudinal stop (120) which connects the end of the outer peripheral surface (29) of the tensioning rod (28 ) forms against the direction (34).

The parts (116 and 118) of the flattened portion (30) are arranged parallel to a common geometric plane, not designated, which runs through the stops (38 and 120) and parallel to the axis (15). With regard to this plane, part (116) is advantageously set back relative to part (118) towards axis (15). Compared to this plane, the part (116) has a nose (185) projecting in the direction (34), which is formed by the shoulder (117) and the outer peripheral surface (29) of the tensioning rod (28) and the stop (38) of which is the end in the direction of (34).

On the part (118) in the same number as leaf springs (115) plates (121) are attached, which rest flat over their entire length on the part (118) of the flat (30) and which hold the receptacle in two outer end regions (122) cover the torsion bar, reaching into the area of the part (116). In an intermediate area (123), between the two end areas (122), the plates partially cover the receptacle (31) without reaching to the part (116).

The plate (121) is delimited by two longitudinal main surfaces parallel to one another and to the axis (15), of which only the surface (124) facing away from the axis (15) is described. The shape of the other surface with which the plate (121) just rests on the part (118) of the flat (30), as has already been stated above, is derived from the shape of this surface (124) via the parallelism.

Due to a suitable dimensioning, the surface (124) of the plate (121) lies essentially in a common plane with the stops (38 and 120) and adjoins this stop (120) over the entire longitudinal extent of the plate (121) with a straight longitudinal edge (125). In the end regions (122), the surface (124) in the direction (126) from the stop (120) to the stop (38) in each case connects to the part (116) of the flattened portion (30) by means of a longitudinal edge (127) flat, rectangular longitudinal section (129) which is oriented approximately 45 ° with respect to the remaining part of the surface (124) in such a way that it continuously approaches the part (116) of the flattened portion in the direction (126). In the intermediate region (123), the surface (124) with a longitudinal edge (128) arranged in the same plane of the part (116) of the flat (30) runs in the direction of the receptacle (31) of the torsion bar (32) by means of a flat, rectangular one Longitudinal section (130), which has the same orientation as the sections (129) in order to continuously approach the receptacle (31).

In the longitudinal direction, the surface (124) is delimited by transverse edges (131) of the plate (121), which mutually connect the edge (125) and an edge (127). The surface (124) is further delimited by transverse edges (132) of the plate (121), each of which connects an edge (127) with a U-shaped incision (133) which is approximately at the end of the receptacle (31) of the torsion bar ( 32) coincides in the direction (175) against the direction (126). The U-shaped incisions (133) each connect the edge (132) with a transverse edge (134) of the plate (121) adjoins the edge (128) and thereby delimits the section (130) in the longitudinal direction.

Functionally, the plate (121) can be regarded as a one-piece part with the tension rod (28), on which it has the same surface as the parts (116 and 118) of the flattened portion (30) (124) and with the stops (38 and 120) forms a flattening that is interrupted locally, ie between the transverse edges (132) of the end regions (122) and along the stop (38), which can also be seen as represented by the tension rod (28) itself.

The plate (121) is fastened to the part (118) of the flat (30) on which it lies flat by means of screws (135), here three in the intermediate area (123) and one in the end areas (122). The screws (135) are each screwed in an axis (136) perpendicular to the part (118) of the flat (30). The axes (136) are arranged in the same plane parallel to the axis (15) and are evenly distributed in the longitudinal direction. Five of these screws are shown as a non-limiting example, although other numbers can of course be selected.

Each of these screws (135) has a head (137) opposite the part (118) of the flat (30). In the end zones (122), the heads are supported directly on the surface (124) of the plate (121). In the intermediate areas (123), the heads (137) are not supported directly on the plate (121), but with the interposition of a flat strip (138) of a leaf spring (139) which has a shape which will be explained later. The strip (138) is in contact with the heads (137) of the screws and washers (140) in question. The washers (140) have the same thickness in the longitudinal direction of the axis (136) for all screws (135) in question, between the bar (138) of the leaf spring (139) and the surface (124) of the plate (121) in the area (123) a longitudinal guide (141), which has a constant width in the direction parallel to the axes (136) of the screws (135), ie perpendicular to the bar (138) and the surface (124) of the plate (121) in the intermediate region (123 ). This width is approximately the same and practically somewhat larger than a predetermined, constant thickness of the leaf spring (115).

In the longitudinal direction, the leaf spring (139) is delimited by transverse edges (142), which are at a distance from one another in the longitudinal direction, which is between the distances between the transverse edges (134) of the plate (121) and the transverse edges (132) of this plate (121) so that the transverse edges (142) of the U-shaped incisions (133) of the plate (121) are arranged opposite.

In the direction (175) opposite to the direction (126), the leaf spring (139) is delimited with a longitudinal edge (143) of its bar (138). The position of this edge (143) is arbitrary as long as it describes a geometrically cylindrical path around the axis (15) with a diameter corresponding to the inner peripheral surface (13) of the bore (11). This also applies in the same way to the heads (137) of the screws (135). This edge (143) is set back with respect to the edge (125) of the plate (121) in the illustrated embodiment.

In the direction (126), opposite the edge (143), the strip (138) of the leaf spring (139) connects via a longitudinal fold (144) to a further, flat, longitudinal strip (145) in such a way that it progressively fits in Direction (126) moves from a plane extending the bar (138), ie also from the flattened portion (30), in which it is oriented approximately 45 ° with respect to the bar (138). The fold (144) is arranged in the section (123) approximately opposite the connection between the section (130) of the surface (124) of the plate (121) and the rest of this surface.

Opposite its connection to the bar (138) along the fold (144), the bar (145) itself passes through an approximately semi-cylindrical longitudinal fold (146) through 180 ° into a bar (147) which is on the flattened portion (30) facing side is parallel to it. The longitudinal fold (146) also lies within the cylindrical envelope, which is defined by the inner peripheral surface (13) of the bore (11). In the absence of a deformation stress of the leaf spring (139), i.e. in the absence of the leaf spring (115) to be explained, the bar (147) is at a distance from the bar (146).

The flat bar (147) is aligned approximately perpendicular to the section (130) and ends directly opposite it with a longitudinal stop (148). In the absence of an elastic deformation force for the leaf spring (139), the longitudinal stop (148) is a distance away from the section (130) by a distance which corresponds approximately to the thickness of a leaf spring (115) in order to cooperate with such a leaf spring to open it to hold the flattened portion (30) of the tensioning rod (28) by means of the plate (121) under the conditions described below.

The stop itself is advantageously defined in a manner not shown by folding the leaf spring (139) back to the level of its bar (147).

In order to cooperate on the one hand with the rear end fold (26) of a pressure plate (9) and on the other hand with the tension rod (28), in particular with the aid of the respective leaf spring (139), each leaf spring (115) has a shape which will now be described.

This shape of the leaf spring (115) is essentially flat and rectangular and is defined by two essentially flat, mutually parallel surfaces (149, 150) which define the thickness of the leaf spring (115) already mentioned between them. If the leaf spring (115) is considered attached to the tension rod (28), the surfaces (149 and 150) point backwards and forwards with respect to the direction (10).

The two surfaces (149, 150) are delimited by two transverse edges (151) which are spaced apart in the longitudinal direction, which is identical to the distance between the edges (131) of the plate (121) with which they coincide when the Leaf spring (115) is mounted on the tension rod (28). They are also delimited by two longitudinal edges (152, 153), one of which points in the direction (175) opposite the direction (126) and the other in the direction (126) when the leaf spring (115) is mounted on the tension rod (28) . The edge (152) then coincides with the edge (125) of the plate (121) and with the edge (143) of the strip (138) of the leaf spring (139).

Along the edge (152) there are as many notches (154) as there are screws (135), with a longitudinal division corresponding to that of the screws (135) and with a dimension which in function of that of the heads (137) of the screws (135) and the spacer washers (140) are selected such that the leaf spring (115) in the state mounted on the tensioning rod (28) is received in an edge region (155) inside the guide (141), and that the notches are each on the heads (137) the screws (135) in the end regions (122) of the plate (121) and on the spacers (140) in the intermediate region (123) fit so that they are against both the heads (137) and the spacers (140) Support in the longitudinal direction in both directions and in direction (175) against direction (126), whereby the leaf spring (115) is fixed in both longitudinal directions and in direction (175) against direction (126) with respect to the tension rod (28). A fixation of the leaf spring (115) in the direction of the axes (136) is ensured by the dimensions of the guide (141) in relation to the thickness of the leaf spring (115) between the surfaces (149 and 150).

In a longitudinal region (156) that extends along the edge region (155) and that with the section (130) of the surface (124) of the plate (121) and with the stop (148) of the strip (147) of the leaf spring (139 ) coincides, the leaf spring (115) has in its surface (149) a Lämgsrille (157), which corresponds approximately to a rib (148) of the surface (150) with the thickness of the leaf spring (115) between the surfaces (149 and 150) . This groove (157) and this rib (158) extend over a dimension in the longitudinal direction which essentially corresponds to the dimension in the longitudinal direction which separates the transverse edges (142) of the leaf spring (139). This groove (157) and this rib (158) extend in a longitudinal dimension between the respective transverse bottoms (159) of longitudinal notches (160) which are fitted in the transverse edges (151) of the leaf spring (115) such that the rib (158 ) does not form an obstacle when the leaf spring (115) is attached with its surface (150) to the surface (124) of the plate (121), in particular in the end regions (122). Otherwise, the rib (158) forms a projection on the surface (150) of the leaf spring with a thickness which corresponds essentially to the distance that the surface (124) of the plate (121) from the part (116) of the flat (30 ) separates.

In relation to the shape of the portion (130) which is inclined approximately 45 ° with respect to the rest of the surface (124) of the plate (121), the groove (157) and the rib (158) along the edge region (155) of the Leaf spring (115) each defined by a flat longitudinal section (161, 162) with a rectangular cross-section and form a shoulder that is approximately 45 ° to the rest of the corresponding associated surface (149, 150) in the edge region (155) of the leaf spring (115) is aligned. If the leaf spring (115) is inserted with its edge region (155) into the guide (141) and is supported with the notches (154) in particular on the spacer disks (140), then the section (162) of the rib (158) rests the section (130) of the surface (124) of the plate (121), or is in the immediate vicinity of this section (130). Then the bar is supported (147) the leaf spring (139) with its stop (148) flat on the section (161), the stop (148) being aligned at approximately 90 ° to it. The stop (148) then forms a cam for the leaf spring (115) in the direction (126), whereby the leaf spring (115) is locked with respect to the tension rod (28).

The transition of the sections (161, 162) to the rest of the surfaces (149 and 150) in the direction (126) occurs in each case via a section (163, 164), the shape of which is selected such that it does not oppose this locking. The two sections (163, 164) have, for example, a flat, rectangular, elongated shape and are aligned, for example, perpendicular to the sections (161, 162). As a result, they are about 45 ° to the rest of the faces (149 and 150).

Preferably, the section (164) is offset with respect to the edge (152) of the leaf spring (115) in the same manner as the shoulder (117) with respect to the stop (148) of the strip (147) of the leaf spring (139), which makes it easier for everyone to assemble Leaf spring (115) on the tension rod (28) from the mouth (20) via the slot (19) easier.

For this purpose, the leaf spring (115) is presented in the extension of the slot (19) outside of it in such a way that its edge (152) is aligned in the longitudinal direction and points in the direction (175) opposite to the direction (126) that each notch ( 154) is aligned in the direction (126 and 175) with the spacer washers (140) or the heads (137) of the screws (135) which they are to encompass, as shown in FIG. 3A. The tension rod (28) preferably assumes its end orientation shown in FIG. 1, which corresponds to the vented state of the bellows (49) and in which the levers (35, 36) bear against the stops (37) in direction (34).

By holding the leaf spring (115) in the immediate vicinity of its edge (153) and then displacing it in the direction (175) with respect to the support cylinder (1), the edge region (115) is inserted into the slot (119) which corresponds to the flattened portion (30 ) is opposite, whereby the edge (152) is continuously introduced between the strip (147) of the leaf spring (139) and the surface (124) of the plate (121) in the end regions (122). Then in the course of the further displacement, the edge (152) abuts against the bar (147) of the leaf spring (139), the rib (158) of the surface (150) of the leaf spring (115) which has already exceeded the stop (38) , is located opposite the part (116) of the flat (30), which makes it possible to lay the leaf spring (115) flat with its surface (150) on the surface (124) of the plate (121) in the area (122) . Then, by manually pushing the edge (153) of the leaf spring (115) in the direction (175) opposite to the direction (126), as shown in FIG. 3B, the strip (147) is elastically retracted Leaf spring (139) caused, the stop (148) is then supported on the surface (149) of the leaf spring (115). When the edge region (155) of the leaf spring (115) is inserted further into the guide (141), the rib (158) of the surface (150) engages between the transverse edges (132) of the end regions (122) of the plate (121), whereby the notches (154) engage with the spacers (140) or the screw heads (137) until they come to a stop in direction (175).

Then the stop (148) of the strip (147), which was previously held back by the support on the surface (149) of the leaf spring (115), reaches the area of the groove (157), as a result of which it is released and becomes underneath approximately 90 ° on the section (161) due to elastic relaxation of the leaf spring (139), whereby the locking of the leaf spring (1159 is achieved in the end position.

An edge region which adjoins the edge (153) and which is in the form of a hook-shaped, rearward with respect to the direction (10), of the surface (115) projecting longitudinal edge (165) is then aligned with the cylindrical, geometric envelope about the axis (2) of the outer peripheral surface (8) of the support cylinder (1), as shown in Fig. 1 in an upper End position is shown.

It can be seen that in order to achieve the interaction of the notches (154) with the spacer disks (140) and the screw heads (137) for exact alignment of the edge region (155) of the leaf spring (115) at the end of the insertion into the guide (141) an aid can be used by means of a longitudinal stop of the rib (158) against the transverse edges (132) delimiting the end regions (122) of the plate (121) by means of the bottoms (159) of the notches (160), which are therefore spaced apart from one another in the longitudinal direction , which is approximately the same and slightly less than the longitudinal spacing of the edges (132). A transverse stop of the same rib (158) by means of its section (162) in the direction (175) on the section (130) of the region (123) of the plate (121) is also helpful.

It can be seen that the mounting of a leaf spring (115) on the tension rod (128) takes place exclusively from the mouth (20) of the slot (19), i.e. no special work in the area of the tension rod (28) is required. Any alignment of the tension rod (28) about its axis (15) under normal operating conditions is suitable, although it is preferred that the tension rod (28) be brought into the orientation corresponding to the vented bellows (49) for this purpose.

This also applies to the disassembly of the leaf spring (115), which is done with the aid of a tool shown in FIG. 4 according to a procedure shown in FIGS. 5 to 7.

In order to disassemble the leaf spring (115), it is necessary to release the section (161) of the groove (147) in the direction (126) by moving the stop (148) of the leaf spring (139) away.

For this purpose, any flat tool can be inserted between the surface (149) of the leaf spring (115) and the upstream flank (21) of the slot (19) to apply pressure to the longitudinal flat surface of the strip (147) of the leaf spring ( 139) to exercise, which lies between the fold (146) and the stop (148). This surface forms an actuating surface for the leaf spring (139), whereby the bar (147) is moved back elastically in the direction of the bar (145). When the section (161) is released, it is sufficient to exert a tensile force in the direction (126) on the edge (153) of the leaf spring (115) in order to be able to pull the leaf spring (115) out.

Since it is difficult to grasp the edge (153) directly, a tool (166) is provided for this purpose, which is shown in FIG. 4 and can also be seen in FIGS. 5 to 7. This tool (166) serves for simultaneously releasing the section (161) and for gripping the hook-shaped edge (165) of the edge (153) of the leaf spring (115) in order to facilitate its removal.

The tool (166), which can be easily made from two plates welded together, is essentially in the form of a flat, rectangular plate which is thin enough to pass over the mouth (20) between the leaf spring (115) and the upstream Flank (21) of the slot (19) can be inserted, but is also thick enough to be firm.

The tool (166) has two substantially flat, mutually parallel surfaces (167, 168) which are intended to point upstream and downstream with respect to the direction (10) during use. The tool (166) has a rectilinear insertion edge (169) which is intended to be aligned in the longitudinal direction and to rest against the surface of the bar (147) of the leaf spring (139) in order to move away from the section (161) the surface (149) of the leaf spring (115) to release the stop (148) of this strip (147).

The insertion edge (169) of the tool (166) shown in FIGS. 5 to 7 in different working positions has a longitudinal dimension which essentially corresponds to the longitudinal distance between the edges (142) of the leaf spring (139). The insertion edge (169) connects with its two ends to a likewise straight transverse edge (170), which are designed to at least approximately coincide with the edges (142).

In relation to their transition to the edge (169), the edges (170) as well as the surfaces (167 and 168) are curved up to an edge (171) parallel to the edge (169) in order to form a handle (172). This handle (172) remains at every working position of the tool (166) outside the slot (19) at a sufficient distance from the peripheral surface (8) of the support cylinder (1) to allow easy handling of the tool (166). The dimensioning of this distance lies in the normal abilities of a person skilled in the art who can also choose to replace the handle (172) by other means for gripping the tool.

In order to facilitate the extraction of the leaf spring (115) after the section (161) has been freed from the stop (148), the surface (168) of the tool (166) has a fixed, projecting longitudinal edge (173) which has a longitudinal shoulder (174 ) which points in direction (126). With respect to this direction, this shoulder (174) is at a distance from the edge (179) which essentially corresponds to the distance in this direction that the hook-shaped edge (165) of the leaf spring (115) has to the transition between the section (161) and the edge region (155), which enables the function that will be described with reference to FIGS. 5 to 7.

In order to release the leaf spring (115) fastened on the tension rod (28) and pull it out via the slot (19), the tool (166) is inserted into the slot by a movement in the direction (175) against the direction (126), whereby the edge (169) points in the direction (175) and the surface (168) which supports the edge (173) points in the direction (10), as shown in FIG. 5. The tension rod (28) assumes one of its normal operating orientations, preferably the orientation corresponding to a ventilation of the bellows (49). If during the movement the tool (166), the edge (169) of which progressively moves the bar (147) of the leaf spring (139) back towards the bar (145) by placing it against the actuating surface, its edge (169) begins between the stop ( 148) of the leaf spring (139) and the groove (157) of the surface (149) of the leaf spring (115), which causes the stop (148) to be supported elastically on the initial region of the surface (167), then the shoulder ( 174) the edge (143) of the leaf spring (115) and hooks with the hook-shaped edge (165), as shown in FIG. 6.

It is then sufficient, as shown in FIG. 7, to exert a tensile force on the tool (166) in direction (126) in order to pull out the leaf spring (115), the shoulder (174) of the tool (166) applying the force thus applied transmits the hook-shaped edge (165).

As soon as the bar (147) of the leaf spring (139) is released by the tool, it resumes its alignment parallel to the bar (145).

A new leaf spring (115) is introduced in the manner described with reference to FIG. 3B.

In an embodiment variant shown in FIGS. 3A and 4, the interaction of the tool (166) with the leaf spring (115) can be facilitated by means of a hole in order to facilitate their extraction (186) happen, which is arranged in the leaf spring (115) centrally between its transverse edges (115) and between the groove (157) and the longitudinal edge (153), for example also centrally, and by means of a fixed to the tool (166) Approach (187) is effected, which replaces the longitudinal edge (173) and which forms a projection from the surface (168) midway between its transverse edges (170) and such a transverse level that the approach (187) into the hole (186) of the Leaf spring (115) penetrates when the tool (166) introduced in the manner described above comes into a position such that the stop (148) rests on an edge region of the surface (167) adjoining the edge (169). The shoulder (187) forms on the surface (168) of the tool (166) a shoulder pointing in the direction (126) and is suitable for transmitting a tensile force to the leaf spring (115), which in this direction applies to the handle (172) of the Tool (166) is exerted, which allows the leaf spring (115) to be pulled out even if the hook-shaped longitudinal edge (165) should have broken.

The leaf spring (115) is dimensioned in the direction (126) such that when the tension rod (28) is aligned, which is shown in FIG. 13, the bellows (49) are partially inflated and the stop (18 ) with the transition of the downstream flank (22) of the slot (19) to the inner peripheral surface (13) of the bore (11) corresponds to the hook-shaped edge with the axis (2) cylindrical peripheral surface (8) of the support cylinder (1) in coincides approximately in the middle of the mouth (20). In this state, the leaf spring (115) rests without deformation with its surface (150) on the surface (124) of the plate (121), on the stop (38) and on the transition between the downstream flank (22) of the slot (19 ) and the inner peripheral surface (13) of the bore (11). In addition, the leaf spring (115) maintains a distance from the flank (22) of the slot (19), which is aligned accordingly.

In the final orientation of the tension rod (28) shown in Fig. 11, which is obtained by maximum inflation of the bellows (19), i.e. when the profiled rod (39) abuts the inner peripheral surface (14) of the bore (12), the stop (38) is opposite to the direction (34) to the transition between the downstream flank (22) of the slot (19) and the Circumferential surface (13) of the bore (11) is reset. The leaf spring (115) is then supported flat in the elastically deformed state on the downstream flank (22) of the slot (19), which forms a contact surface. Due to the rotation of the leaf spring (115) about the axis (15), its hook-shaped edge (165) protrudes slightly from the geometrical covering of the outer peripheral surface (8) of the support cylinder (1) with an upstream end position in the direction (10). The protrusion formed in this way is of the order of magnitude of 1.0 to 1.5 mm, these numerical values being given, for example, but not by way of limitation.

In the other end orientation of the tension rod (28) with respect to the axis (15) shown in FIG. 1, the leaf spring (115) assumes an alignment in an upper position with the hook-shaped edge (165) when it is not under tension , in which this follows the upstream flank (21) of the slot (19) at the level of the mouth (20), as shown in Fig. 1. In this end orientation of the tensioning rod (28), its stop (38) is offset in the direction (34) with respect to the orientation described with FIG. 13 or 11, the stop (38) into the mouth (18) of the slot up to approximately in whose middle protrudes.

The dimensioning of the leaf spring (115) necessary for this purpose lies in the normal abilities of a person skilled in the art.

It is recalled that the torsion bar (32) loads the tension rod (28) in direction (34), ie in the direction of the first End orientation in which the levers (35, 36) are supported on the stop means (37), as shown in Fig. 1.

Under these conditions, the winding and hooking of a pressure plate (9) on the outer peripheral surface (8) of the support cylinder (1) can be carried out in a semi-automatic manner, which will be described below.

At the beginning, the bellows (49) is vented so that the tension rod (28) and the leaf spring (115) assume their positions described in relation to FIG. 1.

While the support cylinder (1) stands still, the front end fold (24) of the pressure plate (9) is hooked onto the nose. Then the carrier cylinder (1) is rotated in the direction (10) about its axis (2) at a significantly slower speed than the speed used for printing. As this rotation progresses, a longitudinal roller (176) rotatably attached to the housing (3) about a transverse axis (177) is supported on the outer circumferential surface (8) of the support cylinder (1) by interposing the pressure plate (9) and causes a progressive Winding up the pressure plate (9). The resilient pressing of the roller (176) can result from its nature, for example if the roller is formed from an elastically compressible material, in which case the axis (177) can be arranged fixedly with respect to the housing (3), or it can be due to a elastic arrangement of the axis (177) on the housing (3) result by means known to a person skilled in the art.

In a manner also known to a person skilled in the art, the means with which the roller (176) is arranged on the housing (3) allow it to be moved back by hanging the front end fold (24) of the pressure plate (9) onto the nose (23) enable. Then the roller (176) is brought to bear against the pressure plate (9) immediately in the direction (10) after the nose (23).

After this application of the roller (176), the support cylinder (1) is rotated in the direction (10).

The bellows (49) mostly remains in the vented state during the circulation, i.e. until the roller (176) comes close enough to the slot (19) so that the rear edge (27) of the pressure plate (9) wound on the outer circumference (8) of the support cylinder (1) tends to enter the slot (19 ) penetrate, as shown in Fig. 11.

The bellows (49) is then inflated by the means described in relation to FIGS. 8A, 8B, 9, 9A, 9B or 15, 16, 16A, 16B, whereby the hook-shaped edge (165) of the leaf spring (115) in its outer end position is brought, in which it protrudes beyond the slot (19), as shown in Fig. 11.

Due to a suitable dimensioning of the pressure plate (9) between its folded ends (24, 26) with respect to the diameter of the outer peripheral surface (8) of the support cylinder (1) on the one hand and due to a sufficiently small dimensioning of the hook-shaped edge (165) in consideration of the mutual distance of the flanks (21 and 22) of the slot (19) on the other hand, the outer rear end of the pressure plate (9) immediately after the hook-shaped edge (165) is brought to the level of the mouth (20) of the slot (19). After the rotational movement of the support cylinder (1) has continued until the mouth (20) of the slot (19) is opposite the roller (176) which elastically pushes the rear end edge (27) of the pressure plate (9) into the slot ( 19) can occur, the bellows (49) is inflated, so that at the same time as the edge (27) of the pressure plate (9) penetrates into the slot (19), the hook-shaped edge (165) on its way to the retracted position penetrates into this slot (19), as shown in FIG. 12, first by a sliding movement of the leaf spring (115) on the ramp forming downstream flank (22) of the slot (19), and then by an increasing movement of the leaf spring (115) away from the flank (22).

Before the tension rod (28) has reached its rearward end orientation corresponding to the retracted end position of the hook-shaped edge (165) by turning about the axis (15) in the direction (34), this begins on the fold of the rear end (26) of the pressure plate (9) so that the continuation of the rotation of the tension rod (28) in the direction (34) up to its end orientation shown in Fig. 14 causes an elastic deflection of the leaf spring (115) so that it counter to the direction (34) its hook-shaped edge (165) is retained inside the rear end fold of the pressure plate (9), which is retained by its front fold (24) on the nose (23), the leaf spring (115) forcing in the direction (34) of the stop (38) of the tension rod (28) is pressed, as shown in Fig. 14, after the tension rod (28) has reached its final orientation.

After the bellows (49) has been vented in this way, the leaf spring (115) transmits a stress in the circumferential direction between the two outer folds (24 and.) Onto the pressure plate (9) wound on the outer circumferential surface (8) of the support cylinder (1) 26) due to the torsion bar (32). The magnitude of the tension is a function of the adjustment of the stops (37). The transmission of this tension between the pull rod (28) and the rear end fold (26) of the pressure plate (9) by means of the elastically curved leaf spring (115) makes it possible to maintain an approximately constant value for the tension applied to the pressure plate (9), even if this should lengthen slightly during the printing process due to a known phenomenon.

The roll (176) can then be withdrawn for printing.

Bleeding the bellows (49) and moving the tension rod (28) to its final orientation shown in Fig. 14 can be carried out during the slow rotation of the support cylinder (1) or while it has been stopped, such that the roller (76) , which is then still arranged opposite the mouth (20) of the slot (19), ensures an aid to the anchoring process by elastically tending to push the rear end fold (26) of the pressure plate (9) towards the support cylinder (1 ) to press.

Other means can be used for this purpose, one of which is shown as a non-limiting example in Figures 17A and 17B.

In the case of this variant, the roller (176) is replaced by an elongated pressure element (178) which, like the roller (176), extends over the entire longitudinal dimension of the outer peripheral surface (8) of the support cylinder (1).

The pressure element (178) is rigid, but opposite the outer circumferential surface (8) of the support cylinder (1) it has a coating (179) made of an elastic material, such as rubber, which can be compressed like the roller (176).

The pressure element (178) merges into a lever (180) in each of the two end regions. The two levers (180), which are identical to one another, can be pivoted on the housing (3) of the machine about a common longitudinal axis (181) which is offset in the circumferential direction of the axis (2) with respect to the pressure element (178).

The rod of an actuator (183) can be pivoted on each of the levers (180) about a longitudinal axis (182) offset from the axis (181). arranged, the body of which is articulated about a longitudinal axis (184) on the housing (3) of the machine. The axes (182 and 184) are common to the two actuators (183).

For a suitable supply of the actuators (183) with pressure fluid, in particular with compressed air, the pressure element (178) can be brought into an active position, which is shown in solid lines in FIG. 17A, in which it is elastic with its coating (179 ) on the outer peripheral surface (8) of the support cylinder (1) with the interposition of the pressure plate (9). If the supply of pressure fluid is interrupted, the pressure element (179) is moved back from the support cylinder (1) to a retracted position, which is shown in broken lines in FIG. 17A, in which it is further from the axis (2) of the support cylinder ( 1) is removed than in the active position.

A person skilled in the art will easily understand that if, during the winding of the pressure plate (9) onto the outer peripheral surface (8) of the support cylinder (1), the mouth (20) of the slot (19) and the rear end fold (26) of the pressure plate ( 9) opposite the still retracted pressure element (178), by causing it to be brought into the active position at the same time as controlling the movement of the tension rod (28) into its final orientation corresponding to the lower position of the hook-shaped edge (165), the joint movement of the penetration of the hook-shaped edge (165) and the rear edge (27) of the pressure plate (9) into the interior of the slot (19) under the conditions described in relation to the roller (176).

After anchoring is performed, the pressure element (178) is returned to its retracted position, which it maintains during printing.

Of course, one skilled in the art will readily understand that the technical context in which the present invention has been described, as well as the implementation of the invention that has been described, are only non-limiting examples, from which numerous changes can be made without departing from Is left within the scope of the present invention.

Claims (12)

Device for holding a printing plate (9) on a support cylinder (1) in a rotary printing press, the support cylinder (1) having an outer circumferential surface (8) cylindrical to an axis of rotation (2) of the support cylinder (1) and at least one longitudinal bore (11) on the inside ), which opens into the outer peripheral surface (8) by means of a longitudinal slot (19), with means (28, 115) for retaining in particular a rear end fold (26) of the plate (9) in the slot, which is otherwise in relation to the support cylinder (1) with a front edge (end edge 24) with respect to a predetermined direction of rotation (10) of the support cylinder (1) about its axis of rotation (2) is held by the plate (9) in the wound state on the outer peripheral surface (8) of the support cylinder (1) is tensioned, the means for retaining the rear end fold (26) including: - hook-forming means (115) with at least one radially to the axis of rotation (2) of the support cylinder (1) outer and counter to the direction of rotation hooks (165), - Means (28, 32, 39, 49, 105) for actuating the hook-forming means (115) which are at least partially arranged in the bore (11) of the support cylinder (1) and which are suitable for controlling the hook (165) in a controlled manner To reciprocate between a front end position relative to the direction of rotation (10) of the support cylinder (1) to enable the rear end fold to be hooked or unhooked on the hook (165) and a rear position relative to the direction of rotation of the support cylinder (1) End position to exert a tensile force against the direction of rotation (10) of the support cylinder (1) on the rear end fold (26) hooked on the hook (165), the hook (165) then entering the interior of the slot (19) with respect to the outer one The peripheral surface (8) of the support cylinder (1) is withdrawn, characterized in that that the hook-forming means (115) are embedded in the slot (19) and the hook (165) in the front end position protrudes over the outer circumferential surface (8) of the support cylinder (1), and that the fastening means (28, 39, 49, 105) are suitable for retracting the hook (165) in the during the movement from the front end position to the rear end position Slot (19) and during the movement from the rear end position to the front end position to cause the hook (165) to protrude with respect to the outer peripheral surface (8) of the support cylinder (1). Device according to Claim 1, characterized in that the actuating means (28, 32, 39, 49, 105) have a longitudinal tensioning rod (28) which is arranged in the bore (11) of the support cylinder (1) and which extends around a longitudinal axis (13) is rotatably guided, which is arranged between the axis of rotation (2) of the support cylinder (1) and the slot (19), and contain drive means (32, 39, 49, 105) in order to control the tension rod (28) about the axis of rotation (13 ) to reciprocate with respect to the support cylinder (1) between two end orientations corresponding to the front and rear end positions of the hook (165), and that the hook-forming means (115) contain at least one longitudinal blade (115) which has a first radially with respect to the Axis of rotation (2) of the support cylinder (1) has an inner end region (155) which is fixedly connected to the tension rod (28) inside the bore (11), and a second, longitudinal end region (edge 165) which is radially outside with respect to the Shoot axis of the support cylinder (1) and which forms the hook (165), the sheet (115) being elastically deformable between its first end region (155) and its second end region (165). Apparatus according to claim 2, characterized in that the drive means (32, 39, 49, 105) means (32) for resiliently loading the tension rod (28) in the direction of its end orientation corresponding to the rear end position of the hook (165) and means (39, 49, 105), which form a simple actuator that controls the tension rod in a controlled manner its end orientation is loaded according to the front end position of the hook (165). Apparatus according to claim 3, characterized in that the means (32) for elastically loading the tension rod (28) include a torsion bar coaxial therewith. Device according to one of claims 2 to 4, characterized in that the first edge zone (155) of the blade (115) is detachably connected to the tension rod (28). Device according to one of claims 2 to 5, characterized in that the sheet (115) with respect to the direction of rotation (10) of the support cylinder (1) in front of the axis of rotation (15) of the tension rod (28) between its first edge region (155) and its second Edge region (165) runs along the tension rod (28). Apparatus according to claim 6, characterized in that the tensioning rod (28) has a longitudinal nose which is arranged between its axis of rotation and the slot and which extends from behind with respect to the direction of rotation (10) of the support cylinder (1) between the first edge zone (155) and the second edge zone (165) abuts the sheet (155). Device according to one of claims 2 to 7, characterized in that the second edge zone (165) with respect to the second edge zone (155) is offset forward with respect to the direction of rotation (10) of the support cylinder (1). Apparatus according to claim 8, characterized in that the slot is bounded forwards with respect to the direction of rotation (10) of the support cylinder (1) by a longitudinal, front flank (22) which is in relation to the outer peripheral surface (8) of the support cylinder (1 ) is inclined so that it is based on this circumferential surface with respect to the direction of rotation (10) of the support cylinder (1) before its transition to the bore (11) of the support cylinder (1). Device according to one of claims 1 to 9, characterized in that the slot with respect to the direction of rotation (10) of the support cylinder (1) is bounded to the rear by a longitudinal rear flank (21) which with respect to the outer surface (8) of the Support cylinder (1) is inclined such that it connects to the outer surface (8) in relation to the direction of rotation (10) of the support cylinder (1) before its transition to the bore (11) of the support cylinder (1). Device according to claims 9 and 10, characterized in that the front and rear flanks (21, 22) of the slot (19) are parallel to each other. Rotary printing press, comprising a housing (3) and a support cylinder (1) which has an outer circumferential surface (8) which is cylindrical with respect to a longitudinal axis of rotation and which contains at least one longitudinal bore (11) on the inside which extends in the outer circumferential surface (8) opens a longitudinal slot (19), characterized in that it contains a device according to one of claims 1 to 11, a longitudinal pressure element (178) opposite the outer peripheral surface (8) of the support cylinder (1) and means (180) for holding of the pressure element (178) on the housing in a movable manner between a support position elastic to the axis of rotation (2) on a pressure plate (9) which is attached to the support cylinder (1) with its front edge and during winding by means of rotations of the support cylinder (1) about the axis of rotation (2) in the given direction of rotation (10) on the outer peripheral surface (8) of the support cylinder (1), and one for ckgezogenen the elastic supporting position of the axis of rotation (2) back position, and in that the actuating means (28, 39, 49, 105) means (183) included with respect to the overall

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