EP4031376B1 - Sheet-fed printing press and a method for operating a sheet-fed printing press - Google Patents

Description

The invention relates to a sheet-fed printing press according to the preamble of claim 1 and a method for operating a sheet-fed printing press.

In sheet-fed printing presses, a swing gripper is often used in the system area. The oscillating gripper performs an alternating pivoting movement, gripping the sheet at a first reversal point and transferring it to an acceptance drum in its forward movement, in order to then brake and reverse again in order to swing back to the first reversal point. Usually, the swing gripper is driven by a mechanical transmission, which contains cam discs, for example, and converts a rotational movement of the receiving drum into a pivoting movement. The acceptance drum itself is connected to a main drive motor via a gear train. Because of the movement reversal of the swing gripper, negative effects can occur on the gear train and the printing units driven by it, for example due to vibrations and/or flank changes on the gears in the gear train.

through the DE 10 2006 004 572 A1 a sheet-fed printing press is known in which vibrations are to be minimized by means of a differential gear.

through the DE 31 38 540 A1 a sheet-fed printing press is known in which the rocking gripper is decoupled from the wheel train and is driven by means of an individual drive that is different from the main drive.

through the DE 196 16 755 A1 a sheet-fed printing press is known in which the swing gripper is driven by means of an individual drive that is different from the main drive is integrated into the gear train for safety reasons to avoid damage to the sheet-fed press that could result in the event of non-synchronized movement of the swing gripper and the receiving drum.

through the WO 2016/071870 A1 a sheet-fed printing machine is known, by means of which a sheet-like substrate guided on a transport path can be successively printed on both sides in multi-color printing at two printing points spaced apart in the transport path. The multi-color printing is carried out by a respective collecting printing unit in such a way that the partial print images of several forme cylinders are collected on a collecting cylinder before they are delivered together to the substrate at the printing point.

through the DE 10 2008 060 291 A1 , the DE 100 40 951 A1 and the DE 41 09 824 A1 a sheet-fed printing press with a rocking gripper and an acceptance drum downstream of this is known, with a pivoting gear being arranged to couple a rotational movement of a shaft of the receiving drum and an alternating pivoting movement of the rocking gripper limited by two end positions, and with an acceptance drum wheel non-rotatably connected to this shaft via a gear train is arranged connected to a main drive motor of the sheet-fed printing press. through the DE 10 2008 060 291 A1 , the DE 100 40 951 A1 and the DE 41 09 824 A1 a method for operating such a sheet-fed printing press is known in each case.

The invention is based on the object of creating a sheet-fed printing press and a method for operating a sheet-fed printing press.

The object is achieved according to the invention by the features of claim 1 and the features of claim 10.

The advantages that can be achieved with the invention are, in particular, that a Print quality can be improved especially at high printing speeds and / or changing printing speeds such as when starting up the printing press. Even at high printing speeds, an edge change in the gear train is preferably prevented by introducing an angular position-dependent torque component to compensate for the inertia of the oscillating gripper. A state of tension in the wheel train that is as uniform as possible over all printing speeds is preferably achieved by means of a torque component that is dependent only on the printing speed. Without this torque component, on the other hand, there is a tension in the gear train that is dependent on the printing speed and thus a register behavior that is dependent on the printing speed.

A sheet-fed printing press preferably has at least one sheet feeder and has at least one oscillating gripper mounted pivotably about a pivot axis and at least one acceptance drum downstream of the oscillating gripper, with at least one in particular mechanical pivoting gear being arranged, which is used to couple a rotational movement of a shaft of the acceptance drum and an alternating and is formed limited by two end positions pivoting movement of the swing gripper. A toothed wheel which is non-rotatably connected to the shaft of the acceptance drum and is referred to as an acceptance drum wheel is connected via a gear train containing this acceptance drum wheel to a main drive motor of the sheet-fed printing press, in particular in a torque-transmitting manner. For example, the swing gripper is part of the sheet feeder, particularly when a feed device is considered part of the sheet feeder.

The printing machine is characterized in that an active, designed as a compensation motor compensation actuator in torque in particular bypassing the wheel train transmitting way with the acceptance drum, especially with their Shaft connected is arranged. In addition, the printing press is characterized in that the active compensating actuator has a rotor and a stator and that the rotor is connected to the receiving drum coaxially and/or without play. For example, the rotor is connected coaxially and/or with no play to the shaft of the acceptance drum. This results in the advantage that installation space can be kept small or that a tooth flank change can be prevented particularly effectively. In a further development, the printing press is preferably characterized in that the rotor of the active compensation actuator is permanently connected to the receiving drum or its shaft in a rotationally fixed manner.

In a development, the printing machine is preferably characterized in that the active compensation actuator is designed as an electric motor, in particular as a torque motor, or that the active compensation actuator is designed as a hydraulic motor or a pneumatic motor.

In a further development, the printing press is preferably characterized in that a first printing unit of the sheet-fed printing press is arranged in such a way that a first printing unit gear wheel driving this first printing unit moves along the gear train between a gear wheel of the gear train assigned to the main drive motor and driving torque and referred to as the main drive wheel on the one hand and the Acceptance drum wheel is arranged on the other hand. In such a constellation, compensation is particularly important. In a further development, the printing press is preferably characterized in that a second printing unit of the sheet-fed printing press is arranged in such a way that a second printing unit gear wheel driving this second printing unit is arranged along the gear train between the main drive wheel on the one hand and the first printing unit gear wheel on the other. In such a constellation, successful compensation is particularly advantageous because otherwise there is a risk of

Register errors would be even more critical. In a further development, the printing machine is preferably characterized in that the first printing unit as Collective printing unit is formed and / or that the second printing unit is designed as a collective printing unit. Especially in printing machines with collective printing units, the highest level of precision is important, which is why register errors between printing units or system errors must be avoided in particular.

In a further development, the printing press is preferably characterized in that at least three or at least five or at least seven or at least eight or at least nine or at least ten gears are arranged along the gear train between a main drive wheel of the gear train that is assigned to the main drive motor and drives torque and the receiving drum wheel of the gear train are. The longer the gear train, the more errors could occur without compensation because a long gear train is more elastic than a short one.

In a further development, the printing press is preferably characterized in that the active compensation actuator is signal-connected to control means of a controller in which a compensation specification designed as an allocation specification is stored or implemented, with a variable representing a current angular position of a machine axis and/or a current one Angular speed of the machine axis representing variable as an input variable and a compensation torque representative variable as an output variable. In a further development, the printing press is preferably characterized in that a respective transport period is a shortest repeating sequence of angular positions of the machine axis, after which the receiving drum assumes a position with the same effect again, and that the compensation specification is designed to control the active compensation actuator in such a way or to regulate that at least during a portion of the respective transport period by means of the active compensation actuator a main torque opposite compensation torque is introduced into the wheel train and that the main torque of the main drive motor in the Gear train introduced and / or torque is to be introduced.

A method for operating a sheet-fed printing press is described, with the sheet-fed printing press preferably having at least one sheet feeder and with the sheet-fed printing press having at least one rocking gripper and at least one receiving drum downstream of the rocking gripper, and with at least one swivel gear being arranged, by means of which a rotational movement of the receiving drum and an alternating pivoting movement of the oscillating gripper limited by two end positions and wherein a main drive wheel is a gear wheel which drives a torque referred to as the main torque from a main drive motor of the sheet-fed printing press into a gear train and wherein a gear wheel which is non-rotatably connected to the acceptance drum and referred to as the acceptance drum wheel is a component of this gear train is. The acceptance drum wheel is connected via this gear train to the main drive wheel, in particular in a torque-transmitting manner. A compensation axis is an axis of rotation via which a torque can be introduced into the wheel train by means of an active compensation actuator and is at the same time the axis of rotation of the acceptance drum wheel or arranged along the wheel train between the acceptance drum wheel and the main drive wheel. A machine axis is a repeating sequence of angular positions, each of which is clearly linked to a respective angular position of the receiving drum, and a respective transport period is the shortest repeating sequence of angular positions of the machine axis, after which the receiving drum assumes a position with the same effect again. The active compensating actuator is controlled or regulated in such a way that, at least during a portion of the respective transport period, a compensating torque that opposes the main torque is introduced into the wheel train by means of the active compensating actuator.

In a further development, the method is characterized preferably characterized in that a first printing unit of the sheet-fed printing press is arranged in such a way that a first printing unit gear wheel driving this first printing unit is arranged along the gear train between the main drive wheel of the gear train on the one hand and the acceptance drum wheel on the other hand and that this compensation axis is at the same time the axis of rotation of the acceptance drum wheel or along the Gear train is arranged between the acceptance drum wheel and the first printing unit gear.

In a further development, the method is preferably characterized in that a feedback section of the respective transport period is a section during which the torque is transmitted from the oscillating gripper via the swivel gear to the shaft of the acceptance drum and that the active compensation actuator is controlled or regulated in such a way that at least during the feedback section of the respective transport period, a compensation torque opposite to the main torque is introduced into the wheel train by means of the active compensation actuator.

In a further development, the method is preferably characterized in that the active compensation actuator is controlled or regulated in such a way that during at least 50% or at least 75% or at least 90% or at least 95% or 100% of the respective transport period by means of the active compensation actuator a dem Main torque opposite compensation torque is introduced into the gear train.

In a development, the method is preferably characterized in that the size of the compensation torque introduced by means of the active compensation actuator is determined as a function of an angular position of the machine axis and/or is determined as a function of an angular speed of the machine axis.

In a further development, the method is preferably characterized in that a clamping specification is stored as a uniquely stored allocation specification between the variable representing the angular velocity of the machine axis as an input variable on the one hand and a variable representing a clamping torque dependent thereon as an output variable on the other hand, and that a clamping component of the respective compensation torque is determined by deriving the twisting moment associated with the current angular velocity of the machine axis from the twisting rule.

In a further development, the method is preferably characterized in that a system specification is stored as a uniquely stored allocation specification between the variable representing the angular velocity of the machine axis and the variable representing the angular position of the machine axis as input variables on the one hand and a variable representing a contact torque dependent thereon as output variable on the other hand, and that a system component of the respective compensation torque is determined by deriving the system torque associated with the current angular velocity and the current angular position of the machine axis from the system specification.

Exemplary embodiments of the invention are shown in the drawings and are described in more detail below.

Fig. 1

eine schematische Darstellung einer Bogendruckmaschine;

Fig. 2

eine schematische Darstellung einer Druckstellengruppe einer Druckmaschine gemäß Fig. 1;

Fig. 3

eine schematische Darstellung einer Annahmetrommel mit Teilen eines Schwenkgetriebes;

Fig. 4

eine schematische Darstellung einer Annahmetrommel mit Teilen eines Schwenkgetriebes;

Fig. 5

eine schematische Darstellung eines Schwinggreifers mit Teilen eines Schwenkgetriebes;

Fig. 6

eine schematische Darstellung ähnlich Fig. 2 mit Darstellung des Räderzug;

Fig. 7

einen schematischen beispielhaften Verlauf eines zwischen Schwinggreifer und Annahmetrommel ausgetauschten Drehmoments in Abhängigkeit von einem Maschinenwinkel;

Fig. 8

eine Darstellung gemäß Fig. 7, zusätzlich mit einem beispielhaften Verlauf eines idealen Kompensationsdrehmoments und eines resultierenden Drehmoments;

Fig. 9

eine Darstellung gemäß Fig. 7, zusätzlich mit einem beispielhaften Verlauf eines begrenzten Kompensationsdrehmoments und eines resultierenden Drehmoments;

Fig. 10

eine Darstellung gemäß Fig. 7, zusätzlich mit einem beispielhaften Verlauf eines konstanten Kompensationsdrehmoments und eines resultierenden Drehmoments.

Show it:

1

a schematic representation of a sheet-fed printing machine;

2

a schematic representation of a printing point group of a printing press according to 1 ;

3

a schematic representation of an acceptance drum with parts of a swivel gear;

4

a schematic representation of an acceptance drum with parts of a swivel gear;

figure 5

a schematic representation of a swing gripper with parts of a swivel gear;

6

a schematic representation similar 2 with depiction of the wheel train;

7

a schematic exemplary course of an exchanged between swing gripper and receiving drum torque as a function of a machine angle;

8

a representation according to 7 , additionally with an exemplary course of an ideal compensation torque and a resulting torque;

9

a representation according to 7 , additionally with an exemplary course of a limited compensation torque and a resulting torque;

10

a representation according to 7 , additionally with an exemplary course of a constant compensation torque and a resulting torque.

A sheet processing machine 01 preferably has at least one, preferably as Sheet feeder 03 configured substrate source 03 for sheets 02, i.e. sheet-type substrate 02, in particular sheet-type printing material 02. Sheet-fed processing machine 01 is embodied as a sheet-fed printing press 01. The sheet processing machine 01 preferably has a plurality of processing units 06; 07; 08; 09, each of which is more preferably designed to process sheets 02. At least one of the processing units 06; 07; 08; 09 as printing unit 06; 07; 08; 09 trained. More preferably, several of the processing units 06; 07; 08; 09 as printing units 06; 07; 08; 09 trained. Alternatively or additionally, at least one of the processing units 06; 07; 08; 09 as shaping work 06; 07; 08; 09 and/or as an application work 06; 07; 08; 09 for applying additional elements, for example security elements, to the substrate 02. Under a printing unit 06; 07; 08; 09 should preferably also be a primer 06; 07; 08; 09 and/or a coating unit 06; 07; 08; 09 to be understood. Through the processing plants 06; 07; 08; 09, sheets 02 can be processed, in particular printed. The sheet-fed printing press 01 preferably has at least one printing point group 04 with a plurality of printing units 06; 07; 08; 09 on. With this at least one printing point group 04, the respective sheets 02 can preferably be printed one or more times on one or both sides in one or more colors, or are printed accordingly.

Sheet processing machine 01 preferably has at least one product delivery 41 embodied, for example, as a stack delivery 41. At the at least one product delivery 41, the processed, in particular printed, sheets 02 are laid out in stacks or continuously as products or intermediate products (this is also an example 1 removable). In the embodiment that is preferred here and shown in the figures, the sheet processing machine 01 is embodied as a security printing machine 01 and is configured in particular to produce products or products to be processed further from sheets 02 that are already printed or unprinted, in particular sheets of securities 02, such as sheets 02 with a plurality of banknotes per sheet 02 produce intermediates. Alternatively, the sheet processing machine 01 as sheet-fed printing press 01.

A transport path provided for transporting the sheets 02 through the sheet processing machine 01 is the spatial area that a sheet 02 occupies at least once during its intended transport through the sheet processing machine 01. The transport path provided for transporting sheets 02 preferably starts at substrate source 03 and preferably ends in product delivery 41. Along the transport path provided for transporting sheets 02 between substrate source 03 and product delivery 41, transport means 14; 16; 18; 31; 32; 33; 34; 36; 37; 38; 39; 58; 59, in particular sheet transport means 14; 16; 18; 31; 32; 33; 34; 36; 37; 38; 39; 58; 59 arranged. Such sheet transport means 14; 16; 18; 31; 32; 33; 34; 36; 37; 38; 39; 58; 59 are, for example, as acceptance drums 14, transport drums or transport cylinders 14; 16; 18; 31; 32; 33; 34; 36; 38; 39; 58; 59 or as a chain gripper system 37.

The printing units 06; 07; 08; 09 of the printing point group 04. The sheet-fed printing press 01 preferably has at least one first printing position 11, which is assigned to at least one first printing unit 06. Two first printing units 06; 07 arranged and form these two first printing units 06; 07 together have a double printing position 11 or a first double printing position 11. The sheet-fed printing press 01 preferably has at least one second printing position 12, which is assigned to at least one second printing unit 08. Two second printing units 08; 09 arranged and form these two second printing units 08; 09 together a double imprint 12 or second double imprint 12.

The sheet-fed printing press 01 can also have further printing units, which, in particular, independently of the designation as the first printing unit or second printing unit, are placed before or after the at least one first printing unit 06; 07 and/or before or after the at least one second printing unit 08; 09 can be arranged. The printing units 06; 07; 08; 09 of the printing point group 04 can be used individually or in groups in several separate units 04.1; 04.2 on the transport route or all arranged in a common unit. In principle, two printing units 06; 07; 08; 09, two one-sided pressure points 11; 12 printing units 06; 07; 08; 09, a printing unit 08 arranged on one side and—upstream or preferably downstream—two printing units 06 forming a double printing unit 06, 07 or a double printing point 11; 07, or four in pairs a double printing unit 06, 07; 08, 09 or a double pressure point 11; 12 forming printing units 06; 07, 08; 09 be provided. At least two pressure points 11; 12 are provided one behind the other in the transport path provided for the transport of sheets 02, of which at least one, preferably at least the second, is designed as a double printing point 11 or more preferably both printing points 11; 12 as double pressure points 11; 12 are executed.

In a preferred embodiment, the printing units 06; 07; 08; 09 of the printing point group 04 in a printing point group 04 forming a printing tower 04, for example in two stacked units 04.1; 04.2, e.g. B. Printing units 04.1; 04.2 planned. The transport path provided for the transport of sheets 02 between the printing points 11; 12 runs from top to bottom here. This is to be understood not only as a movement that is always directed downwards along the entire intended transport path, but as a result of a transport movement that leads from top to bottom. The two pressure points 11; 12 training printing units 06; 07; 08; 09 are advantageously arranged one above the other in the same frame assigned to the printing point group 04, or in two arranged one above the other, each with one printing unit 04.1; 04.2 associated subframes arranged.

The printing units 06; 07; 08; 09 of the spaced-apart pressure points 11; 12 can in principle be based on different printing processes. At least the printing unit(s) 08; 09 is or are preferably based on an indirect printing process. The at least one printing unit 08; 09 of the first or upstream printing point 11 or each of the two printing units 06, 07 acting together as an upstream double printing point 11, also designed as based on an indirect printing process.

At least one vibrating gripper 13 is preferably arranged along the transport path provided for transporting the sheets 02, particularly in the area of the substrate source 03 or downstream of the substrate source 03. The at least one rocking gripper 13 serves in particular to grip sheets 02 that are lying in an aligned position, accelerate them to machine speed in a preferably pivoting movement, and then transfer them to a first acceptance drum 14 in particular. Starting from this, in particular, first acceptance drum 14, the transport path provided for transporting the sheets 02 is initially preferably defined by a series of rotating transport means 14; 16; 18; 31; 32; 33; 34; 36; 38; 39; 58; 59, ie transport cylinders 14; 16; 18; 31; 32; 33; 34; 36; 37; 38; 39; 58; 59 fixed. The acceptance drum 14 and the subsequent transport cylinder 14; 16; 18; 31; 32; 33; 34; 36; 38; 39; 58; 59 preferably have grippers for this purpose, through the coordinated opening and closing of which the sheets 02 can be passed on preferentially. This series of rotating transport means 14; 16; 18; 31; 32; 33; 34; 36; 38; 39; 58; 59 preferably includes at least one transport cylinder 16; 18 of a printing unit 06; 08, for example at least one cylinder 16 of the first printing unit 11 configured as a collecting cylinder 16 and/or transfer cylinder 16 and/or impression cylinder 16, and more preferably also at least one cylinder 18 configured as a collecting cylinder 18 and/or transfer cylinder 18 and/or impression cylinder 18 second printing unit 08.

On the output side of the last printing point 12 to a subsequent unit or to the product delivery 41, this can also be done via a system based on sheet transfer between cylinders and/or drums, but is preferably carried out by a transport system 37 with circulating traction means, e.g. B. a chain gripper system 37 causes. Downstream of the last printing point 11 can be on the transport path - preferably on both sides - at least one drying device, in particular a radiation dryer, such as. B. IR or UV dryer may be provided.

A respective printing unit 06 designed for indirect printing; 07; 08; 09 comprises a transfer cylinder 16; 17; 18; 19 formed cylinder 16; 17; 18; 19, e.g. B. Printing cylinder 16; 17; 18; 19 with a counter-pressure cylinder 16; 17; 18; 19 effective cylinder 17; 16; 18; 19, e.g. B. Printing cylinder 17; 16; 18; 19, a pressure point 11; 12 trains. In the case of a double pressure point 11; 12 is the respective impression cylinder 17; 16; 18; 19 effective printing cylinders 17; 16; 18; 19 also by an ink-carrying printing unit cylinder 17; 16; 18; 19, in particular the transfer cylinder 17; 16; 18; 19 of the first mentioned printing unit 06; 07; 08; 09 a double printing unit 06; 07, 08; 09 training printing unit 06; 07; 08; 09 formed. The transfer cylinder 17; 16; 18, 19 acts—in relation to the paint flow upstream—with at least one imaging cylinder 21; 22; 23; 24, e.g. B. Printing cylinder 21; 22; 23; 24, e.g. B. at least one forme cylinder 21; 22; 23; 24 together, which upstream by a suitable inking device 26; 27; 28; 29, e.g. B. an inking unit 26; 27; 28; 29, is colored or can be colored with printing ink.

The forme cylinder 21; 22; 23; 24 and the associated inking unit 26; 27; 28; 29 can in principle be based on any printing process, but are preferred as based on a, in particular indirect, planographic printing process or on a, in particular indirect, letterpress or relief printing process, in particular Letterset printing process based trained. For this purpose, the forme cylinder 21; 22; 23; 24 on its circumference in the former embodiment, a flat printing form, not shown here, e.g. B. an offset printing form for wet or dry offset, which is suitable for flat printing with an inking unit, for the case of wet offset z. B. a roller inking unit 26; 27; 28; 29 with an upstream ink fountain and with a dampening system, and for dry offset z. B. with a short inking unit 26 comprising, for example, a cup roller and a squeegee device; 27; 28; 29 interacts.

At least one of the printing units 06; 07; 08; 09 as collective printing unit 06; 07; 08; 09, ie in particular for simultaneous, in particular multicolored, printing of two partial print images. The at least one first printing unit 06 is preferably embodied as a collective printing unit 06 and/or both first printing units 06; 07 as collective printing units 06; 07 and/or the at least one second printing unit 08 is configured as a collective printing unit 08 and/or both second printing units 08; 09 as collective printing units 08; 09 trained. The at least one as collective printing unit 06; 07; 08; 09 trained printing unit 06; 07; 08; 09 includes as a transfer cylinder 16; 17; 18; 19 as a collecting cylinder 16; 17; 18; 19 effective ink-carrying printing unit cylinder 16; 17; 18; 19, which relative to the ink flow upstream with at least two imaging printing cylinders 21; 22; 23; 24, e.g. B. at least two forme cylinders 21; 22; 23; 24 interacts, which through respective inking devices 26; 27; 28; 29, e.g. B. inking units 26; 27; 28; 29 can be colored. The forme cylinders 21; 22; 23; 24 and associated inking units 26; 27; 28; 29 of a collective printing unit 06; 07; 08; 09 may all be designed in the above sense as planographic or letterpress, or partly planographic and another part letterpress. In the case of an opposite printing unit 07; 06; 09; 08 can also be used in the manner mentioned as a collective printing unit 07; 06; 09; 08 be formed and in the manner set out above as a collecting cylinder 17; 16; 19; 18 effective transfer cylinder 17; 16; 19; 18 have. The printing cylinders 16; 17 of the first printing point 11 are preferably double-sized, ie designed to accommodate two sheets of printing material 02 on the circumference. The printing cylinders 18; 19 of the second printing point 12 are preferably triple-sized, ie designed to accommodate three sheets of printing material 02 on the circumference. In an alternative embodiment, the printing cylinders 18; 19 of the second pressure point 12 double-sized.

Per pressure point 11; 12 is one of the two, the pressure point 11; 12 forming printing cylinder 16; 17; 18; 19 as a transport cylinder 16; 17; 18; 19 and is effective as such and preferably comprises one or more holding devices, in particular so-called gripper strips, on the circumference.

Sheet-fed printing press 01 has at least one gear train 51, in particular gear train 51. This gear train 51 comprises a number of gears 46; 49; 52; 53; 61; 62; 63; 64; 66; 67; 68; 69 meshing with each other through their teeth and is thus able to transmit torque. The gear train 51 preferably includes such gears 46; 49; 52; 53; 61; 62; 63; 64; 66; 67; 68; 69, each rotatably connected to a respective shaft of a respective transport means 14; 16; 18; 31; 32; 33; 34; 36; 38; 39; 58; 59 are connected. Sheet-fed printing press 01 has at least one main drive motor 48, which is preferably embodied as an electric motor 48. The main drive motor 48 is preferably connected in a torque-transmitting manner to a gear wheel 49 of the wheel train 51 designed as a main drive wheel 49 . The main drive wheel 49 is that gear wheel 49 via which a main torque from the main drive motor 48 can be introduced into the wheel train 51 or is introduced. For example, but not necessarily, further torque transmitters are arranged between the main drive wheel 49 and a rotor of the main drive motor 48, in particular gear wheels and/or belts and/or friction wheels and/or gears and/or chains. In an alternative embodiment, the main drive wheel 49 is non-rotatably connected to the rotor of the main drive motor 48 .

The sheet-fed printing press 01 preferably has the at least one sheet feeder 03. Sheet-fed printing press 01 has at least one rocking gripper 13, which is mounted pivotably in particular about a pivot axis 42, and at least one acceptance drum 14 arranged downstream of rocking gripper 13. For example, sheet feeder 03 has at least one rocking gripper 13 and/or acceptance drum 14. The acceptance drum 14 is preferably used to take over sheets from the oscillating gripper 13 . At least one swivel gear 43, in particular mechanical, is arranged, which is designed for coupling and in particular for converting a rotational movement of a shaft 44 of the acceptance drum 14 and an alternating swivel movement of the swing gripper 13 limited by two end positions. This shaft 44 of the receiving drum 14 does not have to be in the form of a continuous shaft 44, but can essentially consist of two drum journals, for example. Acceptance drum 14 is non-rotatably connected to a gear wheel 46 referred to as acceptance drum wheel 46, in particular via a shaft 44 of acceptance drum 14. Acceptance drum wheel 46 is part of gear train 51. Preference is therefore given to non-rotatably connected to shaft 44 of acceptance drum 14 and as acceptance drum wheel 46 gear wheel 46 is connected to the main drive motor 48 of the sheet-fed printing press 01 via the gear train 51 containing this acceptance drum wheel 46, in particular in a torque-transmitting manner.

A first transport means 31, which is preferably embodied as a first transport cylinder 31, is preferably arranged along the transport path provided for the transport of sheets 02 following the acceptance drum 14. This transport means 31 is preferably non-rotatably connected to a gear wheel 61 of the wheel train 51 which engages with the acceptance drum wheel 46 .

Along the transport path provided for transporting sheets 02 to this First transport means 31 is preferably a transport cylinder 16 of the first printing unit 06, which is embodied, for example, as an impression cylinder 16 and/or as a transfer cylinder 16 and/or as a collecting cylinder 16. This transport cylinder 16 of the first printing unit 06 is preferably arranged in a rotationally fixed manner connected to a first printing unit gear wheel 52. This first printing unit gear wheel 52 is preferably part of the gear train 51.

A number of further transport means 32; 58; 59 arranged and in particular interposed. Each of these number of further transport means 32; 58; 59 a further gear wheel 62; 63; 64 assigned and in particular rotatably connected to this. This number is, for example, at least one or at least two or at least three. Correspondingly, a corresponding number of gears 62; 63; 64 arranged, in particular at least one or at least two or at least three.

In an alternative or additional development, the printing press 01 is preferably characterized in that a first printing unit 06 of the sheet-fed printing press 01 is arranged in such a way that a first printing unit gear wheel 52 driving this first printing unit 06 drives along the gear train 51 between a main drive motor 48 assigned to it and drives it and designated as the main drive wheel 49 gear 49 of the gear train 51 on the one hand and the acceptance drum wheel 46 on the other hand. In an alternative or additional development, the printing press 01 is preferably characterized in that the first printing unit 06 is embodied as a collective printing unit 06.

Along the transport route provided for the transport of sheets 02 after the Transport cylinder 16 of the first printing unit 06 is preferably a transport cylinder 18 of the second printing unit 08, which is embodied, for example, as an impression cylinder 18 and/or as a transfer cylinder 18 and/or as a collection cylinder 18. This transport cylinder 18 of the second printing unit 08 is preferably non-rotatably connected to a second printing unit gear wheel 53. This second printing unit gear wheel 53 is preferably part of the gear train 51.

Sheets are preferably transported from one printing point 11, in particular from its printing unit cylinder 16 acting as transport cylinder 16, to the further downstream printing point 12, in particular to its printing unit cylinder 18 acting as transport cylinder 18, via at least one rotating transport means 33; 38; 39, e.g. B. a transport cylinder 33; 38; 39 or a so-called transport drum 33; 38; 39, which preferably comprises at least one holding device, in particular a so-called gripper strip, on the circumference. The transport between the two pressure points 11; 12 is thus preferably based on a transport system with successive sheet transfer between cylinders 16 involved in the transport; 18 and/or means of transport 33; 38; 39. In the design of the printing point group 04 with a transport path running from top to bottom between the printing points 11; 12 the sheet transfer takes place e.g. B. each of a higher with its axis cylinder 16; 18 or means of transport 33; 38; 39 ago.

A number of further transport means 33; 38; 39 arranged and in particular interposed. These other means of transport 33; 38; 39 are preferred as transport cylinders 33; 38; 39 trained. Each of these number of further transport means 33; 38; 39 each have a further gear wheel 66; 67; 68 assigned and in particular rotatably connected to this. This number is, for example, at least one or at least two or at least three.

Correspondingly, a corresponding number of gears 66; 67; 68 arranged, in particular at least one or at least two or at least three.

A number of further transport means 34; 36; 37 arranged and in particular interposed. For example, a further transport means 34, preferably embodied as a transport cylinder 34, is arranged along the transport path provided for the transport of sheets 02 directly after the transport cylinder 18 of the second printing unit 08. A further toothed wheel 69 is preferably assigned to this further transport means 34 and is in particular connected to it in a rotationally fixed manner. For example, a drive transport means 36, in particular a drive transport cylinder 36, is arranged along the transport path provided for the transport of sheets 02 directly after this additional transport means 34. The main drive wheel 49 is preferably assigned to this drive transport means 36 and, in particular, is connected to it in a rotationally fixed manner. For example, a transport system 37 embodied preferably as a chain gripper system 37 is arranged downstream of the drive transport means 36 , which more preferably extends to the product display 41 . Alternatively, the further transport of the sheets 02 after the drive transport means 36 can also take place via rotating transport means, in particular transport cylinders.

In an alternative or additional development, the printing press 01 is preferably characterized in that a second printing unit 08 of the sheet-fed printing press 01 is arranged in such a way that a second printing unit gear wheel 53 driving this second printing unit 08 can be moved along the gear train 51 between the main drive wheel 49 on the one hand and the first printing unit gear wheel 52 is arranged on the other hand. In an alternative or additional development, the printing press 01 preferably characterized in that the second printing unit 08 is designed as a collective printing unit 08.

In an alternative or additional development, printing press 01 is preferably characterized in that at least three or at least five or at least seven or at least eight or at least nine or at least ten gears 46; 49; 52; 53; 61; 62; 63; 64; 66; 67; 68; 69 are arranged.

Printing press 01 is characterized in that an active compensating actuator 47 is connected to the receiving drum 14 and/or to the shaft 44 of the receiving drum 14 in a manner that transmits torque, in particular bypassing the gear train 51 . The active compensation actuator 47 is preferably designed as a compensation motor 47 and/or preferably has a rotor and a stator. The rotor is preferably connected coaxially and/or without play to the acceptance drum 14, in particular to the shaft 44 of the acceptance drum 14. The active compensation actuator 47 is preferably embodied as an electric motor 47, in particular as a torque motor 47. A torque motor is preferably an electric motor with a high number of poles to understand with hollow shaft. A torque motor preferably has a particularly high torque and/or a relatively low speed and/or is preferably designed as a direct drive. The rotor of the compensating actuator 47 is preferably arranged further to the outside with respect to its axis of rotation 54 than the stator. Alternatively, the active compensating actuator 47 is designed as a hydraulic motor 47 or as a pneumatic motor 47 . In an alternative or additional development, the printing press 01 is preferably characterized in that the rotor of the active compensation actuator 47 is non-rotatably, in particular permanently non-rotatably, with the Acceptance drum 14 and in particular to the shaft 44 of the acceptance drum 14 is connected. This means in particular that no additional transmission is interposed. Alternatively, for example, a backlash-free gear is interposed.

In an alternative or additional development, the printing press 01 is preferably characterized in that the active compensation actuator 47 is in signal communication with control means of a controller 71, in which a compensation specification designed as an assignment specification is stored or implemented, with a current angular position of a machine axis 56 and/or or a current angular velocity of the machine axis 56 as an input variable and a compensation torque Z2; Z3; Z4 as output size. At least one angular position transmitter 72 is preferably arranged and connected to the controller 71 . Angular position sensor 72 preferably measures an angular position of a rotating component, for example a means of transport 34 or that of the rotor of main drive motor 48. In this way, the controller is preferably informed about the angular position and/or the angular speed of machine axis 56 at all times.

In an alternative or additional development, printing press 01 is preferably characterized in that a respective transport period is the shortest repeating sequence of angular positions of machine axis 56, after which acceptance drum 14 assumes a position with the same effect again, and that the compensation rule is designed to to control or regulate the active compensation actuator 47 in such a way that, at least during a portion of the respective transport period, a main torque opposite compensation torque Z2 by means of the active compensation actuator 47; Z3; Z4 is introduced into the gear train 51 and that the main torque is a torque introduced and/or to be introduced into the gear train 51 by the main drive motor 48 .

As described, at least one in particular mechanical pivoting gear 43 is preferably provided, which is designed to couple and in particular to convert a rotational movement of a shaft 44 of the receiving drum 14 and an alternating pivoting movement of the swing gripper 13 limited by two end positions. This swivel gear 43 has, for example, at least one cam carrier 73 and preferably two cam carriers 73, which are more preferably non-rotatably connected to the receiving drum 14 and in particular to its shaft 44. This swivel gear 43 preferably has at least one pick-off element 74 and more preferably two pick-off elements 74, which are more preferably arranged non-rotatably connected to the swinging gripper and arranged to interact with a respective one of the cam carriers 73. Due to the moment of inertia of the oscillating gripper 13, a cyclic curve of a transmitted torque Z1 results when it is accelerated. In a feedback section C1-E1, a torque is effectively transmitted to the shaft 44 of the receiving drum 14 via the swivel gear 43. This could lead to a flank change of the teeth taking place in the train of wheels 51, which could have negative effects on the printed image and/or a transport register. (Such a course of a torque Z1 exchanged between swing gripper 13 and receiving drum 14 is also shown in FIG 7 shown schematically. A machine angle 56 is shown on the abscissa and the torque M is shown on the ordinate. First, the rocking gripper is at rest (position A1) and grips a sheet 02. Then the rocking gripper 13 is accelerated, reaching maximum acceleration at position B1. Initially, there is no further acceleration at position C1, but rather the transfer of the sheet to the acceptance drum 13. This is followed by negative acceleration up to position E1, which reaches its maximum value at position D1. The area between C1 and E1 is also referred to as the feedback section. From position E1 there is renewed acceleration in the opposite direction up to position G1, which reaches its maximum value at position F1. Position G1 corresponds to the position A1 of the next cycle.)

In order to prevent an edge change and/or to be able to maintain tension states in the wheel train 51 independently of the machine speed, a compensation torque Z2; Z3; Z4 fed.

A method for operating a sheet-fed printing press 01 is described, wherein the sheet-fed printing press 01 preferably has the at least one sheet feeder 03 and wherein the sheet-fed printing press 01 has the at least one rocking gripper 13, which is mounted pivotably in particular about its pivot axis 42, and at least one acceptance drum 14 arranged downstream of the rocking gripper 13, and wherein at least one in particular mechanical swivel gear 43 is arranged, by means of which a rotational movement of the acceptance drum 14 and an alternating swivel movement of the swing gripper 13 limited by two end positions are coupled. A main drive wheel 49 is a gear wheel 49 that drives a torque referred to as the main torque from a main drive motor 48 of the sheet-fed printing press 01 into a gear train 51. A toothed wheel 46 connected non-rotatably to the acceptance drum 14 and referred to as the acceptance drum wheel 46 is part of this gear train 51 and more preferably connected via this gear train 51 to the main drive wheel 49, in particular in a torque-transmitting manner. A compensation axis 54 is an axis of rotation 54, for example an axis of rotation 54 of a gear wheel 46, via which a torque can be introduced into the wheel train 51 by means of an active compensation actuator 47. This compensation axis 54 is at the same time the axis of rotation 57 of the acceptance drum wheel 46 or is arranged along the wheel train 51 between the acceptance drum wheel 46 and the main drive wheel 49 . Such an axis of rotation is to be understood in the mathematical sense.

A machine axis 56 is a repetitive sequence of angular positions, each of which is clearly linked to a respective angular position of the acceptance drum 14 . This Angular positions of the machine axis 56 can match a real component or represent a virtual machine axis 56 .

A respective transport period is a shortest repeating sequence of angular positions of the machine axis 56, after which the acceptance drum 14 assumes a position with the same effect again. A position with the same effect is to be understood, for example, as the same position after one revolution if it is a single-size receiving drum 14 .

The active compensation actuator 47 is controlled or regulated in such a way that, at least during a portion of the respective transport period, a compensation torque Z2; Z3; Z4 is introduced into the wheel train 51.

This compensation torque Z2; Z3; Z4 has, for example, a tension component and/or a contact component. The tension component preferably serves to generate tension that is always as similar as possible in the train of wheels 51, even when operating at different speeds, so that the quality and/or position of the printed images does not depend on the machine speed. The tension component is defined, for example, as a function of the machine speed and preferably remains constant when the machine speed remains the same. The contact portion preferably serves to prevent an edge change. It is therefore dependent on the current angular position. In addition, the investment portion is preferably also modified by a factor that includes the current machine speed, in particular quadratically. This takes into account the higher accelerations for the direction reversal at higher machine speeds.

In 8 is exemplary in addition to the exchanged torque Z1 according to 7 a course of an ideal compensation torque Z2 is shown. This is essentially a mirroring of the curve of the exchanged torque Z1, but with an offset applied. In particular, the above exemplary positions A1; B1; C1; D1; E1; F1; G1 of the course of the exchanged torque Z1 a respective corresponding position A2; B2; C2; D2; E2; F2; G2 assigned to the course of the ideal compensation torque Z2. In total, a constant resultant torque R1 then results.

In 9 example in addition to the exchanged torque Z1 according to 7 a course of a limited compensation torque Z3 is shown. The course of the limited compensation torque Z3 largely corresponds to that of the ideal compensation torque Z2, but with the difference that only a constant compensation torque Z3 is exerted between the positions H2 and J2. This results in a changed course of the resulting torque R2, which, however, preferably remains negative even at the position K with the smallest resulting torque R2 in terms of absolute value and prevents an edge change.

In 10 is again the exchanged torque Z1 according to FIG 7 and additionally a constant compensation torque Z4 is shown, as well as the resulting torque R3, the form of which now essentially corresponds to that of the exchanged torque Z1 and still remains negative due to a suitable selection of the constant compensation torque Z4 and prevents an edge change.

In an alternative or additional refinement, the method is preferably characterized in that a first printing unit 06 of sheet-fed printing press 01 is arranged in such a way that a first printing unit gear wheel 52 driving this first printing unit 06 can be moved along gear train 51 between the main drive wheel 49 of gear train 51 on the one hand and the Acceptance drum wheel 46 arranged on the other hand and that this compensation axis 54 is at the same time the axis of rotation 57 of the acceptance drum wheel 46 or is arranged along the gear train 51 between the acceptance drum wheel 46 and the first printing unit gear wheel 52 .

In an alternative or additional development, the method is preferably characterized in that a feedback section C1-E1 of the respective transport period is a section - i.e. in particular a sequence of angular positions - during which the torque is applied from the oscillating gripper 13 via the swivel gear 43 to the shaft 44 is transmitted to the acceptance drum 14 and that the active compensation actuator 47 is controlled or regulated in such a way that, at least during the feedback section C1-E1 of the respective transport period, a compensation torque Z2 opposed to the main torque is generated by means of the active compensation actuator 47; Z3; Z4 is introduced into the wheel train 51.

In an alternative or additional development, the method is preferably characterized in that the active compensation actuator 47 is controlled or regulated in such a way that during at least 50%, more preferably at least 75%, even more preferably at least 90%, even more preferably at least 95% and even more preferably 100% of the respective transport period by means of the active compensation actuator 47 a compensation torque Z2 opposed to the main torque; Z3; Z4 is introduced into the wheel train 51.

In an alternative or additional development, the method is preferably characterized in that the magnitude of the compensation torque Z2; Z3; Z4 is determined as a function of an angular position of the machine axis 56 and/or is determined as a function of an angular speed of the machine axis 56.

In an alternative or additional development, the method is distinguished preferably characterized in that a tensioning specification is stored as a uniquely stored assignment specification between the angular velocity of the machine axis 56 as an input variable on the one hand and a tensioning moment dependent thereon as an output variable on the other hand and that a tensioning component of the respective compensation torque Z2; Z3; Z4 is determined by deriving the twisting moment associated with the current angular velocity of the machine axis 56 from the twisting rule. The angular velocity of the machine axis 56 preferably enters this bracing specification linearly and/or the bracing component forms a constant offset in the course of the compensation torque if the angular velocity of the machine axis 56 remains constant.

In an alternative or additional development, the method is preferably characterized in that a system specification is stored as a uniquely stored allocation specification between the angular velocity of machine axis 56 and the angular position of machine axis 56 as input variables on the one hand and a contact torque dependent thereon as output variable on the other hand and that a system component of the respective compensation torque Z2; Z3; Z4 is determined by deriving the contact torque associated with the current angular velocity and the current angular position of the machine axis 56 from the contact rule. The system specification is intended to ensure that the corresponding gear flanks are always in contact and that there is no flank change. The angular speed of the machine axis 56 is preferably included in this system specification as a square, in particular in a proportionality factor which the amplitude over the course of the compensation torque Z2; Z3; Z4 changes even if the angular velocity of the machine axis 56 remains constant. The basic course of the compensation torque Z2 is preferred; Z3; Z4 stored in a memory, in particular in the form of a table of interpolation points, and/or derived from theoretical and/or metrologically determined data. In particular, the moment of inertia of the swing gripper 13, the geometry of the Slewing gear and preferably also includes friction losses in the determination. Energy that is withdrawn from the swing gripper 13 by the compensation torque is preferably at least partially fed into a circuit connected to the main drive motor 48 and/or used to operate the main drive motor 48 .

The compensation rule is preferably made up of at least the bracing rule and the installation rule. For example, the compensation rule consists of a sum of the bracing rule and the installation rule. The compensation torque to be applied is preferably calculated at regular intervals by means of the bracing specification and/or the installation specification and/or the compensation specification and is more preferably supplied to a drive controller of the active compensation actuator 47 as the setpoint torque. For example, this regular calculation takes place at least ten times per transport cycle, more preferably at least a hundred times, even more preferably at least a thousand times. For example, this regular calculation takes place at least once every 100 ms (hundred milliseconds), more preferably at least once every 10 ms and even more preferably at least once every 5 ms.

The first pressure point 11 forming cylinder 16; 17 and the second pressure point 12 forming cylinder 18; 19 are arranged, for example, in the same frame one above the other or in two partial frames arranged one above the other. The or the intermediate transport means 33; 38; 39 is or are z. B. also in the common frame, in one of the above Subframes, in a specially provided intermediate frame or - in the case of several means of transport 33; 38; 39 - possibly divided into the above Subframes and / or the intermediate frame provided.

The transport path running from top to bottom should not only be understood to mean a downward movement over the entire transport path, but e.g. B. also transport routes, the one or more - for example, offset in the lateral direction to each other arranged rotating transport means 33; 38; 39 conditional - include transport path sections with sideways or even upward transport direction.

In an alternative embodiment, the sheet-fed printing press 01 has a transport path that runs sideways and/or the sheet-fed printing press has at least four printing units, each of which has exactly one impression cylinder, exactly one transfer cylinder and exactly one forme cylinder. Exactly one transport cylinder is preferably arranged along a transport path provided for sheets between two such impression cylinders.

Reference List

01

Sheet processing machine, sheet printing machine, security printing machine

02

Sheet, substrate, printing material, security sheet

03

substrate source, sheet feeder

04

Printing point group, printing tower

04.1

Aggregate, pressure unit

04.2

Aggregate, pressure unit

05

-

06

Printing unit, collective printing unit, first

07

Printing unit, collective printing unit, first

08

Printing unit, collective printing unit, second

09

Printing unit, collective printing unit, second

10

-

11

Pressure point, double pressure point, first

12

Bruise, double bruise, second

13

swing gripper

14

acceptance drum

15

-

16

Cylinders, printing unit cylinders, collecting cylinders, transfer cylinders, impression cylinders, transport cylinders

17

Cylinders, printing unit cylinders, collection cylinders, transfer cylinders, impression cylinders

18

Cylinders, printing unit cylinders, collecting cylinders, transfer cylinders, impression cylinders, transport cylinders

19

Cylinders, printing unit cylinders, collection cylinders, transfer cylinders, impression cylinders

20

-

21

Cylinder, printing unit cylinder, forme cylinder

22

Cylinder, printing unit cylinder, forme cylinder

23

Cylinder, printing unit cylinder, forme cylinder

24

Cylinder, printing unit cylinder, forme cylinder

25

-

26

Inking device, inking unit, roller inking unit

27

Inking device, inking unit, roller inking unit

28

Inking device, inking unit, roller inking unit

29

Inking device, inking unit, roller inking unit

30

-

31

Transport means, sheet transport means, transport cylinder, transport drum

32

Transport means, sheet transport means, transport cylinder, transport drum

33

Transport means, sheet transport means, transport cylinder, transport drum

34

Transport means, sheet transport means, transport cylinder, transport drum

35

-

36

Transport means, sheet transport means, transport cylinder, transport drum, drive transport means, drive transport cylinder

37

Transport system, chain gripper system

38

Transport means, sheet transport means, transport cylinder, transport drum

39

Transport means, sheet transport means, transport cylinder, transport drum

40

-

41

Product display, stack display

42

pivot axis (13)

43

swivel gear

44

shaft (14)

45

-

46

Gear, acceptance drum wheel

47

compensation actuator, compensation motor, motor, electric motor, torque motor, hydraulic motor, pneumatic motor,

48

Main drive motor, electric motor

49

Gear, main drive wheel

50

-

51

gear train, gear train

52

Printer gear, first

53

Printer gear, second

54

Compensation axis, rotation axis

55

-

56

machine axis

57

axis of rotation (14)

58

Means of transport, transport cylinder

59

Means of transport, transport cylinder

60

-

61

Gear (31)

62

Gear (58)

63

Gear (59)

64

Gear (32)

65

-

66

Gear (33)

67

Gear (38)

68

Gear (39)

69

Gear (34)

70

-

71

steering

72

angular position sensor

73

Curved beam (43)

74

pickoff

A1

Position (Z1)

A2

Position (Z2)

B1

Position (Z1)

B2

Position (Z2)

C1

Position (Z1)

C2

Position (Z2)

D1

Position (Z1)

D2

Position (Z2)

E1

Position (Z1)

E2

Position (Z2)

F1

Position (Z1)

F2

Position (Z2)

G1

Position (Z1)

G2

Position (Z2)

H2

Position (Z3)

J2

Position (Z3)

K

Position (R2)

M

torque

R1

torque, resulting

R2

torque, resulting

R3

torque, resulting

Z1

torque, transmitted

Z2

compensation torque

Z3

compensation torque

Z4

compensation torque

Claims (15)

1. Sheet-fed printing press (01), wherein the sheet-fed printing press (01) has at least one swinging gripper (13) and at least one accepting drum (14) arranged downstream of the swinging gripper (13), and wherein at least one swivel gear mechanism (43) is arranged, which is designed to couple a rotational movement of a shaft (44) of the accepting drum (14) and an alternating swiveling movement of the swinging gripper (13), said alternating swiveling movement being limited by two end positions, and wherein a gear (46), which is fixedly connected to the shaft (44) of the accepting drum (14) for conjoint rotation and is referred to as the accepting drum gear (46), is connected to a main drive motor (48) of the sheet-fed printing press (01) via a gear train (51) that includes this accepting drum gear (46), characterized in that an active compensation actuator (47), designed as a compensation motor (47), is connected to the accepting drum (14) in a torque-transmitting manner, and in that the active compensation actuator (47) has a rotor and a stator, and in that the rotor is connected to the accepting drum (14) coaxially and/or without play.
2. Sheet-fed printing press according to claim 1, characterized in that the active compensation actuator (47) is designed as an electric motor (47) or as a torque motor (47).
3. Sheet-fed printing press according to claim 1 or 2, characterized in that the rotor of the active compensation actuator (47) is fixedly connected to the accepting drum (14) for conjoint rotation.
4. Sheet-fed printing press according to claim 1 or 2 or 3, characterized in that a first printing unit (06) of the sheet-fed printing press (01) is arranged in such a way that a first printing unit gear (52), which drives this first printing unit (06), is arranged along the gear train (51) between a torque-introducing gear (49) of the gear train (51) on the one hand, which is associated with the main drive motor (48) and is referred to as the main drive gear (49), and the accepting drum gear (46) on the other hand.
5. Sheet-fed printing press according to claim 4, characterized in that a second printing unit (08) of the sheet-fed printing press (01) is arranged in such a way that a second printing unit gear (53), which drives this second printing unit (08), is arranged along the gear train (51) between the main drive gear (49) on the one hand and the first printing unit gear (52) on the other hand.
6. Sheet-fed printing press according to claim 4 or 5, characterized in that the first printing unit (06) is designed as a collect printing unit (06), and/or in that the second printing unit (08) is designed as a collect printing unit (08).
7. Sheet-fed printing press according to claim 1 or 2 or 3 or 4 or 5 or 6, characterized in that at least three or at least five or at least seven or at least eight or at least nine or at least ten gears (46; 49; 52; 53; 61; 62; 63; 64; 66; 67; 68; 69) are arranged along the gear train (51) between a torque-introducing main drive gear (49) of the gear train (51), which is associated with the main drive motor (48), and the accepting drum gear (46) of the gear train (51).
8. Sheet-fed printing press according to claim 1 or 2 or 3 or 4 or 5 or 6 or 7, characterized in that the active compensation actuator (47) is signal-connected to control means of a controller (71), in which a compensation specification designed as an association specification is stored or implemented, with a variable representing a current angular position of a press axis (56) and/or a variable representing a current angular velocity of the press axis (56) as input variable and a variable representing a compensation torque (Z2; Z3; Z4) as output variable, and in that the press axis (56) is a repeating sequence of angular positions which are each unequivocally linked to a respective angular position of the accepting drum (14), and in that these angular positions of the press axis (56) coincide with a real component or represent a virtual press axis (56).
9. Sheet-fed printing press according to claim 8, characterized in that a respective transport period is a shortest repeating sequence of angular positions of the press axis (56), after which the accepting drum (14) again assumes a position that has the same effect, and in that the compensation specification is designed to control or adjust the active compensation actuator (47) in such a way that, at least during a sub-section of the respective transport period, a compensation torque (Z2; Z3; Z4) in the opposite direction to a main torque is introduced into the gear train (51) by means of the active compensation actuator (47), and in that the main torque is a torque which is introduced and/or is to be introduced into the gear train (51) by the main drive motor (48).
10. Method for operating a sheet-fed printing press (01), wherein the sheet-fed printing press (01) has at least one swinging gripper (13) and at least one accepting drum (14) arranged downstream of the swinging gripper (13), and wherein at least one swivel gear mechanism (43) is arranged, by means of which a rotational movement of the accepting drum (14) and an alternating swiveling movement of the swinging gripper (13) are coupled, said alternating swiveling movement being limited by two end positions, and wherein a main drive gear (49) is a gear (49) which introduces a torque, referred to as the main torque, from a main drive motor (48) of the sheet-fed printing press (01) into a gear train (51), and wherein a gear (46), which is fixedly connected to the accepting drum (14) for conjoint rotation and is referred to as the accepting drum gear (46), is part of this gear train (51), characterized in that a compensation axis (54) is a rotation axis (54), via which a torque can be introduced into the gear train (51) by means of an active compensation actuator (47) designed as a compensation motor (47), and in that this compensation axis (54) is at the same time the rotation axis (57) of the accepting drum gear (46) or is arranged along the gear train (51) between the accepting drum gear (46) and the main drive gear (49), and in that a press axis (56) is a repeating sequence of angular positions which are each unequivocally linked to a respective angular position of the accepting drum (14), and in that these angular positions of the press axis (56) coincide with a real component or represent a virtual press axis (56), and in that a respective transport period is a shortest repeating sequence of angular positions of the press axis (56), after which the accepting drum (14) again assumes a position that has the same effect, and in that the active compensation actuator (47) is controlled or adjusted in such a way that, at least during a sub-section of the respective transport period, a compensation torque (Z2; Z3; Z4) in the opposite direction to the main torque is introduced into the gear train (51) by means of the active compensation actuator (47) .
11. Method according to claim 10, characterized in that a first printing unit (06) of the sheet-fed printing press (01) is arranged in such a way that a first printing unit gear (52), which drives this first printing unit (06), is arranged along the gear train (51) between the main drive gear (49) of the gear train (51) on the one hand and the accepting drum gear (46) on the other hand, and in that this compensation axis (54) is at the same time the rotation axis (57) of the accepting drum gear (46) or is arranged along the gear train (51) between the accepting drum gear (46) and the first printing unit gear (52).
12. Method according to claim 10 or 11, characterized in that a feedback section (C1-E1) of the respective transport period is a section during which torque is transferred from the swinging gripper (13), via the swivel gear mechanism (43), to the shaft (44) of the accepting drum (14), and in that the active compensation actuator (47) is controlled or adjusted in such a way that, at least during the feedback section (C1-E1) of the respective transport period, a compensation torque (Z2; Z3; Z4) in the opposite direction to the main torque is introduced into the gear train (51) by means of the active compensation actuator (47) .
13. Method according to claim 10 or 11 or 12, characterized in that the magnitude of the compensation torque (Z2; Z3; Z4) introduced by means of the active compensation actuator (47) is set as a function of an angular position of the press axis (56) and/or is set as a function of an angular velocity of the press axis (56), or in that the active compensation actuator (47) is controlled or adjusted in such a way that, during at least 50% or at least 75% or at least 90% or at least 95% or 100% of the respective transport period, a compensation torque (Z2; Z3; Z4) in the opposite direction to the main torque is introduced into the gear train (51) by means of the active compensation actuator (47) .
14. Method according to claim 10 or 11 or 12 or 13, characterized in that a tensioning specification is stored as an unequivocal, stored association specification between a variable representing the angular velocity of the press axis (56) as input variable, on the one hand, and a variable representing a tensioning torque dependent thereon as output variable, on the other hand, and in that a tensioning component of the respective compensation torque (Z2; Z3; Z4) is determined by deriving from the tensioning specification the tensioning torque associated with the current angular velocity of the press axis (56).
15. Method according to claim 10 or 11 or 12 or 13 or 14, characterized in that a bearing specification is stored as an unequivocal, stored association specification between the variable representing the angular velocity of the press axis (56) and the variable representing the angular position of the press axis (56) as input variables, on the one hand, and a variable representing a bearing torque dependent thereon as output variable, on the other hand, and in that a bearing component of the respective compensation torque (Z2; Z3; Z4) is determined by deriving from the bearing specification the bearing torque associated with the current angular velocity and the current angular position of the press axis (56).

Images